GIFT OF
Of the 1913 edition of the
Book of Standards this is
copy No. «/& J V
Book of Standards
Containing Tables and Useful
Information Pertaining to Tubular
Goods as Manufactured by
National Tube Company
Pittsburgh, Pa.
Price, Two Dollars
NATIONAL TUBE COMPANY
Pittsburgh, Pa. Nineteen Hundred and Thirteen
0 3 3 £.1
Copyright, 1913,
By
NATIONAL TUBE COMPANY
Pittsburgh, Pa.
AMERICAN BANK NOTE COMPANY, NEW YORK AND PITTSBURGH
National Tube Company
Manufacturers of
Black and Galvanized Wrought Pipe
In sizes from J/s inch to 30 inches
Boiler Tubes
Lap- welded, Spellerized Steel — Shelby Cold Drawn
and Hot Rolled Open Hearth Seamless Steel
Casing, Tubing, Drive Pipe,
Drill Pipe, Gas and Oil Line
Pipe, Working Barrels, Etc.
Water and Gas Mains
Converse and Matheson Lead Joint Pipe
for Water and Gas Mains
Cylinders
Lap-welded and Seamless for Anhydrous
Ammonia, Compressed Air, Carbonic
Acid Gas, Nitrous Oxide Gas, Etc.
Shelby Seamless Steel Mechanical Tubing
and Miscellaneous Forgings
A Complete Line of Malleable, Cast Iron
and Brass Fittings and Valves
ICKJ iXJU J Hi!
B ^DERi
*^;- «T- :
National Tube Company
General Offices
Frick Building, Pittsburgh, Pa.
District Sales Offices
Atlanta, Ga. Boston, Mass. Chicago, 111.
Denver, Colo. New Orleans, La.
New York, N. Y. Philadelphia, Pa.
Pittsburgh, Pa. St. Louis, Mo.
Salt Lake City, Utah
Pacific Coast Representatives
U. S. Steel Products Company
Los Angeles, Cal. San Francisco, Cal.
Portland, Ore. Seattle, Wash.
Export Representatives
U. S. Steel Products Company
New York City
264203
tBqrrio J 3OJ
<gn
.III to
8 ,2 .U
•
FOR 1913 EDITION
NATIONAL TUBE COMPANY
BOOK OF STANDARDS
This correction sheet embraces and supersedes all previous
correction sheets.
Items marked with an asterisk (*) have not been included
in previous sheets.
Please make notation of changes in Book and insert this
sheet in tape in back of Book of Standards.
NOTE
Our records indicate that 1913 Edition Book of Standards
No. O/ was mailed to
Co m p any
City
Street Address ._ __ State
Person Addressed _ __
This correction sheet is being mailed to same address. We
should be notified of any change of address.
T33H3 HOH
ere
38UT JAMOITAH
1O
*Page 35. — South Penn Casing 5TV' size 17 pounds,
coupling data reads as follows :
Diameter 6. 050*
Length 4#"
Weight 6. 759 pounds
This should be changed to read as follows:
Diameter 6.1 55"
Length 5V8"
Weight 8.849 pounds
*South Penn Casing 6^//r size 20 pounds, coupling
data reads as follows:
Diameter 7. 642"
Length 5}£"
Weight 11.133 pounds
This should be changed to read as follows:
Diameter 7.699"
Length 6V8"
Weight 14.458 pounds
NATIONAL TUBE COMPANY
FRICK BLDG., PITTSBURGH, PA.
DISTRICT SALES OFFICES
ATLANTA KANSAS CITY PITTSBURGH
BOSTON NEW ORLEANS ST. LOUIS
CHICAGO NEW YORK ST. PAUL
DENVER PHILADELPHIA SALT LAKE
CITY
PACIFIC COAST REPRESENTATIVES
U. S. STEEL PRODUCTS CO.
SAN FRANCISCO, LOS ANGELES, PORTLAND, SEATTLE
EXPORT REPRESENTATIVES
U. S. STEEL PRODUCTS CO., NEW YORK CITY
PREFACE
IN this edition of our handbook, which is much larger than those
preceding, it has been our aim to give all the dimensions and data
pertaining to tubular goods as manufactured by National Tube Com-
pany, at this date.
We have incorporated in the book certain subjects, closely related to
the uses of pipe and tubes and have given such general information and
engineering data as pertains to the same. In compiling the engineering
data we have relied entirely on the engineering authorities as quoted in
the text. We have also added a glossary of terms relating to the pipe
and fittings trade which will, no doubt, be found of much value to the
users of pipe and fittings.
STANDARD PROCESSES AND MATERIALS
USED IN THE MANUFACTURE
OF TUBULAR GOODS
INTRODUCTION
To many users of tubular goods the processes of manufacture, prop-
erties and characteristics of the metal, and indeed, the possibilities of
modem welded tubes and pipe are more or less unknown. We, there-
fore, present in this chapter information on these subjects, in a style as
free from technical detail as possible, so that the consumer may know
more about the material he is using, and benefit by the experience and
practice of others. In order to limit this chapter to reasonable space,
it is necessary to confine ourselves to an outline of the more important
methods and materials used in the manufacture of tubular goods of
to-day.
The development of the steel-pipe industry has been phenomenal
during the past nine years, as evidenced by the increase in the output
of the National Tube Company from 416 064 tons in 1900 to i 013 071
tons for the year 1909. The main factor in this great expansion has been
the development of a satisfactory quality of soft weldable steel as a sub-
stitute for wrought iron; the grade of steel made exclusively for this pur-
pose by us to-day has been proved, in all points, superior to the wrought
iron of days gone by. By comparing the properties and characteristics
of wrought iron with those of pipe steel, as made under our process,
we believe the reader will readily understand why this steel has become
the standard material for the manufacture of welded tubes and pipe.
All tubular goods are manufactured by one of two general processes:
either by shaping sheets of metal, termed skelp, into tubes and welding
the edges together; or by forming or drawing the tubes from solid billets
or plates of metal. The products of the various processes are termed
respectively " welded " or "seamless."
WELDED TUBES AND PIPE
Welded tubular goods are made either by the lap- or butt-weld process.
Lap-weld Process. The skelp used in making lap-welded tubes is
rolled to the necessary width and gage for the size tubes to be made, the
7
8 Lap-weld Process
edges being scarfed and overlapped when the skelp is bent into shape,
thus giving a comparatively large welding surface, compared with the
thickness of the plate (see Fig. i). As a result of the work done in
forging down the metal at the weld, tubes made in this way will probably
be stronger at the weld than at any other place.
The skelp is first heated to redness in a
"bending furnace," and then drawn from
the front of the furnace through a die, the
inside of which gradually assumes a circu-
lar shape, so that the skelp when drawn
through is bent into the form of a tube
with the edges overlapping as shown in
Fig. i.
In the next operation the skelp so
formed is heated evenly to the welding
temperature in a regenerative furnace.
Fig. i. Lap-weld When the proper temperature is obtained,
the skelp is pushed through an opening in
the front of this furnace into the welding rolls, passing between two rolls
set one above the other, each having a semicircular groove, so that the
two together form a circular pass. Between these rolls a mandrel is held
in position inside the tube, the lapped edges of the skelp being firmly
pressed together at a welding heat between the mandrel and the rolls.
The tube then enters a similarly shaped pass to correct any irregularities
and to give the outside diameter required. It will be noted that the
outside diameter is fixed by these rolls; any variation in gage, therefore,
makes a proportional variation in the internal diameter. This also ap-
plies to butt-weld pipe. Finally, the tube is passed to the straighten-
ing, or cross rolls, consisting of two rolls set with their axes askew.
The surfaces of these rolls are so curved that the tube is in contact with
each for nearly the whole length of the roll, and is passed forward and
rapidly rotated when the rolls are revolved. The tube is made practi-
cally straight by the cross rolls, and is also given a clean finish with a
thin, firmly adhering scale.
After this last operation the tube is rolled up an inclined cooling
table, so that the metal will cool off slowly and uniformly without in-
ternal strain. When cool enough the rough ends are removed by cold
saws or in a cutting-off machine, after which the tube is ready for inspec-
tion and testing.
In the case of some sizes of double-extra-strong pipe (3 in. to 8 in.)
made by the lap- weld process, the pipes are first made to such sizes as
will telescope one within the other, the respective welds being placed
opposite each other; these are then returned to the furnace, brought
to the proper heat, and given a pass through the welding rolls. While
a pipe made in this way is, in respect to its resistance to internal pres-
sure, as strong or stronger than when made from one piece of skelp,
it is not necessarily welded at all points between the two tubular sur-
faces; however, each piece is first thoroughly welded at the seam before
telescoping.
Properties of Materials 9
Butt-weld Process. Skelp used in making butt-welded pipe comes
from the rolling department of the steel mills with a specified length,
width, and gage, according to the size pipe for which it is ordered. The
edges are slightly beveled with the face of the skelp, so that the surface of
the plate which is to become the inside of the pipe is not quite as wide
as that which forms the outside; thus when the edges are brought to-
gether they meet squarely, as indicated in Fig. 2.
The skelp for all butt-welded pipe is heated uniformly to the welding
temperature, in furnaces similar in general construction to those used in
lap-welding. The strips of steel when
properly heated are seized by their ends
with tongs and drawn from the furnaces
through bell-shaped dies, or rings. The
inside of these dies is so shaped that the
plate is gradually turned around into the
shape of a tube, the edges being forced
squarely together and welded. For some
sizes the pipes are drawn through two
rings consecutively at one heat, one ring
being just behind the other, the second
one being of smaller diameter than the
grst Fig. 2. Butt-weld
The pipes are then run through sizing
and cross rolls similar to those used in the lap-weld process, obtaining
thereby the correct outside diameter and finish.
The pull required to draw double-extra-strong (hydraulic) pipe by
this process is so great, on account of the thickness of the skelp,
that it is found necessary to weld a strong bar on the end of the
skelp, thereby more evenly distributing the strain. With this bar the
skelp is drawn through several dies of decreasing size, and is reheated
between each draw until the seam is thoroughly welded. It is evident
that the skelp is put to a severe test in this operation, and, unless
the metal is sound and homogeneous, the ends will almost always be
pulled off.
Properties of Materials. Experience has developed a grade of soft
steel (which would more properly be called highly refined iron) especially
adapted to the manufacture of welded pipe. Uniformity and homo-
geneity of composition mean satisfactory welding practice and small
scrap losses in manufacture, as well as a better quality of product for
all purposes. This has been our aim for years, to accomplish which it
has been found absolutely essential to control the manufacture of the
metal from the ore to the finished tube or pipe. The practice of the
National Tube Company is to make tube and pipe steel exclusively;
thus by concentrating the attention of a highly trained force of men on
this one grade of metal, the best results can be attained. This steel is
made by the Bessemer or Basic Open-hearth process, according to the
use to which it is to be put, and will average in chemical and physical
properties as follows:
10
Welding and Annealing
Chemical analysis
Physical pulling
tests
0)
a
c
<u
5
rt
o •
^
d
«j
J*
jq
y
0 M
"rt G
"•3 o
1
2
I
-a
1
11
s a
-2 C3
Id
u
^
c/a
PH
H^
H M
W"
«"-
%
%
%
%
Pounds
Pounds
%
%
Bessemer pipe steel . .
Open-hearth pipe steel
.07
.09
.30
.40
.045
• 035
.IOO
.025
36 ooo
33 ooo
58 ooo
53 ooo
22
25
II
In ductility this steel excels any material heretofore used in the manu-
facture of pipe. For bending into coils, or the various shapes required
in electric conduit work, steel pipe is especially adapted. In this work
it has given most satisfactory results; similarly, for boiler tubes or
other purposes, where the metal has to stand cold flanging or other
severe manipulation.
Welding and Annealing. Good welding quality is of prime impor-
tance in pipe steel, and is sought after and maintained by a system of
careful inspection. This not only is an assurance that the seam will be
strong and reliable, but is a quality highly desired in the shop where tubes
or pipes have to be welded to each other, or to other material.
The welding heat naturally produces a larger grain in the metal. This
does not necessarily mean loss of ductility, but, where a large margin of
safety against failure by shock is desired, the grain may be refined by
annealing. The method giving best results, is to heat the steel to a
bright orange color in shop light (1750° F.) for a few minutes, allowing
the piece to cool in the air — very slow cooling is not necessary. .So
treated, the fracture of the metal should show a fine silky texture with-
out any trace of crystallization.
Threading. To insure a good threaded joint between a pipe and a
fitting, it is necessary to have a clean, smoothly cut thread. To cut this
kind of a thread, it is necessary to have a good die, which consists of a
frame or holder and a set of chasers made with proper consideration for
the following points: — lip, clearance, chip space, lead, and number of
chasers.
Lip, which is also known as hook or rake, is the inclination of the
cutting edge of the chaser to the surface of the pipe, as shown in Fig. 3.
This lip may be secured by milling the cutting face of the chaser, as
shown by the full lines, or by inclining the chaser, as shown by the dotted
lines. This lip angle should be from 15° to 25°, depending upon the style
and condition of the chasers and chaser holders.
Clearance. Clearance is the angle between the thread of the chasers
and the threads of the pipe. This clearance may be secured in various
ways, depending upon the position in which the chasers are held in the
frame. The position of the cutting edge of the chaser in relation to the
center line of the pipe while working, determines whether the chasers
Threading
11
shall be set "in" or "out" while the teeth are being machined, as shown
in Figs. 3 and 4.
Chip Space. This is the space required in the holder in front of
the chaser to allow room for the accumulation of chips, and also to pro-
vide means for lubricating the chasers. This space should be secured as
7
iHIP SPACE IN HOLDER
IN CHASER
Fig. 3
Fig. 4
indicated in Fig. 3, which shows the chip space in front of the chaser,
the back of which should be well supported. This is a very important
point and one which is often overlooked. A lack of chip space will
cause the chips to clog and tear the threads.
Lead. Lead is the angle which is machined or ground on the front of
each chaser to enable the die to start on the pipe, and also to distribute
the work of cutting over a number of threads. The lead may be machined
on, or, as is more frequent, it may be ground on after the chasers are
tempered. To secure a good thread, the lead should cover the first three
threads. As the heaviest cutting is done by the lead, it should have a
slightly greater clearance angle than the rest of the threads on the chaser.
When regrinding a chaser that has become dull on the lead, care should
be taken to give each chaser the same length of lead, as otherwise the
work will be unevenly distributed between the chasers.
Number of Chasers. To get good results in threading at one cut, experi-
ence shows that a die should have a suitable number of chasers, the
number being determined by the size of the die. Our experience shows
that dies up to i*4 inches should have four (4) chasers.
inches to 4 inches should have approximately six chasers.
4 inches
7 inches
10 inches
12 inches
14 inches
1 8 inches
to 7 inches
to 10 inches
to 12 inches
to 14 inches
to 1 8 inches
to 20 inches
eight chasers,
ten chasers,
twelve chasers,
fourteen chasers,
sixteen chasers,
eighteen chasers.
Lubrication. Good lard or crude cottonseed oil should be used in
liberal quantities. The best die made will not produce good results with
poor oil.
12 Corrosion
Corrosion. The use of steel for welded pipe was made possible, in
the first place, through the manufacture by the National Tube Company
of a special grade of low-carbon steel, equal in welding quality to the
wrought iron which had formerly been exclusively used for this pur-
pose. Steel pipe has in later years superseded wrought-iron pipe by
proving its superiority in strength, ductility, and finally, as made under
modern processes, by its superior durability. As manufacturers of both
wrought-iron and steel pipe for many years, we have had a special in-
terest in this question of durability, about which there has been so much
debate, and with our dual interest have had exceptional opportunities
to make comparison of these materials under all manner of service.
Moreover, we have always shipped a wrought-iron coupling on steel
pipe, so that in case there was any outside corrosion, a comparison of
the two materials could be readily made under the same conditions. As
a result of an extended study of this question in the laboratory and in
the field, and with the experience of many large consumers of pipe, who
have made careful observations from cases where both iron and steel
pipe were used under the same conditions, there was no further room
for doubt as to the advantage of steel pipe, made under our methods of
manufacture, in respect to its resistance to corrosion, particularly as to
pitting; hence we abandoned the manufacture of charcoal and puddled
iron for welded tubes and pipe after January, 1909.
For the information of those wishing to follow up the discussion of
this subject, and obtain data regarding the tests and experiments which
have been made on the relative corrosion of iron and steel, we give a list
of publications below to which reference may be made: *
Proceedings of Engineers' Society of Western Pennsylvania, 1907.
T. N. Thomson, two reports, 1908-10, American Society of Heating
and Ventilating Engineers.
American Society for Testing Materials, 1906, 1908 (Howe).
"Corrosion of Iron," A. Sang (McGraw-Hill Publishing Company).
(Extensive bibliographs.)
"Corrosion and Preservation of Iron and Steel," A. S. Cushman and
Hy. A. Gardner (McGraw-Hill Publishing Company).
"Metallurgy of Iron and Steel," Bradley Stoughton.
"Electrolytic Theory of the Corrosion of Iron and Its Applications,"
Wm. H. Walker (Journal Iron and Steel Institute, 1909).
"Function of Oxygen in the Corrosion of Metals," Wm. H. Walker
(Transactions American Electrochemical Society, Vol. 14, p. 175).
"Corrosion of Iron and Steel," by J. N. Friend, 1911 (Longmans,
Green and Company).
" Corrosion of Boiler Tubes/' Jour. Am. Soc. Nav. Engrs., May, 1904.
National Tube Co. bulletins are published from time to time giving
results of experience on this subject.
Cause of Corrosion. There is hardly space here to go very deeply into
the question of corrosion in all its phases, about which there is still some
* An additional list of references will be found in appendix. (See index for
page number.)
Mill Inspection and Tests 13
difference of opinion, but a few underlying facts which have recently been
well established by experiments may be useful to those interested in
protecting the metal.
It has been noticed by many who have worked on the problem of
corrosion, that differences of electrolytic potential between two adja-
cent places on the surface of the metal causes local pitting. This differ-
ence may be due to lack of homogeneity in the metal, but more often is
caused by foreign matter, electro-negative to iron, attached to the sur-
face; such as mill scale, carbon, or rust itself. Without going into a
discussion as to the fundamental causes, it has been clearly established
that corrosion consists of two main reactions, viz.: the solution of a
small portion of the iron in water, and the subsequent oxidation of the
ferrous iron in solution to ferric hydroxide, which is then precipitated
out as " rust. " The amount of the corrosion is still further increased by
the combination of free oxygen with the hydrogen, which was deposited
on the surface of the metal when iron went into solution. This cycle of
reactions is repeated, and the rust continues to accumulate so long as both
water and air are present. Other agencies may accelerate the process
of corrosion, but in the absence of either one of these elements no cor-
rosion can take place. Steel will remain clean and bright for an indefi-
nite time in dry air, and also in water that is free from air. Hence
the necessity to see to it that, as far as possible, oxygen and other cor-
rosive gases are removed from water, and that iron and steel exposed
to moist air are protected by impervious and durable coatings.
We invite correspondence on this subject with our research department.
MU1 Inspection and Tests. Every piece of pipe made in National
Tube Company's mills is inspected for surface defects, and must stand
an internal hydrostatic pressure test, without leaking, before shipment.
Machines for applying this test are installed at convenient places through-
out the mill. The amount of pressure applied depends on the use to
which the pipe or tube is to be put, but in no case is it deemed advisable
to test the finished pipe to more than one-half the elastic limit of the
material, this being, however, as a rule, considerably above the actual
working pressure. All boiler tubes and lap-weld pipe for certain purposes
are subject to a flattening -test made on the crop ends cut from each
piece of pipe. This is done to insure strong welds and sound material.
(For list of test pressures see pp. 68-76.)
Besides the regular internal pressure tests described above, lap-welded
boiler tubes for locomotive service are given individual inspection and
tests at the mill as follows:
1. Inspection of external and internal surface (the latter by the aid
of reflected light).
2. The ends on being cut off are placed in a flanging press, designed
by us especially for this purpose. The rough end is first pressed flat by
a horizontal hydraulic press, then a die attached to a vertical plunger
comes down and turns over a flange on the cut end of the sample, this
combines a flattening, crushing-down, and flange test in one. As this
test is made on each end of every locomotive boiler tube, the customer
14 Shelby Seamless Steel Tubes
has the utmost assurance that the material is of uniformly satisfactory
quality. Tubes which fail to stand this test, on account of imperfect
welding, are given another run through the furnace and rewelded, and
are again subjected to the same test on the ends. Other physical tests
are described in Standard Specifications for Locomotive Boiler Tubes,
given on pages 99 to 102.
3. Our research department is continually testing and experimenting
with the material for locomotive boiler tubes; this being the most severe
service to which tubes are put, it is naturally the branch of the business
to which we give most attention. To this end, tests of the safe ending
quality are made on each lot; roller expander tests in the flue sheet, to
determine the power of the material to withstand repeated working in
the flue sheet without developing brittleness, are also made from time
to time. Improvements in this line are reflected in the product designed
for other purposes, where the demands of service are not so rigorous.
SHELBY SEAMLESS STEEL TUBES
Methods of Manufacture. The process employed in the manufac-
ture of Shelby Seamless Tubes in our mill may be classified as follows:
*** fi,nish'
(b) Cold finish.
A. Tubes made from solid round billets ..... j
(
B. Tubes made from steel plates . . . . j <?> ?°1t,fi,ni.sh/
( (b) Cold finish.
Class A includes by far the larger percentage of seamless tubes.
The preliminary operations are the same for hot and cold-finished
tubes made from solid round billets. The steel, of a special quality,
made by the basic open-hearth process, is rolled into rounds approxi-
mating in diameter that of the finished tube; these are cut to suitable
length to contain sufficient steel for a required length tube, then heated
to a soft plastic state and pierced. Before heating these billets a hole
is drilled in the center of one end, so that the piercing point may be
started accurately in the center of the billet, thereby minimizing, so far
as possible, the variations of thickness in the wall. There results from
this operation a rather rough, thick-walled seamless tube, retaining on its
surface evidence of the manipulation required to work the hot billet into
this shape. The roughly pierced tube is now transferred, without loss
of time and without reheating, to a rolling mill, where it is passed between
rolls having semicircular grooves between which various sizes of mandrels
are placed, and are supported in this position on the ends of stiff bars.
By repeatedly passing the rough tube through these rolls and over man-
drels, the steel is gradually elongated and the walls proportionately
reduced in gage.
Hot-finished Tubes are taken direct from the rolling mill while still
retaining sufficient heat, and passed through a reeling machine of special
design, which further slightly reduces the gage. The tube is straight-
ened and given a burnished finish by this last operation.
Materials 15
Cold-finished Tubes. Where cold finish is required, the ends of the
tubes after they leave the rolling mill are reduced, so that they may be
firmly caught by the heavy tongs of the drawbench. They are first
immersed in hot dilute acid to remove all scale outside and inside,
so that a smooth, even surface may result from the cold drawing
which follows. A mandrel is held in position by a long bar which lies
inside the tube, and holds the mandrel just even with the die while the
tube is being drawn. All tubes, except those having an inside diameter
smaller than six-tenths of the outside diameter or smaller than l/2 inch,
are drawn over mandrels varying in diameter until the required diameter
and thickness are obtained. The drawing operation hardens the steel,
so that it is usually necessary to anneal the tube after each pass to restore
its ductility, after which it is necessary to again put it through the
acid pickling bath to remove the oxide-of-iron scale from the surface.
After the last drawing operation the hammered points are cut off, and
the tube is ready for testing and final inspection.
Tubes Made from Steel Plates. As in the case of tubes made from
round billets, these may be hot or cold finished, according to require-
ments. Hot-finished tubes are not as smooth as those cold drawn, hence,
when it is necessary to produce a tube with smooth walls, it is given two
or three cold passes, each operation being preceded by annealing and
pickling.
The "cupping" process is used in making seamless tubes over $¥2 inches
outside diameter. Plates of the best-quality basic open-hearth steel of
the required thickness are trimmed into circular shape and heated to a
bright redness, then pressed roughly into the shape of a cup. This is re-
peated three or four times, reheating between each operation, and using
smaller dies and punches as the process proceeds, until the cup has the
shape of a cylinder closed at one end.
The piece is then taken to the drawbench, where it is further elongated
and reduced in gage by forcing through dies of successively decreasing
diameter.
Where a number of drawings are required, the piece is reheated before
each draw. Finally the closed end, or head, is cut off and the tube cut
to length.
Carbonic Acid Cylinders. These are made from specially selected
steel plates (see cylinder specifications). The preliminary operations in
the making of these cylinders are as above described, except that the
head is not cut off, and the other or open end is swaged down to receive
a head.
Materials. Three principal classes of material are used in the manu-
facture of seamless steel tubes, namely:
.17%-carbon open-hearth steel,
• 35%-carbon '
3V2%-nickel "
all of which are of special quality as before stated. In addition to these
standard materials, tubes for special purposes are made from special
16 Physical Properties of Shelby Seamless Steel Tubes
materials, such as chrome- vanadium steels, higher-carbon steels, etc. The
physical qualities of all these materials vary with the heat treatment,
especially after the cold-drawing operation, which hardens the tube.
The .17%-carbon steel tubes are suitable for boiler tubes and other
purposes requiring great ductility; the .35%-carbon steel tubes are suit-
able for purposes in which higher elastic limits and ultimate strengths
are required; and the sV2% nickel-steel tubes are suitable for purposes
requiring ductility combined with high elastic limits and ultimate
strengths.
Hot-finished tubes are not given any further heat treatment after leav-
ing the hot mills. Cold-drawn tubes, however, are given regular heat
treatments, which consist of either a soft anneal or a hard (finish) anneal,
while for special purposes the heat treatment is varied to give properties
suited to the purpose for which the tubes are to be used.
The average chemical and physical qualities of the three main classes
of materials, when same are given the regular heat treatments after the
final cold drawing, are shown in the following table.
Physical Properties of Shelby Seamless Steel Tubes
.17 Per Cent Carbon Steel.
Chemical Analysis:
Carbon. 14 to . 19 per cent.
Manganese 40 to .60 per cent.
Sulphur 015 to .040 per cent.
Phosphorus oio to .035 per cent
Temper 5. Physical Properties: (Unannealed)
Elastic limit 60 ooo to 70 ooo pounds per square inch.
Ultimate strength 6s ooo to 80 ooo pounds per square inch.
Elongation in 2 inches. . . 12 to 1 8 per cent.
Elongation in 8 inches. . . 3 to 7 per cent.
Reduction of area 20 to 30 per cent.
* Foot-pounds Energy Absorbed under Impact, 6.97.
(Material of this temper is of the maximum strength, with but slight ductility.
The surface is bright and free from scale. Material of this temper is usually
furnished for hose poles, cream separator bowls, etc.)
* The impact test is made on a machine of special design, constructed as
follows: A pendulum with a light rigid frame system and a heavy lower part is
hung on roller bearings; these are supported in a frame of sheet iron, attached
to a heavy cast iron base. The pendulum is always dropped from a fixed
height; in swinging, it moves before it a pointer which records the maximum
height to which the pendulum swung. In making a test, the specimen to be
tested is clamped firmly in the base of the machine; it is placed so that it will
be struck by the pendulum at the lowest point in the swing. The test piece is
&/IQ inch X S/IQ inch X 2^4 inches long, with a 60° notch cut Vie inch deep,
i% inches from the end of the piece. When the test piece is firmly clamped in
the base, the pendulum is suddenly released and, when striking the test piece,
it is checked a certain amount depending on the toughness of the test piece.
The height of the swing after hitting the test piece is recorded by the pointer.
Knowing the weight of the pendulum, the height of the free swing and the
height of the swing after striking the test piece, it is possible to calculate the
foot-poands energy absorbed by the test piece.
Physical Properties of Shelby Seamless Steel Tubes 17
.17 Per Cent Carbon Steel (Continued).
Finish Anneal
Temper T. Physical Properties:
Elastic limit 50 ooo to 65 ooo pounds per square inch.
Ultimate strength 60 ooo to 75 ooo pounds per square inch.
Elongation in 2 inches. . . 1 8 to 25 per cent.
Elongation in 8 inches. . . 10 to 16 per cent.
Reduction of area 35 to 45 per cent.
Foot-pounds Energy Absorbed under Impact, 7.07.
(This temper is furnished for general mechanical purposes. It is slightly
softer and considerably more ductile than Temper S. The surface is not bright,
but free from scale.)
Temper U. Physical Properties: (Special Anneal)
Elastic limit 40 ooo to 54 ooo pounds per square inch.
Ultimate strength 53 ooo to 65 ooo pounds per square inch.
Elongation in 2 inches. . . 35 to 45 per cent.
Elongation in 8 inches. . . 15 to 20 per cent.
Reduction of area 40 to 50 per cent.
Foot-pounds Energy Absorbed under Impact, 8.70.
(Material of this temper will stand a moderate amount of cold forming, such as
is necessary in the manufacture of bedsteads, etc. The surface is very slightly
scaled.)
Temper V. Physical Properties: (Medium Anneal)
Elastic limit 35 ooo to 48 ooo pounds per square inch.
Ultimate strength 52 ooo to 65 ooo pounds per square inch.
Elongation in 2 inches. . . 50 to 60 per cent.
Elongation in 8 inches. . . 22 to 28 per cent.
Reduction of area 50 to 60 per cent.
Foot-pounds Energy Absorbed under Impact, 9.67.
(Material of this temper has lost all traces of the effect of cold drawing, and is
in excellent shape for machining. However, the tools must have about 30 degrees
top rake as the material comes away in long tough chips.)
Soft Anneal
Temper W. Physical Properties:
Elastic limit 27 ooo to 35 ooo pounds per square inch.
Ultimate strength 47 ooo to 55 ooo pounds per square inch.
Elongation in 2 inches. . . 55 to 65 per cent.
Elongation in 8 inches. . . 28 to 33 per cent.
Reduction of area 52 to 62 per cent.
Foot-pounds Energy Absorbed under Impact, 9.73.
(This temper is suitable for boiler tubes for all purposes. The material is soft
and ductile and will stand considerable cold forming. The surface is slightly
scaled.)
Temper X. Physical Properties: (Special Anneal)
Elastic limit 30 ooo to 35 ooo pounds per square inch.
Ultimate strength 50 ooo to 56 ooo pounds per square inch.
Elongation in 2 inches. . . 55 to 65 per cent.
Elongation in 8 inches. . . 28 to 3^ per cent.
Reduction of area 55 to 65 per cent.
Foot-pounds Energy Absorbed under Impact, 9.42.
(This temper is suitable for all purposes requiring high ductility and resistance to
shock, combined with highest tensile strength consistent with its ductility. Stay
bolts are always furnished of this temper. The surface is considerably scaled.)
18 Physical Properties of Shelby Seamless Steel Tubes
.17 Per Cent Carbon Steel (Continued).
Temper F. Physical Properties: (Retort Anneal)
Elastic limit 22 ooo to 28 ooo pounds per square inch.
Ultimate strength 45 ooo to 52 ooo pounds per square inch.
Elongation in 2 inches. . . 60 to 70 per cent.
Elongation in 8 inches. . . 30 to 40 per cent.
Reduction of area 60 to 70 per cent.
Foot-pounds Energy Absorbed under Impact, 9.25.
(This temper is suitable for cold forming operations requiring maximum duc-
tility. Sizes smaller than \\'z inches outside diameter can be furnished retort
annealed if so specified. The surface of these tubes will be free from scale.
Sizes larger than i^ inches outside diameter will be annealed in the open furnace
and the surface slightly scaled.)
Temper Z.:
(Material of this temper is hot rolled and the physical properties will vary
with the wall thickness of the tubes. For wall thicknesses %e mch and lighter,
the physical properties will correspond very closely to Temper U. For heavier
walls, the physical properties will correspond very closely to Temper W.)
.30 to .40 Per Cent Carbon Steel.
Chemical Analysis:
Carbon 30 to .40 per cent.
Manganese 40 to .60 per cent.
Phosphorus oio to .035 per cent.
Sulphur 015 to .040 per cent.
Temper S. Physical Properties: (Unannealed)
Elastic limit 75 ooo to 90 ooo pounds per square inch.
Ultimate strength 85 ooo to 100 ooo pounds per square inch.
Elongation in 2 inches. . . 10 to 15 per cent.
Reduction of area 12 to 1 8 per cent.
Foot-pounds Energy Absorbed under Impact, 2.22.
(Material of this temper is hard and the surface bright. It has the maximum
strength, but little ductility. It should not be used where it will be subjected to
shock. Material which is to be heated above 500° C. during subsequent manu-
facture should be furnished of this temper.)
Finish^ Anneal
Temper T. Physical Properties:
Elastic limit 70 ooo to 85 ooo pounds per square inch.
Ultimate strength 80 ooo to 95 ooo pounds per square inch.
Elongation in 2 inches. . . 20 to 30 per cent.
Elongation in 8 inches. . . 12 to 1 8 per cent.
Reduction of area 25 to 32 per cent.
Foot-pounds Energy Absorbed under Impact, 3.55.
(This temper is usually furnished for automobile purposes requiring high-
carbon steel.)
Medium Anneal
Temper U. Physical Properties:
Elastic limit 50 ooo to 65 ooo pounds per square inch.
Ultimate strength 65 ooo to 80 ooo pounds per square inch.
Elongation in 2 inches. . . 35 to 45 per cent.
Elongation in 8 inches. . . 20 to 30 per cent.
Reduction of area 35 to 42 per cent.
Foot-pounds Energy Absorbed under Impact, 5.55.
(This temper is suitable for purposes requiring high-tensile strength, good
ductility and shock-resisting power.)
Physical Properties of Shelby Seamless Steel Tubes 19
31/2 Per Cent Nickel Steel.
Chemical Analysis:
Carbon 20 to .30 per cent.
Nickel 3 .00 to 4.00 per cent.
Manganese 40 to .60 per cent.
Phosphorus oio to .030 per cent.
Sulphur 015 to .040 per cent.
Temper S. Physical Properties:
Elastic limit 85 coo to 100 ooo pounds per square inch.
Ultimate strength 95 coo to no ooo pounds per square inch.
Elongation in 2 inches. . . 10 to 18 per cent.
Reduction of area 22 to 32 per cent.
Foot-pounds Energy Absorbed under Impact, 2.60.
(Material which is to be subsequently heat treated or heated above 500° C.
in manufacturing processes should be furnished of this temper.)
Finish Anneal
Temper W. Physical Properties:
Elastic limit 75 ooo to 90 ooo pounds per square inch.
Ultimate strength 85 ooo to 105 ooo pounds per square inch.
Elongation in 2 inches. . . 15 to 25 per cent.
Reduction of area 25 to 35 per cent.
Foot-pounds Energy Absorbed under Impact, 4.76.
(This temper is ideal for auto axles and all work requiring material of high-
tensile strength and shock-resisting power.)
Medium Anneal
Temper U. Physical Properties:
Elastic limit 45 ooo to 60 ooo pounds per square inch.
Ultimate strength 70 ooo to 85 ooo pounds per square inch.
Elongation in 2 inches. . . 40 to 50 per cent.
Elongation in 8 inches. . . 20 to 28 per cent.
Reduction of area 45 to 50 per cent.
Foot-pounds Energy Absorbed under Impact, 9.18.
(Material of this temper is very ductile, has high shock-resisting power and is
of relatively high tensile strength. It should find many uses where safety in
construction is an important factor.)
Hot-finished boiler tubes have a slightly higher elastic limit and ulti-
mate strength than the annealed cold-drawn, a fair average of their
physical qualities being as follows:
Yield point 42 ooo pounds per square inch.
Ultimate strength 62 ooo pounds per square inch.
Elongation in 8 in 22 per cent.
Reduction in area 48 per cent.'
To suit the requirements of various customers, special treatments are
given tubes, which produce a wide range in their physical qualities.
Typical results obtained for two special treatments of ,17%-carbon steel
tubes are:
(i) (2)
Yield point 23 ooo pounds per square inch 34 ooo pounds per square inch.
Ultimate strength . 48 ooo pou nds per squ are inch 5 5 ooo pounds per squ are inch .
Elongation in 8 in. 35 per cent 28 per cent.
Reduction of area . 60 per cent 53 per cent.
20 Tests and Mill Inspection
All three of the main classes of material will case-harden, and this fact
is taken advantage of by many users of case-hardened goods.
It will thus be seen that, with the variety of materials used for making
tube and the various treatments afforded, almost any reasonable speci-
fication may be met, and the wants of a great variety of users may be
satisfied.
Tests and Mill Inspection. For the purpose of obtaining tubes of
highest quality, a system of inspections and tests, that will eliminate de-
fective material, is regularly used. The inspections start with the bloom
from which the round billets are made. Each bloom is laid on an inspec-
tion table and examined on all sides for defects. Blooms appearing defec-
tive are rejected. The next inspection takes place after tubes leave the
hot mills. This inspection is for the purpose of eliminating surface
defects. A final inspection for surface and gage is given the tubes
after finishing, and just before packing or loading, to insure that material
comes up to specifications.
Tests. Annealing operations are conducted in furnaces of special
construction, equipped with pyrometers. Tests are made regularly to
insure uniformity in the work.
All boiler tubes, both hot-finished and cold-drawn, are tested to 1000
pounds per square inch, hydrostatic pressure. Other tests applied to
boiler tubes are given under the subject, "Specifications for Boiler
Tubes."
It is advisable that the purpose for which the tubes are to be used
be made known to the manufacturer, that the order may be executed
intelligently, and that the limitations and difficulties of the process of
manufacture be known in a general way by the purchaser, so that he
may bear these things in mind in drawing up his specification. Our
engineers will be pleased to comment on proposed specifications, and
discuss details with those interested. A free discussion of such matters
will, we believe, be of considerable benefit to all concerned.
MARKING
To readily identify " National " material, and as protection to manu-
facturer and consumer alike, the practice of the National Tube Company
is to roll in raised letters of good size on each few feet of every length
of welded pipe the name " NATIONAL " (except on the smaller butt-
welded sizes, on which this is not mechanically feasible).
General Notes 21
GENERAL NOTES
1 . All weights are figured on the basis of one cubic inch
of steel weighing .2833 pound and iron 2 per cent less.
2. All material will be cut to length when so ordered,
with extreme variation not exceeding one-eighth of an inch
over or under, unless otherwise arranged.
3. All pipe threaded to Briggs standard gages as made
by Pratt and Whitney Company, Hartford, Conn.
4. In ordering designate weight or thickness desired,
but not both.
5. All weights given in the tables are limited to three
decimal places.
6. All weights given in the tables are for black pipe and
couplings; galvanized pipe and couplings will be slightly
heavier.
7. The outside diameter of all classes of pipe, casing,
tubing, tubes, etc., heavier than standard is the same out-
side diameter as standard, the extra thickness always being
on the inside.
8. Pipe and tubing are known and spoken of by their
nominal inside diameters from K inch to 15 inches, inclusive.
Casing is known by its inside diameter.
9. Above 15 inches inside diameter, pipe and tubing are
always known and spoken of by their outside diameters, and
when ordering, thickness desired must be specified.
10. Square and Rectangular Pipe are known by their
outside dimensions.
1 1 . All sizes of Converse, Matheson and Kimberley Joint
Pipe and Bedstead Tubing are known by their outside
diameters.
12. All Boiler Tubes are known by their outside diameters.
13. All dimensions of tubular goods are subject to change
without notice.
14. For illustrations showing joints see pages 77 to 84.
15. For lists of test pressures see pages 68 to 76.
22 Standard Pipe
Standard Pipe — Black and Galvanized
All Weights and Dimensions are Nominal
Diameters
1
Weight per foot
1
Couplings
Size
•3
1
.y
g
! a
I
s
^
5
|
s
£
H
a
ilHi
g
1
g
bO
'S
X
ts
&
H o
H
Q
3
*
%
• 405
.269
.068
.244
.245
27
.562
7/8
.029
•V4
• 540
.364
.088
.424
.425
18
.685
I
.043
%
.675
• 493
.091
.567
.568
18
.848
^
.070
%
.840
.622
.109
.850
.852
14
1.024
.116
%
1.050
.824
.113
I.I30
1. 134
14
1.281
1%
.209
i
I.3I5
1.049
.133
1.678
1.684
11%
1.576
1%
.343
i^4
I. 660
1.380
.140
2.272
2.281
n%
i.95o
2%
.535
i%
1.900
1.610
.145
2.717
2.731
11%
2.218
2%
• 743
2
2.375
2.067
.154
v 3.652
3.678
n%
2.760
2%
1. 208
2%
2.875
2.469
.203
5-793
5-819
8
3.276
2%
1.720
3
3-500
3.068
.216
7-575
7.616
8
3.948
2.498
3%
4.000
3.548
.226
9.109
9.202
8
4-591
3%
4.241
4
4.500
4.026
.237
10.790
10.889
8
5.091
3%
4-741
4%
S.ooo
4.5o6
.247
12.538
12.642
8
5-591
3%
5.241
5
5.563
5-047
.258
14.617
14.810
8
6.296
41/8
8.091
6
6.625
6.065
.280
18.974
19-185
8
7-358
9-554
7
7.625
7-023
.301
23-544
23.769
8
8.358
4%
10.932
8
8.625
8.071
.277
24.696
25.000
8
9-358
4%
13.905
8
8.625
7.98i
.322
28.554
28.809
8
9-358
45/8
13.905
9
9-625
8.941
• 342
33.907
34.188
8
10.358
m
17.236
10
10.750
0.192
.279
31 . 201
32.000
8
11.721
6%
29-877
10
io.75o
0.136
• 307
34.240
35.000
8
11.721
.<*%
29.877
10
io.75o
O.O2O
.365
40.483
41.132
8
11.721
6%
29.877
II
11.750
1. 000
• 375
45-557
46.247
8
12.721
61/8
32.550
12
12.750
2.090
• 330
43-773
45.000
8
13.958
6%
43.098
12
12.750
2.0OO
• 375
49.562
50.706
8
13.958
!&%
43.098
13
14.000
3.250
.375
54.568
55.824
8
15.208
6%
47.152
14
15.000
14.250
.375
58-573
6o.375
8
16.446
m
59-493
15
16.000
15.250
.375
62.579
64.500
8
17.446
6%
63.294
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered.
Taper of threads is % inch diameter per foot length for all sizes.
The weight per foot of pipe with threads and couplings is based on a length ot
20 feet, including the coupling, but shipping lengths of small sizes will usually
average less than 20 feet.
All weights given in pounds. All dimensions given in inches.
On sizes made in more than one weight, weight desired must be specified.
For general notes see page 21.
For test pressures see page 68. For illustration showing joint see page 77.
Line Pipe 23
Line Pipe
All Weights and Dimensions are Nominal
Diameters
|
Weight per foot
•s
Couplings
Size
_
_,
|
•a
w "a
i
jh
^
a
1
a
g
rtT-j.S
*G5
i
•a
43
bfl
** s*s<
s
§
'S
m
|
1
43 ™ &
H 8
H
rt
Q
ij
y*
.405
.269
.068
.244
.246
27
.582
m
.043
V±
.540
.364
.088
• 424
.426
18
.724
i%
.069
%
.675
.493
.091
.567
• 571
18
.898
!%
.126
%
.840
.622
.109
.850
.856
14
1.085
1%
.205
%
1.050
.824
.113
1.130
1.138
14
1.316
2%
.316
i
1.315
1.049
.133
1.678
1.688
11%
1.575
28/8
.445
!^4
i. 660
1.380
.140
2.272
2.300
11%
2.054
2%
• 974
i%
1.900
I.6io
.145
2.717
2.748
n%
2.294
2%
1.103
2
2.375
2.067
.154
3.652
3 7i6
11%
2.841
3%
2.146
2%
2.875
2.469
.203
5-793
5.88i
8
3.389
4%
3.387
3
3-Soo
3.o68
.216
7-575
7.675
8
4.014
4%
4.076
4.000
3.548
.226
9.109
9.261
8
4.628
m
5-Sio
4
4-500
4.026
.237
10.790
10.980
8
5-233
4%
6.673
4%
5.000
4.5o6
.247
12.538
12.742
8
5-733
4%
7-379
5
5.563
5-047
.258
14.617
14.966
8
6.420
m
H-730
6
6.625
6.065
.280
18.974
19.367
8
7.482
m
13.869
7
7.625
7-023
.301
23-544
23-975
8
8.482
5Vs
15.883
8
8.625
8.071
• 277
24.696
25.414
8
9.596
6y8
24.130
8
8.625
7.981
.322
28.554
29.213
8
9.596
6^8
24.130
9
9-625
8.941
• 342
33-907
34-612
8
10.596
6^8
26.838
10
10.750
10 . 192
.279
31.201
32.515
8
11-958
6^/8
39-772
10
10.750
10.136
.307
34-240
35.504
8
11.958
6%
39-772
10
10.750
10. O20
.365
40.483
41.644
8
11-958
6%
39-772
II
H.750
11.000
• 375
45-557
46.805
8
12.958
6%
43.326
12
12.750
12.090
• 330
43-773
45-217
8
13.958
6%
46.898
12
12.750
12.000
• 375
49.562
50.916
8
13.958
6%
46.898
13
14.000
13.250
-375
54.568
56.649
8
15.446
7%
65.506
14
15.000
14.250
• 375
58.573
60.802
8
16.446
7%
70.031
15
16.000
15.250
.375
62.579
64.955
8
17.446
7%
74-555
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered.
Taper of threads is % inch diameter per foot length for all sizes.
The weight per foot of pipe with threads and couplings is based on a length of
20 feet, including the coupling, but shipping lengths of small sizes will usually
average less than 20 feet. All weights given in pounds. All dimensions given
in inches.
On sizes made in more than one weight, weight desired must be specified.
For general notes see page 21.
For test pressures see page 68. For illustration showing joint see page 77.
24
Drive Pipe
Drive Pipe
All Weights and Dimensions are Nominal
Size
Diameters
Weight per foot
Couplings
4
4%
6
8
.
iSO.D.
2oO.D.
2.875
3.5oo
4.000
4-500
5.000
5.563
6.625
7-625
8.625
8.625
8.625
9.625
0.750
0.750
0.750
1.750
2.750
12.750
14.000
15.000
16.000
17.000
18.000
20.000
2.067
2.469
3.068
3.548
4.026
4.506
5-047
6.065
7.023
8.071
7.981
7.917
8.941
0.192
0.136
O.O2O
1. 000
2.O90
2.000
3.250
14.250
15.250
I6.2I4
17.182
I9.I82
.154
.203
.216
.226
.237
.247
.258
.280
.301
.277
.322
.354
.342
.279
• 307
.365
.375
.330
• 375
.375
.375
• 375
.393
1409
.409
3-652
5-793
7-575
9-109
10.790
12.538
14.617
18.974
23-544
24.696
28.554
31.270
33.907
31.201
34.240
40.483
45-557
43.773
49.562
54.568
58.573
62.579
69.704
76.840
85-577
3-730
5.906
7.705
9-294
10.995
12.758
14.989
19.408
24.021
25-495
29.303
32.334
34-711
32.631
35.628
41.785
46.953
45.358
51.067
56.849
61.005
65 . 161
73-000
81.000
90.000
2.923
3.486
4. in
4.723
5-223
5-723
6.410
7-473
8.474
9-588
9-588
9.882
10.588
11.950
11.950
H.950
12.950
13.950
13.950
15.438
16.438
17.438
18.675
19.913
21.913
4Vs
4Vs
SVs
5%
61/8
7%
7%
7%
2.380
3.748
4-493
5-973
6 740
7-439
11.871
13.956
15-955
24-343
24-343
31 -320
27.035
40.108
40.108
40.108
43.664
47-220
47 • 220
66.024
70.533
75.043
91.746
109 . 669
121.298
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered.
Taper of threads is % inch from 2 inches to 5 inches, and 9ie inch from 6 inches
to 20 inches.
The weight per foot of pipe with threads and couplings is based on a length of
20 feet, including the coupling, but shipping lengths of small sizes will usually
average less than 20 feet.
All weights given in pounds. All dimensions given in inches.
On sizes made in more than one weight, weight desired must be specified.
For general notes see page 21.
For test pressures see page 69.
For illustration showing joint see page 77.
Extra Strong Pipe — Double Extra Strong Pipe 25
Extra Strong Pipe — Black and Galvanized
All Weights and Dimensions are Nominal
Size
Diameters
Thickness
Weight per foot
plain ends
External
Internal
Vs
.405
.215
.095
.314
y±
• 540
.302
.119
• 535
%
.675
.423
.126
.738
y2
.840
.546
.147
1.087
%
1.050
.742
.154
1.473
i
I.3I5
• 957
.179
2.171
1%
i. 660
1.278
.191
2.996
i%
1.900
1.500
.200
3.631
2
2.375
1-939
.218
5-022
2Y2
2.875
2.323
.276
7.661
3
3-500
2.900
.300
10.252
3V2
4.000
3.364
^.318
12.505
4
4.5oo
3.826
'.337
14.983
4V2
5.000
4.290
• 355
17.611
5
5.563
4.813
.375
20.778
6
6.625
5.761
.432
28.573
7
7.625
6.625
.500
38.048
8
8.625
7-625
.500
43-388
9
9.625
8.625
.500
48.728
10
10.750
9-750
.500
54-735
II
n.750
10.750
.500
60.075
12
12.750
11.750
.500
65.415
13
14.000
13.000
.500
72.091
14
15.000
14.000
.500
77-431
15
16.000
15.000
.500
82.771
The permissible variation in weight is 5 per cent above and 5 per cent below.
Double Extra Strong Pipe — Black and Galvanized
All Weights and Dimensions are Nominal
Size
Diameters
Thickness
Weight per foot
plain ends
External
Internal
%
.840
.252
.294
1.714
8/4
1.050
.434
.308
2.440
I
I.3I5
• 599
• 358
3.659
34
i. 660
.896
.382
5-214
iV2
1.900
1. 100
.400
6.408
2
2.375
1.503
.436
9.029
zVz
2.875
1.771
• 552
13-695
3
3.5oo
2.300
.600
18.583
3V2
4.000
2.728
.636
22 . 850
4
4.500
3.152
.674
27.541
4V6
5.000
3.58o
.710
32.530
5
5.563
4.063
• 750
38.552
6
6.625
4.897
.864
53.160
7
7-625
5.875
.875
63.079
8
8.625
6.875
.875
72 . 424
The permissible variation in weight is 10 per cent above and 10 per cent below.
The following notes apply to both tables.
Furnished with plain ends and in random lengths unless otherwise ordered.
All weights given' in pounds. All dimensions given in inches. For general
notes see page 21. For test pressures see page 69.
26 Standard Boston Casing
Standard Boston Casing
All Weights and Dimensions are Nominal
Diameters
%
Weight per foot
Couplings
Size
13
g
^
o
w
•S
§
% &
S'gJ!
•8*8
s.§
r! fci
1
1
§
X
H
1
g
1
as!
&&
3
j
i
2
2.250
2.050
.100
2.296
2.340
14
2.714
2%
1.361
2*4
2.500
2.284
.108
2.759
2.820
14
2.964
2%
1.499
2%
2.750
2.524
.113
3.182
3.250
14
3.214
2%
1.804
2%
3.000
2.768
.116
3-572
3.650
14
3.464
2%
1.957
3
3.250
3.010
.120
4. on
4 loo
14
3.771
3Vs
2.612
3V4
3.500
3.250
•125
4.505
4.600
14
4.021
3%
2.799
m
3-750
3.492
.129
4.988
5.100
14
4.271
3Vs
2.987
3%
4.000
3.732
.134
5.532
5.650
14
4.521
3%
3.174
4
4.250
3.974
.138
6.060
6.200
14
4.771
3%
3.923
4V4
4.500
4.216
.142
6.609
6.750
14
5.021
3%
4.141
4V*
4.500
4.090
.205
9.403
9.500
14
5.021
3%
4.141
4V2
4.750
4.460
.145
7.131
7.250
14
5.271
3%
4.360
4%
4-750
4.364
.193
9.393
9.500
14
5.271
3%
4.360
4%
5.000
4.696
.152
7.870
8.000
14
5.521
3%
4.578
5
5.250
4.944
.153
8.328
8.500
14
5.828
4¥s
5.929
5
5.250
4.886
.182
9.851
10.000
14
5.828
4Vs
5.929
5
5.250
4.886
.182
9.851
10.000
H%
5.800
4Vs
5.742
5
5.250
4.768
.241
12.892
13.000
11%
5.800
4Vs
5.742
5
5.250
4.648
.301
15.909
16.000
n%
5.800
4%
5.742
58/16
5.500
5.192
.154
8.792
9.000
14
6.078
4%
6.200
5%
6.000
5.672
.164
IO.222
10.500
14
6.664
m
7.729
5%
6.000
5.620
.190
11.789
12.000
n%
6.636
Ws
7.516
5%
6.000
5-552
.224
I3.8l8
14.000
n%
6.636
4Vs
7.516
5%
6.000
5-450
• 275
I6.8I4
17.000
11%
6.636
4%
7.516
6V4
6.625
6.287
.169
11.652
I2.0OO
14
7.308
9.825
6Vi
6.625
6.255
.185
12.724
13.000
14
7.308
4%
9.825
6%
7.000
6.652
.174
12.685
13.000
14
7.692
4%
10.497
6%
7.000
6.538
.231
16.699
17.000
11%
7.664
4%
10.225
7%
7-625
7.263
.181
14.390
14.750
14
8.317
4%
11.401
7%
8.000
7.628
.186
15.522
16.000
H%
8.788
5%
15.308
7%
8.000
7.528
.236
19.569
20.000
ii%
8.788
5%
15.308
81/4
8.625
8.249
.188
16.940
17.500
«%
9.413
m
16.461
8V4
8.625
8.191
.217
19.486
20.000
n%
9.413
16.461
8%
8.625
8.097
.264
23-574
24.000
11%
9.413
sVs
16.461
8%
9.000
8.608
.196
18.429
19.000
11%
9.788
5%
I7-I53
9%
10.000
9.582
.209
21.855
22.750
n%
0.911
6%
26.136
10%
II.OOO
10.552
.224
25.780
26.750
11%
1.911
6%
28.536
n%
I2.00O
H.5I4
.243
30.512
31.500
n%
2.911
6Vs
31.051
12%
13.000
12.482
.259
35.243
36.500
11%
4.025
m
37-499
I3V2
14.000
13.448
.276
40.454
42.000
11%
5.139
6Vs
44-495
I4V2
15.000
14.418
.291
45.714
47.500
n%
16.263
m
52.401
is%
16.000
15.396
.302
50.632
52.500
11%
17.263
6%
55-779
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered. Taper of threads is % inch diameter per foot length for all sizes.
Thickness of walls make it impracticable to cut threads of coarser pitch than
shown on table. The weight per foot of casing with threads and couplings is
based on a length of 20 feet, including the coupling, but shipping lengths of small
sizes will usually average less than 20 feet. All weights given in pounds. All
dimensions given in inches.
On sizes made in more than one weight or thread, weight and number of threads
desired must be specified. For general notes see page 21.
For test pressures see page 70. For illustration showing joint see page 78.
Inserted Joint Casing 27
Inserted Joint Casing
All Weights and Dimensions are Nominal
Diameters
Joint
Weight
Size
External
Internal
Thick-
ness
per foot
plain
ends
Threads
per inch
Length
of Joint
Diam-
eter of
— "L"
J?'DM
2
2.250
2.050
.100
2.296
14
.967
2.340
2*4
2.500
2.284
.108
2.759
14
.992
2.606
2%
2.750
2.524
.113
3.182
14
.017
2.866
2%
3.000
2.768
.116
3-572
14
.042
3.122
3
3.250
3.010
.120
4. on
14
.067
3.38o
3-500
3.250
• 125
4.505
14
.092
3-640
$1/2
3-750
3.492
.129
4.988
14
.117
3-898
38/4
4.000
3.732
•134
5-532
14
.142
4.158
4
4.250
3-974
.138
6.060
14
.167
4.416
4%
4.5oo
4.216
.142
6.609
14
.192
4 674
4y2
4-750
4.460
.145
7.I3I
14
.217
4-930
4%
5.000
4.696
.152
7.870
14
.242
5-194
5
5.250
4-944
.153
8.328
14
.267
5.446
58/16
5.5oo
5.192
.154
8.792
14
.292
5-698
5%
6.000
5.672
.164
10.222
14
.342
6.218
5%
6.000
5.620
.190
11.789
•373
6.246
6y*
6.625
6.287
.169
11.652
14
.405
6.853
6%
7.000
6.652
.174
12.685
14
.442
7.238
?y4
7.625
7-263
.181
14.390
14
.505
7-877
7%
8.000
7.628
.186
15.522
ny2
• 573
8.238
8U
8.625
8.249
.188
16.940
ny2
.636
8.867
8%
9.000
8.608
.196
•18.429
11^2
.673
9.258
9%
IO.OOO
9.582
.209
21.855
ny2
.773
10.284
105/8
II.OOO
10.552
.224
25.780
.873
11.314
11%
I2.0OO
H.5I4
.243
30.512
11%
.973
12.352
i2y2
13.000
12.482
.259
35-243
.073
13.384
i3y2
14.000
13.448
.276
40.454
11^2
2.173
14.418
I4^2
15.000
14.418
.291
45.714
n%
2.273
15.448
151,2
16.000
15.396
.302
50.632
ny2
2.373
16.470
1
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished in random lengths unless otherwise ordered.
Regular taper of threads is % inch diameter per foot length for all sizes, but will
furnish H inch, % inch, or % inch taper if so ordered.
All weights given in pounds. All dimensions given in inches.
On sizes made in more than one weight or thread, weight and number of
threads desired must be specified.
Thickness of walls make it impracticable to cut threads of coarser pitch than
shown on table.
For general notes see page 21.
For test pressures see page 71.
For illustration showing joint see page 78.
28 Boston Casing — Pacific Couplings
Boston Casing — Pacific Couplings
All Weights and Dimensions are Nominal
Diameters
|
Weight per foot
w rj
Couplings
Size
1
1
1
1
! «
*u y
|
£
_rj
1
W
I
A
£
a
|1|
H o
$1
1
.$
Q
m
5
bO
1
3%
4.000
3.732
.134
5-532
5.678
14
4-525
4Vs
4.367
4
4.250
3-974
.138
6.060
6.223
14
4.828
4Vs
4.844
4V4
4.500
4.216
.142
6.609
6.779
14
5-078
4%
5.H5
4V4
4.500
4.090
.205
9.403
9-547
14
5.078
4%
5.H5
4%
4-750
4.460
.145
7.I3I
7.309
14
5.328
4%
5.387
4V2
4-750
4.364
.193
9-393
9-550
14
5.328
4Vs
5.387
48/4
5.000
4.696
.152
7.870
8.093
14
5.664
4%
6.456
5
5.250
4-944
.153
8.328
8.562
14
5.914
4%
6.764
5
5.250
4.886
.182
9.851
10.071
14
5-914
4%
6.764
5
5.250
4.886
.182
9.851
10.057
"%
5.886
4%
6.575
5
5.250
4.768
.241
12.892
13.085
14
5.914
4%
6.764
5
5.250
4.768
.241
12.892
13.072
n%
5.886
4Vs
6.575
5
5.250
4.648
• 301
15.909
16.062
"%
5.886
4Vs
6.575
5%
6.000
5.672
.164
10.222
10.528
14
6.692
4%
9.052
5%
6.000
5.620
.190
11.789
12.063
11%
6.664
4%
8.814
5%
6.000
5-552
.224
I3.8l8
14.069
11%
6.664
4%
8.814
5%
6.000
5.450
• 275
I6.8I4
17.033
11%
6.664
4%
8.814
6%
6.625
6.287
.169
11.652
11.986
14
7.317
4%
9-955
6V4
6.625
6.255
.185
12.724
13.046
14
7.317
9-955
61/4
6.625
6.255
.185
12.724
13.028
11%
7.289
46/8
9.696
6%
7.000
6.652
.174
12.685
13.122
14
7.816
4%
12.274
6%
7.000
6.538
.231
16.699
17.076
11%
7.788
4%
12.000
7%
8.000
7.628
.186
15.522
16.038
11%
8.788
m
15.308
7%
8.000
7.528
.236
19.569
20.037
H%
8.788
3%
15.308
8%
9.000
8.608
.196
18.429
19-123
«%
9-9II
sH
19.667
9%
10.000
9.582
.209
21.855
22.802
11%
11.084
5%
25.624
9%
10.000
9-434
.283
29.369
30.250
H%
11.084
5%
25.624
10%
11.000
10.552
.224
25.780
26.978
11%
12.084
6Vs
33.764
11%
I2.OOO
H.5I4
.243
30.512
31.872
«%
13-139
6%
38.477
I2V2
13.000
12.482
.259
35-243
36.685
11%
14.139
6%
41.568
I3V2
14.000
13.448
.276
40.454
41-975
IlV2
15.139
6%
44.659
I4V2
15.000
14.418
.291
45.714
48.018
n%
16.500
6V8
61.800
151/2
16.000
15.396
.302
50.632
53.068
11%
17.500
61/8
65.758
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered. Taper of threads is % inch diameter per foot length for all sizes.
The weight per foot of casing with threads and couplings is based on a length
of 20 feet, including the coupling, but shipping lengths of small sizes will usually
average less than 20 feet. All weights given in pounds. All dimensions given in
inches. On sizes made in more than one weight or thread, weight and number of
threads desired must be specified.
Thickness of walls make it impracticable to cut threads of coarser pitch than
shown on table. For general notes see page 21.
For test pressures see page 70. For illustration showing joint see page 78.
California Diamond BX Casing
29
California Diamond BX Casing
All Weights and Dimensions are Nominal
Diameters
~
Weight per foot
1
Couplings
Size
"«j
s
JU
^3
1
G
u
1
1
1
I
a
1
w
1
s§!
1
[3
jjj
p
*
5%
6.000
5-352
.324
19 . 641
20.000
10
6.765
7%
15.748
6%
6.625
6.049
.288
19.491
20.000
IO
7.390
7%
18.559
6^4
6.625
5.921
.352
23.582
24.000
10
7.390
7%
18.559
6H
6.625
5.855
.385
25.658
26.000
10
7.390
7%
18.559
614
6.625
5-791
.417
27.648
28.000
10
7.390
7%
18.559
6%
7.000
6.456
.272
19-544
20.000
10
7.698
7%
17-943
6^/8
7.000
6.276
.362
25-663
26.000
IO
7.698
7%
17-943
65/8
7.000
6.214
• 393
27.731
28.000
10
7.698
7%
17-943
6%
7.000
6.154
.423
29.712
30.000
10
7.698
7%
17.943
7%
8.000
7-386
• 307
25.223
26.000
IO
8.888
8%
27.410
8%
8.625
8.017
• 304
27.016
28.000
10
9.627
33.096
8%
8.625
7-921
• 352
31 . 101
32.000
10
9.627
sy8
33.096
sy4
8.625
7.825
.400
35-137
36.000
IO
9.627
sy8
33.096
314
8.625
7-775
• 425
37-220
38.000
10
9.627
33.096
814
8.625
7-651
.487
42.327
43.000
IO
9.627
8-^B
33.096
9%
IO.OOO
9.384
.308
31.881
33-000
10
11.002
8y8
38.162
10
10.750
10.054
• 348
38.661
40.000
IO
n.866
sy8
45.365
10
10.750
9.960
• 395
43.684
45-000
10
11.866
45.365
10
10.750
9.902
.424
46.760
48.000
10
11.866
8^
45.365
IO
10.750
9.784
.483
52.962
54-000
10
11.866
sy8
45.365
11%
I2.0OO
11.384
.308
38.460
40.000
10
13.116
81/8
50.445
i2y2
13.000
12.438
.281
38.171
40.000
10
14.116
8^
54.508
12%
13-000
12.360
.320
43.335
45.000
10
14.116
81-8
54.5o8
i2y2
13.000
12.282
• 359
48.467
50.000
IO
14.116
sy8
54.508
i3y2
I4.OOO
13-344
.328
47.894
50.000
IO
15.151
9y8
67.912
isy2
l6.000
15.198
.401
66.806
70.000
10
17-477
9%
98.140
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered.
Taper of threads is % inch diameter per foot length for all sizes.
The weight per foot of casing with threads and couplings is based on a length
of 20 feet, including the coupling, but shipping lengths of small sizes will usually
average less than 20 feet.
All weights given in pounds. All dimensions given in inches.
This casing not furnished in lighter weights, but can be made heavier than
shown above.
When one size of casing is intended to telescope with another, it should always
be specified when ordering.
On sizes made in more than one weight, weight desired must be specified.
For general notes see page 21. For test pressures see page 71.
For illustration showing joint see page 82.
30
Tubing
Oil Well Tubing
All Weights and Dimensions are Nominal
Diameters
I
Weight per foot
I
Couplings
Size
1
1
I
.y
11
-3 1
11
O)
H
'3
i
|
H
pt <u
H g
F
3
a
IV4
i. 660
1.380
.140
2.272
2.300
n%
2.054
2%
• 974
1.900
1.610
.145
2.717
2.748
n%
2.294
2%
1 . 103
2
2.375
2.041
.167
3.938
4.000
n%
2.841
3%
2.146
2
2.375
1-995
.190
4.433
4.500
2.841
3%
2.146
2%
2.875
2.469
.203
5.793
5.897
n%
3-449
3.636
2%
2.875
2.441
.217
6.160
6.250
n%
3-449
4Vs
3.636
3
3-500
3.068
.216
7.575
7.694
n%
4.074
4%
4.366
3
3-500
3.018
.241
8.388
8.500
11%
4.074
4Vs
4-366
3
3-500
2.922
.289
9.910
10.000
4-074
4%
4.366
3%
4.000
3.548
.226
9.109
9.261
8
4.628
5-510
4
4.500
4.026
.237
10.790
10.980
8
5.233
4^8
6.673
4
4-500
3-990
.255
11.561
11.750
8
5-233
4Vs
6.673
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered.
Taper of threads is 3/4 inch diameter per foot length for all sizes.
The weight per foot of tubing with threads and couplings is based on a length
of 20 feet, including the coupling, but shipping lengths of small sizes will usually
average less than 20 feet.
All weights given in pounds. All dimensions given in inches.
On sizes made in more than one weight, weight desired must be specified.
For general notes see page 21. For test pressures see page 69.
For illustration showing joint see page 81.
California Special External Upset Tubing
All Weights and Dimensions are Nominal
Diameters
1
Weight per foot
I
Couplings
Size
1
1
1
•AM
*& W)
P3T3.S
•8-S
OJ.S
1
0)
1)
bO
<u
2^ 9*3.
jU.rt
g
ef
w
g
H
PM §
H 8
rd
H
§
Q
1
1
3
3.500
3.018
.241
8.388
8.627
IO
4.504
5%
7.627
4
4.500
3.958
.271
12.240
12.500
10
5-349
-61/8
9-5II
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered.
Taper of threads is % inch diameter per foot length for all sizes.
The weight per foot of tubing with threads and couplings is based on a length of
20 feet, including the coupling, but shipping lengths will usually average less than
20 feet.
All weights given in pounds. All dimensions given in inches.
For general notes see page 21. For test pressures see page 76.
For illustration showing joint see page 82.
California Drive Pipe — Bedstead
Tubing
31
California Diamond BX Drive Pipe
All Weights and Dimensions are Nominal
Diameters
Weight per foot
a
Couplings
Size
1
13
a
|
"O
g
o
1
"d
1
H
bO
W
1
H
I
P J
aJ
1
1
8
1
'53
41£
4-750
4.082
• 334
15.752
I6.0OO
10
5.357
6%
10. 112
4^>
5.000
4.506
.247
12.538
12.850
IO
5.686
10.734
4V2
5.000
4-424
.288
14-493
15.000
10
5.923
6Vs
14.299
The permissible variation in
weight is
5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random
lengths unless otherwise
ordered
Taper of threads is s/
§ inch diameter per foot length for
all size
s.
The weight per foot of pipe
with threads and couplings is based on a
length
of 20 feet, including the couplin
g, but shipping lengths of small sizes will
usually
average
less than 20 feet. All
weights given in pounds
All dimensions given
in inches. On sizes made in more than one weight, weight desired must be specified.
For general notes see page 21.
For test pressures see page 76. For illustration showing joint s
ee page 82.
Bedstead Tubing
All Weights and Dimensions are Nominal
Diameters
Thickness
Weight per foot
plain ends
External
Internal
.375
245
.065
.215
.500
370
.065
.301
.625
487
.069
.409
.750
594
.078
.559
.840
684
.078
.634
.875
.719
.078
.663
i
.000
844
.078
.768
i
.050
894
.078
.809
i
.250
i.
072
.089
1.103
i
.315
i.
137
.089
1.165
i
.500
i.
3io
.095
1.425
i
.660
i.
470
• 095
I.S87
i
.900
i.
682
.109
2.084
2
.000
i.
782
.109
2.201
2
.000
1.760
.120
2.409
2
.375
2.
H5
.130
3-II7
2
• 375
2.
107
.134
3-207
2
.500
2.
232
.134
3-386
2
.875
2.
509
.183
5.261
3
ooo
2.67O
.165
4-995
The permissible variation in weight is 5 per cent above and 5 per cent below.
This tubing furnished with plain ends pointed tool cut, with surface cleaned for
enameling purposes, and cut to any length that may be desired. Bedstead Tubing
is not subjected
to hydraulic
test. All weights given
in pounds. All
dimen-
sions given in inches. On sizes made in
more than one weight, weight or thick-
ness desired must be specified.
For general notes see page 21.
32 Flush Joint Tubing
Flush Joint Tubing
All Weights and Dimensions are Nominal
Size
Diameters
Thick-
ness
Weight
per foot
plain
ends
Threads
per inch
Length
of joint
External
Internal
3
3-500
3.068
.216
7-575
14
1%
3>V2
4.000
3.548
.226
9.109
14
1%
4
4-500
4.026
.237
10.790
«y2
I»/4
4Y2
5.000
4.506
.247
12.538
11%
1%
5
5.563
5-047
.258
14.617
«%
2
6.000
5-440
.280
17.105
ii%
2
6
6.625
6.065
.280
18.974
ii%
2
7.000
6.398
.301
21.535
«%
2
7
7.625
7.023
.301
23-544
"%
2
8.000
7.356
.322
26.404
10
2
8
8.625
7.98i
.322
28.554
10
2
9.000
8.316
.342
31.624
10
2
9
9.625
8.941
• 342
33.907
10
2
IO.OOO
9.270
.365
37-559
10
2V4
10
10.750
IO.O2O
.365
40.483
IO
2V4
I2.OOO
11.250
.375
46.558
10
m
12
12.750
12.000
.375
49.562
10
2V4
13
14.000
13.124
.438
63.441
8
2y2
14
15-000
14.124
.438
68.119
8
2%
IS
I6.OOO
I5.OOO
.500
82.771
8
*£
18 1
O.D./
I8.OOO
17.000
.500
93.451
8
2%
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished in random lengths unless otherwise ordered.
^Taper of threads is 8/i& inch diameter per foot length for all sizes, unless other-
wise specified.
Weights lighter than those given in above table are not suitable for flush joints.
All weights given in pounds. All dimensions given in inches.
For general notes see page 21.
For test pressures see page 75.
For illustration showing joint see page 80.
Allison Vanishing
Thread
Tubing 33
Allison Vanishing Thread Tubing
— Ends Upset
All Weights and Dimensions are Nominal
Diameters
Weight per foot
JM
1
Couplings
Size
1
1
•^
1
it
J
I
?3
3
H
^
1
d
H
£
1
*8
H
d
p
3
3
'53
2
2.375
2
.067
.154
3.652
3
-731
n%
2%
„
3.057
3%
2.484
afc
2.875
2
.469
.203
5.793
5
.903
8
3Vi
rt
3.616
4Vs
3-845
3
3-500
3.068
.216
7.575
7
.699
8
3H
4.237
4%
4-557
3%
4.000
3
.548
.226
9.109
9
.287
8
4%
6
4.848
6.036
4
4-500
4
.026
.237
10.790
10.984
8
|ii
ie
5.345
4%
6.768
4%
5-000
4
.506
.247
12.538
12
• 744
8
5%6
5.842
4%
7.426
5
5.563
5
.047
.258
i
4.617
14
.962
8
5%
6.509
5Vs
11.821
6
6.625
6.065
.280
18.974
19
• 359
8
6%
7.627
SVs
13.931
7
7.625
7
.023
.301
23 544
23 957
8
7%
8.621
5Vs
15.778
8
8.625
7
.981
.322
2
8.554
29
.196
8
8%
9.729
6%
24.119
Allison Vanishing Thread Tubing — Not
Upset
All
Weights and Dimensions are Nominal
Diameters
Weight per foot
g
Couplings
Size
13
1
1
J9
."
1
<L>
g
Hd§
i
i
1
1
H
to
W
a
£
ft
1
1
114
i. 660
1.38
3 .I4O
2.272
2.303
n%
2.070
27/8
1.052
i%
1.900
1.61
3 .145
2.717
2
75i
n%
2 309
2%
1.188
2
2.37
5
2.06
7 -154
3.^
52
3
723
n%
2.870
3%
2.315
2%
2.875
2.46
9 .203
5-793
5
893
8
3.429
3.625
3
3-500
3.o6
8 .216
7-575
7-689
8
4.050
4Vs
4.338
3%
4.oc
0
3-54
8 .226
9-1
00
9
276
8
4.661
5.782
4
4-500
4.02
6 .237
10.790
10.973
8
5.158
4^&
6.512
4%
S.ooo
4-50
6 .247
12.538
12
733
8
5.655
4Vs
7.171
5
5.563
5.04
7 .258
14.617
14
946
8
6.322
5%
11.456
6
6.625
6.06
5 .280
18.974
19
338
8
7-377
SVs
13.446
7
7.62
5
7.02
3 -301
23-5
44
23
936
8
8.371
15.296
8
8.625
7-98
i -322
28.554
29
167
8
9-479
6%
23.465
The following notes apply to both tables.
The permissible variation in
weight is 5 per cent above
and 5 per cent below.
Furnished with threads and
couplings and in random
lengths unless otherwise
ordered.
Taper of threads is 3/4 inch diameter per foot length for all sizes.
The weight per foot of tubing with threads and couplings is based on a length
of 20 feet, including the coupling, but shipping lengths of small sizes will usually
average less than 20 feet.
All weights
given in pounds. All dimensions f
nven in
inches.
For general
notes see page 21. For test
pressures see page 75.
For illustration showing joint see page 81.
34 Special Rotary Pipe
Special Rotary Pipe
All Weights and Dimensions are Nominal
Size
Diameters
Thickness
Weight per foot
Threads
per inch
Couplings
External
a
Plain ends
H
Diameter
1
I
1
2%
4
4
5
5
6
6
2.875
2.875
4-Soo
4-500
S.ooo
5.000
5.563
5.563
6.625
6.625
2.323
2.143
3.958
3-826
4.388
4.290
4-955
4.813
5-937
5.761
.276
.366
.271
.337
.306
• 355
• 304
.375
• 344
• 432
7.661
9.807
12 . 240
14.983
15-340
I7.6II
17.074
20.778
23.076
28.573
7-830
IO.OOO
12.500
15.000
15.500
18.000
17.500
2I.OOO
23.500
29.000
8
8
8
8
8
8
8
8
8
8
3-603
3.693
5.228
5.240
5.604
5-740
6.373
6.272
7-435
7-334
5Vs
5%
5%
6%
SVs
6%
6%
7%
7%
5.888
7-316
8.901
11.720
8.270
12.950
14.620
16.442
17-254
19-451
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered. Taper of threads is % inch diameter per foot length for all sizes.
The weight per foot of pipe with threads and couplings is based on a length of
20 feet, including the coupling, but shipping lengths of small sizes will usually
average less than 20 feet. All weights given in pounds. All dimensions given in
inches. On sizes made in more than one weight, weight desired must be specified.
For general notes see page 21. For test pressures see page 76.
For illustration showing joint see page 79.
Special Upset Rotary Pipe
All Weights and Dimensions are Nominal
Size
Diameters
1
Weight per foot
Threads
per inch
Couplings
External
Internal
a
s
Threads
and
couplings
Diameter
!
u
1
2V2
2%
4
4
f
6
2.875
2.875
4.5oo
4.500
5.563
5.563
6.625
6.625
2.323
2.143
3-958
3.826
4-975
4.859
6.065
5.76i
.276
.366
.271
• 337
.294
.352
.280
.432
7.661
9.807
12.240
14.983
16.544
19.590
18.974
28. 573
7-841
IO.OOO
12.632
15.323
17.000
20.000
19.551
28.948
8
8
8
8
8
8
8
8
3.564
3.678
5.256
5.256
6.303
6.303
7-350
7-350
6V8
7%
7%
81/8
8$
8%
6.743
7.844
14.296
14.296
18.472
18.472
22.994
22.994
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered. Taper of threads is % inch diameter per foot length for all sizes.
The weight per foot of pipe with threads and couplings is based on a length
of 20 feet, including the coupling, but shipping lengths of small sizes will usually
average less than 20 feet. All weights given in pounds. All dimensions given in
inches. On sizes made in more than one weight, weight desired must be specified.
For general notes see page 21. For test pressures see page 76.
For illustration showing joint see page 79.
South Penn Casing — Reamed and Drifted Pipe 35
South Penn Casing
All Weights and Dimensions are Nominal
Diameters
1
Weight per foot
T£^
Couplings
Size
1
|
^4
o
|
$ I
d»d.S
T3 o
1
t>
4.)
,C
ti
W
1
g
.S
'3
£
fl3 a ^
jirf
H 8
II
.3
Q
M
5
bo
1
•58/i6
5-500
5-044
.228
12.837
13.000
nVs
6.050
4%
6.759
58/46
5-500
4.892
• 304
16.870
17.000
ny2
6.050
4%
6.759
6V4
6.625
6.257
.184
12.657
13.000
«MS
7.280
SVs
10 . 630
6%
6.625
6.135
.245
16.694
17.000
ny2
7.280
SVs
10.630
6%
7.000
6.538
.231
16.699
17.000
10
7.642
SVs
H.I33
6%
7.000
6.450
.275
I9-75I
20.000
IO
7.642
SVs
II. 133
6%
7.000
6.334
.333
23.7H
24.000
10
7.699
6%
14.458
8V4
8.625
8.097
.264
23-574
24.000
8
9.358
6y8
18.577
8*4
8.625
8.003
.311
27.615
28.000
8
9.358
61/8
18.577
10
10.750
10.192
.279
31-201
32.515
8
11.958
6%
39-772
10
10.750
10.146
.302
33.699
35-000
8
11.958
6%
39-772
121/2
13.000
12 . 278
.361
48 . 730
50.000
8
14.085
7Vs
46.464
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered. Taper of threads is % inch diameter per foot length for all sizes,
except the 8H inch, 10 inch, and 12^5 inch which are % inch taper.
The weight per foot of casing with threads and couplings is based on a length of 20
feet, including the coupling, but shipping lengths of small sizes will usually average
less than 20 feet. All weights given in pounds. All dimensions given in inches.
On sizes made in more than one weight, weight desired must be specified.
For general notes see page 21. For test pressures see page 71.
For illustration showing joint see page 83.
Reamed and Drifted Pipe
All Weights and Dimensions are Nominal
Size
Diameters
Thickness
Weight per foot
Thread's
per inch
Couplings
External
Internal
Plain ends
Threads
and
couplings
LJ
1
a
1
I
s
$
2
2
2%
3
3%
4
4%
2.375
2.375
2.875
3-500
4.000
4.5oo
S.ooo
5.563
6.625
2.067
2.041
2.469
3-068
3.548
4.026
4.5o6
5-047
6.065
.154
.167
.203
.216
.226
.237
.247
.258
.280
3.652
3-938
5.793
7-575
9.109
10.790
12.538
14.617
18.974
3.697
4.000
5.843
7.675
9.261
10.980
12.742
14.966
19.367
v?Jx!N
M M 00 00 00 00 00 00 00
2.773
2.773
3.265
4.014
4.628
5.233
5-733
6.420
7.482
3%
3%
4%
41/8
4%
4%
4%
SVs
M
i. 806
i. 806
2.625
4.076
5.510
6.673
7.379
11.730
13.869
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths, 20 feet and
shorter, unless otherwise ordered. Taper of threads is s/4 inch diameter per foot
length for all sizes. The weight per foot of pipe with threads and couplings is
based on a length of 20 feet, including the coupling, but shipping lengths of small
sizes will usually average less than 20 feet. On sizes made in more than one
weight, weight desired must be specified. All weights given in pounds. All
dimensions given in inches. For general notes see page 21. For test pressures
see page 73. For illustration showing joint see page 79.
36
Air Line Pipe — Full Weight Drill Pipe
Air Line Pipe
All Weights and Dimensions are Nominal
Diameters
jj
Weight per foot
O
.5
Couplings
Size
13
13
5
o
%
»d ^
a
S
Jj
£
u
0>
§"
%
-a
£H
1
S g"a
i
a
0)
&. '
&
M
H 8
H
s
^
i%
1.900
1.582
•159
2.956
3.oo
n%
2.387
2l%6
1.364
2
2.375
2.043
.166
3.916
4.00
2.976
3%
2.416
2%
2.875
2.423
.226
6.393
6.50
8
3-544
4
3.772
3
3-500
2.990
.255
8.837
9.00
8
4.272
4%
5.899
4
4.5oo
3.996
.252
H.433
H.75
8
5-500
4^2
9.124
5
5.563
4-977
.293
16.491
17.00
8
6.652
6
16 . 720
6
6.625
6.025
.300
20.265
21. OO
8
7.833
6
21.826
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered.
The above pipe is fitted with special air line couplings recessed for lead calking.
Taper of threads is 94 inch diameter per foot length for all sizes.
The weight per foot of pipe with threads and couplings is based on a length
of 20 feet, including the coupling, but shipping lengths of small sizes will usually
average less than 20 feet. All weights given in pounds. All dimensions given
in inches. For general notes see page 21.
For test pressures see page 73. For illustration showing joint see page 80.
Full Weight Drill Pipe
All Weights and Dimensions are Nominal
Diameters
w
w
Weight per foot
1
Couplings
Size
1
1
1
1
w
•9
a
1,1
1
1
|
5
o3
S
a
(— i
H
1
H 8
1
S
1
1
4
4.5oo
4.026
.237
10.790
11.055
8
5.228
M
8.901
4
4.500
3-990
.255
11.561
11.815
8
5.228
SVs
8.901
4%
5.000
4.506
.247
12.538
12.744
8
5.604
5Vn
8.270
5
5.563
5-047
.258
14.617
15.055
8
6.373
14.620
6
6.625
6.065
.280
18.974
19.463
8
7-435
6%
17.254
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered. Taper of threads is SA inch diameter per foot length for all sizes.
The weight per foot of pipe with threads and couplings is based on a length
of 20 feet, including the coupling, but shipping lengths of small sizes will usually
average less than 20 feet. All weights given in pounds. All dimensions given
in inches. On sizes made in more than one weight, weight desired must be
specified. For general notes see page 21.
For test pressures see page 76. For illustration showing joint see page 80.
Dry Kiln Pipe— Tuyere Pipe
37
Dry Kiln Pipe
All Weights and Dimensions are Nominal
Diameters
i
Weight per foot
1
Couplings
Size
External
Internal
•
^
o
•g
Plain ends
Threads
and
couplings
Threads pe
Diameter
X
-5
a
1
5
M
1
i
I.3IS
1.049
.133
1.678
1.697
11%
1.700
2%
.702
34
i. 660
1.380
.140
2.272
2.304
n%
2. 121
2%
1. 134
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with threads and couplings and in random lengths unless otherwise
ordered.
Taper of threads is % inch diameter per foot length for all sizes.
The weight per foot of pipe with threads and couplings is based on a length of
20 feet, including the coupling, but shipping lengths of small sizes will usually
average less than 20 feet.
All weights given in pounds. All dimensions given in inches.
For general notes see page 21.
For test pressures see page 76.
For illustration showing joint see page 83.
Tuyere Pipe
All Weights and Dimensions are Nominal
Size
Diameters
Thickness
Weight per foot,
plain ends
External
Internal
i
1%
I.3IS
i. 660
• 957
1.278
.179
.191
2.171
2.996
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished with plain ends and in random lengths unless otherwise ordered.
This pipe is made in random lengths up to 40 feet.
All weights given in pounds. All dimensions given in inches.
For general notes see page 21.
For test pressures see page 76.
38 Locomotive Boiler Tubes — Seamless
Locomotive Boiler Tubes — Seamless — Open Hearth Steel
All Weights and Dimensions are Nominal
(For test pressures see page 102.)
Diameters
Thickness
Weight
Length of tube
per square foot
Square foot of
surface per
lineal foot
Exter-
nal
Inter-
nal
Inches
B.W.G.
foot
Exter-
nal
surface
Inter-
nal
surface
Exter-
nal
surface
Inter-
nal
surface
i%
1.310
.095
13
1.425
2.546
2.9IS
• 392
.342
IV2
1.282
.109
12
1.619
2.546
2.979
.392
• 335
1%
1.280
.no
1.632
2.546
2.984
.392
.335
1%
1.260
.120
ii
1.768
2.546
3-031
• 392
.329
*H
1.250
.125
1.835
2.546
3.055
.392
.327
i%
1.232
•134
10
1-954
2.546
3.100
• 392
.322
iy2
1.230
.135
1.968
2.546
3.105
.392
.322
i%
1.204
.148
9
2.137
2.546
3.172
.392
.315
i%
i. 200
.ISO
2.162
2.546
3.183
.392
.314
I8/4
1.560
.095
13
1.679
2.182
2.448
.458
.408
1%
1-532
.109
12
1.910
2.182
2.493
• 458
.401
1%
1.530
.110
1.926
2.182
2.496
.458
.400
1%
1.510
.120
II
2.089
2.182
2.529
• 458 ,
.395
1%
1.500
• 125
2.169
2.182
2.546
.458
• 392
1%
1.482
.134
10
2.312
2.182
2-577
.458
.387
i8/i
1.480
.135
2.328
2.182
2.580
.458
• 387
1%
1-454
.148
9
2.532
2.182
2.627
.458
.380
i%
1.450
.150
2.563
2.182
2.634
.458
.379
i%
1.685
.095
13
1. 806
2.037
2.266
.490
.441
1%
1.657
.109
12
2.055
2.037
2.305
.490
• 433
I7/8
1.655
.110
2.073
2.037
2.307
.490
• 433
1%
1.635
.120
II
2.249
2.037
2.336
.490
.428
1%
1.625
.125
2.336
2.037
2.350
.490
.425
1%
1.607
134
10
2.491
2.037
2.376
.490
.420
1%
1.605
.135
2.508
2.037
2 379
.490
.420
1%
1.579
.148
9
2.729
2.037
2.419
.490
-413
j7/8
1-575
.ISO
2.763
2.037
2.425
.490
.412
2
1.810
.095
13
1.932
.909
2. no
.523
.473
2
1.782
.109
12
2.2OI
.909
2.143
.523
.466
2
1.780
.no
2.22O
.909
2.145
.523
.466
2
1.760
.120
II
2.409
• 909
2.170
.523
.460
2
I-75O
.125
2.5O3
.909
2.182
.523
.458
2
I 732
.134
IO
2.670
• 909
2.205
• 523
• 453
Locomotive Boiler Tubes — Seamless 39
Locomotive Boiler Tubes — Seamless — Open Hearth Steel (Concluded)
All Weights and Dimensions are Nominal
(For test pressures see page 102.)
Diameters
Thickness
Weight
Length of tube
per square foot
Square foot of
surface per
lineal foot
S
Exter-
nal
Inter-
nal
Inches
B.W.G.
toot
Exter-
nal
surface
Inter-
nal
surface
Exter-
nal
surface
Inter-
nal
surface
2
1.730
.135
2.688
1.909
2.207
.523
.452
2
1.704
.148
9
2.927
1.909
2.241
.523
• t^
.446
2
1.700
.150
2.963
1.909
2.246
.523
.445
21/4
2.060
.095
13
2.186
1.697
.854
.589
• 539
2.032
.109
12
2.492
1.697
.879
.589
• 531
2H
2.030
.110
2.514
1.697
.881
.589
.531
21/4
2.OIO
.120
n
2.729
1.697
.900
.589
.526
2%
2.00O
.125
2.836
1.697
.909
.589
• 523
a$$
1.982
.134
10
3-028
1.697
.927
.589
.518
2H
1.980
• 135
3-049
1.697
.929
.589
.518
2^4
1.954
.148
9
3.322
1.697
• 954
.589
.511
1.950
.I5O
3.364
1.697
• 958
.589
.510
2l/2
2.310
•095
13
2.440
1.527
.653
.654
.604
2^/2
2.282
.109
12
2.783
1.527
.673
.654
' -597
2%
2.280
.no
2.807
1.527
.675
.654
.596
2%
2.260
.120
II
3.050
1.527
.690
.654
• 591
2V2
2.250
.125
3.170
1.527
.697
.654
• 589
2M>
2.232
.134
IO
3.386
1.527
.711
.654
.584
2l/2
2.230
• 135
3.409
1.527
.712
.654
.583
2.204
.148
9
3.717
1.527
.654
.577
2.200
.150
3.764
1.527
.654
• 575
3
2.810
.095
13
2.947
1.273
• 359
.785
.735
3
2.782
.109
12
3.365
1.273
• 373
.785
.728
3
2.780
.no
3-395
1.273
• 374
.785
• 727
3
2.760
.120
n
3.691
1.273
.383
.785
.722
3
2.750
.125
3.838
1.273
.388
• 785
.719
3
2.732
.134
10
4.101
1.273
• 398
.785
.715
3
2.730
.135
4.130
1.273
.399
.785
.714
3
2.704
.148
9
4.5o8
1.273
.412
.785
.707
3
2.700
.150
4.565
1.273
.414
• 785
.706
40 Locomotive Boiler Tubes — Lap Welded
Locomotive Boiler Tubes — Lap Welded — Open Hearth Steel
All Weights and Dimensions are Nominal
(For test pressures see page 72.)
Diameters
Thickness
Weight
per
foot
Length of tube
per square foot
Square foot of
surface per
lineal foot
Exter-
nal
Inter-
nal
Inches
B.W.G.
Exter-
nal
surface
Inter-
nal
surface
Exter-
nal
surface
Inter-
nal
surface
i%
i%
i%
i%
i%
i%
i%
i%
i%
2
2
2
2
2
2
2
2
2
2l4
2>4
2y4
2y4
2y4
2%
2y4
2y4
a%
2y2
2y2
2y2
2y2
2y2
2y2
2y2
2y2
2y2
3
3
3
3
3
3
3
3
3
.560
• 532
• 530
.510
.500
.482
.480
• 454
• 450
.810
.782
.780
.760
.750
.732
• 730
.704
.700
.060
.032
.030
.010
.000
.982
.980
• 954
• 950
.310
2.282
2.280
2.260
2.250
2.232
2.230
2.204
2.200
2.810
2.782
2.780
2.760
2.750
2.732
2.730
2.704
2.700
.095
.109
.110
.120
.125
.134
.135
.148
.150
.095
.109
.110
.120
.125
.134
.135
.148
-ISO
.095
.109
.110
.120
.125
.134
.135
.148
.150
.095
.109
.110
.120
•125
.134
.135
.148
.150
.095
.109
.110
.120
.125
.134
.135
.148
.150
13
12
II
10
9
•• — ••
12
1.679
1.910
1.926
2.089
2.169
2.312
2.328
2.532
2.563
1.932
2.201
2.22O
2.409
2.503
2.670
2.688
2.927
2.963
2.186
2.492
2.514
2.729
2.836
3.028
3-049
3-322
3.364
2.440
2.783
2.807
3.050
3-170
3-386
3.409
3.717
3.764
2.947
3.365
3-395
3.691
3.838
4.101
4.130
4.508
4.565
2.182
2.182
2.182
2.182
2.182
2.182
2.182
2.182
2.182
• 909
• 909
.909
.909
.909
.909
• 909
.909
.909
.697
.697
.697
.697
-697
.697
.697
.697
.697
.527
.527
.527
.527
.527
.527
.527
.527
.527
.273
.273
.273
.273
.273
.273
.273
• 273
.273
2.448
2.493
2.496
2.529
2.546
2.577
2.580
2.627
2.634
2. IIO
2.143
2. 145
2.170
2.182
2.205
2.207
2.241
.246
.854
.879
.881
.900
.909
.927
.929
.954
.958
.653
.673
.675
.690
.697
.711
.712
.733
.736
.359
.373
.374
.383
.388
.398
.399
.412
.414
.458
.458
.458
.458
.458
• 458
• 458
• 458
.458
.523
.523
.523
.523
.523
.523
.523
• 523
.523
.589 ,
.589
.589
.589
.589
.589
.589
.589
.589
.654
.654
.654
.654
.654
.654
.654
.654
.654
.785
.785
• 785
.785
.785
.785
.785
.785
.785
.408
.401
.400
.395
.392
.387
.387
.380
-379
• 473
.466
.466
.460
.458
.453
• 452
.446
.445
• 539
• 531
.531
.526
.523
.518
.518
.511
• 510
.604
.597
.596
.591
.589
.584
.583
.577
.575
.735
.728
.727
.722
.719
• 715
.714
.707
.706
II
10
9
13
12
II
IO
9
13
12
II
10
9
13
12
II
10
9
Standard Boiler Tubes and Flues— Lap Welded 41
Standard Boiler Tubes and Flues — Lap Welded
All Weights and Dimensions are Nominal
(For test pressures see page 72.)
Diameters
Thickness
Weight
Length of tube
per square foot
Square feet of
surface per
lineal foot
Exter-
nal
Inter-
nal
Inches
B.W.G.
foot
Exter-
nal
surface
Inter-
nal
surface
Exter-
nal
surface
Inter-
nal
surface
i3/i
1.560
.095
13
1.679
2.182
2.448
.458
.408
2
1.810
.095
13
1.932
• 909
.no
.523
.473
21/4
2.060
.095
13
2.186
.697
.854
.589
• 539
2%
2.282
.109
12
2.783
.527
.673
.654
• 597
23/4
2.532
.109
12
3-074
.388
.508
.719
.662
3
2.782
.109
12
3.365
.273
.373
.785
.728
314
3.010
.120
II
4.011
.175
.269
.850
.788
3V2
3.260
.120
II
4-331
.091
.171
.916
.853
33/4
3-510
.120
II
4.652
I.oiS
.088
.981
.918
4
3-732
.134
10
5-532
.954
.023
1.047
.977
4V2
4.232
.134
IO
6.248
.848
.902
1.178
1.107
5
4.704
.148
9
7.669
.763
.812
1.308
1.231
6
5.670
.165
8
10.282
.636
.673
1.570
1.484
7
6.670
.165
8
12.044
.545
• 572
1.832
1.746
8
7.670
.165
8
13.807
• 477
.498
2.094
2.008
9
8.640
.180
7
16.955
.424
.442
2.356
2.261
10
9-594
.203
6
21 . 24O
.381
.398
2.617
2.511
n
10.560
.220
5
25.329
• 347
.361
2.879
2.764
12
11.542
.229
28.788
.318
.330
3-I4I
3.021
13
12.524
.238
'4
32.439
.293
• 304
3.403
3.278
14
13.504
.248
36.424
.272
.282
3.665
3.535
15
14.482
.259
3
40.775
.254
.263
3.926
3-791
16
I5.46o
.270
45-359
.238
.247
4.188
4.047
42 Matheson Joint Pipe
Matheson Joint Pipe
All Weights and Dimensions are Nominal
Outside
Weight per foot
External
diameter
Thickness
diameter
of rein-
forcing
ring — D
Length of
joint — L
Weight of
lead per
joint
Plain
ends
Complete
2.OO
.095
2.966
2.16
1-932
1-952
I.OO
3.00
.109
4-034
2.26
3.365
3-392
1-75
4.00
.128
5.236
2.32
5-293
5-339
2.75
S.oo
.134
6.268
2.38
6.963
7.019
3-50
6.00
.140
7.446
2.50
8.762
8.872
4-75
7.00
.149
8.484
2.58
10.902
11.028
5-50
8.00
.158
9.646
2.73
13.233
13.405
6.75
8 oo
.185
9.700
2.78
15.441
15.614
6.75
9.00
.167
10.684
2.73
15-754
15-945
8.25
9.00
.196
10.742
2.90
18.429
18.621
8.50
9.00
.250
10.850
3-07
23.362
23-557
9.00
IO.OO
.175
11.846
2.82
18,363
18.610
9-50
10. OO
.208
11.912
2.85
21.752
22.001
9-75
10.00
.270
12.036
3.06
28.057
28 . 309
IO.OO
II. OO
.185
12.886
2.91
21.368
21 . 638
II. OO
11.00
.220
12.956
2.93
25-329
25.6OO
II. OO
II. OO
.290
13.096
3-17
33.171
33-445
12.50
12.00
.194
14.048
3.00
24.461
24.880
13.25
12. OO
.244
14.148
3-40
30.635
31.057
14.25
12.00
.310
14.280
3-76
38.703
39-129
16.50
I3.OO
.202
15.084
3-07
27.610
28.060
15.25
13-00
.247
15.174
3-40
33.642
34-095
15.50
13-00
.310
15.300
3.76
42.014
42.472
18.00
14.00
.2IO
16.370
3-15
30.928
31.536
17.25
I4.OO
.250
16.450
3-53
36.713
37.324
19.25
14.00
.310
16.570
3.84
45.325
45-941 •
20.75
15-00
.222
17-394
3-24
35.038
35-686
19.25
15-00
.260
17.470
3-53
40.930
41.581
20.25
I5.OO
.320
17.590
3.84
50.171
50.826
22.25
16.00
.234
18.438
3-32
39-401
40.089
22.00
16.00
.270
18.510
3-62
45-359
46.050
23.25
16.00
• 330
18.630
3-75
55-228
55.923
24.25
17.00
.240
19.470
3-41
42.959
43.687
23-75
18.00
.245
20.730
3-50
46.458
47.384
25-75
18.00
.310
20.860
3.87
58.568
59-501
28.50
19.00
.259
21 . 778
3-57
51.840
52.815
29.00
20.00
.272
22.804
3.64
57.309
58.332
31.00
20.00
• 375
23 . oio
4-17
78.599
79.631
35-50
22.00
.301
24.882
4.06
69.756
71.098
40.25
22.00
.400
25 . 080
4.65
92.276
93-629
45-50
24.00
.330
26.980
4.26 ,
83.423 ,
84.882
48.00
26.00
.362
29.064
4-40
99-122
100.697
55-25
28.00
.396
31 • 672
4.58
116.746
119.021
65.00
30.00
• 432
33 - 764
4-75
136.421
138.851
75-00
The permissible variation in- weight is 5 per cent above and 5 per cent below.
Furnished in random lengths unless otherwise ordered. The weight per foot
complete is based on a length of 18 feet of pipe, but shipping lengths of small
sizes will usually average less than 18 feet. On sizes made in more than one weight,
weight desired must be specified. Column marked weight complete includes the
ring but not the lead. Pipe furnished black, galvanized, or dipped. Lead not
furnished. All weights given in pounds. All dimensions given in inches. For
general notes see page 21. For list of test pressures see page 73. For illustra-
tion showing joint see page 84.
Converse Lock-joint Pipe 43
Converse Lock-joint Pipe
All Weights and Dimensions are Nominal
Weight
Hub — cast iron
per foot
Exter-
nal di-
ameter
Thick-
ness
Weight
per foot
plain ends
Weight
of lead
for field
end
complete
including
hub
leaded on
Diam-
eter
Length
Weight
D
mill end
2.00
.095
1.932
3%
3%
4.25
1. 00
2.207
3.00
.109
3.365
sVs
3%
8.50
2.25
3-931
4.00
.128
5-293
6^4
4
10.50
3.00
5-991
5.00
.134
6.963
714
4*4
15.00
3-75
7.932
6.00
.140
8.762
8*4
4%
19.00
4-50
9.969
7.00
.149
10.902
9V2
4V2
24.00
5-50
12.419
8.00
.158
13.233
10%
4%
28.25
6.50
15.008
8.00
.185
I5.44I
ioV2
4%
28.25
6.50
17.190
9.00
.167
15-754
"p
4%
34-50
8.50
17.958
9.00
.196
18.429
4%
34-50
8.50
20.602
9.00
.250
23.362
11%
34-50
8.50
25-477
IO.OO
.175
18.363
123/4
5
39-00
9.00
20.801
10.00
.208
21 . 752
123/4
5
39-00
9.00
24.148
10.00
.270
28.057
123/4
5
39-00
9.00
30.375
II. OO
.185
21.368
133/4
5
41-50
IO.OO
23-963
11.00
.220
25.329
13%
5
41.50
IO.OO
27-875
II. OO
.290
33.171
13%
5
41.50
IO.OO
35.619
12.00
.194
24.461
15
SV2
55-00
II. OO
27.795
12. OO
.244
30.635
15
5V2
55-00
11.00
33.885
12.00
.310
38.703
15
5%
55-00
II. OO
41.844
I3.OO
.202
27.610
16%
5%
59-00
12.00
31.179
13.00
.247
33.642
SVa
59-00
12. OO
37-129
13.00
.310
42.014
16%
59-00
12.00
45.387
14.00
.210
30.928
5%
67.00
14.50
35-013
14.00
.250
36.713
17^8
5%
67.00
14-50
40.714
14.00
.310
45.325
171/8
58/4
67.00
14.50
49.204
15.00
.222
35.038
183/8
58/4
78.00
15.50
39-731
15.00
.260
40.930
183/8
53/4
78.00
15.50
45.538
15.00
.320
50.171
5%
78.00
15.50
54.646
16.00
.234
39.401
19%
IO2.OO
25-00
45.847
16.00
.270
45.359
198/i
6V1
102. OO
25.OO
5L7I3
16.00
.330
55.228
I93/4
6V4
102. OO
25.00
61.428
17.00
.240
42.959
20%
6V4
110.00
26.OO
49-850
18.00
.245
46.458
22^/8
63/4
I4O.OO
3O.OO
55-123
18.00
.310
58.568
221/8
6%
I4O.OO
30.00
67.030
19.00
.259
51.840
23%6
63/4
150.00
32.00
61.081
20.00
.272
57.309
7V4
iSo.OO
37-00
68.337
20.00
.375
78.599
24% 6
7V4
iSo.OO
37-00
89.244
22.00
.301
69.756
26%
7%
215.00
45-00
82.868
22.00
.400
92.276
265/8
73/4
215.00
45-00
104.958
2*4.00
• 330
83.423
29
8V4
275-00
So.oo
99.789
26.00
.362
99-122
31%
83/4
360.00
64.00
120.555
28.00
.396
116.746
3315/16
9V4
425.00
77.00
142.000
, 30.00
• 432
136.421
10
525.00
82.00
166.828
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished in random lengths unless otherwise ordered. The weight per foot
complete is based on a length of 18 feet, including the hub, but shipping lengths of
small sizes will usually average less than 18 feet. On sizes made in more than
one weight, weight desired must be specified. Pipe furnished black, galvanized,
or dipped. Lead for field end not furnished. All weights given in pounds.
All dimensions given in inches. For general notes see page 21. For list of
test pressures see page 74. For illustration showing joint see page 84.
44 Kimberley Joint Pipe
Kimberley Joint Pipe
All Weights and Dimensions are Nominal
T?Ytf»r
Weight per foot
Collar
Weisht
exter-
nal di-
ameter
Thick-
ness
Plain
ends
Complete
excluding
lead
Diam-
eter
D
Length
Weight
of lead
required
6.00
.140
8.762
9.623
7.63
6
15.50
10. OO
7.00
.149
IO.O02
11.930
8.64
6
18.50
13.50
8.00
.158
13.233
14.371
9.65
6
20.50
15.50
8.00
.185
I5-44I
16.579
9.65
6
20.50
15.50
9.00
.167
15-754
17-032
10.65
6
23.00
17.25
9.00
.196
18.429
19.707
10.65
6
23.00
17.25
9.00
.250
23.362
24 . 640
10.65
6
23.00
17-25
10.00
.175
18.363
19.779
11.66
6
25.50
19.00
10.00
.208
21 . 752
23.169
11.66
6
25.50
19.00
10.00
.270
28.057
29.474
11.66
6
25.50
19.00
11.00
.185
21.368
22.924
12.67
6
28.00
23.25 .
II. OO
.220
25.329
26.884
12.67
6
28.00
23.25
11.00
.290
33.171
34.727
12.67
6
28.00
23.25
12. OO
.194
24.461
26.128
13.67
6
30.00
25.50
12.00
.244
30.635
32.302
13-67
6
30.00
25.50
12.00
.310
38.703
40.370
13.67
6
30.00
25.50
13.00
.202
27.610
29-443
14.68
6
33-00
27.50
13-00
.247
33.642
35-475
14.68
6
33-00
27.50
I3.OO
.310
42.014
43.848
14.68
6
33-00
27.50
14.00
.210
30.928
32.873
15.68
6
35-00
29.50
I4.OO
.250
36.713
38.657
15-68
6
35-00
29.50
I4.OO
.310
45.325
47.269
15-68
6
35-00
29.50
15-00
.222
35.038
37.094
16.69
6
37-00
3i.5o
15.00
.260
40.930
42.986
16.69
6
37-00,
3i.5o
15 00
.320
50.171
52.226
16.69
6
37-00
31.50
16.00
.234
39.401
41.596
17.70
6
39-50
34.36
16.00
.270
45.359
47-554
17.70
6
39-50
34.36
16.00
.330
55.228
57-422
17.70
6
39-50
34.36
17.00
.240
42.959
47-737
19.06
9
86.00
64.00
18.00
.245
46.458
51.486
20.07
9
90.50
69.00
18.00
.310
58.568
63.596
20.07
9
90.50
69.00
19.00
.259
51.840
57.H8
21.07
9
95-00
72.50
20.00
.272
57.309
62.865
22.08
9
IOO.OO
78.00
20.00
.375
78.599
84.154
22.08
9
100.00
78.00
22.00
.301
69.756
75.839
24.09
9
109.50
89.50
22.00
.400
92.276
98.359
24.09
9
109.50
89.50
24-00
.330
83.423
90.034
26.11
9
119.00
97.50
26.0O
.362
99-122
106.260
28.12
9
128.50
105.50
28.00
.396
116.746
124.413
30.13
9
138.00
113.50
3O.OO
-432
136.421
144.616
32.14
9
147.50
121.50
The permissible variation in weight is 5 per cent above and 5 per cent below.
Furnished in random lengths unless otherwise ordered.
The weight per foot complete excluding lead is based on a length of 18 feet
of pipe, but shipping lengths of small sizes will usually average less than 18 feet.
On sizes made in more than one weight, weight desired must be specified.
Pipe furnished black, galvanized, or dipped. Collars are shipped loose, to be put
on in field. Weight of lead specified is for a complete joint, both sides of collar.
Lead not furnished. All weights given in pounds All dimensions given in
inches.
For general notes see page 21. For list of test pressures see page 74.
For illustration showing joint see page 83.
Square Pipe — Rectangular Pipe 45
Square
Pipe
All Weights and Dimensions are Nominal
Size
Thickness
Weight per foot
plain ends
External
Internal
%
.607
.134
1.46
i
.800
.100
1.25
i
.750
.125
1-55
i
.624
.188
2. II
114
1. 000
.125
1.97
Hi
.982
.134
2.05
Hi
• 938
.156
2.29
Hi
.874
.188
2.48
Hi
.750
.250
3.28
iy<2
.250
.
.125
2-33
1^2
.220
.140
2.55
H2
.188
.156
2.78
1^2
.124
.188
3-05
1%
.OOO
.250
4.00
ll^lQ
.407
.140
2.76
I1VlO
• 375
.156
3.00
jl^Q
.311
.188
3-75
lliie
.187
.250
4.60
2
• 750
.125
3-io
2
• 732
.134
3-18
2
.710
.145
3-52
2
.624
.188
4-39
2
.500
.250
5-40
2-Vis
.124
.188
5.6o
3 ~
2.6oo
.200
7.06
•- Rectangular Pipe
All Weights and Dimensions are Nominal
Si TO.
ize
Thickness
Weight per foot
plain ends
External
Internal
H4Xi
.97oX .720
.140
1.67
i^4 x i
.874X .624
.188
2.05
H^XHi
.256X1.006
.122
2.05
H£XX%
.2ioX .960
.145
2.24
HfcXHi
.i88X .938
.156
2.40
i^Xi^i
.I24X .874
.188
2.85
HijXi^i
.oooX -750
.250
3-67
2 XHi
.732X .982
.134
2.53
2 XH'2
.710X1.210
.145
3.oo
2 XiMj
.624X1.124
.188
3-6i
2 Xl%
.500X1.000
.250
4.65
2^5X1%
.210X1.210
.145
3-52
2^2 XH£
.124X1.124
.188
4-39
2-v^xiy*
.000X1.000
.250
5-40
3 X2
.624X1.624
.188
5.6o
3 X2
.600X1.600
.200
6.00
The following notes apply to both tables.
The permissible variation in weight is 5 per cent above and 5 per cent below.
Cut to any length that may be desired
All weight
5 given in pounds. All
dimensions given in inches. For sections see pages 8
>-88. On sizes made in
more than one weight, weight or thickness desired must be specified.
For general notes see page 21.
46 Weight per Foot of Pipe
Weight per Foot of Pipe (Nominal Inside Diameter)
Inside
diam-
eter
Birmingham Wire Gage
16
1 15 | 14
13
| „ | „
Fractions and decimals of an inch
.065
.068
.072
.083
%9
.09375
• 095
.100
.109
.120
%
.125
Vs
I
%
%
%
I
1%
m
2
2V2
3
3V2
4
4V2
6
8
9
10
ii
12
.236
.244
.2 =
'.IS
-4<
.jB
• 7.
6
'9>r
>3
^0
>2
.285
.405
.524
.671
.857
.311
.446
.581
.747
• 957
1.222
1.568
.314
• 451
.588
• 755
.968
1.237
1.587
1.831
2.313
.325
.469
.614
.790
.014
.297
.666
.922
.429
• 344
.501
.658
.850
1.095
1.403
1.805
2.084
2.637
3.220
3-947
.365
• 538
.711
.922
I.I9I
I-53I
1.973
2.281
2.890
3-530
4-331
.373
• 554
• 734
• 954
1.234
1.588
2.049
2.369
3-003
3.671
4.505
5-173
5.840
Inside
1 diam-
eter
Birmingham Wire Gage
6
5 | 4
3 1
2
Fractions and decimals of an inch
.203
%a
.21875
.220
.238
y±
.250
• 259
%2
.28125
.284
Vs
y*
%
%
%
i
4
iV2
2
2V2
k
4
. 4V2
6
8
9
10
ii
12
• 730
1.023
1.381
1.836
2.410
3.158
3.679
4.709
5-793
7.148
8.232
9.3i6
10.400
11.620
13.923
16.091
18.259
20.427
22.866
25-034
27 . 202
.750
1.065
I.45I
1.942
2.561
3.367
3.927
5-037
6.205
7-665
8.834
10.002
11.170
12.485
14.966
17.303
19.639
21.975
24.604
26.940
29.276
•751
1.069
1.456
1-950
2.572
3.383
3-947
5.063
6.238
7.706
8.881
10 . 056
11.231
12.554
15.049
17-399
19.748 :
22.098 '.
24.741 :
27.091 :
29.440 ;
1. 110
1.530
2.064
2.737
3-614
4.224
5-431
6.702
8.291
9.562
[0.833
[2.104
[3.535
[6.234
[8.776
21.318
23.860
26.720
29 . 262
51.803
1. 134
1.575
2.136
2.843
3.764
4.405
5.673
7.008
8.677
10.012
11-347
12.682
14-185
17.021
19.691
22 . 361
25.031
28.035
30.705
33-375
1.150
1.607
2.188
2.921
3-875
4-539
5.853
7.236
8.965
10.348
11.731
13.114
14.671
17.609
20.375
23.141
25.907
, 29.019
31.785
34.552
1.678
2.309
3-105
4.141
4.862
6.289
7.791
9.668
11.170
12.672
14.174
15-865
19.055
22 . O59
25.062
28.066
31-445
34-449
37-453
1.686
2,323
3.127
4-173
4.901
6.342
7-858
9-754
11.271
12.787
14.304
16.012
19.233
22.266
25.299
28.332
31-745
34.778
37-8II
Weight per Foot of Pipe 47
Weight per Foot of Pipe (Nominal Inside Diameter) (Continued)
Birmingham Wire Gage
Inside
10
9
8
7 1
diam-
eter
Fractions and decimals of an inch
%2
8/16
• 134
.148
• ISO
. 15625
.165
.180
.1875
.200
: i/8
.387
.406
.408
14
.581
.619
.624
.640
.660
.692
• 70S
.726
%
• 774
.833
.841
.865
.898
•951
.976
I.OI4
1/2
1. 010
1.093
1.105
1.141
1.189
1.268
1.306
1.367
SA
1.310
1.425
1.441
I.49I
1-559
1.672
1.727
I.8J5
1.690
1.844
1.866
1-933
2.026
2.181
2.257
2.381
j$i
2.183
2.389
2.419
2.509
2.634
2.845
2.948
3.118
i%
2.527
2.769
2.803
2.909
3-057
3.306
3.429
3.631
2
3.207
3-520
3.564
3-702
3.894
4.219
4.380
4.645
2%
3.922
4-310
4.365
4.536
4-775
5.180
5.381
5.713
3
4-817
5.298
5.366
5-579
5.877
6.382
6.633
7.048
3%
5-532
6.088
6.167
6.414
6.758
7.343
7.634
8.116
4
6.248
6.879
6.968
7.248
7.639
8.304
8-635
9.184
4%
6.963
7.669
7.769
8.083
8.520
9.266
9.637
10.252
5
7.769
8.559
8.671
9.022
9-512
10.348
10 . 764
11-455
6
10.237
10.373
10.794
11.383
12.390
12.891
13.724
7
11.818
11-975
12.463
13.146
14.312
14.893
15.860
8
14 132
14 908
1 6 234
1 6 896
17 996
9
16.670
18.157
18.898
20.132
IO
20 320
21 151
22 535
II
23 . 154
24.671
12
26 807
Birmingham Wire Gage
Inside
i
o
1
00 |
diam-
eter
Fractions and decimals of an inch
5/16
11/32
%
.300
• 3125
• 340
•34375
• 350
.375
.380
.400
%
V2
1-730
%
2.403
2.461
2.578
2.592
2.616
2.703
i
3.252
3-345
3-540
3-565
3.607
3.764
3-794
1^4
4-357
4-497
4-793
4-832
4.896
5.146
5-194
5.382
•fi
5.126
5.298
5-664
5.713
5-793
6.107
6.168
6.408
2
6.648
6.883
7.389
7-457
7.569
8.010
8.096
8.437
2^5
8.250
8.552
9-205
9.292
9.438
IO.OI2
10.125
10.573
3
10.252
10.638
11.474
H.587
n.774
12.515
12.662
13.243
3^2
11.854
12.307
13.290
13.423
13.643
14.518
14.691
15-379
4
13-457
13-975
15.106
15.258
15.512
16.520
16.720
17.515
4^
15.059
15.644
16.921
17.094
I7.38I
18.523
18.750
19.651
5
16.862
17.523
18.966
19.161
19 . 486
20.778
21.034
22.056
6
20.265
21.068
22.822
23.060
23.456
25.031
25-345
26.593
7
23.469
24.405
26.453
26.731
27.194
29.036
29.403
30.865
8
26.673
27-743
30.084
30.402
30.932
33.041
33.462
35-137
9
29.877
31.080
33.716
34-074
34.670
37.046
37-520
39.409
10
33.482
34.835
37.8oi
38.204
38.875
41.552
42.086
44-215
II
36.686
38.173
41.432
41.875
42.613
45.557
46.144
48.487
12
39.890
4L5IO
45.o63
45-547
46.351
49.562
50.203
52.759
48
Weight per Foot of Pipe
Weight per Foot of Pipe (Nominal Inside Diameter) (Continued)
Birmingham Wire Gage
Inside
ooo
|
oooo |
eter
Fractions and decimals of an inch
18/32
Vie
15/82
y2
.40625
.425
• 4375
• 450
.454
.46875
.500
• 550
%
iy*
5-439
5.605
5-712
5.815
5.847
5.963
6.194
6.520
2
6.481
8 542
6.695
8 851
6.833
9 053
6.968
9 251
7.011
7.165
7.476
7-930
10.711
II. 120
11.389
11.654
11.738
12.046
12.682
13.657
3
13.423
13.957
14.309
14-658
14.769
15-175
16.020
17.328
$1/2
15-592
16.227
16.646
17.061
17.193
17.678
18.690
20.265
4
17.762
18.496
18.982
19.464
19.618
20.181
21.360
23 . 202
4%
19.931
20.766
21.318
21.867
22.042
22 . 684
24.030
26.139
5
22.374
23.321
23-949
24-573
24.772
25.503
27.036
29.446
6
26.982
28.142
28.911
29.677
29.921
30.820
32.707
35-685
7
31.320
32 . 681
33.584
34.483
34-770
35.826
38.048
41-559
8
35.659
37-220
38.256
39-289
39.6i9
40.832
43.388
47-433
9
39.998
41.759
42.929
44-095
44.468
45.839
48.728
53.307
10
44.879
46.865
48.185
49-502
49.923
51.471
54-735
59.915
II
49.218
51.404
52.858
54.308
54-771
56.477
6o.o75
65.789
12
53-557
55-944
57-531
59.H4
59.620
61.483
65.415
71.663
Weight per Foot of Pipe 49
Weight per Foot of Pipe (Nominal Inside Diameter) (Concluded)
Inside
Fractions and decimals of an inch
diam-
eter
9/16
%
Hie
%
.5625
.600
.625
.650
.6875
.700
.750
1
i
iy2
8,035
8.330
8.510
8.677
8.902
2
10.888
n.374
11.681
11-975
12.390
12.522
13.016
2^/2
13.892
14-578
15.018
15.446
16.061
16.260
17.021
3
17.647
18.583
19.190
19.784
20.651
20.933
22.027
3^2
20.651
21.787
22.528
23.256
24.322
24.671
26.032
4
23.654
24.991
25.866
26.727
27-993
28.409
30.037
4%
26.658
28.195
29.203
30.198
31-665
32.147
34-043
5
30.040
31-803
32.961
34.io6
35.798
36.356
38.552
6
36.421
38.608
40.050
41-479
43.596
44.295
47 059
7
42.428
45.016
46.725
48.421
50.939
5L772
55.o69
8
48.436
51.424
53-400
55.363
58.281
59.248
63.079
9
54-443
57.833
60.075
62.305
65 . 624
66.724
71.089
10
6l . 202
65.042
67.585
70.115
73-885
75-134
80.101
ii
67.209
71.450
74-260
77-057
81.227
82.611
88. ill
12
73-217
77.858
80.935
83.999
88.570
90.087
96.121
Inside
Fractions and decimals of an inch
eter
18Ae
7/8
15/16
.800
-8125
.850
.875
.900
.9375
I
%
3/l
I
1%
2
13-457
13.558
13.844
14.017
2^5
17.729
17.897
18.383
18.690
3 /
23.069
23.321
24.057
24-530
24.991
25.657
26.700
27.341
27.659
28.596
29.203
29-797
30.663
32.040
4 /
31.613
3L998
33-135
33.876
34.603
35.670
37.38o
35.885
36.337
37.674
38.548
39-409
40.676
42.720
5
40.695
41.223
42.785
43.810
44.821
46.313
48.733
6
49.769
50.438
52.426
53-734
55-029
56.946
60.075
7
58.313
59-116
61.504
63.079
64.641
66.959
70.756
8
66.857
67.793
70.582
72.424
74-253
76.972
81.436
9
75-401
76.471
79.66o
81.769
83.865
86.984
92.116
10
85.014
86.233
89.873
92.283
94.679
98.249
104.131
ii
93-558
94-911
98.951
101.628
104.291
108.261
114.811
12
IO2 . 102
103.589
108.029
110.973
H3.903
118.274
125.491
• •••.-• •• - :. •'•"•'• • J\- •
50 Weight per Foot of Tubes
Weight per Foot of Tubes (or Outside Diameter Pipe)
Outside
diam-
eter
Birmingham Wire Gage
15
14
13
12
ii
10
9
Fractions and decimals of an inch
.072
.083
8/32
.09375
.095
.100
.109
.120
%
.125
.134
.148
1. 000
1. 125
1.250
1. 312
1.375
1.500
1.625
1.750
1.875
2.OOO
2.125
2.250
2.500
2.750
3.000
3.250
3-Soo
3-750
4.000
4.250
4.5oo
4-750
5.000
5.250
5-500
6.000
7.000
. 8.000
9.000
10.000
II.OOO
12.000
13.000
14.000
15.000
16.000
17.000
18.000
19.000
20.000
21.000
22.0OO
24.000
26.000
28.000
30.000
.713
.812
.923
1.034
1.089
.907
1.032
1. 157
1.219
1.282
.918
.045
.171
.234
.298
.425
• 552
.679
.806
1.932
2.059
2.186
2.440
2.093
2.947
.961
.094
.228
.294
.361
• 495
.628
.762
.895
2.029
2.162
2.296
2.563
2.830
3-097
.037
.182
.328
.400
• 473
.619
.764
.910
2.055
'2.201
2.346
2.492
2.783
3-074
3.365
3.656
3-947
.127
.288
.448
• 527
.608
.768
.928
2.089
2.249
2.409
2.569
2.729
3.050
3-370
3.691
4.011
4-331
4-652
.168
.335
.501
:584
.668
1.835
2.002
2.169
2.336
2.503
2.670
2.836
3.170
3.504
3.838
4.171
4.505
4.839
5.173
5.506
5.840
.239
.418
• 597
.685
• 776
• 954
2.133
2.312
2.491
2.670
2.849
.3.028
3-386
3-743
4.101
4-459
4-817
5.175
5-532
5.890
6.248
6.606
6.963
7-321
7.679
1.346
1-544
I.74I
1.839
1-939
2.137
2.334
2.532
2.729
2.927
3.124
3-322
3.717
4.112
4.508
4.903
5.298
5.693
6.088
6.483
6.879
7-274
7.669
8,064
8.459
9-250
10.830
•
Weight per Foot of Tubes 51
Weight per Foot of Tubes (or Outside Diameter Pipe) (Continued)
Outside
diam-
eter
Birmingham Wire Gage
8
7
« 1
Fractions and decimals of an inch
.150
%2
• 15625
.165
.180
%6
.1875
.200
.203
%2
.21875
ooo
.125
.250
.312
.375
.500
.625
• 750
.875
2. OOO
2.125
2.250
2.500
2.750
3.OOO
3-250
3-500
3-750
4.000
4.250
4-500
4-750
5.OOO
5.250
5-500
6. ooo
7.000
8.000
9.000
10. OOO
II. OOO
12.000
13.000
14.000
15.000
16.000
17.000
18.000
19.000
20.000
21.000
22.000
24.000
26.000
28.00O
3O.OOO
1.361
1.561
1.762
1.861
1.962
2.162
2.362
2.563
2.763
2.963
3-163
3.364
3.764
4-165
4.565
4.966
5.366
5.767
6.167
6.568
6.968
7.369
7.769
8.170
8.570
9-371
10.973
1.408"
1.616
1.825
1.928
2.033
2.242
2.451
2.659
2.868
3.076
3.285
3-493
3-9II
4.328
4-745
5.162
5-579
5-997
6.414
6.831
7.248
7.665
8.083
8.500
8.917
9-751
11.420
13-089
1.471
1.691
1.912
2.O2I
2.132
2.352
2.572
2.793
3-013
3-233
3-453
3.674
4-II4
4-555
4-995
5.436
5.877
6.317
6.758
7.198
7.639
8.079
8.520
8.960
9.401
10 . 282
12.044
13.807
15.569
1.576
1.816
2.056
2.176
2.297
2.537
2.777
3.018
3.258
3.498
3-739
3-979
4.460
4-940'
5-421
5-901
6.382
6.863
7-343
7.824
8.304
8.785
9.266
9.746
10.227
11.188
13.110
15.033
16.955
18.878
1.627
1.877
2.127
2.251
2.378
2.628
2.878
3-128
3-379
3.629
3.879
4.130
4.630
5.I3I
5.632
6.132
6.633
7-134
7.634
8.135
8.635
9.136
9.637
10.137
10.638
H.639
13-642
15 • 644
17.647
19.649
21.652
1.708
1-975
2.242
2.375
2.509
2.776
3-043
3-310
3-577
3.844
4.111
4.378
4.912
5.446
5.98o
6.514
7.048
7.582
8.116
8.650
9-184
9.718
10.252
10.786
11.320
12.388
14.525
16.661
18.797
20.933
23.069
25.205
1.727
1.998
2.269
2.404
2.540
2.811
3.082
3.354
3.625
3.896
4.167
4.438
4.980
5.522
6.064
6.606
7.148
7.690
8.232
8.774
9.316
9.858
10.400
10 . 942
11.484
12.568
14.736
16.904
19.072
21 . 240
23.408
25.576
27-744
1.825
2.II7
2.409
2.554
2.701
2.993
3.285
3-577
3-869
4.161
4-453
4-745
5.329
5.913
6.497
7.081
7.665
8.250
8.834
9.418
10.002
10.586
11.170
11-754
12.338
13-506
15.842
18.179
20.515
22.851
25.188
27.524
29.860
32.196
52 Weight per Foot of Tubes
Weight per Foot of Tubes (or Outside Diameter Pipe) (Continued)
Birmingham Wire Gage
Outside
5
4
3
2
I
diam-
eter
_, Fractions and decimals of an inch
H
%2
5/16
.220
.238
.250
.259
.28125
.284
.300
• 3125
I.OOO
1.832
1.936
2. OO2
2.049
2.158
2.171
2.242
2.294
1. 125
2.126
2.254
2.336
2.395
2.534
2.550
2.643
2.7II
1.250
2.42O
2.572
2.670
2.741
2.909
2.930
3-043
3.128
1.312
2.565
2.729
2.835
2.912
3.096
3.118
3.242
3-335
1.375
2.713
2.890
3-003
3.087
3.285
3.309
3-444
3.546
1.500
3.007
3.207
3-337
3-432
3.660
3.688
3.844
3.963
1.625
3-301
3.525
3.671
3.778
4.036
4.067
4-245
4.380
1.750
3-594
3.843
4.005
4.124
4.411
4.446
4.645
4-797
1.875
3.888
4.161
4.338
4.470
4.787
4.825
5.046
5-214
2.000
4.182
4.478
4.672
4.815
5.162
5.204
5.446
5.632
2.125
4.476
4.796
5.oo6
5-i6i
5.538
5.584
5.847
6.049
2.250
4-769
5.H4
5-340
5.507
5.913
5.963
6.247
6.466
2.5OO
5-357
5-749
6.007
6.198
6.664
6.721
7.048
7-300
2.750
5-944
6.385
6.675
6.890
7.415
7-479
7.849
8.135
3-000
6.531
7.020
7-342
7.582
8.166
8.238
8.650
8.969
3-250
7.H9
7.656
8.010
8.273
8.917
8.996
9-451
9.804
3-500
7.706
8.291
8.677
8.965
9.668
9-754
10.252
10.638
3-750
8.294
8.927
9-345
9-656
10.419
10.512
H.053
11.472
4.000
8.881
9.562
10.012
10.348
11.170
11.271
11.854
12.307
4.250
9.469
10.198
10.680
11.039
11.921
12.029
12.655
13.141
4-500
10.056
10.833
H.347
11.731
12.672
12.787
13-457
13-975
4-750
10.643
11.468
12.015
12 . 422
13.423
13.546
14.258
14.810
5.000
11.231
12.104
12.682
13.114
14.174
14.304
15.059
15.644
5.250
11.818
12.739
13.350
13-805
14.925
15.062
15.860
16.479
5-500
12.406
13-375
14.017
14-497
15 • 676
15.820
16.661
17.313
6.000
I3.58o
14.646
15.352
15.880
17.177
17-337
18.263
18.982
7.000
15-930
17.188
18.022
18.646
20.181
20.370
21 . 467
22.319
8.000
18.280
19.730
20.692
21.412
23.185
23-403
24.671
25.657
9.000
20.629
22.271
23.362
24.179
26.189
26.437
27.875
28.994
IO.OOO
22.979
24.813
26.032
26.945
29.193
29.470
31.079
32.332
11.000
25.329
27-355
28.702
29.711
32.196
32.503
34.283
35.670
I2.OOO
27.678
29.897
31.372
32.477
35-200
35.536
37.487
39-007
13.000
30.028
32.439
34-043
35.243
38.204
38.569
40.691
42.345
14.000
32.377
34.981
36.713
38.009
41.208
41.602
43.895
45-682
15.000
34.727
37.523
39.383
40.775
44.212
44-636
47.099
49.020
16.000
40 . 065
42 . 053
43 . 542
47.215
47 . 669
50 . 303
52.357
17.000
42.606
44 . 723
46 . 308
50.219
50 . 702
53 • 507
55 • 695
18.000
47 • 393
49 . 074
53 . 223
53 • 735
56.711
59 . 032
19.000
51 . 840
56 . 227
56.768
59.915
62 370
20.000
59.231
59.8oi
63.119
65.708
2I.OOO
62 . 835
66 . 323
69.045
22.000
69 . 527
72.383
24.000
26.000
28.000
30.000
Weight per Foot of Tubes 53
Weight per Foot of Tubes (or Outside Diameter Pipe) (Continued)
Birmingham Wire Gage
Outside
° 1
OO
000
diam-
eter
Fractions and decimals of an inch
*%2
%
18/32
• 340
•34375
• 350
• 375
.380
.400
.40625
.425
.000
2.396
2.409
2.429
2.503
.125
2.850
2.868
2.896
3.003
cSI.1
.250
3-304
3.327
3.364
3.504
.312
3.529
3-554
3.596
3-752
3-782
• 375
3.758
3-786
3-831
4.005
4.038
4.165
4-203
.500
4.212
4-244
4.298
4.505
4-545
4.699
4-745
4.879
.625
4.666
4.703
4.766
5.006
5.052
5-233
5.287
5.446
• 750
5.120
5.162
5-233
5.506
5.560
5.767
5.830
6.014
.875
5-573
5.621
5-700
6.007
6.067
6.301
6-372
6.581
.000
6.027
6.080
6.167
6.508
6.574
6.835
6.914
7.149
.125
6.481
6.539
6.635
7.008
7.082
7.369
7-457
7.716
.250
6.935
6.998
7.102
7.509
7.589
7.903
7-999
8.283
.500
7.843
7.916
8.036
8.510
8.603
8.971
9.084
9.418
• 750
8.751
8.834
8.971
9-512
9.618
10.039
IO.I69
10.553
3.000
9.659
9-751
9-905
10.513
10.633
11.107
11.253
11.688
3.250 10.566
10.669
10 . 840
11.514
11.647
12.175
12.338
12.822
3.500 n.474
H.587
11.774
12.515
12.662
13.243
13.423
13-957
3-750
12.382
12.505
12.709
13.517
13.677
I4-3II
14.507
15.092
4.000
13.290
13.423
13.643
14.518
14.691
15-379
15.592
16.227
4.250
14.198
14.341
14.578
15.519
15.706
16.447
16.677
I7.36i
4.500
15.106
15-258
15.512
16.520
16.720
17.515
17.762
18.496
4-750
16.013
16.176
16.447
17.522
17-735
18.583
18.846
19.631
5.000
16.921
17.094
I7.38I
18.523
18.750
19.651
19.931
20.766
5.250
17.829
18.012
18.316
19.524
19.764
20.719
2I.OI6
21.900
5-500
18.737
18.930
19.250
20.525
20.779
21.787
22.IOO
23.035
6.000
20.552
20.765
2I.I2O
22.528
22.808
23.923
24.270
25.305
7.000
24.184
24-437
24.858
26.533
26.867
28.195
28.609
29.844
8.000
27.815
28.108
28.596
30.538
30.925
32.467
32.947
34.383
9.000
3L446
31-779
32.334
34-543
34.983
36.739
37-286
38.922
IO.OOO
35-077
35-451
36.072
38.548
39-042
41.011
41.625
43.461
11.000
38.709
39-122
39-810
42-553
43-100
45.283
45.964
48.000
12.000
42.340
42.793
43.548
46.558
47-159
49-555
50.303
52.539
13.000
45-971
46.464
47-286
50.563
51.217
53.827
54.641
57.078
14.000
49.602
50.136
5L024
54.568
55.276
58.100
58.980
61.617
15.000
53-234
53.807
54.762
58.573
59-334
62.372
63.319
66.156
16.000
56.865
57.478
58.500
62.579
63.393
66 . 644
67.658
70.695
17.000
60.496
61 . 150
62.238
66.584
67.451
70.916
71.997
75.235
18.000
64.127
64.821
65.976
70.589
7I.5IO
75-188
76.336
79-774
19.000
67.759
68.492
69.714
74-594
75.568
79.46o
80.674
84.313
20.000
7L390
72.164
73-452
78.599
79 . 626
83.732
85.013
88.852
2I.OOO
75-021
75.835
77.190
82.604
83.685
88.004
89.352
93-391
22.000
78.652
79.506
80.928
86.609
87.743
92.276
93.691
97-930
24.000
85.915
86.849
88.405
94.619
95.860
100.820
102.368
107.008
26.OOO
IO2 . 629
103 . 977
109 . 364
III.O46
116.086
28.00O
117.908
119.724
125.164
3O.OOO
54 Weight per Foot of Tubes
Weight per Foot of Tubes (or Outside Diameter Pipe) (Continued)
Birmingham Wire Gage
Outside
oooo
diam-
eter
Fractions and decimals of an inch
7/l6
15/32
V2
9/16
• 4375
.450
.454
.46875
.500
.550
.5625
.000
.125
.250
.312
.375
.500
4.964
5.046
5-071
5.162
5-340
5.58o
.625
5.548
5.647
5.677
5-788
6.007
6.314
• 750
6.132
6.247
6.284
6.414
6.675
7-048
7-134
.875
6.716
6.848
6.890
7.040
7-342
7.783
7-884
2.000
7-300
7-449
7.496
7-665
8.010
8.517
8.635
2.125
7.884
8.050
8.102
8.291
8.677
9-251
9-386
2.250
8.469
8.650
8.708
8.917
9-345
9.985
10.137
2.5OO
9.637
9.852
9.920
IO.I69
10.680
H.454
11.639
2.750
10.805
n.053
11.132
11.420
12.015
12.922
13.141
3.000
n.973
12.255
12.345
12.672
13.350
14-391
14.643
3.250
I3.I4I
13.456
13-557
13.923
14-685
15.860
16.145
3-500
14.309
14-658
14.769
I5-I75
16.020
17.328
17.647
3-750
15-477
15.860
I5.98I
16.427
17-355
18.797
19.149
4.000
16.646
17.061
17.193
17.678
18 . 690
20.265,
20.651
4.250
17-814
18.263
18.406
18.930
20.025
21.734
22.152
4-500
18.982
19.464
19.618
20.181
21.360
23 . 202
23.654
4-750
20.150
20.666
20.830
21.433
22.695
24.671
25.156
5.000
21.318
21.867
22.042
22.684
24.030
26.139
26.658
5-250
22.486
23.069
23-254
23.936
25.365
27.6o8
28.160
5-Soo
23.654
24.270
24.467
25.188
26.700
29.076
29 . 662
6.000
25.991
26.673
26.891
27.691
29.370
32.013
32.666
7.000
30.663
31-479
31 • 740
32.697
34-710
37-887
38.673
8.000
35.336
36.285
36.588
37.703
40.050
43.761
44-681
9.000
40.008
41.091
41-437
42.710
45-390
49.636
50.689
10.000
44.681
45.897
46.286
47.716
50.730
55-510
56.696
11.000
49-354
50.704
51.135
52.722
56.070
61.384
62 . 704
I2.00O
54.026
55-510
55.984
57-729
61.410
67.258
68.711
13.000
58.699
60.316
60.832
62.735
66.750
73.132
74.719
14.000
63.371
65.122
65.681
67.741
72.091
79.006
80.726
15.000
68.044
69.928
70-530
72.748
77-431
84.880
86.734
16.000
72.716
74-734
75-379
77-754
82.771
90.754
92.742
17.000
77.389
79-540
80.228
82.760
88. in
96.628
98.749
18.000
82.061
84.346
85.076
87.767
93-451
IO2 . 5O2
104-757
19.000
86.734
89.152
89.925
92.773
98.791
108.376
110.764
20.000
91.407
93.958
94-774
97-779
104.131
114.250
116.772
2I.OOO
96.079
98.764
99.623
102.786
109.471
120.125
122.780
22.000
100.752
103.570
104.472
107.792
114.811
125.999
128.787
24.OOO
110.097
113.182
114.169
117.805
125.491
137.747
140.802
26.000
119.442
122.795
123.867
127.817
136.172
149-495
152.818
28.00O
128.787
132.407
133.564
137.830
146.852
161.243
164.833
3O.OOO
138.132
142.019
143.262
147.843
157.532
172.991
176.848
Weight per Foot of Tubes 55
Weight per Foot of Tubes (or Outside Diameter Pipe) (Continued)
Fractions and decimals of an inch
Outside
diam-
eter
%
His
%
.600
.625
.650
.6875
.700
• 750
.800
.000
.125
.250
.312
• 375
.500
.625
• 750
7.369
7.509
7.636
7.801
.875
8.170
8.343
8.504
8.719
2.OOO
8.971
9.178
9-371
9.637
2.125
9-772
IQ.OI2
10.239
10.555
2.250
10.573
10.847
11.107
11.472
H.587
12.015
12.388
2.500
12.175
12.515
12.842
13.308
13-457
14.017
14.525
2.750
13-777
14.184
14.578
15.144
15.326
16.020
16.661
3.OOO
15-379
15.853
I6.3I3
16.979
17-195
18.022
18.797
3.250
16.981
17-522
18.049
18.815
19.064
20.025
20 933
3-500
18.583
19.190
19 . 784
20.651
20.933
22.027
23 069
3-750
20.185
20.859
21.520
22.486
22.802
24.030
25.205
4.OOO
21.787
22.528
23.256
24.322
24.671
26.032
27.341
4.250
23.389
24.197
24.991
26.158
26.540
28.035
29-477
4-500
24.991
25.866
26.727
27-993
28.409
30.037
31.613
4-750
26.593
27.534
28 . 462
29.829
30.278
32.040
33-749
5.000
28.195
29.203
30.198
31.665
32.147
34-043
35.885
5.250
29.797
30.872
3L933
33-500
34.oi6
36.045
38.021
5-500
31-399
32.541
33.669
35.336
35-885
38.048
40.157
6.000
34.603
35.878
37.140
39-007
39.623
42.053
44.429
7.000
41.011
42.553
44.082
46.350
47-099
50.063
52.973
8.000
47 • 419
49.228
51.024
53.692
54-575
58.073
61.517
9.000
53.827
55.903
57.966
61.035
62.051
66.083
70.061
10.000
60.236
62.579
64.908
68.378
69.527
74-093
78.605
11.000
66.644
69.254
71.850
75 - 720
77-003
82.103
87.150
12.000
73.052
75.929
78.792
83.063
84 . 480
90.113
95.694
13.000
79.460
82.604
85-734
90.405
9L956
98.123
104.238
14.000
85.868
89.279
92.677
97.748
99-432
106.134
112.782
15.000
92.276
95.954
99.619
105.091
106.908
114.144
121.326
16.000
98.684
102 . 629
106.561
"2.433
114.384
122.154
129.870
17.000
105.092
109.304
H3.503
119.776
121.860
130.164
138.414
18.000
111.500
115-979
120.445
127.118
129.336
138.174
146.958
19.000
117.908
122.654
127.387
I34.46I
136.812
146.184
155.503
20.000
124.317
129.330
134.329
141.804
144.288
154.194
164.047
21.000
130.725
136.005
141.271
149.146
151.765
162.204
172.591
22.00O
137.133
142.680
148.213
156.489
159-241
170.215
181.135
24.000
149-949
156.030
162.098
I7I.I74
174.193
186.235
198.223
26.000
162.765
169.380
175.982
185.859
189.145
202.255
215.312
28.000
175.581
182.730
189.866
200.545
204.097
218.275
3O.OOO
188.397
196.081
203.750
215.230
219.050
234.296
56 Weight per Foot of Tubes
Weight per Foot of Tubes (or Outside Diameter Pipe) (Concluded)
. Fractions and decimals of an inch
Outside
diam-
eter
18/16
7/8
1%6
i%
.8125
.850
-875
.900
.9375
I
1. 125
.000
.125
.250
.312
.375
.500
.625
• 750
.875
2.000
2.125
2.250
12.474
12.709
12.849
2.500
14.643
14.978
15.185
2.750
16.812
17.248
17 522
3.000
18.982
19.517
19.858
20.185
20.651
21.360
3.250
21.151
21.787
22 . 194
22 . 588
23-154
24.030
3-500
23.321
24-057
24-530
24.991
25.657
26.700
3-750
25.490
26.326
26.867
27-394
28.160
29.370
4.000
27.659
28.596
29.203
29-797
30.663
32.040
4.250
29.829
30.865
31-539
32.200
33.166
34-710
4-500
31.998
33-135
33.876
34.603
35.670
37.38o
4-750
34.168
35 • 404
36.212
37.006
38.173
40.050
5-000
36.337
37.674
38.548
39.409
40.676
42.720
5-250
38.506
39-943
40.884
41.812
43-179
45-390
5-500
40.676
42.213
43-221
44-215
45-682
48.060
6.000
45-015
46.752
47.893
49-021
50.689
53-400
7.000
53.692
55.830
57.238
58.634
60.701
64.080
8.000
62.370
64.908
66.584
68.246
70.714
74-761
9.000
71.048
73.986
75.929
77.858
80.726
85.441
10.000
79.725
83.064
85.274
87.470
90.739
96.121
II.OOO
88.403
92.143
94.619
97.082
100.752
106.801
I2.0OO
97.080
IOI.22I
103.964
106.694
110.764
117.481
13.000
105.758
110.299
113.309
116.306
120.777
128.161
142.680
14.000
114.436
119-377
122.654
125.919
130.790
138.842
154.695
15.000
16.000
123.113
I3I.79I
128.455
137-533
132.000
141.345
135.531
145.143
140.802
150.815
149-522
160.202
166.710
178.725
17.000
140 . 469
I46.6II
150.690
154.755
160.828
170.882
190.740
18.000
149 . 146
155.690
160.035
164.367
170.840
181.562
202 . 756
19.000
157.824
164.768
169.380
173.979
180.853
192.242
214.771
20.000
166.502
173.846
178.725
183.591
190.866
202.923
226.786
21.000
175.179
182.924
22.000
183-857
I92.0O2
24.00O
201.212
210.158
26.OOO
218.567
228.315
28.000
3O.OOO
i
Length of Pipe for One Square Foot of Surface 57
Length of Pipe for One Square Foot of Surface
Size
g
«
•3
w
Standard weight
pipe
Extra strong pipe
Double extra strong
pipe
Thickness
Length of
pipe in ft.
per.sq. ft. oi
Thickness
Length of
pipe in ft.
per sq. ft. of
Thickness
Length of
pipe in ft. per
sq. ft. of
External
surface
Internal
surface
External
surface
J|
External
surface
f|
11
y
%
%
%
%
i
IV4
1%
2
2%
3%
4
44
5
6
8
8
9
10
10
10
II
12
12
13
14
15
.405
.540
.675
.840
1.050
1.315
1. 660
1.900
2.375
2.875
3-500
4.000
4.5oo
5.000
5.563
6.625
7.625
8.625
8.625
9.625
0.750
0.750
0.750
i.75o
2.750
2.750
4.000
5.000
6.000
.068
.088
.091
.109
.113
.133
.140
.145
.154
.203
.216
.226
.237
.247
.258
.280
.301
.277
.322
• 342
.279
.307
.365
• 375
• 330
.375
• 375
.375
.375
9-431
7-073
5.658
4-547
3.637
2.904
2.301
2.010
1. 608
1.328
I.09I
• 954
.848
.763
.686
.576
.500
• 442
• 442
.396
• 355
.355
.355
.325
.299
.299
.272
.254
.238
14.199
10.493
7-747
6.141
4.635
3.641
2.767
2.372
1.847
1.547
1.245
1.076
.948
.847
.756
.629
.543
• 473
.478
.427
.374
.376
.381
.347
.315
.318
.288
.268
.250
.095
.119
.126
.147
.154
.179
.191
.200
.218
.276
.300
.318
.337
.355
.375
.432
.500
.500
9-431
7-073
5.658
4-547
3.637
2.904
2.301
2.OIO
I. 608
1.328
I.09I
.954
.848
.763
.686
.576
.500
.442
17.766
12.648
9.030
6.995
5-147
3-991
2.988
2.546
1.969
1.644
I.3I7
1. 135
.998
.890
• 793
.663
.576
.500
^
.294
.308
.358
.382
.400
.436
•552
.600
.636
.674
.710
• 750
.864
.875
.875
4-547
3.637
2.904
2.301
2.OIO
1. 608
1.328
I.09I
.954
.848
.763
.686
.576
.500
• 442
15.157
8.801
6.376
4.263
3-472
2.541
2.156
i. 660
1.400
1. 211
1.066
.940
.780
.650
.555
.500
.500
.396
.355
.442
• 391
.500
.500
.325
.299
.355
.325
.500
.500
.500
.272
.254
.238
.293
.272
.254
58
Properties of Pipe
Strength factor Q ••
y
Properties of Pipe
foot pounds _ 7 27 OOP _i_ _ 9 7
1000 y i ooo 12 2 O. D.
= distance of farthest fiber from axis.
Exter-
nal
diam-
eter
Thick-
ness
Weight
per
foot
Mo-
ment of
inertia
Section
modu-
lus
Area of
metal,
square
inches
Radius
of gyra-
tion
squared
Radius
of gyra-
tion
Strength
factor
O.D.
7
i/y
A
R*=I/A
R
Q
.375
.065
.215
0007939
.004234
.06330
.01254
.1120
.009526
.405
.068
.244
001064
.005252
.07199
.01477
.1215
.01182
.405
.095
.314
001216
.006004
.09252
.01314
.1146
.01351
.500
.065
.301
002148
.008592
.08883
.02418
.1555
.01933
.540
.088
.424
003312
.01227
.1250
.02651
.1628
.02760
• 540
.119
• 535
.003766
.01395
.1574
.02393
• 1547
.03138
.625
.069
.409
004729
.01513
.1205
.03924
.1981
.03405
.675
.091
.567
.007291
.02160
.1670
.04367
.2090
.04860
.675
.126
.738
.008619
.02554
.2173
.03966
.1991
.05746
• 750
.078
• 559
.009421
.02512
.1647
.05721
.2392
.05652
.840
.078
.634
.01369
.03261
.1867
.07334
.2708
.07336
.840
.109
.850
.01709
.04069
.2503
.06828
.2613
.09156
.840
• 147
1.087
.02008
.04780
.3200
.06273
• 2505
.1076
.840
.294
I.7I4
.02424
.05772
• 5043
.04807
.2192
.1299
.875
.078
.663
.01566
.03578
.1953
.08016
.2831
.08051
1. 000
.078
.768
.02418
.04836
.2259
.1070
.3271
.1088
I 050
.078
.809
.02831
.05392
.2382
.1189
.3448
.1213
1.050
.113
1.130
.03704
.07055
.3326
.1113
• 3337
.1587
1.050
.154
1-473
.04479
.08531
.4335
.1033
.3214
.1919
1.050
.308
2.440
.05792
.1103
.7180
.08068
.2840
.2482
1.250
.089
1. 103
.05502
.08803
.3246
.1695
.4117
.1981
1.315
.089
1.165
•06474
.09847
.3428
.1889
.4346
.2216
1.315
• 133
1.678
•08734
.1328
• 4939
.1769
.4205
.2989
1.315
.179
2.171
.1056
.1606
.6388
.1653
.4066
.3614
1.315
.358
3.659
.1405
.2136
1.076
.1305
.3613
.4807
1.500
• 095
1.425
.1039
.1386
.4193
.2479
• 4979
.3118
1.500
.109
1.619
.1159
.1545
.4763
.2433
• 4933
-3477
1.500
.110
1.632
.1167
.1556
.4803
.2430
.4930
.3502
1.500
.120
1.768
.1248
.1664
.5202
.2398
.4897
• 3743
1.500
.125
1.835
.1287
.1716
.5400
.2383
.4881
.3860
1.500
.134
1-954
.1354
.1806
• 5750
.2355
.4^53
.4063
1.500
• 135
1.968
.1362
.1815
.5789
.2352
.4850
.4085
1.500
.148
2.137
.1454
.1938
.6286
.2312
.4809
.436i
1.500
.150
2.162
.1467
.1956
.6362
.2306
.4802
.4402
1.660
.095
1.587
• 1435
.1729
.4671
.3073
• 5543
.3891
1.660
.140
2.272
.1947
.2346
.6685
.2913
• 5397
.5278
1.660
.191
2.996
.2418
.2913
.8815
.2743
• 5237
.6555
1.660
.382
5-214
• 3411
.4110
1-534
.2224
.4716
.9247
1.750
.095
1.679
.1697
.1939
• 4939
.3435
.5861
.4363
1.750
.109
1.910
.1900
.2171
.5619
.3381
.5815
.4885
Properties of Pipe 59
Properties of Pipe (Continued)
, f „ footpounds /VX27
Strength factor Q = — = - X —
DOO _ i o 7
X — _ _
1000 y i ooo 12 2 O. D.
y = distance of farthest fiber from axis.
Exter-
nal
diam-
eter
Thick-
ness
Weight
foot
Mo-
ment of
inertia
Section
modu-
lus
Area of
metal,
square
inches
Radius
of gyra-
tion
squared
Radius
of gyra-
tion
Strength
factor
O.D.
7
l/y
A
R*=I/A
7*
Q
• 750
.no
1.926
.1914
.2187
.5667
.3377
.5811
.4922
• 750
.120
2.089
.2052
.2345
.6145
• 3339
-5779
.5276
• 750
.125
2.169
.2119
.2422
.6381
.3320
.5762
.5448
• 750
.134
2.312
.2236
.2555
.6803
.3287
• 5733
.5750
• 750
.135
2.328
.2249
.2570
.6849
.3283
• 5730
.5782
-750
.148
2.532
.2410
• 2754
• 7449
.3235
.5688
.6197
• 750
.150
2.563
• 2434
.2782
• 7540
.3228
.5682
.6259
.875
.095
i. 806
.2110
.2251
.5312
.3972
.6302
.5064
.875
.109
2.055
.2367
.2524
.6047
• 3913
.6256
.5680
.875
.110
2.073
.2384
.2543
.6099
• 3909
.6252
.5722
.875
.120
2.249
•2559
.2730
.6616
.3868
.6219
.6142
.875
• 125
2.336
.2644
.2820
.6872
.3848
.6203
.6346
-875
.134
2.491
• 2793
.2980
• 7329
.3811
.6174
.6704
.875
.135
2.508
.2810
.2997
.738o
.3807
6170
.6743
.875
.148
2.729
.3016
.3217
.8030
.3756
.6128
.7237
.875
.150
2.763
.3046
.3250
.8129
• 3748
.6122
.7311
.900
.109
2.084
.2468
.2598
• 6l33
.4024
.6344
.5846
.900
.145
2.717
• 3099
.3262
• 7995
.3876
.6226
.7340
.900
• 159
2.956
• 3322
• 3497
.8697
.3820
.6181
.7869
.900
.200
3-631
•3912
.4118
1.068
.3663
.6052
.9265
1.900
.400
6.408
.5678
.5977
1.885
.3013
.5489
1-345
2. OOO
• 095
1 932
.2586
.2586
.5685
.4548
.6744
.5817
2. OOO
.109
2.201
.2904
.2904
.6475
.4485
.6697
.6534
2. OOO
.no
2.22O
.2926
.2926
.6531
.4480
.6693
.6584
2. OOO
.120
2.409
.3144
.3144
.7087
.4436
.6660
•7074
2.000
•125
2.503
.3250
.3250
.7363
.4414
.6644
-7313
2.000
• 134
2.670
• 3437
.3437
.7855
.4375
.6614
.7732
2. OOO
.135
2.688
• 3457
• 3457
.7910
• 4371
.6611
• 7778
2.000
.148
2.927
• 3715
• 3715
.8611
.4315
.6569
.8360
2. OOO
.150
2.963
• 3754
.3754
.8718
.4306
.6562
.8447
2.250
.095
2.186
.3741
.3325
.6432
.5816
.7626
.7482
2.250
.100
2.296
.3911
• 3477
.6754
• 5791
.7610
.7822
2.250
.109
2.492
.4212
.3744
• 7332
.5745
.7579
.8423
2.250
.no
2.5U
.4245
• 3773
• 7395
• 5740
.7576
.8489
2.250
.120
2.729
.4568
.4061
.8030
.5689
.7543
.9137
2.250
.125
2.836
.4727
.4201
.8345
.5664
.7526
• 9453
2.250
.134
3.028
.5006
.4449
.8908
.5619
.7496
1. 001
2.250
.135
3-049
.5036
.4476
.8970
.5614
.7493
1.007
2.25O
.148
3-322
.5425
.4822
• 9773
.5550
• 7450
1.085
2.250
.150
3.364
.5483
.4874
.9896
.5541
.7444
1.097
60 Properties of Pipe
Properties of Pipe (Continued)
^trrntrth firtar O f°Ot Pounds I ~ 2? °°° - x 9 /
ocrcngtn idcior ^/ — — s\ /\ — ~ »
1000 y i ooo 12 2 O. D.
y = distance of farthest fiber from axis.
Exter-
nal
diam-
eter
Thick-
ness
Weight
foot
Mo-
ment of
inertia
Section
modu-
lus
Area of
metal,
square
inches
Radius
of gyra-
tion
squared
Radius
of gyra-
tion
Strength
factor
O.D.
/
l/y
A
R*=I/A
R
Q
2.375
.130
3-II7
.5796
.4881
.9169
.6321
• 7951
1.098
2.375
.134
3.207
• 5943
.5005
• 9434
.6300
• 7937
1.126
2.375
.154
3.652
.6657
,5606
.075
.6196
.7871
1.261
2-375
.166
3.916
.7066
.5951
.152
.6134
.7832
1-339
2-375
.167
3.938
.7100
• 5979
.158
.6129
.7829
1.345
2.375
.187
4.380
• 7748
.6525
.285
.6028
^.7764
1.468
2.375
.190
4-433
.7842
.6604
.304
.6013
• 7754
1.486
2.375
.218
5.022
.8679
.7309
.477
.5875
.7665
1.644
2.375
.436
9.029
I.3H
1.104
2.656
• 4937
.7027
2.485
2.500
.095
2.440
.5198
.4158
.7178
.7241
.8510
.9356
2.500
.108
2.759
.5816
.4653
.8116
.7167
.8466
1.047
2.500
.109
2.783
.5863
.4690
.8188
.7161
.8462
1.055
2.500
.110
2.807
.5910
.4728
.8259
• 7155
.8459
1.064
2.500
.120
3.050
.6369
.5095
.8972
.7098
.8425
1.146
2.500
.125
3.170
.6594
.5275
• 9327
.7070
.8409
1.187
2.500
.134
3.386
.6992
• 5594
.9960
.7020
.8378
1.259
2.500
.135
3.409
.7036
.5628
1.003
• 7014
.8375
1.266
2.500
.148
3.717
• 7592
.6074
1.094
.6942
.8332
1.367
2.500
.150
3.764
.7676
.6141
1.107
.6931
.8325
1.382
2.750
.109
3-074
.7898
• 5744
.9044
.8733
• 9345
1.292
2.750
.113
3.182
.8152
.5929
.936i
.8708
• 9332
1.334
2.875
.183
5.261
1.408
.9798
1.548
.9100
• 9540
2.205
2.875
.203
5-793
1-530
1.064
1.704
.8976
• 9474
2-394
2.875
.217
6.160
i.6n
1. 121
i. 812
.8890
.9429
2.521
2.875
.226
6.393
1.662
I.I56
1.881
.8835
.9400
2.601
2.875
.276
7.661
1.924
1-339
2.254
.8539
.9241
3.012
2.875
• 552
13.695
2.871
1.997
4.028
.7126
.8442
4-493
3.000
.095
2-947
.9156
.6104
.8670
1.056
1.028
1-373
3.ooo
.109
3.365
1.036
.6905
.9900
.046
.023
1.554
3.000
.no
3-395
1.044
.6961
.9987
.046
.023
1.566
3.ooo
.116
3-572
1.094
.7297
.051
.041
.020
1.642
3.000
.120
3.691
1.128
.7518
.086
.039
.019
1.691
3.000
.125
3.838
1.169
.7791
.129
.035
.017
1.753
3.000
.134
4.101
1.241
.8277
.207
.029
.014
1.862
3.000
.135
4.130
1.249
.8330
.215
.028
.014
1.874
3.000
.148
4.508
1.352
• 9013
.326
.019
.010
2.028
3.ooo
.150
4.565
1.367
.9116
.343
.018
.009
2.051
3.ooo
.165
4-995
1.481
.9876
.470
.008
.004
2.222
3.250
.120
4.011
1.447
.8906
.180
.226
.107
2.004
3.500
.120
4-331
1.822
1.041
.274
• 430
.196
2.343
Properties of Pipe 61
Properties of Pipe (Continued)
o ^ t „. ^ f°ot pounds / ^, 27 ooo ^ i o /
Strength factor Q = = - X -* X — = a •
1000 y i ooo 12 2 0. D.
y = distance of farthest fiber from axis.
Exter-
nal
diam-
eter
jThick-
ness
Weight
per
foot
Mo-
ment of
inertia
Section
modu-
lus
Area of
metal,
square
inches
Radius
of gyra-
tion
squared
Radius
of gyra-
tion
Strength
factor
O.D.
/
I/y
A
R*=I/A
R
Q
3.500
.125
4.505
1.890
1.080
1. 325
1.426
.194
2.430
3-Soo
.216
7-575
3.017
1.724
2 228
I -354
.164
3-879
3.500
.218
7.641
3.040
1-737
2 . 248
1.352
.163
3.908
3.500
.241
8.388
3.294
1.882
2.467
1-335
• 155
4.235
3.500
.255
8.837
3-443
1.967
2.60O
1.324
.151
4.427
3.500
.289
9-910
3-788
2.164
2.915
1.299
.140
4.870
3.500
.300
10.252
3.894
2.225
3.016
1.291
.136
5.007
3.500
.600
18.583
5-993
3.424
5.466
1.096
.04?
7.705
3-750
.120
4.652
2.257
1.203
1.368
1.649
.284
2.708
3-750
.129
4.988
2.408
1.284
1.467
1.641
.281
2.800
4.000
.128
5-293
2.921
1.461
1.557
1.876
• 370
3.286
4.000
.134
5-532
3.044
1.522
1.627
1.870
.368
3.425
4.000
.226
9-109
4-788
2.394
2.68o
1.787
• 337
5-386
4.000
.250
IO.OI2
5.200
2.6oo
2.945
1.766
.329
5.850
4.000
.318
12.505
6.280
3-140
3.678
1.707
.307
7.065
4.000
.636
22.850
9.848
4.924
6.721
1.465
.210
11.08
4.250
.138
6.060
3-772
1-775
1.783
2.116
• 455
3-994
4.500
• 134
6.248
4-384
1.948
1.838
2.385
• 544
4.384
4.500
.142
6.609
4.620
2.053
I 944
2-377
• 542
4.620
4.5oo
.205
9.403
6.393
2.841
2.766
2.311
• 520
6-393
4.500
.237
10.790
7-233
3.214
3-174
2.279
.510
7.233
4.500
.250
11-347
7.563
3.36l
3.33^
2.266
• 505
7.563
4.500
.252
".433
7-613
3.383
3.363
2.264
.505
7.613
4.5oo
• 255
11.561
7.688
3.417
3-401
2 . 26l
.504
7.688
4.500
.271
12.240
8.082
3-592
3.6oo
2.245
-498
8.082
4.500
337
14-983
9.610
4.271
4.407
2.181
• 477
9.610
4.500
.674
27.541
15.28
6.793
8.101
1.887
• 374
15.28
4-750
• 145
7.I3I
5.566
2.344
2.098
2.653
.629
5-273
4-750
• 193
9-393
7.185
3.025
2.763
2.600
.613
6.807
4-750
• 334
15.752
11.36
4.783
4.634
2.452
.566
10.76
5.000
• 134
6.963
6.068
2.427
2.048
2.962
.721
5.46r
5.000
.148
7.669
6.645
2.658
2.256
2.945
.716
5.98o
5.000
.152
7.870
6.808
2.723
2.315
2.941
.715
6.127
5.000
.247
12.538
10.44
4-177
3-688
2.832
.683
9-399
5.000
.250
12.682
10.55
4.220
3-731
2.828
.682
9.496
5.000
.288
14-493
11.88
4-751
4.263
2.786
.669
10.69
S.ooo
.306
15.340
12.48
4-992
4-512
2.766
.663
11.23
S.ooo
• 355
17.611
14.05
5.621
5.180
2.712
.647
12.65
S.ooo
.710
32.530
22.62
9.047
9.569
2.364
.537
20.35
5.250
.153
8.328
7-963
3-034
2.450
3.250
.803
6.826
62 .Properties of Pipe
Properties of Pipe (Continued)
, , ~ foot pounds
Strength factor Q = =
/ 27000 I
_9 /
= X "X
1000 y i ooo 12 2 U. D.
y = distance of farthest fiber from axis.
Exter-
nal
diam-
eter
Thick-
ness
Weight
per
foot
Mo-
ment of
inertia
Section
modu-
lus
Area of
metal,
square
inches
•fe- K'-
squared tlon
Strength
factor
O.D.
7
i/y
A
R*=I/A\ R Q
5.250
.182
9-851
9.315
3.549
2.898
3.215
1.793
7.985
5.250
.241
12.892
11.92
4 542
3-792
3-144
1.773
10.22
5.250
.301
15.909
14-38
5-478
4.680
3-073
1-753 i 12.33
5-500
.154
8.792
9.248
3.363
2 586
3-575
1.891 1 7.566
5.500
.228
12.837
13.14
4.78o
3.776
3 481
1.866 j 10.75
5.500
.304
16.870
16.80
6. in
4.962
3-386
1.840
13-75
5.563
.258
14.617
15.16
5-451
4.300
3.526
1.878
12,26
5.563
.293
16.491
16.89
6.073
4-851
3.482
1.866
13-66
5.563
.304
17.074
17.42
6.263
5.023
3-469
1.862
14.09
5.563
.375
20.778
20.67
7-431
6. 112
3.382
1.839
16.72
5.563
• 750
38.552
33.63
12.09
II.34
2.966
1.722
27.21
6. ooo
.140
8.762
11.07
3.690
2.577
4-295
2.072
8.302
6.000
.164
IO.222
12. 8l
4.270
3.007
4.261
2.064
9-6o8
6. ooo
.165
10.282
12.88
4-294
3.025
4 259
2.064
9.662
6.000
.190
11.789
14.65
4-883
3.468
4.224
2.055
10.99
6. ooo
.224
I3.8l8
16.98
5.659
4-065
4-177
2.044
12.73
6. ooo
.275
I6.8I4
20.31
6.770
4.946
4.106
2.026
15.23
6. ooo
.280
17.105
20.63
6.876
5.032
4.100
2.025
15-47
6. ooo
.324
19.641
23-34
7.78i
5-777
4.040
2.010
17.51
6.625
.169
11.652
17.87
5-395
3.428
5-214
2.283
12.14
6.625
.184
12.657
19.32
5-834
3.723
5.100
2.278
13.13
6.625
.185
12.724
19.42
5-863
3-743
5-188
2.278
13.19
6.625
.245
16.694
25.02
7-554
4-9II
5-096
2.257
17.00
6.625
.280
18.974
28.14
8.496
5.581
5-042
2.245
19.12
6.625
.281
19.039
28.23
8.522
5.6oo
5.041
2.245
19.17
6.625
.288
19-491
28.84
8.707
5-734
5.030
2.243
19-59
6.625
.300
20.265
29.88
9.020
5.96i
5.012
2.239
20.29
6.625
• 344
23.076
33-57
10.14
6.788
4-946
2.224
22.80
6.625
.385
25.658
36.87
II. 13
7 547
4.886
2.210
25.05
6.625
.417
27.648
39.36
11.88
8.133
4.839
2.200
26.73
6.625
.432
28.573
40.49
12.22
8.405
4-817
2.195
27.50
6.625
.864
53.l6o
66.33
20.02
15-64
4.242
2.060
45.o6
7.000
.149
10.902
18.82
5.378
3-207
5-870
2.423
12.10
7.000
.165
12.044
20.70
5.915
3-543
5.843
2.417
13 31
7.000
.174
12.685
21.75
6.213
3-731
5-828
2.414
13.98
7.000
.231
16.699
28.17
8.048
4.912
5-734
2.395
i8.il
7.000
.272
19-544
32.58
9-310
5-749
5-667
2.381
20.95
7.000
.275
19.751
32.90
9-400
5-810
5-662
2.380
21.15
7.000
.301
21.535
35.6i
IO.I7
6.335
5.621
2.371
22.89
7.000
.333
23.7H
38.85
II. 10
6.975
5-570
2.360
24-97
Properties of Pipe 63
Properties of Pipe (Continued)
, .. ~ foot pounds / v 27 ooo i
Strength factor Q = = - X -* X —
9 /
1000 y i ooo 12 2 O. D.
y = distance of farthest fiber from axis.
' Exter-
nal
diam-
eter
Thick-
ness
Weight
per
foot
Mo-
ment of
inertia
Section
modu-
lus
Area of
metal,
square
inches
Radius
of gyra-
tion
squared
Radius
of gyra-
tion
Strength
factor
O. D.
/
i/y
A
R*=I/A
R
Q
7.000
.362
25.663
41.70
11.92
7-549
5.524
2.350
26.81
7.000
.393
27.731
44.67
12.76
8.157
5.476
2-340
28.72
7.625
.181
14.390
29-34
7.695
4.233
6.931
2.633
17.31
7.625
.301
23.544
46.52
12. 2O
6.926
6.716
2-592
27.45
7.625
.500
38.048
71-37
18.72
11.19
6.377
2.525
42.12
7.625
,875
63.079 107.5
28.18
18.56
5-791
2.406
63.41
8.000
.I5&
13.233
29-93
7.484
3.893
7.690
2-773
16.84
8.000
.165
13.807
31.18
7-795
4.061
7.677
2.771
17.54
8.000
.185
15.441
34.69
8-674
4-542
7.639
2.764
19.52
8.000
.186
15.522
34.87
8-717
4.566
7.637
2.763
19.61
8.000
.236
19.569
43-41
10.85
5.756
7-542
2.746
24.42
8.000
-307
25.223
54.98
13-74
7-420
7-410
2.722
30.92
8.000
.322
26.404
57.34
14.33
7.767
7.382
2.717
32.25
8.625
.188
16.940
44.36
10.29
4.983
8.902
2.984
23.14
8.625
.217
19.486
50.69
11-75
5-732
8.843
2.974
26.44
8.625
.264
23.574
60.66
14.07
6.934
8.747
2.958
31.65
8.625
.277
24.696
63.35
14.69
7.265
8.721
2-953
33.05
8.625
.304
27.016
68.87
15.97
7-947
8.666
2.944
35-93
8.625
.311
27.615
70.28
16.30
8.123
8.652
2.941
36.67
8.625
.322
28.554
72.49
16.81
8.399
8.630
2.938
37-82
8.625
-352
31 • ioi
78.41
18.18
9.149
8.571
2.928
40.91
8.625
.354
31.270
78.80
18.27
9.198
8.567
2.927
4I.II
8.625
.400
35-137
87.61
20.32
10.34
8.476
2.911
45-71
8.625
• 425
37.220
92.27
21.40
10.95
8.428
2.903
48.14
8.625
.487
42.327
103.4
23-99
12.45
8.308
2.882
53-97
8.625
.500
43-388
105.7
24 51
12.76
8.283
2.878
55.16
8.625
.875
72.424
162.0
37.56
21.30
7-604
2-757
84.51
9.000
.167
15-754
45.21
10.05
4-634
9-756
3.123
22.61
9.000
.180
16.955
48.52
10.78
4.988
9.728
3.H9
24.26
9.000
.196
18.429
52.55
11.68
5-421
9.694
3.H3
26.27
9.000
.250
23.362
65.82
14.63
6.872
9.578
3-095
32.91
9.000
• 342
31.624
87.30
19.40
9.302
9.385
3-063
43.65
9.625
• 342
33.907
107.6
22.35
9-974
10.79
3.284
50.30
9.625
.500
48.728
149-6
31.09
14-33
10.44
3.231
69.96
10. OOO
• 175
18.363
65.20
13-04
5.402
12.07
3-474
29-34
IO.OOO
.203
21 . 24O
74-99
15.00
6.248
12.00
3.465
33.75
IO.OOO
.208
21.752
76.72
15-34
6.399
11.99
3.463
34-53
IO.OOO
.209
21.855
77.07
15.41
6.429
H.99
3.462
34.68
IO.OOO
.270
28.057
97-75
19.55
8.253
11.84
3-441
43-99
10 000
.283
29.369
102.0
20.41
8.639
11.81
3-437
45-92
64
Properties of Pipe
Strength factor Q
Properties of Pipe (Continued)
foot pounds / vx 27 ooo
2-JL.
2O. D.
y sa distance of farthest fiber from axis.
Exter-
nal
diam-
eter
Thick-
ness
Weight
per
foot
Mo-
ment of
inertia
Section
modu-
lus
Area of
metal,
square
inches
Radius
of gyra-
tion
squared
Radius
of gyra-
tion
Strength
factor
O.D.
/
i/y
A
R*=I/A
R
Q
10.000
.308
31.881
IIO. 2
22.05
9.378
11-75
3.428
49.60
IO.OOO
.365
37-559
128.4
25.68
11.05
11.62
3.409
57.78
10.750
.279
31 . 201
125-9
23.42
9.178
13.71
3-703
52.69
10.750
.302
33.699
135-4
25.19
9.913
13-66
3.695
56.67
10.750
.307
34.240
137-4
25-57
10.07
13-64
3.694
57.52
10.750
.348
38.661
154-0
28.65
H.37
13-54
3.68o
64.46
10.750
.365
40.483
160.7
29.90
11.91
13.50
3.674
67.28
10.750
.395
43-684
172.5
32.09
12.. 85
13.42
3.664
72.20
10.750
.424
46.760
183.6
34.16
13-75
13-35
3.654
76.87
10.750
.483
52.962
205-7
38.28
15.58
13.21
3.634
86.12
10.750
.500
54-735
212.0
39-43
16.10
13.16
3.628
88.72
11.000
,185
21.368
91-93
16.71
6.286
14.62
3.824
37.6i
11.000
.220
25.329
108.3
19.69
7.451
14-53
3.812
44.29
11.000
.224
25.780
IIO. I
2O.02
7.583
14.52
3.811
45-05
11.000
.290
33.I7I
I40.O
25.46
9.757
14-35
3-788
57-27
11.750
• 375
45-557
217.0
36.93
13.40
16.19
4.024
83.10
11.750
.500
60.075
280.1
47.68
17.67
15.85
3.981
107-3
12.000
.194
24.461
125.4
20.90
7-195
17-43
4-175
47.02
12.000
.229
28.788
146.7
24-45
8.468
17.33
4.162
55-02
12.000
.243
30.512
I55-I
25.86
8.975
17.29
4.158
58.18
12.000
.244
30.635
155-7
25.96
9.012
17.28
4-157
58.40
12.000
.308
38.460
193-5
32.24
11.31
17.10
4-135
72.55
12.000
.310
38.703
194-6
32.44
11.38
17.09
4-134
72.98
12.000
.375
46.558
231.6
38.60
13.70
16.91
4.112
86.85
12.750
.330
43-773
248.5
38.97
12.88
19.30
4-393
87.69
12.750
.375
49.562
279-3
43-82
14.58
19.16
4-377
98.59
12.750
.500
65.415
361.5
56.71
19.24
18.79
4-335
127.6
13-000
.202
27.610
166.3
25.59
8.122
20.48
4-525
57-57
13.000
.238
32.439
194-3
29.90
9.542
20.37
4.513
67.27
13.000
.247
33.642
2OI.3
30.96
9.896
20.34
4.510
69.67
13.000
.259
35.243
210.5
32.38
10.37
20.30
4.506
72.85
13-000
.281
38.171
227.2
34-95
11.23
20.23
4.498
78.63
13.000
.310
42.014
248.9
38.30
12.36
20.14
4.488
86.17
13.000
.320
43-335
256.4
39-44
12.75
20. ii
4.484
88.74
13.000
.359
48.467
285.0
43.85
14.26
19.99
4-471
98.65
13.000
.361
48.730
286.5
44.07
14-33
19.98
4-470
99-16 |
I4.OOO
.210
30.928
216.3
30.90
9-098
23.78
4.876
69.53
14.000
.248
36.424
253.4
36.20
10.71
23.65
4-863
81.46
I4.0OO
.250
36.713
255.3
36.47
10.80
23.64
4.862
82.06
14.000
.276
40.454
280.3
40.04
11.90
23-55
4.853
90.09
Properties of Pipe 65
Properties of Pipe (Concluded)
P.L ^.i- t ^ r\ f°°t pounds
Strength factor Q = =
7_27ooo_ i 9 /
lf
= A A —
1000 y i ooo 12 2 U. JL>.
y = distance of farthest fiber from axis.
Exter-
nal
diam-
eter
Thick-
ness
Weight
foot
Mo-
ment of
inertia
Section
modu-
lus
Area of
metal,
square
inches
Radius
of gyra-
tion
squared
Radius
of gyra-
tion
Strength
factor
O.D.
. /
l/y
A
R*=I/A
R
Q
14.000
.310
45.325
312.5
44.64
13-33
23.44
4.841
100.4
14.000
.328
47.894
329-4
47.05
14.09
23.38
4.835
105.9
14.000
• 375
54.568
372.8
53.25
16.05
23.22
4.819
119.8
14.000
.438
63.441
429.5
61.36
18.66
23.01
4.797
138.1
14.000
.500
72.091
483.8
69.11
21.21
22.81
4.776
155.5
15.000
.222
35.038
281.4
37.52
10.31
27.30
5.225
84.43
15.000
.259
40.775
325.9
43.45
11.99
27.17
5.213
97-77
15.000
.260
40.930
327.1
43.6i
12.04
27.17
5.212
98.13
15.000
.291
45.714
363.8
48.51
13.45
27.05
5.201
109.1
15.000
.320
50.171
397-7
53-03
14.76
26.95
5.I9I
II9-3
15.000
• 375
58.573
461.0
61.46
17.23
26.75
5.172
138.3
15.000
.438
68.119
531.6
70.88
20.04
26.53
5.I5I
159.5
15.000
.500
77-431
599-3
79-91
22.78
26.31
5.130
179.8
16.000
• 234
39-401
360.2
45-02
11.59
31.08
5-575
101.3
16.000
.270
45-359
412.8
51.60
13-34
30.94
5.562
116.1
16.000
.302
50.632
458.9
57.37
14.89
30.81
5.551
129.1
16.000
.330
55.228
498.9
62.36
16.25
30.71
5-541
140.3
16.000
• 375
62.579
562.1
70.26
18.41
30.54
5.526
158.1
16.000
.401
66.806
598.1
74.76
19.65
30.44
5.517
168.2
16.000
.500
82.771
731-9
91.49
24-35
30.06
5.483
205.9
17.000
.240
42.959
443-8
52.21
12.64
35.12
5.926
«7.5
17.000
• 393
69.704
707.2
83.21
20.50
34-49
5.873
187.2
18.000
.245
46.458
538.6
59.85
13.67
39-41
6.278
134-7
18.000
.310
58.568
674.1
74-90
17.23
39-13
6.255
168.5
18.000
.409
76.840
874-8
97-20
22.60
38.70
6.221
218.7
18.000
.500
93-451
1053-
117.0
27-49
38.31
6.190
263.3
19.000
.259
51-840
669.6
70.49
15.25
43-91
6.627
158.6
20.000
.272
57.309
820.3
82.03
16.86
48.66
6.976
184.6
20.000
• 375
78.599
III3.
Hi. 3
23.12
48.16
6.940
250.5
20.000
.409
85-577
1208.
120.8
25.17
48.00
6.928
271.8
22.000
.301
69.756
1208.
109.8
20.52
58.87
7.672
247-1
22.0OO
.400
92.276
1584.
144.0
27.14
58.34
7.638
323.9
24.OOO
.330
83.423
1719.
143.2
24-54
70.05
8.369
322.3
26.000
.362
99-122
2396.
184 3
29.16
82.18
9.065
414.7
28.000
.396
116.746
3272.
233 7
34-34
95-27
9.760
525.8
30.000
• 432
136.421
4386.
292.4
40.13
109.3
10.45
658.0
66 Bending Properties of Square Pipe
Bending Properties of Square Pipe
Solid
Solid
h
^>
aJ
w
square bar
round bar
•^ j3
8
.2
IB
•a
(steel) of
(steel) of
11
"8
same
same
(U <U
a
1
i
IZj
o
I
strength
strength
Size
I
1
8
1
1
o
11
0)
11
O w
I
*
o
CO
CO
Jti
CO
'Hit
a
K g,
CO
7/8
.134
i.46
.429
.037
.085
13/16
2.25
15/16
2.35
I3/4
I
.100
1.25
.367
.049
.098
13/16
2.25
I
2.67
l8/4
I
.125
1.55
.455
.056
.113
7/8
2.60
ll/lQ
3.01
1%
I
.188
2. II
.620
.070
.141
15/l6
2.99
T-l/S
3.38
2
iy4
.125
1.97
.579
.120
.192
iMe
3.84
i*4
4-17
2H
.134
2.05
.603
.125
.2OI
ii/iQ
3.84
1^4
4.17
2V4
iH
.156
2.29
.673
.138
.222
iys
4.30
I5/16
4.60
2%
\\JA
.188
2.48
.729
•154
• 247
iMj
4.30
1%
5-05
1\A
.250
3.28
.964
.177
.283
I3/16
4.80
I7/16
5-52
2%
l\fa
.125
2.33
.685
.218
.291
I3/16
4.80
I7/16
5-52
2%
1^2
.140
2.55
• 750
.237
.316
5.31
6.01
2%
iy2
.156
2.78
.817
.255
.341
iy4
5.31
m
6.01
2%
iy2
.188
3-05
.897
.288
.385
i5/i6
5.86
I9/16
6.52
27/8
iy2
.250
4.00
1.176
.338
• 451
!%
6.43
7.60
3
.140
2.76
.811
.348
.412
1%
6.43
J%
7-05
27/8
iHle
.156
3-00
.882
.377
• 447
1%
6.43
1%
7.05
3
1%
.188
3-75
1.103
.428
.508
fffa
7-03
"?
8.18
3y8
i^Vie
.250
4.60
1.353
.509
.604
I®AQ
8.30
;8.77
3^4
2
.125
3.10
.911
.551
.551
iy>
7.65
1% 8
8.18
3-V4
2
.134
.935
.583
.583
i%
7.65
8.77
3^4
2
.145
3-52
1.035
.620
.620
I9/16
8.30
l7/g
9-39
3%
2
.188
4.39
1.291
.753
• 753
1%
8.98
2
10.68
3%
2
.250
5-40
1.588
.911
Is/4.
10.41
2Vs
12.06
33/4
2y2
.188
1.647
1.559
1 .247
I15/46
12.76
2^/16
14.28
3
.200
7.06
2.076
2.941
1.961
&
17.22
2%
20.20
47/8
For sections see pages 85 and 86.
All dimensions given in inches.
All weights given in pounds.
In calculating the moments of inertia and section moduli the fillets were dis-
regarded.
The solid bars of same strength are given to the nearest merchant bar size.
The ratio of the flexural strength of steel to that of timber is assumed as ten
to one.
Bending Properties of Rectangular Pipe
67
Bending Properties of Rectangular Pipe
Solid
-Solid
u
1
a
.2
08
1
1
square bar
(steel) of
round bar
(steel) of
In
1
Ti
o
a
1
same
same
'** S
Size
§
s
i
"o
strength
strength
|«
3
J3
°
a
§
Is
H
I
! S
h
1
1
|
be O
1
|l
*O 0°
go
^g,
^^
CO
&
.140
1.67
•491
.108
.172
i
3-40
18/16
3-77
21/8
iHXi
.188
2.05
.603
.128
.204
iyie
3.84
34
4-17
a%
iy2xi}4
.122
2.05
.603
.185
.247
iys
4-30
18/8
5-05
2y2
iy2xiy*
.145
2.24
.658
.209
.279
i8A«
4.80
I%6
5.52
2y2
1^2X1*4
.156
2.40
.706
.220
.294
18/16
4-80
I7/16
5-52
2%
1^X1%
.188
2.85
.838
.248
• 330
M4
5.31
iy2
6.01
28/4
iy2xiH
.250
3-67
1.079
.289
.385
I5/16
5.86
I9/16
6.52
2%
2 xiy4
.134
2.53
.744
.408
.408
1%
6.43
1%
7-05
2%
2 xiy2
.145
3.00
.882
• 495
• 495
17/16
7-03
iiy16
7.60
3y8
2 xiy2
.188
3-6i
1.061
• 598
.598
i9/ie
8.30
i18Ae
8.77
38/8
2 xiy2
.250
4-65
1.367
.718
.718
i%
8.98
i15/4e
10.02
3y2
2y2xiy2
.145
3-52
1.035
.864
.691
i%
8.98
H%6
10.02
3y2
2y2xiy2
.188
4-39
1.291
1.055
.844
Utte
9.68
2
10.68
3%
2y2xiy2
.250
5-40
1.588
1.286
1.029
I18/16
11.17
21/4
13.52
4
3 X2
.188
5.6o
1.647
2.054
1.369
2
13.60
2^6
15.86
48/8
3 X2
.200
6.00
1.764
2.156
1.437
2M"
14.46
27/16
15.86
48/8
For sections see pages 87 and 88.
All dimensions given in inches.
All weights given in pounds.
The sections are supposed to have their greatest dimensions in the plane of the
loading.
In calculating the moments of inertia and section moduli the fillets were dis-
regarded.
The solid bars of same strength are given to the nearest merchant bar size.
The ratio of the flexurai strength of steel to that of timber is assumed as ten
to one.
68 Hydrostatic Test Pressures
Hydrostatic Test Pressures
Standard Pipe — Black and Galvanized
Size
Weight
per foot
com-
plete
Test pressure in
pounds
Size
Weight
per foot
com-
plete
Test pressure in
pounds
Butt
Lap
Butt
Lap
I
i
8/4
I
iVi
i%
2
2%
3»
4%
5
.245
.425
-568
.852
1. 134
1.684
2.281
2.731
3.678
5.8i9
7.616
9.202
10.889
12.642
14 810
700
700
700
700
700
700
700
700
700
800
800
IOOO
1000
IOOO
IOOO
IOOO
IOOO
IOOO
IOOO
IOOO
6
8
8
9
10
10
10
ii
12
12
13
14
IS
19-185
23.769
25.000
28.809
34-188
32.000
35-000
41.132
46.247
45-000
50.706
55.824
60.375
64.500
IOOO
IOOO
800
IOOO
900
600
800
900
800
600
800
700
700
600
Line Pipe
Size
Weight
per foot
com-
plete
Test pressure in
pounds
Size
Weight
per foot
com-
plete
Test pressure in
pounds
... Butt
Lap
Butt
Lap
Vs
V4
%
%
8/4
I
1^4
iy2
2
2V2
|i
&
5
.246
.426
• 571
.856
1.138
1.688
2.300
2.748
3.7i6
5.881
7.675
9.261
10.980
12.742
14.966
700
700
700
700
700
700
1200
I20O
1200
1200
1200
1700
1800
1800
1800
1700
1600
1600
1500
6
7
8
8
9
10
10
10
II
12
12
13
14
15
19-367
23-975
25.414
29.213
34.6i2
32.515
35.504
41.644
46.805
45-217
50.916
56.649
60.802
64.955
1500
1200
IOOO
1200
I2OO
800
900
IOOO
900
800
900
750
750
750
Hydrostatic Test Pressures 69
Hydrostatic Test Pressures (Continued)
Drive Pipe Extra-Strong Pipe — Black and Galvanized
Size
Weight
per foot
complete
Test
pressure
in
pounds
Size
Weight per
foot
plain ends
Test pressure in
pounds
Butt
Lap
2
2^2
3
3*6
41/2
5
6
7
8
8
8
9
10
10
IO
II
12
12
13
14
I7O.D.
iSO.D.
2oO.D.
3-730
5.906
7-705
9.294
10.995
12.758
14.989
19.408
24.021
25-495
29.303
32.334
34-711
32.631
35.628
41.785
46.953
45-358
51-067
56.849
61.005
65.161
73-000
81.000
90.000
750
750
750
75b
750
750
750
750
750
650
750
750
750
650
750
750
750
600
750
750
750
500
500
500
500
n
i
8/4
I
IV4
iy2
2
2y2
3y2
4
&
6
7
8
9
10
II
12
13
14
15
• 314
• 535
.738
1.087
1.473
2.171
2.996
3.631
5.022
7.661
10.252
12.505
14.983
17.611
20.778
28.573
38.048
43.388
48.728
54-735
60.075
65.415
72.091
77-431
82.771
700
700
700
700
700
700
1500
1500
1500
1500
1500
2500
2500
200O
200O
2OOO
2000
I800
I800
I800
1500
1500
1500
I2OO
1 100
IIOO
IOOO
IOOO
IOOO
Oil-Well Tubing
In addition to the above test, on sizes Vs"
to i" inclusive, the pipe is jarred with a
hammer while under pressure.
Double Extra-Strong Pipe —
Black and Galvanized
Size
Weight
per foot
complete
Test
pressure
in
pounds
Size
Weight per
foot
plain ends
Test pressure in
pounds
Butt
Lap
M
iVa
2
2
21/2
m
3
3
3
3$
4
4
2.300
2.748
4.000
4 5oo
5.897
6.250
7.694
8.500
IO.OOO
9.261
10.980
11.750
1800
1800
2200
2500
2000
22OO
I800
2OOO
2200
1500
1500
I800
y2
%
i
i}4
iy2
2
2y2
3y2
4
4y2
6
8
1.714
2.440
3-659
5.214
6.408
9.029
13.695
18.583
22.850
27.541
32.530
38.552
53.i6o
63.079
72.424
700
700
700
2200
2200
220O
2200
3000
3000
3000
3000
2500
2500
2000
2000
2000
2OOO
2000
70 Hydrostatic Test Pressures
Hydrostatic Test Pressures (Continued)
Standard Boston Casing
Size .
Weight
per foot
complete
Test pres-
sure in
pounds
Size
Weight
per foot
complete
Test pres-
sure in
pounds
2
2V4
2%
28/4
2 34
2 82
3 25
3.65
750
750
750
750
5%
5%
5%
12. OO
14.00
17 oo
12.00
800
900
IOOO
750
3V4
3%
38/i
4.10
4.60
5 10
750
750
75o
750
61/4
65/8
6%
7V4
13.00
13.00
17.00
14.75
800
750
900
75o
4V4
4%
6. 20
6.75
9-50
7-25
750
750
900
750
7%
7%
8V4
16.00
20.00
17-50
20.00
750
800
750
800
4%
48/4
5
5
9-50
8.00
8.50
IO.OO
900
750
750
800
8%
9%
105/8
24.00
19.00
22.75
26.75
800
750
750
750
5
5g
55/86
13.00
16.00
9.00
10.50
IOOO
1200
750
750
H%
12%
13%
14%
15%
31.50
36.50
42.00
47.50
52.50
500
500
500
500
500
Boston Casing — Pacific Couplings
Size
Weight
per foot
complete
Test pres-
sure in
pounds
Size
Weight
per foot
complete
Test pres-
sure in
pounds
38/4
4
4V4
5.678
6.223
6.779
9-547
750
750
750
900
55/8
6V4
6V4
17.033
11.986
13.046
13.028
IOOO
750
800
800
4%
4%
48/4
5
7.309
9 550
8.093
8.562
75o
900
75o
750
65/8
6%
7%
7%
13.122
17.076
16.038
20.037
750
900
75o
800
5
5
5
5
10.071
10.057
13-085
13-072
800
800
IOOO
IOOO
85/8
9%
9%
105/8
19-123
22 . 802
30 . 250
26.978
750
750
900
750
5
5%
5%
55/8
16.062
10.528
12.063
14.069
I2OO
750
800
900
12%
13%
14%
31.872
36.685
41-975
48.018
53-068
5oo
500
500
5oo
500
Hydrostatic Test Pressures 71
Hydrostatic Test Pressures (Continued)
California Diamond BX Casing
Size
Weight
per foot
complete
Test pressure
in pounds
Size
Weight
per foot
complete
Test pressure
in pounds
5%
20.00
1500
8*4
38.00
1300
6V4
20.00
1400
8V4
43-00
1500
6U
24.00
1500
9%
33-00
IOOO
6V4
26.00
1600
10
40.00
800
61/4
28.00
1700
10
45.oo
900
6%
20.00
1 200
10
48.00
IOOO
6%
26.00
1400
10
54 oo
1200
6%
28.00
1500
11%.
40.00
800
6%
30.00
1600
12%
40.00
700
7%
26.00
I2OO
12%
45-00
800
8%
28.00
IOOO
12%
50.00
900
8-Vi
32.00
IIOO
I3V2
50.00
800
8V4
36.00
1200
15%
70.00
800
South Penn Casing
Size
Weight
per foot
complete
Test pressure
in pounds
Size
Weight
per foot
complete
Test pressure
in pounds
58/io
13.000
IOOO
6%
24.000
I2OO
58/16
17.000
1 200
8^4
24.000
IOOO
6V4
13.000
800
8V4
28.000
I2OO
m
17.000
IOOO
IO
32.515
800
6%
17.000
900
10
35-000
000
6%
20.000
IOOO
12%
50.000
800
Inserted Joint Casing
Size
Weight
per foot
plain ends
Test pressure
in pounds
Size
Weight
per foot
plain ends
Test pressure
in pounds
2
2.296
75o
5%
11.789
800
2*4
2.759
750
6^4
11.652
750
2%
3.182
750
6%
12.685
750
2%
3-572
750
7U
14.390
750
1%
4. on
4.505
75o
750
1
15.522
16.940
75o
750
3%
4.988
750
18.429
750
38/4
5-532
750
9%
21.855
750
4
6.060
750
-10%
25.780
750
4V4
6.609
750
11%
30.512
500
4%
7.131
750
12%
35-243
500
4»/4
7.870
750
13%
40.454
500
5
8.328
750
14%
45-714
500
58Ae
8.792
750
15%
50.632
500
5%
10.222
750
72 Hydrostatic Test Pressures
Hydrostatic Test Pressures (Continued)
Standard Boiler Tubes and Flues — Lap Welded
External
diameter
Weight
per foot
Test pressure
in pounds
External
diameter
Weight
per foot
Test pressure
in pounds
i%
|
1.679
1.932
2.186
2.783
750
75o
750
75o
6
8
9
10.282
12.044
13.807
16.955
500
500
500
500
2%
3
3V4
3V2
3 074
3.365
4. on
4.331
750
750
750
75o
10
ii
12
13
21 . 240
25.329
28.788
32.439
500
500
500
500
33/4
4
4Va
5
4.652
5-532
6.248
7.669
750
750
500
500
14
15
16
36.424
40.775
45-359
500
500
500
Locomotive Boiler Tubes. Lap Welded — Open-hearth Steel
External
diameter
Thickness
Test pressure
in pounds
External
diameter
Thickness
Test pressure
in pounds
1%
l8/4
1%
1%
.095
.109
.110
.120
900
900
900
IOOO
2V4
2V4
2V4
m
.134
.135
.148
.150
IOOO
IOOO
IOOO
IOOO
1%
1%
1%
1%
.125
.134
.135
.148
IOOO
IOOO
IOOO
IOOO
2V2
2V2
2V2
2V2
.095
.109
.110
.120
800
800
800
800
I8/4
2
2
2
.150
.095
.109
.no
IOOO
900
900
900
2V2
2V2
*%
2V2
.125
.134
.135
.148
800
900
900
IOOO
2
2
2
2
.120
.125
.134
.135
IOOO
IOOO
IOOO
IOOO
2V2
3
3
3
.150
.095
.109
.110
IOOO
750
750
750
2
2
2^4
3%
.148
.150
.095
.109
IOOO
IOOO •*
900
900
3
3
3
3
.120
.125
.134
.135
750
750
900
900
2V4
2%
2V4
.110
.120
.125
900
IOOO
IOOO
3
3
.148
.150
IOOO
IOOO
.
Hydrostatic Test Pressures
73
Hydrostatic Test Pressures (Continued)
Matheson Joint Pipe
External
diameter
Weight
per foot
complete
Test pressure
in pounds
External
diameter
Weight
per foot
complete
Test pressure
in pounds
9
9
9
10
12
12
13
13
1-952
3-392
5 339
7.019
8.872
11.028
13.405
15.614
15-945
18.621
23-557
18.610
22.001
28.309
21.638
25.600
33.445
24.880
31.057
39.129
28.060
34.095
700
700
600
600
600
600
600
700
500
600
700
500
600
700
500
600
700
500
600
700
600
13
14
14
14
15
15
15
16
16
16
17
18
18
19
20
20
22
24
26
28
30
42.472
31.536
37 324
45 941
35 686
41.581
50.826
40.089
46.050
55.923
43.687
47.384
59-501
52.815
58.332
79.631
71.098
93.629
84.882
100.697
119.021
138.851
650
500
550
600
500
55o
600
500
550
600
450
450
500
450
450
500
450
500
450
450
450
450
Reamed and Drifted Pipe
Size
Weight
per foot
complete
Test pressure in
pounds
Butt
Lap
Size
Weight
per foot
complete
Test pressure in
pounds
Butt Lap
2
2
2%
3\2
3.697
4.OOO
5.843
7-675
9.26l
1000
1000
1500
1800
1500
1500
IOOO
10.980
12.742
14.966
19.367
IOOO
IOOO
IOOO
IOOO
Air Line Pipe
Size
Weight
per foot
complete
Test pressure
in pounds
Size
Weight
per foot
complete
Test pressure
in pounds
iV2
3.000
2OOO
4
11.750
1800
2
2V2
4.000
6.500
2000
2OOO
I
17.000
21.000
1700
1600
3
9.000
2000
74 Hydrostatic Test Pressures
Hydrostatic Test Pressures (Continued)
Converse Lock Joint Pipe
External
diameter
Weight
per foot
complete
Test pressure
in pounds
External
diameter
Weight
per foot
complete
Test pressure
in pounds
2
2.207
700
13
45.387
650
3
3-931
700
14
35.013
Soo
4
5-991
600
14
40.714
55o
5
7-932
600
14
49-204
600
6
9.969
600
15
39-731
Soo
7
12.419
600
15
45.538
550
8
15.008
600
15
54.646
600
8
17.190
700
16
45.847
500
9
17.958
500
16
5L7I3
550
9
20.602
600
16
61 . 428
600
9
25 - 477
700
17
49.850
450
10
20.801
5oo
18
55-123
450
10
24.148
600
18
67.030
5oo
10
30.375
700
19
61.081
450
II
23.963
500
20
68.337
450
II
27.875
600
20
89.244
500
II
35 619
700
22
82.868
45o
12
27-795
500
22
104.958
Soo
12
33-885
600
24
99.789
450
12
41-844
700
26
120.555
450
13
3I-I79
500
28
142.000
450
13
37 129
600
30
166.828
450
Kimberley Joint Pipe
External
diameter
Weight
per foot
complete
Test pressure
in pounds
External
diameter
Weight
per foot
complete
Test pressure
in pounds
6
9.623
600
14
38.657
550
7
11.930
600
14
47.269
600
8
I4-37I
600
15
37-094
Soo
8
16.579
700
IS
42.986
550
9
17.032
Soo
15
52.226
600
9
19.707
600
16
41.596
500
9
24 640
700
16
47-554
550
10
19 779
500
16
57.422
600
10
23.169
600
17
47-737
450
IO
29-474
700
18
51.486
450
II
22.924
500
18
63.596
500
II
26.884
600
19
57-118
450
II
34.727
700
20
62.865
450
12
26.128
Soo
20
84.154
500
12
32.302
600
22
75.839
450
12
40.370
700
22
98.359
500
13
29-443
500
24
90.034
450
13
35 - 475
600
26
106.260
450
13
43.848
650
28
124.413
450
14
32.873
Soo
30
144.616
450
Hydrostatic Test Pressures 75
Hydrostatic Test Pressures (Continued)
Allison Vanishing Thread Tubing — Ends Upset
Size
Weight
per foot
complete
Test pressure
in pounds
Size
Weight
per foot
complete
Test pressure
in pounds
2
2V2
336
4
3-731
5.903
7.699
9.287
10.984
1800
2100
1900
1500
1500
4%
i
12.744
14.962
19-359
23-957
29.196
1500
1500
1500
1200
I2OO
Allison Vanishing Thread Tubing — Not Upset
Size
Weight
per foot
complete
Test pressure
in pounds
Size
Weight
per foot
complete
Test pressure
in pounds
&&
iVu
2
2V2
3
3VX2
2.303
2-751
3.723
5.893
7.689
9.276
1200
1700
1700
2OOO
1800
1500
£
1
8
10.973
12.733
14.946
19.338
23.936
29 . 167
1500
1500
1500
1500
1200
1 200
Flush Joint Tubing
Size
Weight
per foot
plain ends
Test pressure
in pounds
Size
Weight
per foot
plain ends
Test pressure
in pounds
3%
41/2
6O.D.
6
?O.D.
80.D.
8
7-575
9 109
10 790
12.538
14 617
17.105
18.974
21.535
23-544
26.404
28.554
1000
IOOO
IOOO
IOOO
IOOO
IOOO
IOOO
IOOO
IOOO
IOOO
IOOO
90.D.
9
loO.D.
10
I20.D.
12
13
14
15
iSO.D.
31 • 624
33.907
37-559
40.483
46.558
49.562
63.441
68.119
82 771
93 451
900
900
900
900
800
800
800
750
750
750
Test applied on pipe prior to threading.
76 Hydrostatic Test Pressures
Hydrostatic Test Pressures (Concluded)
Dry Kiln Pipe Tuyere Pipe
Size
Weight
per foot
complete
Test pres-
sure in
pounds
Size
Weight
per foot
plain ends
Test pres-
sure in
pounds
i
1%
1.697
2.304
700
700
i
iU
2.171
2.996
700
1500
In addition to the above test the
pipe is jarred with a hammer while i
under pressure.
Full Weight Drill Pipe
California Diamond BX Drive Pipe
Size
Weight
per foot
complete
Test pres-
sure in
pounds
4V4
4V2
4V2
16.000
12.850
15.000
1800
1400
1700
Size
Weight
per foot
complete
Test pres-
sure in
pounds
In addition to the above test the
pipe is jarred with a hammer while
under pressure.
Special Upset Rotary Pipe
4
4
4V2
11.055
11.815
12.744
15.055
19.463
1500
1500
1500
1500
1500
Size
Weight
per foot
complete
Test pres-
sure in
pounds
Special Rotary Pipe
2V2
m
4
4
5
6
6
7.841
IO.OOO
12.632
15.323
17.000
20.000
19.551
28.948
2000
2500
1800
2OOO
I600
I9OO
1500
I800
Size
Weight
per foot
complete
Test pres-
sure in
pounds
2V2
2y2
4
4
?
6
6
7.830
IO.OOO
12.500
15.000
15.500
18.000
17.500
21.000
23 500
29.000
2000
2500
I800
2OOO
1600
I800
I600
I800
I5OO
I800
California Special External
Upset Tubing
Size
Weight
per foot
complete
Test pres-
sure in
pounds
3
4
8.627
12.500
2000
1800
Pipe Joints
77
Fig. 5. Typical Section of Standard Pipe Coupling and Joint
(For list of sizes, dimensions and weights see page 22.)
Fig. 6. Typical Section of Line Pipe Coupling and Joint
(For list of sizes, dimensions and weights see page 23.)
Fig. 7. Typical Section of Drive Pipe Coupling and Joint
(For list of sizes, dimensions and weights see page 24.)
78
Pipe Joints
Fig. 8. Typical Section of Standard Boston Casing Coupling and Joint
(For list of sizes, dimensions and weights see page 26.)
Fig. 9. Typical Section of Boston Casing — Pacific Coupling and Joint
(For list of sizes, dimensions and weights see page 28.)
K---L— H
Fig. 10. Typical Section of Inserted Joint Casing
(For list of sizes, dimensions and weights see page 27.)
Pipe Joints
79
Fig. ii. Typical Section of Special Rotary Pipe Coupling and Joint
(For list of sizes, dimensions and weights see page 34.)
Fig. 12. Typical Section of Special Upset Rotary Pipe Coupling and Joint
(For list of sizes, dimensions and weights see page 34.)
Fig. 13. Typical Section of Reamed and Drifted Pipe Coupling and Joint
(For list of sizes, dimensions and weights see page 35.)
80
Pipe Joints
Fig. 14. Typical Section of Flush Joint Tubing
(For list of sizes, dimensions and weights see page 32.)
Fig. 15. Typical Section of Full Weight Drill Pipe Coupling and Joint
(For list of sizes, dimensions and weights see page 36.)
Fig. 1 6. Typical Section of Air Line Pipe Coupling and Joint
(For list of sizes, dimensions and weights see page 36.)
Pipe Joints
81
Fig. 17. Typical Section of Oil Well Tubing Coupling and Joint
(For list of sizes, dimensions and weights see page 30.)
Fig. 1 8. Typical Section of Allison Vanishing Thread Tubing Coupling
and Joint — Not Upset
(For list of sizes, dimensions and weights see page 33.)
Fig. 19. Typical Section of Allison Vanishing Thread Tubing Coupling
and Joint — Ends Upset
(For list of sizes, dimensions and weights see page 33.)
82
Pipe Joints
Fig. 20. Typical Section of California Diamond BX Casing Coupling and Joint
(For list of sizes, dimensions and weights see page 29.)
Fig. 21. Typical Section of California Diamond BX Drive Pipe
Coupling and Joint
(For list of sizes, dimensions and weights see page 31.)
Fig. 22. Typical Section of California Special External Upset Tubing
(For list of sizes, dimensions and weights see page 30.)
Pipe Joints
83
Fig. 23. Typical Section of South Penn Casing Coupling and Joint
(For list of sizes, dimensions and weights see page 35.)
Fig. 24. Typical Section of Dry Kiln Pipe Coupling and Joint
(For list of sizes, dimensions and weights see page 37.)
L— -
Fig. 25. Typical Section of a Kimberley Joint
(For list of sizes, dimensions and weights see page 44.)
84
Pipe Joints
Fig. 26. Typical Section of a Matheson Joint
(For list of sizes, dimensions and weights see page 42.)
Fig. 27. Typical Section of a Converse Lock Joint Hub
(For list of sizes, dimensions and weights see page 43.)
Fig. 28. Typical Section of a Converse Lock Joint Hub and Pipe
(For list of sizes, dimensions and weights see page 43.)
Square Pipe
Sections of Square Pipe
85
Fig. 30
!« f j
Fig. 34
See table, page 45, for various thicknesses and weights manufactured.
86
Square Pipe
Sections of Square Pipe
— H
See table, page 45, for various thicknesses and weights manufactured.
Rectangular Pipe
87
Sections of Rectangular Pipe
n
— 1---
Fig. 37
I
Fig. 39
1
1
Fig. 38
See table, page 45, for various thicknesses and weights manufactured.
88
Rectangular Pipe
Sections of Rectangular Pipe
i
Fig. 42
See table, page 45, for various thicknesses and weights manufactured.
Standard Specifications 89
STANDARD SPECIFICATIONS
It is the aim, as the reader will see by the system of testing and in-
spection heretofore described, to ship nothing but first-class material.
Most orders specify "Steel Pipe" and rely on mill tests for the necessary
inspection, which, as a matter of fact, are often more severe than those
specified by customers. It sometimes happens, however, that speci-
fications contain requirements which are unreasonable, in that they in-
crease the cost of manufacture without safeguarding the customer's
interests by eliminating defective material — such as, for example,
tests to be made on the skelp before welding, which would result in
some cases in the rejection of good steel plates because they happened
to be rolled a little above or below the customary temperature, and
might, on the other hand, allow defective plates to go through to finished
pipe. It is evidently much better to apply all tests after the skelp has
been through the welding furnace and is in the form of finished pipe,
for good steel may be ruined by improper heating in welding.
For standard pipe (lap or butt-welded) we suggest the following
specification, which will insure first-class material without unneces-
sarily increasing the cost of manufacture. These specifications illus-
trate the method of testing generally applicable to tubes and pipe, in
order to insure uniformity and good quality material and workmanship.
We also give our standard specifications for locomotive boiler tubes,
which are fully as strict, if not more so, than any we are required to work
to. It would greatly facilitate the work of inspection if the tests required
on tubes and pipes were standardized. We trust that these specifications
will meet the approval of engineers, architects, and others who wish
to protect their interests, as they have been prepared after careful con-
sideration with that end in view.
The following specifications are known as the 1913 Book of Standards
specifications.
SPECIFICATION FOE STANDARD WELDED PIPE
1. Material. Welded pipe is to be made of uniformly good quality
soft weldable steel, rolled from solid ingots. Sufficient crop shall be cut
from the ends to insure sound material, and the steel shall be given
the most approved treatment in heating and rolling.
2. Process of Manufacture. All pipe shall be made either by the
lap or butt-weld process as specified on order according to the best
methods and practice.
3. Surface Inspection. The pipe must be reasonably straight and
free from blisters, cracks or other injurious defects. Liquor marks
incidental to the manufacture of lap-welded pipe will not be considered
as surface defects. The pipe shall not vary more than one per cent
either way from being perfectly round or true to the standard outside
diameter, except on the small sizes, where a variation of one-sixty-fourth
90 Standard Specifications
of an inch will be accepted. The pipe must not vary more than five
per cent either way from standard weight.
4. Threading and Reaming. Where required, the pipe must have
a good Briggs standard thread, which will make a tight joint when
tested by internal hydrostatic pressure at the mill (paragraph 5). The
thread must not vary more than one and one-half turns either way when
tested with a Pratt & Whitney Briggs standard gage. All burrs at the
ends are to be removed.
5. Internal Pressure Test. The following test pressures will be
applied to the respective sizes of standard Butt and Lap-weld pipe as
indicated in table:
Method of maim- _ .
Nominal size facture pressure
V8 inch to 2 inches (inclusive) Butt Weld 700 pounds
2^2 inches and 3 inches Butt Weld 800 pounds
Up to 8 inches Lap Weld 1000 pounds
9 and 10 inches. Lap Weld 900 pounds
ii and 12 inches Lap Weld 800 pounds
13 and 14 inches Lap Weld 700 pounds
15 inches Lap Weld 600 pounds
NOTE. On 8, 10 and 12 inch sizes which have more than one weight
as standard, we have shown the hydraulic test pressure for the heaviest
weight.
6. Testing of Material. The steel from which the pipe is made
must show the following physical properties:
Pipe Steel
Tensile Strength 52 ooo to 62 ooo pounds per square inch.
Elastic Limit Not less than 30 ooo pounds per square inch.
Elongation in 8 Inches Not less than 20%.
Reduction in Area Not less than 50%.
A test piece cut lengthwise from the pipe and filed smooth on the
edges should bend through 180 degrees with an inner diameter at the
bend equal to the thickness of the material, without fracture.
7. Couplings. The material to be sound and free from injurious
defects. Threads must be clean cut, tapped straight through and of
such pitch diameter as will make a tight joint. The ends must be
countersunk.
8. Thread Protection. Solid tapped rings or split couplings will
be provided as thread protectors on all sizes 4 inches in diameter or
larger. Protection will be provided for smaller sizes when specifically
called for on order.
9. All tests shall be made at mill.
Specification for Matheson Joint Pipe 91
SPECIFICATION FOE MATHESON JOINT PIPE
1. General Description of Pipe. The pipe shall be made of uni-
formly good quality soft welding steel rolled from solid ingots. Suffi-
cient crop shall be cut from the ends to insure sound material. The
pipe shall be manufactured by what is known in the trade as the lap-weld
process and each length shall be fitted with Matheson Joint.
2. Design of Joint. The joint shall be made according to the
schedule of dimensions and weights given on page 42, as closely as it
is practicable to work, especial attention being directed to having the
bell circular and the diameter of the mouth of the bell tc standard
size, in order to allow the lead to flow and be calked when a slight
deflection is made at a joint. Also the depth of insertion must not be
materially increased, in order to not materially increase the length
required to lay the line. In cases where a greater thickness is specified
than shown in the schedule, the form of the bell shall be that for the
next larger diameter on the schedule having about the same thickness.
3. Surface Inspection. The pipe must be reasonably straight and
free from blisters, cracks or other injurious defects. Liquor marks
incidental to the manufacture of lap-welded pipe will not be considered
as surface defects. The pipe shall not vary more than i per cent either
way from the mean outside diameter specified. The pipe must not
vary more than 5 per cent either way from weight as listed; any piece
selected for £est must be at least eighteen feet long. Shorter lengths
may be more than 5 per cent over weight, but must not be more than
5 per cent under weight.
4. Strength of Material. The steel used shall show the following
physical properties on test pieces cut from finished pipe:
Pipe Steel
Tensile strength 52 ooo to 62 ooo pounds per square inch.
Elastic limit Not less than 30 ooo pounds per square inch.
Elongation in 8 inches Not less than 20%.
Reduction in area Not less than 50%.
5. Internal Pressure Test. Each piece of pipe shall be tested to a
hydrostatic pressure not less than that shown in table, page 73, with-
out showing any leak or injury to the metal.
6. Length. The lengths shipped shall not average less than six-
teen (16) feet on the whole order and not more than five per cent (5%)
of the lengths shipped may consist of short pieces joined together, and
no piece so joined may be less than five feet long, nor may more than
one joint be made in any length.
7. Protective Coating.* After forming the joint and applying the
rings, each pipe shall be thoroughly cleaned inside and outside from all
* See articles on Protective Coatings, pages 94 and 106. See index.
92 Standard Specifications
loose scale, dirt, rust, etc., and shall then be heated until perfectly dry.
The pipes shall then be transferred to the dip bath before they become
chilled, and shall remain in the dip sufficient time for the pipe and bath
to reach practically the same temperature. The immersion in the dip
bath shall be horizontal and the pipes shall be lifted out at sufficient
angle to allow the surplus coating to drain off before it has time to
harden. The bath shall be maintained at a practically constant tem-
perature which shall not be less than the boiling point of water. The
compound shall consist of a good quality of refined coal tar pitch free
from water and the lighter oils, and of such uniform consistency that
it will not chip off by blows or friction at 60 degrees Fahr., nor be liable
to soften unduly so as to run when exposed to a reasonable amount of
solar heat.
If any other compound is required, it must be clearly specified, other-
wise the National Tube Company standard pipe dip will be applied.
8. Galvanizing. Where galvanizing is required, the finished pipe
shall be cleaned free from scale by pickling in warm dilute sulphuric
acid; the pipe shall then be washed in a bath of water; then immersed
in an alkaline or neutral bath, then dried and immersed in molten zinc,
being allowed to remain in the bath until it acquires the temperature
of the zinc. No wiping or scraping device shall be used which will render
the zinc coating thin. When cool, the clean galvanized pipe shall be
coated as described in section 7, when specifically required.
9. Loading and Shipping. When loading for transport the pipe
shall be handled in such manner that the least possible injury will be
done to the coating, and after loading on cars, it must be well braced
so as to avoid shifting while in transit.
The contractor shall at his expense and without extra charge, ship
sufficient coating, ready mixed for application by brush, to repair the
unavoidable abrasion that may occur to the coating while in transit.
10. Measurement. The pipe will be measured over-all length and
so charged. Purchaser should use care that in ordering laid length
required he considers the length of over-lap in joint shown by Fig. 26,
page 84.
11. Inspection. The material and workmanship shall at all times
during the course of manufacture be open for inspection by customer
or by an inspector authorized to act in his behalf. All tests shall be
made at the mill and the acceptance by customer or his authorized
inspector shall be final and the makers' liability under this specification
shall thereupon cease. The manufacturer shall furnish the inspector
free of extra charge every reasonable facility required to witness the
tests, and make the inspection called for under this specification, and
shall give the inspector due notice as to when work on the order will
begin.
Specification for Converse Lock Joint Pipe 93
SPECIFICATION FOR CONVERSE LOCK* JOINT PIPE
1. General Description of Pipe. The pipe shall be made of uni-
formly good quality soft welding steel rolled from solid ingots. Sufficient
crop shall be cut from the ends to insure sound material. The pipe shall
be manufactured by what is known in the trade as the lap-weld process
and each length shall be fitted with Converse Lock Joint.
2. Design of Joint. The Converse Lock Joint is made by means
of a cast iron hub whose inner surface has an inwardly projecting ring
at mid-length; on each side of this ring are two wedge-shaped pockets,
diametrically opposite; near each mouth of the hub is a recess for lead.
Close to each end of the pipe are two strong rivets, placed at such
distance from the end that when the pipe is inserted into the hub and
slightly rotated (see illustration page 84), the rivets engage the slopes of
the wedge-shaped pockets and force the end of the pipe against the central
ring of the hub. Lead is then poured into the recess provided for it
and securely calked.
3. Hubs. The Converse Lock Joint Hub shall be cylindrical; shall
be made of the best foundry iron and shall be cast to uniform patterns,
strictly in conformity with diameters of the pipe. Converse Lock
Joint Tees, Elbows and Crosses can be supplied when so ordered.
4. Surface Inspection. The pipe must be reasonably straight and
free from blisters, cracks or other injurious defects. Liquor marks
incidental to the manufacture of lap-welded pipe will not be considered
as surface defects. The pipe shall not vary more than i per cent either
way from the mean outside diameter specified. The pipe must not
vary more than 5 per cent either way from weight as listed; any piece
selected for test must be at least 18 feet long. Shorter lengths may be
more than 5 per cent over weight, but must not be more than 5 per cent
under weight.
5. Strength of Material. The steel used shall show the following
physical properties on test pieces cut from finished pipe:
Tensile strength 52 ooo to 62 ooo pounds per square inch.
Elastic limit Not less than 30 ooo pounds per square inch.
Elongation in 8 inches. Not less than 18%.
Reduction in area Not less than 50%.
6. Internal Pressure Test. Each piece of pipe shall be tested to a
hydrostatic pressure not less than that shown in table, page 74, with-
out showing any leak or injury to the metal.
7. Length. The lengths shipped shall not average less than sixteen
(16) feet on the whole order and not more than five per cent (5%) of
the lengths shipped may consist of short pieces joined together, and no
piece so joined may be less than five feet (5' o") long, nor may more than
one joint be made in any length.
94 Standard Specifications
8. Protective Coating.* After forming the joint and applying the
hubs, each pipe shall be thoroughly cleaned inside and outside from all
loose scale, dirt, rust, etc., and shall then be heated until perfectly dry.
The pipes shall then be transferred to the dip bath before they become
chilled, and shall remain in the dip sufficient time for the pipe and bath
to reach practically the same temperature. The immersion in the dip
bath shall be horizontal and the pipes shall be lifted out at sufficient
angle to allow the surplus coating to drain off before it has time to harden.
The bath shall be maintained at a practically constant temperature
which shall not be less than the boiling point of water. The compound
shall consist of a good quality of refined coal tar pitch free from water
and the lighter oils, and of such uniform consistency that it will not chip
off by blows or friction at 60 degrees Fahr., nor be liable to soften unduly
so as to run when exposed to a reasonable amount of solar heat.
If any other compound is required, it must be clearly specified, other-
wise the National Tube Company standard pipe dip will be applied.
9. Galvanizing. Where galvanizing is required, the finished pipe
shall be cleaned free from scale by pickling in warm dilute sulphuric
acid; the pipe shall then be washed in a bath of water; then immersed
in an alkaline or neutral bath, then dried and immersed in molten zinc,
being allowed to remain in the bath until it acquires the temperature of
the zinc. No wiping or scraping device shall be used which will render
the zinc coating thin. When cool, the clean galvanized pipe shall be
coated as described in section 8, when specifically required.
10. Loading and Shipping. One end of each length of Converse
Joint pipe shall be securely leaded into a hub before shipment is made
from the mill. When loading for transport, the pipe shall be handled
* Note : National Coating.
Where required we can furnish special covering of heavy fabric saturated with
protective compound, which will be applied over the regular coating as described
in paragraph 8. The process of applying this special coating being as follows:
The fabric shall be wound spirally around the pipe overlapping about one inch
on each turn, and shall be thoroughly saturated with the hot compound before
being applied to the pipe. The wrapping will be carried up to but not cover the
joint.
Method of Protecting the Joints when Assembled in the Field :
After the joint has been completely assembled in the ditch, the part left un-
protected should first be wiped free of dirt and moisture and then thickly coated
with compound furnished for that purpose. After this a piece of fabric of suffi-
cient width (wider than the hub) having length enough to encircle the hub a
little more than twice is slashed near each edge with cuts running transversely
about 2 inches apart. This strip of fabric is then saturated with compound and
is then wound tightly over the hub, the slashes permitting it to fit closely thereto
and also permitting the edges of the fabric to be drawn down against the pipe
on each side of the hub. This wrapping of the hub should then be thoroughly
covered with compound.
Compound and fabric used in protecting field joints will be furnished free of
charge when National Coating is specified.
Specification for Pipe for Flanging and Bending 95
in such manner that the least possible injury will be done to the coating,
and after loading on cars, it must be well braced so as to avoid shifting
while in transit.
The contractor shall at his expense and without extra charge, ship
sufficient coating, ready mixed for application by brush, to repair the
unavoidable abrasion that may occur to the coating while in transit.
11. Measurement. The pipe will be measured over-all length and
so charged. Purchaser should use care that in ordering laid length
required, he considers the length of pipe inserted in the hub shown by
Fig. 28, page 84.
12. Inspection. The material and workmanship shall at all times
during the course of manufacture be open for inspection by customer
or by an inspector authorized to act on his behalf. All tests shall be
made at the mill and the acceptance by customer or his authorized
inspector shall be final and the makers' liability under this specification
shall thereupon cease. The manufacturer shall furnish the inspector
free of extra charge every reasonable facility required to witness the
tests, and make the inspection called for under this specification, and
shall give the inspector due notice when work on the order will begin.
SPECIFICATION FOR PIPE FOR FLANGING
AND BENDING
The pipe shall be lap-welded, made of Bessemer or Open Hearth Steel
of the best welding quality, free from blisters, cracks or other injurious
defects.
Inspection and Testing of Material
1. Each length of pipe is to be inspected separately for defects inside
and outside, noting particularly the character of the cross section when
cutting off crop ends.
2. A flattening test is to be made on each crop end with the weld near
the side, crushing the end down to one-quarter the diameter of the pipe;
it must not show cracks in the material or opening at the weld.
3. An internal hydrostatic test is to be made on each length of finished
pipe, using the pressure customary in regular mill practice according
to diameter and thickness specified.
4. The Chief Inspector will file a written report on each order tested
showing the percentage of pieces which fail under each section of this
specification; copy to be forwarded to the office of the General Super-
intendent.
96 Signal Pipe
SIGNAL PIPE
(Standard Specification approved by the Railway Signal Association, Oct., 1910.)
Pipe. i. Pipe must be of soft steel, straight, tough and uniform in
quality; free from cinder pockets, blisters, burns and other injurious
flaws, must be hot galvanized inside and outside, unwiped.
2. The tensile strength^ limit of elasticity and ductility shall be
determined from a test piece cut from finished pipe.
3. The pipe shall have a tensile strength of not less than 52 ooo pounds
per square inch, and an elastic limit of not less than 30 ooo pounds per
square inch, and an elongation of not less than 18 per cent, in a measured
length of eight inches. All pipe must stand a test of 600 pounds per
square inch internal hydrostatic pressure without leak.
A piece of pipe one foot long will be selected at random and be sub-
jected to a flattening test by hammering the piece until the opposite
sides are within twice the thickness of the wall from each other; the
piece shall show no cracks in the steel except at the weld.
4. The weight of one foot of one inch pipe before galvanizing should
be 1.71 pounds, and in no case will pipe be accepted weighing less than
1.63 pounds per foot, weight of plug and coupling not included.
5. The outside diameter of pipe must conform to Briggs standard.
Any pipe enough less than 1.31 inches in diameter to result in a flat
thread will be rejected.
6. The manufacturer shall furnish all necessary facilities for making
tests and the tests shall be made at the mill.
7. Inside diameter of all pipe must be large enough to receive a hard-
ened steel plug of 6%4 inch diameter for a length of six inches.
8. Not more than one per cent of pipe less than fifteen feet long will
be accepted, lengths of seventeen feet and over preferred.
9. The ends of pipe must be cut square and drilled for two Vi-inch
rivets on one end only; first rivet hole shall be drilled two inches
from the end and the second two inches from this and at right angles
to it.
10. Each length of pipe shall have a thread i1/^ inches long, %-inch
total taper per foot, 11% "V" threads to the inch, slightly rounded top
and bottom; the threaded portion of the pipe shall be of such diameter
as to permit the coupling to be screwed on five turns by hand, with per-
missible variation of one turn either way.
Couplings. Couplings must be galvanized, to be 2% inches long
and i% inches outside diameter, of wrought iron, free from defects,
faced at ends and tapped straight through, pitch diameter of thread to
be 1.26 inches, variation not more than .003 of an inch, so as to fit pipe
as per section 10 above.
Plugs. Plugs must be merchant bar steel, ten inches long, 31-32 inch
in diameter, drilled for four H-inch rivets with drill .256; spacing to
be one inch, two inches, four inches, two inches, one inch, the outside
Signal Pipe
97
holes to be in one plane and the inside holes to be in a plane at right
angles to the outside holes.
Rivets. Rivets must be galvanized, must be of soft iron or steel
4 inch in diameter, iHle inches long.
i -inch Signal Pipe
(For specification see page 96.)
Fig- 43- Joint Assembled
256 DR.LL^ ,
tiy
j|;
si~a i|! T
i"-4 2"
7Il=fcl
fc:^
Fig. 44. Plug, Merchant Bar Steel
Fig. 45. Coupling, Wrought Iron, Galvanized
Fig. 46. Rivet, Soft Iron or Steel, Galvanized
98 Standard Specifications
SPECIFICATIONS FOE SPECIAL AMMONIA PIPE
1. Material. Welded pipe is to be made of uniformly good quality
soft weldable steel rolled from solid ingots. Sufficient crop shall be
cut from the ends to insure sound material, and the steel shall be given
the most approved treatment in heating and rolling.
2. Process of Manufacture. All pipe 2 inch and larger to be lap-
welded; smaller sizes to be butt- welded and redrawn from a larger size.
3. Surface Inspection. Pipe must be reasonably straight and free
from blisters, cracks or other injurious defects. Liquor marks inci-
dental to the manufacture of lap-welded pipe will not be considered as
surface defects. The pipe shall not vary more than one per cent either
way from being perfectly round or true to standard outside diameter,
except on the small sizes, where a variation of M>4 of an inch will be per-
mitted. The pipe must not vary more than 5 per cent either way from
the weight specified.
4. Threading and Reaming. Where required pipe must have a
good Briggs Standard thread, which will make a tight joint when tested
by hydraulic pressure at the mill (Paragraph 5). The thread must not
vary more than one and one-half turns either way when tested with a
Pratt & Whitney Briggs Standard gage. All burrs at the ends are to
be removed.
5. Internal Pressure Test. Each length of National Special
Ammonia Pipe when lap-welded shall be tested at the mill to 2000 pounds
hydrostatic pressure; when butt-welded and redrawn, the test pressure
shall be 1500 pounds.
6. Testing of Material. The steel from which the pipe is made
must show the following physical properties:
Pipe Steel
Tensile strength 52 ooo to 62 ooo pounds per square inch.
Elastic limit Not less than 30 ooo pounds per square inch.
Elongation in 8 inches Not less than 20%.
Reduction in area Not less than 50%.
A test piece cut lengthwise from the pipe and filed smooth on the
edges shall bend through 180 degrees with an inner diameter at the
bend equal to the thickness of the material, without fracture.
7. Couplings. The material to be sound and free from injurious
defects. Threads must be clean cut, tapered same as pipe, and of such
pitch diameter as will make a tight joint. The ends must be counter-
sunk.
8. Thread Protection. Solid tapped rings or split couplings will
be provided as thread protectors on pipe 2 inches and larger. Thread
protection will be provided for smaller sizes when specifically called for
on order.
9. All tests shall be made at the mill.
Specifications for Locomotive Boiler Tubes
99
SPECIFICATIONS FOR LAP-WELDED LOCOMOTIVE
BOILER TUBES AND SAFE ENDS
Material
Material must be good welding quality Basic Open Hearth Steel,
Spellerized.
Chemical Composition.
Phosphorus must not be over 04 %
Sulphur must not be over 05 %
Carbon must not be over 12%
Manganese 30 to . 45 %
Sample for chemical analysis to be taken by drilling at several points
around the circumference of the tube.
Dimensions, Weights and Test Pressures
Outside diameter
Decimal
thickness
Nearest
B.W.G.
Weight
per foot,
pounds
Test
pressure,
pounds
c
.095
13
1.68
900
i^i inches <
.no
12
1-93
900
.125
II
2.17
IOOO
(
.135
IO
2.33
1000
(
.095
13
1-93
900
2 inches <
.no
.125
12
II
2 22
2.50
900
IOOO
£
.135
10
2.69
IOOO
(
.095
13
2.19
900
2*4 inches <
.no
12
2.51
900
.125
II
2 84
IOOO
(
.135
10
3-05
IOOO
(
.110
12
2.81
800
2 1/2 inches <
.125
II
3 17
800
(
.135
IO
3 41
900
The permissible variation in weight is 5% above or 5% below that
given above.
Inspection
(a) Tubes shall have a reasonably smooth surface, free from injurious
pits, laminations, cracks, blisters or imperfect welds; they shall also be
free from kinks, bends and buckles, signs of unequal contraction in
cooling or injury during manufacture.
(6) The thickness of the wall shall not vary more than 10% above
or 10 % below the gage specified.
(c) Tubes shall be round within .02 inch.
(d) The mean outside diameter shall not vary more than .015 inch
from the size ordered.
(e) Tubes shall not be less than the length ordered, nor more than
.125 inch longer.
100 Standard Specifications
Physical Tests
A combination of vertical and horizontal flattening and flange test
must be made on the crop end cut from each end of every tube, the flange
being about % inch wide. If required, standard ring, expanding and
flattening tests will also be made (see N. T. Co.'s specification for
seamless tubes page 102), but it is believed that in view of the above
combination test on each tube, for which a special machine has been
designed, further testing is unnecessary.
Internal Pressure Test. Each tube shall be subjected by the manu-
facturer to an internal hydrostatic pressure for the respective size and
gage as given in above table of Dimensions, Weights and Test Pressures.
General Requirements
In addition to the above tests, tubes, when inserted in the boiler,
must stand expanding and beading without showing crack or flaw, or
opening at the weld. Those which fail in this way will be returned to
the manufacturer.
Each tube must be plainly stenciled "Spellerized Steel Tested to . . .
Pounds" (according to the respective size and gage as shown in above
table) and tubes shall be so invoiced.
All tests to be made at place of manufacture, under the supervision
of the Railroad's Inspector or his deputy.
SPECIFICATIONS FOR LAP-WELDED AND SEAM-
LESS STEEL BOILER TUBES FOR MERCHANT
AND MARINE SERVICE
Material
Material must be good quality soft steel rolled from solid ingots.
Sufficient crop shall be cut from the ends to insure sound material.
The permissible variation in weight is 5 per cent above or 5 per cent
below the calculated weight.
Inspection
(a) Tubes shall have a reasonably smooth surface, free from injurious
pits, laminations, cracks, blisters or imperfect welds; they shall also be
free from kinks, bends and buckles, signs of unequal contraction in cool-
ing or injury during manufacture.
(b) The thickness of the wall shall not vary more than 10 per cent
above or below the gage specified, except at the weld where .015 inch
extra thickness will be allowed.
(c) Tubes shall not vary more than one-half (%) of one per cent either
way from being round or true to the mean outside diameter, except in
the smaller sizes where a variation of .015 of an inch will be accepted.
(d) Tubes shall not be shorter than the length ordered, nor more than
.125 inch longer.
Physical Tests
Flattening Test. A section three (3) inches long shall stand ham-
mering flat cold until the inside walls are within three times the thick-
ness of the material without cracking at the bend or elsewhere. In
Specifications for Locomotive Boiler .Tubes1
101
case of Lap-welded tubes for Marine work, the bend at one side shall
be made in the weld.
Flanging Test. For Marine purposes on Lap-welded tubes four (4)
inches and smaller and on all sizes of seamless tubes, a flange three-
eighths (%) of an inch wide shall be turned over at right angles to the
body of the tube without showing crack or opening at the weld.
Internal Pressure Test. Each Lap-welded tube shall be subjected
by the manufacturer to an internal hydrostatic pressure for the respective
size and gage as given in table, page 72. And all Seamless Boiler Tubes
are tested to 1000 pounds.
General Requirements
In addition to the above tests, each tube when inserted in the boiler
must stand expanding and flanging where required without cracking
or opening at the weld. Tubes which fail in this way may be returned
to the manufacturer.
A certificate of test shall be furnished the purchaser of each lot of
tubes, for Marine service, describing the kind of material from which
the tubes were made, and that the tubes have been tested and have met
all the requirements prescribed by the Board of Supervising Inspectors,
Department of Commerce and Labor, Steamboat Inspection Service.
All tests to be made at place of manufacture.
SPECIFICATIONS FOR SEAMLESS COLD DRAWN
LOCOMOTIVE BOILER TUBES AND SAFE ENDS
Material
Tubes to be made of our standard soft Basic Open Hearth Steel.
Chemical Analysis. Sulphur and phosphorus not to exceed .04%.
Sample for chemical analysis to be taken by drilling several points
around the circumference of the tubes.
Dimensions and Weights
Outside diameter
Decimal
thickness
Nearest
B.W.G.
Weight per
foot, pounds
(
.095
13
1.68
i% inches . ... <
.no
12
1.93
.125
ii
2.17
(
.135
10
2.33
(
.095
13
1-93
2 inches <
.no
12
2.22
.125
II
2.50
(
.135
IO
2.69
(
.095
13
2.19
2*4 inches <
.no
.125
12
II
2.51
2.84
(
.135
10
3 05
(
.no
12
2.81
2% inches \
.125
II
3.17
\
.135
10
3-41
102 Specifications for Locomotive Boiler Tubes
Inspection
(a) Tubes shall have a smooth surface, free from injurious pits,
checks, cracks or laminations. Tubes shall be free from bends, kinks,
buckles or other defects which would shorten their life or otherwise limit
their usefulness.
(b) The thickness of the wall shall not vary more than 10% above or
10% below the gage specified.
(c) Tubes shall be round within .02 inch.
(d) The mean outside diameter shall not vary more than .010 inch
from the size ordered.
(e) Tubes shall not be less than the length ordered, nor more than
.125 inch longer.
Physical Tests
1. Ring Tests. Coupons i inch long cut from a tube shall stand
hammering down vertically into the shape of a ring without showing
cracks or flaws when crushed flat.
2. Expanding Tests. Sections of tubes 8 inches long, with or with-
out heating, shall be placed in a vertical position and a smooth tapered
steel pin forced into the end of the tube. Under this test the tube shall
expand to i% times its original diameter without splitting or cracking.
The steel pin used for this test shall be of tool steel and have a taper of
iV2 inches per foot of length. When this test is made hot, the tube
shall be heated to a bright cherry red in daylight, and the pin at a blue
heat forced in as described.
3. Flange Test. For tubes i% inches diameter and larger, coupons
8 inches long, cut from the tube, shall have a flange % inch wide turned
over at right angles to the body of the tube without showing crack or
flaw. For tubes less than i% inches diameter, the width of flange shall
be y& the diameter of the tube. All the work is to be done cold.
4. Flattening Test. A section 4 inches long shall stand hammering
flat cold until the inside walls are in contact, without cracking at the
edges or elsewhere.
Two tubes to be tested as required in preceding paragraphs under
"Physical Tests" in each lot of 250 tubes or less. If only one of the
tubes so tested fails, that tube will be rejected, and the Inspector will
take two more tubes from the same lot and subject both to the same
tests as the one that failed; both of these tubes must be found satis-
factory in order that the lot may be passed.
5. Internal Pressure Test. Each tube must be subjected by the manu-
facturer to an internal hydrostatic pressure of 1000 pounds per square
inch.
General Requirements
In addition to above tests, tubes when inserted into boilers must
stand expanding and beading without showing crack or flaw.
Each tube must be plainly stenciled "Shelby Seamless Cold Drawn
Tested to 1000 Pounds" and tubes must be so invoiced. All tests to
be made at place of manufacture under the supervision of the Railroad
Inspector or his deputy.
Specifications for Tubes for Cream Separator Bowls 103
SPECIFICATIONS FOR SHELBY SEAMLESS COLD
DRAWN STEEL TUBES FOR CREAM SEPARA-
TOR BOWLS AND SIMILAR ARTICLES
Material
Tubes for separator bowls shall be manufactured of our Standard,
Class "A" Basic Open Hearth Steel.
Allowances for Machining
CASE i. The Material Chucked True on the Outside:
To the finished outside diameter add M.6 inch for the outside
diameter of the unfinished bowl.
From the finished inside diameter subtract .222 times the finished
wall thickness plus .051 inch for the inside diameter of the un-
finished bowl.
CASE 2. The Material Chucked True on the Inside:
To the finished outside diameter add .222 times the finished wall
thickness plus .05 1 inch for the outside diameter of the unfinished
bowl.
From the finished inside diameter subtract Vie inch for the inside
diameter of the unfinished bowl.
CASE 3. Method of Chucking Unknown:
Add to the finished outside diameter and subtract from the finished
inside diameter one-fourth (V±) of the finished wall thickness plus
.050 inch for the outside and inside diameters respectively of the
unfinished bowl.
The proper allowances for finished walls from y% inch to l/2 inch, by
l/32 inch steps, are given in table, page 104.
Inspection
(a) Surface. The surface inside and outside must be free from all
defects that are more than .010 inch in depth, or the extent of which
is not clearly discernible.
(b) Limits of Size. The outside diameter shall not vary more than
from full size to .01 inch over, for tubes 2 inches and over in diameter,
nor more than from full size to .005 inch over, for tubes under 2 inches
in diameter. The inside diameter shall not vary more than from full
size to .01 inch under full size. The wall shall not vary more than
10%, above or below, of the specified thickness of wall of the required
tube.
(c) Straightness. Tubes for separator bowls, when cut to the bowl
length by the mill, shall not be more than ^ inch from straight when
measured on the cut bowl.
(d) Length. Bowls cut to length shall not vary in length more than
from full length specified to Vs inch over.
Shipment
Tubes for separator bowls, when shipped in long lengths, shall be
oiled to prevent corrosion. Each tube shall be stenciled with the
104 Specifications for Tubes for Diamond Drill Rods
consignee's name and address and the manufacturer's identification
mark, unless tubes are bundled, in which case one tube of each bundle
shall be so stenciled. When bowls are cut to length by the manufacturer
they shall be boxed for shipment without oiling.
Table of Allowances for Machining Shelby Seamless Steel Tubing for
Tubes 10 inches and Less in Length
!
Case i
Case 2
Case 3
Finished
Increase
Decrease
Increase
Decrease
Increase
Decrease
wall
finished
finished
finished
finished
finished
finished
outside
inside
outside
inside
outside
inside
diameter
diameter
diameter
diameter
diameter
diameter
by
by
by
by
by
by
Inch
Inch
Inch
Inch
Inch
Inch
Inch
Vs
Me
.079
.079
Me
.081
.081
%2
Me
.086
.086
Me
.089
.089
8/ie
Me
.093
•093
Me
.097
.097
%2
Me
.100
.100
Me
.105
.105
V*
Me
.107
.107
Me
.113
.113
9/32
Me
.114
.114
Me
.120
.120
5/ie
^32
8l
.121
.128
.121
.128
Me
Me
.128
.136
.128
.136
%
Me
.135
.135
Me
.144
.144
Me2
Me
Me
.142
.148
.142
.148
£
.152
.152
.159
15/82
Me
.155
.155
Me
.167
.167
%
Me
.162
.162
Me
.175
•I7S
NOTE. For finished wall sizes expressed as decimals, use the tabular allow-
ance for the nearest Vs2.
Case i. — The material chucked true on outside.
Case 2. — The material chucked true on inside.
Case 3 . — Method of chucking unknown.
SPECIFICATIONS FOR SHELBY SEAMLESS COLD
DRAWN STEEL TUBES FOR DIAMOND
DRILL RODS
Material
Tubes for drill rods shall be manufactured from Standard, Class "A"
Basic Open Hearth Steel.
Upsets
The heating for upsetting the ends of tubes for drill rods shall be con-
ducted in such a manner that the surface of the tube shall not be inju-
riously scaled. The heated portion must not extend beyond the portion
being upset, farther than is necessary to insure proper working of the
metal. The heated portion shall in no case extend beyond the dies
Specifications for Tubes for Hose Poles 105
gripping the tube during the operation of upsetting. The upset portion
shall be straight and in line with the tube. The diameter and wall of
the tube beyond the upset portion shall not be reduced by the upsetting
operation.
Inspection
(a) Surface. The outside and inside surface of tubes for drill rods
shall be smooth and free from scale. Slight pits or scratches are not
objectionable unless they may form starting points for corrosion.
(b) Straightness. Tubes for drill rods shall be straightened on the
rotary straightening machine and shall be straight within %2 inch; i.e.,
they shall be capable of being passed through a perfectly straight tube
whose inside diameter is %a inch greater than the outside diameter of
the drill rod.
(c) Limits of Size. The outside diameter of the tube shall not vary
more than from full size to .010 inch over, for tubes i^ inch and over in
diameter, nor more than from full size to .005 inch over, for tubes under
iV2 inch in diameter. On the upset portions the limits shall be from full
size to .030 inch over. The wall of the tube shall not vary more than
10% of the specified thickness above and below. The inside diameter
of the upset shall in no case be greater than that specified, but may be
l/s inch less.
(d) Limits of Length. The length after upsetting shall not be less
than that specified nor more than 3/ie inch greater.
Shipment
Drill Rods shall be oiled before shipment, as a protection against rust.
Each tube shall be stenciled with consignee's name and address and
manufacturer's identification mark, unless tubes are bundled, in which
case one tube of each bundle shall be so stenciled.
SPECIFICATIONS FOR SHELBY SEAMLESS COLD
DRAWN STEEL TUBES FOR HOSE POLES
AND HOSE MOLDS
Material
Tubes for hose poles and hose molds shall be manufactured from
Class "A" Basic Open Hearth Steel.
Inspection
(a) Surface. The outside surface of tubes for hose poles shall be as
smooth as possible, free from all pits and scale marks, seams, scratches,
etc. The inside does not require inspection.
Tubes which are to be used for hose molds shall have an inside surface
of the same character as the outside surface of hose poles.
(b) Straightness. Tubes for hose poles or hose molds shall be as
straight as possible, free from short bends and kinks.
(c) Limits of Size. The outside diameter of tubes for hose poles or
hose molds shall not vary more than from full size to .010 inch over,
106 Protective Coatings
for tubes iVfc inch and over in diameter, nor more than from full size
to .005 inch over, for tubes less than 1^/2 inch in diameter; the inside
diameter shall not vary more than from full size to .005 inch under; the
wall of the tube shall not vary more than 10% of the specified wall
thickness.
Tubes for hose poles that are to be coupled together to form longer
lengths than can be obtained with a single tube, will require machining
to insure proper register of the connected tubes.
(d) Limits of Length. The length of tubes for hose poles or hose
molds shall not be less than the length specified, nor more than 3/ie inch
greater.
Shipment
Hose poles and hose molds shall be oiled and boxed for shipment,
unless otherwise specified.
PROTECTIVE COATINGS
In some cases it is impossible to use a protective coating on tubes,
as for example in boilers or condenser tubes. In many other cases the
metal is left unprotected on account of the difficulty of applying
adequate protection, or the cost. In such cases the life of the metal
depends on the care and experience used in its manufacture. Under
the section on "Corrosion," page 12, the theory and conditions which
cause corrosion, and reasons for abandoning the use of puddled iron
in favor of the special grade of soft steel which has been developed
exclusively for the manufacture of pipe were given. A step of such
importance to the future of the business amounted almost to a
turning point in the industry, but was accomplished gradually during
a period of fifteen years of experimenting, the percentage produc-
tion of steel pipe in our mills being increased year by year until it con-
stituted practically our entire output two years ago. The question of
the durability of the material under natural corrosion was given years
of study, both in the laboratory and field, and the manufacture of
wrought iron was not abandoned until we had ample proof from service
tests covering years of exposure under many conditions that the steel
was as durable as the best puddled iron. Those having any doubt on
this question are invited to take up the matter with our Metallurgical
Department, where a considerable amount of evidence has been accumu-
lated.
Under some conditions, such as hot-water heating systems, where the
water is not changed, or in refrigerating systems where ammonia is in
contact with the metal, corrosion is so slow as to be negligible. But
wherever there is any considerable amount of exposure to corrosive
conditions, suitable protective coatings should be applied, when possible.
Surrounding conditions have so much to do with the proper coating
to be used that we need only outline the matter here, referring those
particularly interested to the publications of the American Paint Manu-
facturers' Association, and the Proceedings of the American Society for
Matheson Joint Pipe 107
Testing Materials, who have done a great deal to put the subject on a
scientific basis, and, by field tests conducted under impartial conditions,
have in some measure been able to lay down certain principles on which
suitable protective coatings may be selected.
For the protection of pipe we either galvanize, dip hot in bituminous
compound, which may afterwards be covered with strong fabric saturated
with protective compound, or paint as specified.
Galvanizing is applied by dipping the clean hot pipe in a bath of pure
zinc kept somewhat above the melting point. The pipe is removed
from the bath covered with zinc inside and outside, and cooled without
wiping.
Bituminous Coating made of the proper consistency for the average
temperature to which the pipe is subjected is applied by dipping, followed
by baking. (See also paragraph 7 — page 91.)
National Coating. By a second operation this bituminous com-
pound which has been baked on the pipe to an enamel like surface is
wrapped with a strip of fabric thoroughly saturated with hot compound.
Immediately after being saturated with the compound the fabric is
stretched tightly over the surface overlapping about one inch on each
turn, covering and firmly adhering to the body coat. Two or three
thicknesses may be applied where desired to meet special conditions.
Paint will be applied according to specification from customer.
MATHESON JOINT PIPE*
Matheson Joint is a pipe joint of the bell and spigot type and is very
similar in appearance to a cast iron pipe joint. There are no loose parts
of any kind, the joint being made directly on the pipe. The pipe used
in connection with this joint ranges in size from 2 inches to 30 inches
outside diameter and the standard thicknesses are much lighter than
any other pipe, but in order to withstand varying pressures the pipe is
made of different thicknesses. For list of sizes, thicknesses, weights
and dimensions see table, page 42. For test pressures see table,
page 73-
The Joint is made by belling out or expanding one end of the pipe in
such a manner as to permit the bell end to slip over the plain or spigot
end of the next length of pipe leaving enough space between the two for
the lead which is to make the joint. After the end of the pipe has been
shaped a wrought band is shrunk on the outside of the bell to reinforce
it at this point and to keep it in shape to withstand the calking of the
lead. The spigot end of the pipe has a recess turned in it which prevents
the lead from blowing out or the pipe from pulling out.
The Particular Advantages of this joint are that it is so designed as
to give a continuous, straight, smooth surface inside which reduces the
friction losses to a minimum.
The lead required per joint is less than for other lead joint pipes of the
same diameter.
* For illustration of joint see page 84.
108 Converse Lock Joint
This style of joint permits variations in alignment and grade which
are often necessary. This feature alone frequently avoids special fittings
and pipe bends.
For very high pressures the joint is reinforced with a clamp and a
rubber packing which increases its efficiency so that it becomes as strong
as the body of the pipe. After the joint has been finished each piece is
tested to a hydrostatic pressure of 450 to 700 pounds, depending on the
size and thickness.
The average length of this pipe is 18 feet or about 300 joints per mile*
The pipe is furnished black (no coating), asphalted, galvanized and
then dipped in asphalt, or with our special National coating, which con-
sists in dipping the pipe and then wrapping it with a fabric that is satu-
rated with a special compound, laid on spirally with a lap of about i inch.
This wrap coating forms the best protection against underground corro-
sion and electrolysis that is known at the present time. The thickness
of the National coating (applied once) is about %4 of an inch and may
be made to any desired thickness by additional coatings or wrappings
while the ordinary dipped coating or paint is about Vioo of an inch thick.
CONVERSE LOCK JOINT*
Converse Lock Joint is a lead joint used in connection with wrought
pipe. The pipe used with this joint ranges in size from 2 inches to
30 inches outside diameter, and in order to withstand varying pressures
the pipe is made of different thicknesses. For list of sizes, thicknesses,
weights and dimensions see table, page 43. For test pressures see
table, page 74.
The joint consists of a cylindrical cast iron hub or sleeve whose length
varies with its diameter. It is provided with an annular ring or pro-
jection midway in its length, so as to form on either side of its center
an annular shoulder against which the ends of the pipe section butt or
bear. The ring is made the same height as the thickness of the metal
in the pipe, so as to give a straight, continuous, smooth surface inside
which reduces the friction losses to a minimum. The hub extends out a
sufficient distance on either side of the central ring to support the pipe.
Between the end of the hub and the central ring is an annular recess for
the reception of the lead. This recess being formed inwardly and being
of a larger diameter at the base than at the mouth, holds the lead securely
in place and prevents its displacement. Inside the hub or sleeve, on
each side of the central ring, are two "T" shaped pockets, diametrically
opposite. Close to each end of the pipe are two rivets, placed at such
distance from the end, that when the pipe is inserted into the hub and
slightly rotated, the rivets engage the slopes of the wedge-shaped pockets
and force the end of the pipe against the central ring of the hub, locking
it in position ready for the lead which is to make the joint. After the
lead is poured the joint is thoroughly calked.
* For illustration of joint see page 84.
Tubular Electric Line Poles 109
Converse Joint Pipe is always shipped with a hub leaded on one end
of each pipe and the other, or spigot end, is provided with rivets for
slipping into the hub end of the next length of pipe.
The lead required for the field joint is slightly in excess of that re-
quired for Matheson Joint Pipe, but is considerably less than other lead
joint pipe of the same diameter. This joint like the Matheson Joint
permits variations in alignment and grade which are often necessary
and this feature alone frequently avoids special fittings and pipe bends.
For very high pressures the joint is reinforced with a clamp and rubber
packing which increases its efficiency considerably. Each piece of pipe
is tested to a hydrostatic pressure of 450 to 700 pounds, depending on
the size and thickness.
The average length of this pipe is 18 feet or about 300 joints per mile.
The pipe is furnished black (no coating), asphalted, galvanized and then
dipped in asphalt, or with our special National Coating which consists in
dipping the pipe and then wrapping it with a fabric that is saturated with
a special compound, laid on spirally with a lap of about i inch. This
wrap coating forms the best protection against underground corrosion
and electrolysis that is known at the present time. The thickness of
the National Coating (applied once) is. about %4 of an inch and may be
made to any desired thickness by additional coating or wrappings.
TUBULAR ELECTRIC LINE POLES
The National Tube Company makes tubular electric line poles of
steel pipe. These poles have great durability, stiffness, and strength.
Steel poles are becoming more generally used for carrying the wires for
the overhead construction on electric railway, telephone, telegraph, and
transmission lines.
Customary Sizes. For railway work the poles most used are 30 feet
long, and are composed of 7-inch, 6-inch, and 5-inch pipes. These are
used for both center-pole and span-wire construction. Anchor poles
are usually of 8-inch, 7-inch, and 6-inch pipes, although they are fre-
quently made of larger sizes, often being of lo-inch, 9-inch, and 8-inch
pipes. Poles 28 and 35 feet long are used to a large extent. Such lengths
as 29, 31, and 32 feet are less common.
The British Standard tramway pole is 31 feet long; their standard
permits no other length. A large assortment of peculiar lengths are
used, some of which are 29 feet 6 inches, others vary one or two inches
from the usual lengths, and at times the length is specified to fractional
inches, even to Vie inch. The last is a practice which seems unwise,
because the practical operation of assembling introduces variations of
Vi inch or V2 inch not infrequently. However, all such peculiar and
difficult requirements, that necessarily increase cost, relate to a very
small percentage of the steel poles made.
Lengths. The length of poles appears to depend mostly upon the
clearance required below the wires, in order to avoid injury to the wires
110 Section Lengths
or injury from chance contact with those carrying high-tension lines.
The length is also affected, to the extent of several feet, by the nature of
ground in which planted and the depth of the frost line. The depth of
planting above the frost line appears to give little aid in holding the pole,
if indeed such depth does not tend to disturb the foundation of that
portion below the frost line.
Telegraph Poles. These considerations make it impossible to give
any general statements as to the lengths of poles for telephone, telegraph,
or transmission lines. In some instances entire lines are carried at great
height, as if the effort were to avoid chance contact. Such height may
be required when the lines are on public highways or at road crossings.
There has appeared, during recent years, a tendency to place the lines
at lower elevation and only to raise them where the line crosses roads
or public property. This seems especially true of the high-voltage lines,
where there appears a strong tendency to have a private right-of-way
strip, even fenced in, and the wires carried low, except at crossings.
The claim has been made that it is cheaper to use very high poles, long
spans, and great sags, but actual installations appear to tend towards
the opposite construction.
Pages 120 to 157, give N. T. Co.'s table of standard poles. Sufficient
variety of lengths, sizes, diameters, and sections are given to meet nearly
all requirements of practice.
Section Lengths. Lengths of sections given in the tables have been
selected so as to employ the regular mill-furnace lengths, without pro-
ducing unnecessary scrap, and at the same time produce poles of light
weight in relation to their strength.
The section lengths given, conform closely to those that are usually
employed. These lengths should be specified, except when the practical
requirements justify the increased cost.
The lengths of the sections of a pole have but little effect upon its
strength, stiffness, or weight. For example: the table shows that a pole
30 feet long of 7-inch, 6-inch, and 5-inch pipe does not vary 3 per cent
in weight for any of the various sections listed, whether of two pieces
or three pieces, — the strength of all are alike, — and the deflection
varies less than 4 per cent. In contrast, notice the great change produced
by increasing the butt section to extra-strong pipe. The strength is
increased about 50 per cent, the weight about 40 per cent, and the deflec-
tion decreased about 30 per cent. However, comparison of the various
sets of section lengths shows that as long as the size and thickness of
pipe remains unchanged, the strength, stiffness, and weight do not
change by more than approximately 6 per cent. Other lengths of pole
or sizes of pipe give slightly different results, as will be seen with a pole
30 feet long having 4-inch extra-strong butt section, and upper sections
of standard pipe, or a pole 35 feet long of 5-inch extra-strong butt and
upper sections standard. This is due to the weakness of the inserted
pipe at the point of emergence from first joint above ground; however,
this is not exhibited by poles of large diameter on either of above lengths.
It is thus evident that the weight, strength, and stiffness of any pole are
Material Used ill
but slightly affected by the lengths of the individual sections, provided
the butt section is not made too short, considering the strengths of the
upper sections.
Odd Sizes. Odd sizes, thicknesses, and weights mean special
production, delay, and increased cost, therefore they should
always be avoided, because such pipe has always to be made to
order.
Use of Standard Pipe. Where it is not practical to use poles
made up of standard or extra-strong pipe, it is advisable to use
only the sizes and weights given in one of the standard lists of
tubular goods given on pages 22-44. These have been collected
into the table given on pages 58-65, and arranged by ascending
sequence in diameter and weight. In this table the properties
of pipe are also given, to enable their ready selection for needs of
poles.
Jointing Special Sizes. Considerations of strength, stiffness, etc.,
at times suggest the advisability of such combinations as 4^/2 inch in
5-inch pipe, but these necessitate the assembling in a machine capable
of forcing the smaller into the larger pipe. A forcing machine of this
kind is expensive to change, and such joints should be used only where
it will be possible to order large numbers of identical poles, unless the
use warrants paying the extra assembling cost incurred where only a
few are made at one time. On short orders (only a few poles), it is
better to use such sizes and thicknesses as will allow the insertion of the
smaller pipe freely by hand, — say at least *4 inch difference in diameter
between the outside diameter of the inserted pipe and the inside diameter
of the larger pipe. This difference should never be less than %6 inch
unless the quantity justifies the use of the forcing equipment, — say
1000 or more identical poles, all to be made and shipped at one time.
In the case of such orders, it is desirable (though not necessary) to have
the outside diameter of the inserted pipe a Kttle larger than the inside
diameter of the outside pipe.
Special Joint Reduction. Considerations of strength, stiffness, and
a great limit of least thickness, sometimes leads to the choice of sizes of
pipe that entail great reductions at the joints, viz., poles of n-inch,
g-inch, y-inch, and 41/2-inch pipes. These require heavy swaging before
assembling the poles. After the poles are assembled there is great risk
of injury to the smaller sections when handling in transit or erection.
It is frequently possible to obtain equal, or even a little greater strength,
by the use of larger and thinner pipes for the upper sections, and to do
this without increasing the total weight appreciably.
Material Used. The material of which these poles are made is usu-
ally known as "Soft Mild Steel." Its ultimate strength will average
not less than 50 ooo pounds per square inch, and its elastic limit —
or yield point — not less than 30 ooo pounds per square inch. For
average values and composition, see pages o-io. It is not considered
good engineering to apply loads that impose stresses in the material
112 Deflection and Set Limits
that are above the yield point. For this reason the tables give the load
that will produce a stress about 10 per cent below the yield point, viz.,
27 ooo, which is 90 per cent of 30 ooo. Although the deflection is
usually closely proportional to the load up to this limit, it is considered
proper to limit the deflection tests to loads that do not produce a fiber
stress exceeding two-thirds of the former figure. The deflection tests
are limited to loads that produce about 18 ooo pounds per square inch
fiber stress. The stiffness of poles depends upon the modulus of elas-
ticity of the material. This physical constant is found to average about
29 ooo ooo for the steel used for poles, and on first loading, to vary to
about the same extent as reported for other iron and steel by authorities
as Lanza and others.
The deflections given are not based, however, on this figure directly,
but are based on the greatest deflections found when testing poles that
appear free from defects. The tabular deflection figures thus give the
limit of deflections that poles will not exceed when tested as indicated.
The average deflection will always be less than the tabulated deflection.
These tabulated deflection figures have been adjusted to compensate
for the ordinary irregularities of size, thickness, composition, and physical
properties that are inseparable from the pipe-making processes.
Deflection Limits. Many specifications have been drawn up requir-
ing poles of widely different lengths and diameters, all to stand the same
deflection; this figure is commonly 6 inches. By reference to the
tables it will be seen that a pole 22 feet long of 13-inch and 1 2-inch
pipe should not be deflected more than about i inch, and that a pole
39 feet long of 4-inch, 3-inch, and 2V6-inch pipe should be deflected
about 1 8 inches when testing for deflection. It is thus evident that a
constant figure like 6 inches for deflection may be six times more than,
or only one-third of the amount that it ought to be. By reference to
the tables it will be seen that a deflection of 6 inches is about the suitable
figure for a pole 31 feet long of 6-inch, s-inch, and 4-inch pipe. It is
noteworthy that this length pole is the British Standard. Some framers
of specifications have attempted to overcome the difficulty by reducing
the limit deflection to 3 inches and some to i1/^ inches. Against such
it is proper to urge that i Vfc inches would not strain a pole 39 feet long
of 4-inch. 3-inch, and 2%-inch pipe sufficiently for the test to give any
indication of the quality of the pole. It is more rational to use such
load as will produce about a constant stress in the material and then fix
the deflection limit to correspond. This has been done in the standard
tables.
Set Limits. Poles are suitable for a certain maximum load that
may be applied without producing appreciable permanent distortion
that is, poles which will stand being bent, and not remain permanently
bent when the load is removed. The load that may be applied should
not produce a fiber stress above the "yield point," — say not over
90 per cent of that for safety. Therefore, say not over 27 ooo pounds
per square inch. Such loads are listed for every pole in the table
column of maximum loads (P). After applying such loads there usually
Dog Guards 113
remains a small fraction as permanent deflection (or set, as it is gen-
erally called). Some specifications have limited this to a constant figure,
such as one inch or one-half inch, but this constant figure is as inappro-
priate for set as a constant figure is inappropriate for deflection. An
able writer on elasticity of materials has said, in equivalent, that bars of
ductile metal, as obtained from the manufacturers, on first application
of any load within the elastic limit show a total elongation, but, on
removal of load, retain in the form of set a portion of the elongation.
Thus the elastic elongation is that portion which is immediately recov-
erable. However, on repeated applications of the same load, the metal
arrives at a state where it acts as though perfectly elastic, provided the
load does not exceed the initial load. Tests have shown that this set
on first loading seldom exceeds 10 per cent of the distortion produced by
that load. The practical difficulties of making these tests and measures
impose a limit of such measures, which for commercial testing of poles
is usually agreed on as % inch of permanent set. Thus a pole, which is
deflected 5 inches on test, should not show a permanent set exceeding %
inch, but a pole that is deflected 15 inches on test may show a set of 1.5
inches without exceeding rational bounds.
Deflection Versus Weight. By comparing the deflections tabulated,
it will be seen that a pole of large diameter and thinner pipe is slightly
stiffer and lighter than one of less diameter and greater thickness. Com-
pare poles No. 7622 and 7651. The strength is say 9 per cent less, while
the stiffness is increased a per cent or so, but there is a saving in weight
of about 23 per cent. The rate of increase of strength and stiffness is,
perhaps, more easily seen by referring to table of pipes on pages 58-65,
and comparing the constants in columns Q and 7, which are proportional
to strength and stiffness respectively; g-inch Standard pipe is about as
stiff as an 8-inch extra-strong pipe, is only a few per cent less in strength,
but it is about 22 per cent lighter than the 8-inch extra -strong. In general
it will be seen that both strength and stiffness increase more rapidly
than the weight as the diameter increases. On the other hand, for
one diameter the weight increases more rapidly than the strength or
stiffness, as the thickness is changed. This points to the advisability
of always using as large a diameter as possible.
Dog Guards. The argument has been advanced against the use of
large diameters and thin pipes that they present greater surface and less
thickness where corrosion is greatest. The deterioration of poles, of
all materials, occurs most rapidly at or near the surface of the ground.
In order to prolong the life of poles it is necessary to protect this portion.
Steel poles lend themselves most readily to such protection because a
" dog guard, " made of a piece of larger and thicker pipe, may be slid over
the pole from the butt end, and then swaged and shrunk on so that say
one-third of its length will be below and two-thirds above the ground line.
These dog guards are applied at a red heat, and effectually prevent water
entering between the pole and dog guard. They are usually made 2 feet
long and Vfe inch thick. They thus would at least double the life of a pole of
extra-heavy pipe, and frequently treble the life of a pole of standard pipe.
114 Dog Guards
The usual practice in "dog guards" is to make them 2 feet long and
of sufficient inside diameter to slide easily over the butt section, as here
tabulated.
Butt of pole
Sleeve before swaging
Nominal
size
Outside
diameter
Outside
diameter
Thickness
Weight
per foot
Weight
per sleeve
3
4
6
7
8
9
10
ii
12
13
3-50
4-50
5.563
6.625
7-625
8.625
9.625
10.75
H.75
12.75
14.00
4-50
5.563
6.625
8.00
9.00
IO.OO
11.00
12.00
13.00
14.00
16.00
• 337
.375
• 432
.500
.500
.500
.500
.500
.500
.500
.500
14.983
20.778
28.573
40.050
45-390
50.730
56.070
61.410
66.750
72.0QI
82.771
29.966
41.556
57.146
80.100
90.780
101.460
112.140
122.820
133.500
144.182
165.542
In the case of old poles that need repair, this has been accomplished
by the use of a "dog guard" placed over the pole and extending about
the ordinary length of joint (18 inches), each way from the injured por-
tion, say 4 feet long, and then the space between sleeve and pole filled
with rich Portland cement grout of i to i or i to 2 mixture made up with
as little water as will allow it to surely fill all irregularities of the
space between sleeve and corroded pole. The following table gives
list of appropriate sizes of sleeve.
Butt of pole
Sleeves four (4) feet long
Nominal
size
Outside
diameter
Outside
diameter
Thickness
Weight
per foot
Weight
of sleeve
3
4
6
8
9
10
II
12
13
3-50
4-50
5.563
6.625
7.625
8.625
9.625
10.75
H.75
12.75
14.00
S.oo
6.625
7-625
8.625
9.625
10.75
11-75
12.75
14.00
15 00
16.00
• 355
• 432
.500
.500
.500
.500
.500
.500
.500
.500
.500
17.611
28.573
38.048
43-388
48.728
54-735
60.075
65.415
72.091
77 • 431
82.771
70.444
114.292
152.192
173.552
194.912
218.940
240 . 300
261.660
288.364
309.724
331.084
Test Conditions. The test condition (butt fixed for 6 feet and load
applied 18 inches below the top) used on these tables is that which the
great majority of specifications impose. It has remained the same for
many years, so that it may, in a general way, be considered the "Stand-
ard" condition for pole tests.
Joints
115
Joints. The joints between the sections of poles are made by insert-
ing the smaller pipe 18 inches into the larger pipe while the latter is at
a red heat, swaging down the heated portion and then allowing the joint
to cool and shrink. The swaging (viz., reducing the diameter) is done
either in a hydraulic press or under a hammer. The former process is
expensive when only a few poles are to be made, but is speedy and pro-
duces as good work as the hammer on large quantities. The choice
Fig. 47. Shop Joint
of method should be left to the maker, unless customer is willing to stand
the increased cost that may be entailed by his specifying the method.
The length inserted is almost invariably 18 inches, but other lengths can
be worked when called for. Fig. 47 shows how the joint appears when
completed. This joint, being assembled in the maker's shop, is usually
called a "shop joint" to distinguish it from the following joint.
Field Joint. For shipment of poles over 40 feet long, two railroad
cars are generally required, and it is at times economical to make the
poles in two parts, with one joint fashioned for customer to assemble
at point of erection. This joint is called a " field joint" and is shown in
Fig. 48. It will be noted that it is slightly tapered to allow easy inser-
tion when assembling in field, for which it is only necessary to have the
two parts accurately in alignment, the lighter one being on rollers, so
Fig. 48. Field Joint
placed that it may be slid endwise without disturbing the alignment;
then heat the outside end for 18 inches to a red heat and insert the
smaller pipe and allow to cool. For flag poles of great length such
joints are essential, three or four being used on one pole when needed.
Another form of field joint has been much used, but it has been discarded
because it seriously weakened the pole and was difficult to assemble.
It was made by boring the larger pipe and turning the smaller pipe, no
taper being used.
Joint Strength. The strength of the swaged joint has frequently
been called into question because of careless workmanship or because
116 Joint Strength
attempted with improper tools. When properly made, it meets all
practical needs, and all those devices that reduce the section of metal at
the joint should be avoided, because they are at best but makeshifts to
hide bad workmanship. The regular swaged joint will easily stand the
drop test given on page 119. No pole or pipe can be so dropped without
shortening its length if dropped on an iron anvil, as has been specified at
times. The experiment has been tried on plain pipe (no joints) and it
has been found that the length is reduced. The reduction in length is
the measure employed to detect telescoping at the joints. While the drop
test does not appear to be good from the standpoint of the theoretical
engineer, still it is one that any buyer can apply at will anywhere. As a
more rational test it has been proposed to subject the poles to an endwise
pressure. The objection to this is that customers would have to incur
some considerable expense to equip for the test. To determine the resist-
ance of the swaged joints, a number were cut from poles of medium-
sized pipes and the endwise thrust measured that would start telescop-
ing. It was found that 30 tons frequently failed to start the joints of
ordinary poles, and that some refused to start at 40 tons. These loads
are more than twice as great as the loads that such poles would be
suited to carry as columns, even if they had no joints.
The question of the effect of the joints on the lateral strength and
stiffness of the poles has often been raised. Many experiments have
been made which have shown that the joints neither increase nor de-
crease the lateral strength, stiffness, or set of poles, provided the joints
are made with a sufficient insertion. These experiments were made by
testing plain pipes, without joints, of various sizes and lengths up to
40 feet. The results were compared with the results of tests of jointed
poles. It was found that deflection measures gave about the same
average value of the modulus of elasticity with and without joints. The
deflections computed, allowing for the double thickness at joints, did
not tally as well with experimental results as when the sections were
each considered uniform from point of emergence to end. The set on
first application of load was as great with plain pipes as with jointed
poles. The crippling never occurred in the joints, but always in the
pipe where strain was greatest.
Theoretical considerations indicate that the proper length of insertion
at each joint depends on the size and thickness. When the outside
pipe is thin the joint should be a little longer than when it is thick.
For thin 13-inch pipe it should be about 20 inches, and for 8-inch pipe
about 13 inches will answer. For the sake of uniformity in the tables,
ordinary practice has been adhered to, and all joints made with 1 8-inch
insertion. This allows a good margin of excess length except on the
12-inch and 1 3-inch pipes. For very small pipes the length of joint
could be reduced to 7 inches or so, say on 3-inch pipe, when lateral
strength is the only consideration; but the practical operations of assem-
bling joints make it advisable to use at least 1 2 inches on such size.
Service Conditions, Wind Loads, etc. Some specifications involve
service conditions for which poles are intended. This Company does
not assume liability for poles meeting service conditions. To aid users
Wind Loads 117
to fix on suitable tests for the poles, we give the usual method of
wind-load calculation. In this it is usual to assume a maximum wind
pressure of 30 pounds per square foot, and equate the resultant wind
load to the strength of the pipes at about the elastic limit. Such
pressure may be said to correspond to 50 to 90 miles per hour, according
to authority accepted. However, it makes little difference what the
velocity is, because pressures of 30 pounds to 50 pounds have been
repeatedly observed in many places; notably at Greenwich, England.
The relation of velocity to pressure is only useful where velocities are
recorded and pressure gages not used. But velocity instruments are
subject to such great errors that it is not necessary to go into any refine-
ment as to the relation of pressure and velocity. The U. S. Weather
Bureau reports the anemometer velocity reading which exceeds the actual
average speed of the wind by over 20 per cent, at 60 miles per hour and
is thought to vary increasingly at higher speeds but this has not been
V2
proven by experiment. The relation, pressure =/= — = pounds per
square foot, relates to actual average wind velocity V in miles per hour.
Experiments are stated to show that the pressure on a circular cylinder
gives a total load equal to half the diameter multiplied by the length
multiplied by the pressure. If the wind moved with an absolutely uniform
velocity it would impose a static load, but the wind is always more or
less puffy, as may be noted by observing stretched wires, ropes, flags, or
trees. They will always be seen swaying or surging. Therefore the
load is a "live load, " and such is usually considered to impose twice the
stress of a "static load." If wires are insulated, the outside diameter
of insulation must be used in reckoning wind load. Where snow and
ice form, the diameter of the wires may be increased by *4 inch, or even
Vif-inch thickness in times of sleet storms. The outside diameter of
such incrustation must be used in figuring wind load. It is frequently
assumed that the maximum wind pressure and the snow load do not
act at the same time. It is practically never necessary to consider the
weight of wires, sleet, etc., because any poles that will stand the lateral
strain are more than ample to carry, as columns, the vertical loads that
will come on them.* Example, — poles spaced 36 per mile, carrying 36
wires No. 10 B. W. G.; 6 cross-arms, 5 inches wide, 6 feet long ; wires
25 feet above ground. Wind on wires (no ice or snow) = (°-13<H2) X % X
2 x (528o/36) x 30 X 36 equals about 1760 pounds. If Vi-inch sleet is
assumed the diameter would be 0.134 plus 0.50, say 0.634, and the load
would be about 8370 pounds. Wind on arms would be 6 X (%2) X 6 X 30,
* Wind stress may be omitted when computing column strength when the
wind stress is less than 25 to 30 per cent, of the stress due to direct column loads
in bridges. By inversion ; column strength may be omitted when its stress is
less than 20 per cent, of the bending stress due to wind. Where it is thought
necessary to consider the combined stress due to bending and to loading as a col-
umn a generally accepted rule is to add the bending and eccentric loading stress
to the direct stress as a column, and keep the sum of the stresses below the per-
missible stress allowed by one of the approved empirical column formulae; remem-
bering that a planted pole considered as a column is equivalent to a pivot ended
column whose length is twice the length of the pole above ground.
118 Wind Loads
equal to about 450 pounds* Wind on pole, — for this assume 1 2 inches
diameter and 29 feet long above ground; (1%2) X 29 X 30 xCVij) equals
about 435 pounds. Therefore, equivalent top load is 435 -r- 2, say 218
pounds. Then the wind loads would be
No ice With sleet and
snow
On wire 1760 8370
On arms 450 450
On pole 218 218
2428 9038
To use pole table for selecting size of pole required for above loads,
note that the tabulated poles are loaded 18 inches below the top and
planted 6 feet, therefore 25 feet center of wind load to ground plus
7 feet 6 inches is 32 feet 6 inches. The nearest longer length listed is
33 feet. Pole 7943 will carry the wind load without ice but no pole is
listed of sufficient strength to carry the wind load with sleet, etc. By
table of Pipe giving / and Q it is seen that the latter wind load would
require a butt section larger than 16 inches outside diameter by % inch
thick. It would, therefore, probably be more economical construction
to use guy lines, as is common practice at corner poles. Since a 33 foot
pole would hardly afford room to distribute the cross arms it may be
necessary to use a longer pole such as 34 feet or 35 feet, say number
8063 or 8103 for the pole with no ice.
Painting. Poles are always painted before leaving the maker's
works. Unless customers specify the color, domestic poles are painted
black and export poles red. It would appear probable that the best
practice would be to dip them in hot molten asphaltic pipe coating, but
the demand for such treatment has not yet justified equipment for such
dipping.
Pole Tables. The National Tube Company's table of Standard poles
is given on the following pages. It is recommended not to depart from
the section lengths given in the table. The table is preceded by an explan-
atory note and the Standard Specification for Poles. These tables are as
condensed as possible in order to allow ready comparison and selection.
Tubular Electric Line Pole Tables
These tables of poles, pages 120 to 157, give all essential details for maker and
user.
Pole number is given for purpose of reference and identification.
Column headed "Size of butt" gives the nominal size of pipe used in the butt
section. The upper sections are each one inch, pipe size, smaller than the sec-
tion next below, except that 2^-inch is used in 3 -inch.
Column headed "Thickness" gives the nominal thickness of each section, from
the bottom up, by the use of symbols/ and E, which mean standard and extra
* It is not the custom of engineers to consider the wind load a live load on
structures firmly held by their foundations nor on pieces rigidly attached
thereto. This is different from the above calculation of load on wires which
are flexibly attached.
Specifications for Poles
119
strong, respectively; e.g., Ejf means extra -strong pipe in bottom section and
standard pipe the two upper sections.
Column headed " Maximum load (P)" gives the load that pole will carry,
applied 18 inches below the top when pole is planted or "fixed'5 for a distance
of 6 feet. It is figured at 27 ooo pounds per square inch fiber stress in the material.
Column headed "Load (L) for deflection Z>" gives the load that it is suitable
to specify when poles must be tested for deflection. This deflection test load
is about two-thirds of the maximum load P.
Column headed "Deflection for load Z," gives the maximum deflection in inches
at point of load when pole is fixed as a cantilever for a distance of 6 feet and load
L is applied 18 inches below top. D= deflection limit.
Column headed "Factor 'R" gives the rate of deflection in inches per 100 pounds
load.
Column headed " Factor m " gives a factor for computing the approximate deflec-
tion D' at any point situated "n" inches above the point of application of the load,
by means of formula D' = D(m-\-n)/m, all other conditions remaining as before.
By reason of the slight, unavoidable variations in manufacture, the data
shown in the following tubular electric line pole tables are not absolutely correct,
but the element of error is very small.
Any pole given in these tables will conform to the following specifications:
Specifications. All poles shall be composed of wrought -steel pipes. Joints
shall be made by inserting the smaller pipe cold into the larger pipe a distance
of 18 inches, and while the latter is hot, swaging it upon the smaller and allowing
them to cool and shrink. No shims, wires, liners, pins, rivets, pu-nch marks, or
any device that weakens material at joint will be allowed.
Any pole when fixed for a distance of six feet from the butt end and tested as
a cantilever with the load given in column P, applied 18 inches below the top,
shall not show a set or permanent deflection in excess of 10 per cent of the tem-
porary deflection under this load, but this set limit may not be placed at less
than l/2 inch in any case. Any pole tested as before, but with the load in pounds
given in column L, shall not show a temporary deflection in inches, at the point
of load, exceeding the figure given in column D.
Any pole when dropped three times, butt foremost, from a height of six feet
upon a solid wood block on a rigid base shall not telescope at the joints.
Weight of completed pole shall not vary more than 5 per cent above or 5 per
cent below the weight given in column headed "Weight."
The following list gives pipes used for poles given on pages 120 to 157.
Nom-
inal
Thick-
.203
.216
.237
.258
.280
.301
.322
• 342
.365
.375
.375
.375
Weight
per foot
Moment
of
inertia
5-793
7-575
10.790
14.617
18.974
23-544
28.554
33.907
40.483
45-557
49.562
54.568
1.5296
3-0172
7.2326
15.162
28.142
46.515
72.489
107.58
160.73
216.98
279-33
372.76
Nom-
inal
size
Thick-
ness
.276
.300
.337
.375
.432
.500
.500
.500
.500
.500
.500
.500
Weight
per foot
Moment
of
inertia
7.661
10.252
14.983
20.778
28.573
38.048
43-388
48.728
54.735
60.075
65.415
72.091
1.9242
3.8943
9-6105
20.671
40.491
71.370
105.72
149.63
211.95
280.12
361.54
483.76
120
Tubular Electric Line Pole Tables
Length of Pole, 22 Feet
Sections: 18 feet 6 inches and 5 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
P
Load
for
deflec-
tion D
L
Deflec-
tion for
load I,
D
Factor
R
Factor
m
7000
3
169
//
267
180
4.19
2.33
114
7001
4
238
499
350
3-41
• 975
H3
7002
5
324
"
846
550
2.55
.465
114
7003
6
425
"
I 318
900
2.25
.250
114
7004
7
530
•«
1893
1300
1.96
.151
US
7005
8
647
"
2 609
1700
1.65
.0970
us
7006
9
770
11
3469
2300
1.50
.0654
US
7007
10
919
4641
3100
1.36
.0438
116
7008
ii
1046
5732
3800
1.23
.0324
116
7009
12
1146
"
6801
45oo
1. 13
.0252
116
7010
13
1258
"
8265
5500
1.03
.0188
H5
7011
3
220
Ef
347
220
3.96
i. 80
113
7012
4
315
663
450
3-30
.735
112
7013
5
433
"
i 141
750
2.58
.345
113
7014
6
602
"
1897
1300
2.26
.174
113
7oi5
7
798
••
2905
1900
1.88
.0988
113
7016
8
920
44
3805
2500
1.67
.0666
114
7017
9
1044
44
4 826
3200
1.50
.0471
114
7018
10
1182
"
6 120
4000
1.33
.0333
114
7019
ii
1314
"
7401
5000
1.26
.0251
114
7020
12
1438
8802
5800
1. 12
.0194
114
7021
13
1582
"
10727
7200
1.05
.0146
H5
7022
3
229
EE
347
220
3.96
1. 80
114
7023
4
329
663
450
3-30
.734
H3
7024
5
454
"
i 141
*750
2.58
•344
H4
7025
6
632
"
1897
1300
2.26
.174
114
7026
7
846
«.
2905
1900
.87
.0986
H5
7027
8
993
"
3805
2500
.66
.0665
115
7028
9
1118
"
4 826
3200
.50
.0470
116
7029
10
1256
"
6 120
4000
.33
.0332
H5
7030
II
1385
••
7401
5000
.26
.0251
US
7031
12
1510
"
8802
5800
.12
.0194
IIS
7032
13
1661
10727
7200
.05
.0146
116
Tubular Electric Line Pole Tables 121
Length of Pole, 23 Feet
Sections: 19 feet 6 inches and 5 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
7033
3
177
//
250
170
4-85
2.85
122
7034
4
249
466
300
3-57
1. 19
122
7035
5
339
"
791
550
3-12
.567
122
7036
6
444
"
I 233
800
2-44
• 305
122
7037
7
553
«•
1771
1200
2.22
.185
123
7038
675
2440
1600
1.90
.119
123
7039
9
804
"
3245
2200
1.76
.0798
123
7040
10
959
4342
29OO
1.55
.0535
123
7041
II
1092
5362
3600
1.42
.0395
123
7042
12
1 195
"
6362
4200
1.29
.0307
123
7043
13
1313
"
7732
5200
i. 20
.0230
123
7044
3
230
Ef
324
22O
4.84
2. 2O
121
7045
4
330
620
400
3-59
.897
120
7046
5
454
11
1068
700
2-95
.421
121
7047
6
631
"
1774
I2OO
2.56
.213
121
7048
7
836
2 718
I800
2.18
.121
121
7049
8
964
"
3559
2400
1.95
.0813
122
7050
9
1093
4515
3000
• 73
.0575
122
7051
10
1236
"
5725
3800
• 54
.0406
122
7052
ii
1375
••
6923
4500
.38
.0306
122
7053
12
1503
8234
55oo
.31
.0238
123
7054
i
1654
"
10 034
6800
.21
.0178
124
7055
3
239
EE
324
220
4.84
2.20
122
7056
4
344
620
400
3-58
.896
122
7057
5
475
"
I 067
700
2.95
.421
122
7058
6
660
"
I 774
1200
2.54
.212
122
7059
7
884
2 718
I800
2.16
.120
123
7060
8
1036
"
3559
2400
1.95
.0812
123
7061
9
1167
4514
3000
1.73
• 0575
124
7062
10
1310
"
5725
3800
1.54
.0405
123
7063
II
1446
"
6923
45oo
1.38
.0306
123
7064
12
1576
8234
55oo
1. 31
.0238
124
7065
13
1733
10034
6800
1. 21
.0178
124
122
Tubular Electric Line Pole Tables
Length of Pole, 24 Feet
Sections: 18 feet 6 inches and 7 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
P
Load
for
deflec-
tion D
L
Deflec-
tion for
loadL
D
Factor
R
Factor
m
7066
3
181
//
235
160
5-57
3-48
127
7067
4
253
438
300
4.38
1.46
124
7068
5
346
"
743
500
3-47
.694
126
7069
6
454
1158
750
2-79
• 372
127
7070
7
568
1664
IIOO
2.48
.225
128
7071
8
694
2292
1500
2.16
.144
129
7072
9
827
3049
2000
1.94
.0968
129
7073
10
987
4079
270O
1.75
.0648
129
7074
ii
1127 "
5037
3400
1.63
.0480
131
7075
12
1237
5977
4OOO
1.49
.0372
130
7076
13
1357
7263
4800
1.34
.0280
131
7077
3
231 Ef
305
200
5-40
2.70
124
7078
4
331 !
582
400
4-44
i. ii
121
7079
5
455
1002
650
3.37
.519
122
7080
6
631
1667
IIOO
2.88
.262
123
7081
7
836
<•
2553
1700
2.52
.148
124
7082
8
967
3343
2200
2.19
.0996
125
7083
9
IIOI
-"
4241
2800
1-97
.0702
126
7084
10
1249
r*?
5378
3600
1.78
.0495
127
7085
ii
1395
6503
4200
1.57
.0374
128
7086
12
1529
"
7735
5200
1.50
.0289
128
7087
13
1681
"
9426
620O
1.34
.0216
128
7088
3
244
EE
305
200
5.36
2.68
126
7089
4
350
"
582
400
4.40
1. 10
124
7090
5
484
IOO2
65O
3-34
.514
126
7091
6
673
"
1667
IIOO
2.85
.259
127
7092
7
903
«•
2553
1700
2.50
.147
128
7093
8
1069
3343
2200
2.17
.0986
129
7094
9
1205
11
4241
2800
1.95
.0696
130
7095
10
1353
"
5378
3600
1.77
.0491
130
7096
ii
1495
«•
6503
42OO
1.56
.0371
130
7097
12
1631
"
7735
5200
i.5o
.0288
131
7098
13
1792
9426
6200
1.33
.0214
129
Tubular Electric Line Pole Tables 123
Length of Pole, 24 Feet
Sections: 19 feet, 4 feet, and 4 feet
Maxi-
Load
Deflec-
Number
Size
of
butt
Weight
Thick-
ness
mum
load
for
deflec-
tion D
tion for
loadL
Factor
Factor
P
L
D
R
m
7099
4
259
///
438
300
4-35
1.45
125
7100
5
351
743
500
3-45
.690
126
7101
6
463
1 159
750
2.78
• 371
127
7102
7
58i
"
1664
1 100
2.46
.224
129
7103
8
713
2292
1500
2.16
.144
129
7104
9
853
3049
2OOO
1.93
.0966
129
7105
10
1020
"
4079
2700
1.75
.0647
129
7106
II
Il64
5037
3400
1.63
.0478
130
7107
12
1287
"
5977
4000
1.49
.0372
130
7108
13
1418
7264
4800
1.34
.0279
131
7109
4
339
Eff
582
400
4.40
1. 10
122
7110
5
463
IO02
650
3-35
.515
123
7111
6
645
"
1667
1 100
2.86
.260
124
7112
7
856
2553
1700
2.50
.147
124
7H3
8
995
"
3343
22OO
2.18
.0992
126
7114
9
1 134
v
4241
2800
1.96
.0699
127
7H5
10
1289
*.'
5378
3600
1.77
.0492
127
7116
ii
1440
"
6503
4200
1.56
.0372
128
7117
12
1587
7735
5200
1.50
.0288
129
7118
13
1751
"
9426
6200
1-34
.0216
130
7119
4
349
EEf
582
4OO
4-36
1.09
124
7120
5
480
"
1002
650
3 33
.512
125
7121
6
669
"
1667
IIOO
2.84
.258
126
7122
7
895
2553
1700
2.48
.146
127
7123
8
1053
"
3343
2200
2.16
.0984
129
7124
9
H93
•«
4241
2800
1.95
.0695
130
7125
10
1349
"
5378
3600
1.76
.0490
130
7126
ii
1496
6503
4200
1.56
.0371
131
7127
12
1645
"
7735
5200
1.49
.0287
131
7128
13
1814
"
9426
620O
1.33
.0215
131
7129
4
357
EEE
582
40O
4-36
1.09
125
7130
5
491
"
1002
650
3-33
.512
126
7i3i
6
685
1667
IIOO
2.84
.258
127
7132
7
918
"
2553
1700
2.48
.146
128
7133
8
1091
3343
220O
2.16
.0984
129
7134
9
1251
«
4241
2800
1.95
.0695
130
7135
10
1408
•
5378
3600
1.76
.0490
130
7136
II
1556
*
6503
4200
1.56
.0371
131
7137
12
1702
'
7735
5200
1.49
.0287
132
7138
13
1872
9426
6200
1.33
.0215
131
124
Tubular Electric Line Pole Tables
Length of Pole, 25 Feet
Sections: 19 feet 6 inches and 7 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
P
Load
for
deflec-
tion D
L
Deflec-
tion for
loadL
D
Factor
R
Factor
m
7139
3
188
//
221
150
6.21
4.14
135
7140
4
264
413
280
4.87
1.74
133
7141
5
360
"
701
450
3-71
.825
134
7142
6
473
1092
750
3-32
• 443
135
7143
7
591
"
1569
IOOO
2.68
.268
136
7144
8
722
"
2161
1400
2.39
.171
137
7145
9
861
"
2875
1900
2.19
.115
137
7146
10
1027
"
3845
2600
2.01
.0773
137
7147
II
H73
««
4749
3200
1.83
.0572
138
7148
12
1286
5635
3900
1.73
.0444
138
7149
13
1412
"
6848
4800
1. 60
.0333
138
7150
3
241
Ef
287
190
6.10
3-21
132
7i5i
4
346
549
350
4.62
1.32
129
7152
5
475
**
945
650
4.01
.617
131
7153
6
660
1572
IOOO
3- II
.311
131
7154
7
874
.1".COZ
2407
1600
2.82
.176
132
7155
8
IOII
3152
2IOO
2.50
.119
133
7156
9
1150
i **OQJ
3998
2700
2.25
.0835
134
7157
10
1304
4" 005
5071
3400
2.0O
.0589
134
7158
II
1456
"
6132
4000
1.78
.0445
136
7159
12
1595
«
7293
4800
1.65
• 0344
136
7160
13
1753
"
8888
OOOO
1.55
.0258
137
7161
3
255
EE
287
190
6.06
3-19
135
7162
4
365
11
549
350
4-59
I-3I
132
7163
5
505
"
945
650
3-98
.612
134
7164
6
701
1572
IOOO
3-09
.309
135
7165
7
941
"
2407
1600
2.80
.175
136
7166
8
III2
"
3152
2100
2.48
.118
137
7167
9
1254
"
3998
2700
.24
.0830
138
7168
10
1408
"
5071
3400
.99
.0585
137
7169
II
1555
•«
6132
4000
• 77
.0442
138
7170
12
1696
"
7293
4800
.65
.0343
139
7171
13
1864
8888
6000
.54
.0256
138
Tubular Electric Line Pole Tables 125
Length of Pole, 25 Feet
Sections: 19 feet, 5 feet, and 4 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
7172
4
266
///
4i3
280
4-90
i 75
130
7173
5
362
701
450
3-74
.830
132
7174
6
477
"
1092
750
3-34
• 445
134
7175
7
600
"
1569
IOOO
2.69
.269
135
7176
8
737
"
2161
1400
2.41
.172
136
7177
9
881
2875
1900
2. 2O
.116
136
7178
10
1053
"
3845
2600
2.02
•0775
137
7179
II
1205
"
4749
3200
1.83
• 0573
138
7180
12
1332
"
5635
3900
1-73
• 0444
138
7181
13
1468
"
6848
4800
1. 60
.0333
138
7182
4
346
Eff
549
350
4.66
1.33
126
7183
5
474
«
945
650
4-05
.623
127
7184
6
660
"
1572
IOOO
3-14
.314
129
7185
7
875
"
2407
1600
2.85
.178
130
7186
8
1018
3152
2100
2.50
.119
131
7187
9
1162
'•
3998
2700
2.27
.0840
133
7188
10
1323
"
5071
3400
2.01
.0592
134
7189
ii
1480
6132
4000
1-79
.0447
135
7190
12
1633
"
7293
4800
1.66
.0345
135
7191
13
1800
8888
600O
1.55
.0259
136
7192
4
360
EEf
549
350
4-62
1.32
130
7193
5
495
11
945
650
4.00
.616
131
7194
6
689
1572
IOOO
3.io
.310
132
7195
7
923
"
2407
1600
2.80
.175
134
7196
8
1091
"•
3152
2100
2.48
.118
136
7197
9
1236
••
3998
2700
2.25
.0832
137
7198
10
1397
"
5071
3400
2.0O
.0587
137
7199
ii
1551
6132
4000
1.77
.0443
137
7200
12
1705
"
7293
4800
1.65
.0343
137
7201
13
1879
8888
6000
1.54
.0257
138
7202
4
367
EEE
549
350
4.62
1.32
130
7203
5
506
**
945
650
4.00
.616
132
7204
6
706
"
1572
IOOO
3.io
.310
133
7205
7
947
"
2407
1600
2.80
.175
134
7206
8
1129
"
3152
2100
2.48
.118
136
7207
9
1294
••
3998
27OO
2.25
.0832
137
7208
10
1456
"
5071
3400
2.00
.0587
137
7209
II
1610
"
6132
4000
1.77
•0443
137
7210
12
1762
41
7293
4800
1.65
.0343
138
7211
13
1937
8888
6OOO
1.54
.0257
138
126
Tubular Electric Line Pole Tables
Length of Pole, 26 Feet
Sections: 20 feet 6 inches and 7 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
P
Load
for
deflec-
tion D
L
Deflec-
tion for
load L
D
Factor
R
Factor
m
7212
3
196
//
209
140
6.83
4 88
143
7213
4
275
(
39i
250
5.13
2.05
141
7214
5
375
663
-450
4.38
• 973
142
7315
6
492
1033
700
3.66
.523
144
7216
7
6i5
"
1484
1000
3-i6
.316
145
7217
8
751
"
2044
1400
2.83
.202
145
7218
9
895
«
2719
1800
2.45
.136
145
7219
10
1068
3638
2400
2.19
.0912
145
7220
ii
1218
"
4493
3000
2.03
.0675
147
7221
12
1336
"
5330
3600
1.88
.0523
146
7222
13
1467
"
6478
4200
1.65
.0393
147
7223
3
252
Ef
272
180
6.82
3-79
140
7224
4
36i
519
350
5 43
1.55
137
7225
5
496
"
894
600
4.36.
.726
139
7226
6
689
1487
IOOO
3-66
.366
140
7227
7
912
2277
1500
3-12
.208
140
7228
8
1054
"
2982
2000
2.80 .140
141
7229
9
1 199
"
3782
2500
2.46 .0985
142
7230
10
1359
"
4797
3200
2.22
.0695
143
7231
ii
1516
"
5800
3900
2.05
.0525
145
7232
12
1660
"
6899
45oo .
1.83
.0406
144
7233
13
1825
"
8407
5500
I.67
.0304
145
7234
3
265
EE
272
180
6.79
3-77
143
7235
4
38o
"
519
350
5-39
1-54
141
7236
5
525
'<
894
600
4-33
.721
142
7237
6
730
44
1487
IOOO
3.64
.364
143
7238
7
979
"
2277
1500
3-09
.206
144
7239
8
1156
"
2982
20OO
2.78
.139
146
7240
9
1302
3782
25OO
2.45
.0979
146
7241
10
1462
"
4797
3200
2.21
.0691
146
7242
ii
1615
..
5800
3900
2.04
.0522
146
7243
12
1761
44
6899
45oo
1.82
.0405
146
7244
13
1936
8407
5500
1.66
.0302
146
Tubular Electric Line Pole Tables 127
Length of Pole, 26 Feet
Sections: 18 feet 6 inches, 6 feet 6 inches, and 4 feet
Size
Number of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
7245 4
272
///
391
250
5.28
2. II
134
7246 ; 5
37i
663
45o
4-49
•998
137
7247 6
490
1033
700
3-74
• 534
139
7248 7
617
1484
1000
3-21
321
141
7249 8
758
,
2044
1400
2.87
.205
142
7250 9
907
•«
2719
1800
2.48
.138
143
7251 10
1084
3638
2400
2.22
.0924
143
7252 ii
1243
"
4493
3000
2.O4
.0681
145
7253 12
1376
5330
3600
1.90
.0527
145
7254 13
1515
"
6478
4200
1.66
.0396
146
7255 4
3So
Eff
519
350
5.71
1.63
129
7256 5
480
894
600
4.55
.758
I3i
7257
6
667
1487
1000
3.81
.381
132
7258
7
885
"
2277
1500
3-23
-215
133
7259
8
1032
2982
2OOO
2.88
.144
136
7260
9
1181
3782
2500
2.53
.101
137
7261 10
1347
"
4797
3200
2.28
.0711
139
7262 ii
I5H
58oo
3900
2.09
.0535
141
7263 12
1668
"
6899
4500
1.86
.0413
141
7264 13
1839
"
8407
55oo
1.70
.0309
141
7265
4
368
EEf
519
350
5-57
1.59
134
7266 5
507
894
600
4-45
• 741
136
7267 ! 6
706
1487
IOOO
3-73
.373
137
7268 1 7
947
2277
1500
3 15
.210
140
7269
8
1126
2982
2000
2.8o
.140
142
7270
9
1277
••
3782
2500
2.47
.0988
143
7271
10
1443
4797
3200
2.23
.0698
143
7272
ii
1603
"
58oo
3900
2.06
.0527
145
7273
12
1763
6899
45oo
1.84
.0408
145
7274
13
1941
"
8407
55oo
1.67
.0304
143
7275
4
375
EEE
519
350
5-57
1.59
134
7276
5
518
"
894
600
4 45
• 741
136
7277
6
722
1487
IOOO
3-72
• 372
138
7278
7
971
"
2277
1500
3 IS
.210
140
7279
8
1164
"
2982
200O
2.80
.140
143
7280
9
1335
••
3782
2500
2.47
.0988
143
7281
10
1502
4797
320O
2.23
.0698
144
7282
ii
1662
"
58oo
3900
2.06
.0527
145
7283
12
1819
6899
45oo
1.84
.0408
146
7284
13
1999
8407
5500
I.67
.0304
143
128
Tubular Electric Line Pole Tables
Length of Pole, 27 Feet
Sections: 18 feet 6 inches and 10 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
P
Load
for
deflec-
tion D
L
Deflec-
tion for
loadL
D
Factor
R
Factor
m
7285
3
198
//
199
130
7.70
5-92
145
7286
4
276
371
250
6.30
2.52
141
7287
5
378
"
629
400
4-72
1.18
144
7288
6
498
980
650
4.10
.631
146
7289
7
625
1408
950
3-59
, .378
148
7290
8
764
1940
1300
3-15
.242
149
7291
9
913
2580
1700
2.75
.162
ISO 1
7292
10
1088
3451
2300
2.51
.109
ISO
7293
ii
1249
"
4262
2800
2.24
.0800
152
7294
12
1374
5057
3400
2.IO
.0619
152
7295
13
1506
"
6146
4000
1.86
.0465
152
7296
3
249
Ef
258
170
7 96
4-68
139
7297
4
353
493
350
6.86
1.96
134
7298
5
487
11
848
550
4-98
.906
137
7299
6
675
"
1410
950
4-32
• 455
133
7300
7
893
"
2160
1400
3-58
.256
140
7301
8
1038
"
2829
1900
3.25
.171
142
7302
9
1187
3588
2400
2.88
.120
144
7303
10
1351
4551
3000
2.53
.0842
145
7304
ii
1517
••
5503
3700
2.33
.0631
148
7305
12
1666
6545
4500
2.19
.0486
147
7306
13
1830
"
7976
5200
1.90
-0365
147
7307
3
267
EE
258
170
7-77
4-57
144
7308
4
38i
493
350
6.65
1.90
140
7309
5
529
"
848
550
4.83
.879
143
73io
6
734
"
1410
950
4.19
.441
145
7311
7
989
»
2160
1400
3.47
.248
147
7312
8
1183
"
2829
1900
3-14
.165
150
7313
9
1335
"
3588
2400
2.78
.116
151
7314
10
1499
"
4551
3000
2.47
.0822
151
7315
ii
1659
««
5503
3700
2.29
.0619
152
7316
12
1811
"
6545
45oo
2.16
.0479
152
7317
13
1988
7976
5200
1.86
.0358
151
Tubular Electric Line Pole Tables 129
Length of Pole, 27 Feet
Sections: 18 feet 6 inches, 6 feet 6 inches, and 5 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
73i8
4
278
///
371
250
6.30
2.52
138
7319
5
378
629
400
4.76
1. 19
140
7320
6
500
"
980
650
4.11
.632
144
7321
7
631
1408
950
3.6o
• 379
147
7322
8
777
"
1940
1300
3.15
.242
148
7323
9
931
"
2580
1700
2.77
.163
149
7324
10
IH3
3451
2300
2.51
.109
149
7325
ii
1276
"
4262
2800
2.24
.0801
151
7326
12
1417
5057
3400
2. II
.0620
151
7327
13
1561
"
6146
4000
1.86
.0465
152
7328
4
356
Eff
493
350
6.86
1.96
131
7329
5
487
848
550
5.01
.910
133
7330
6
678
"
1410
950
4-33
-456
135
7331
7
900
2160
1400
3.6o
• 257
137
7332
8
1051
"
2829
1900
3 25
.171
140
7333
9
1204
?!
3588
2400
2.88
.120
143
7334
10
1375
4551
3000
2.53
.0844
144
7335
ii
1545
"
5503
3700
2.34
.0632
147
7336
12
1709
6545
4500
2.19
.0487
147
7337
13
1884
"
7976
5200
1.90
.0365
147
7338
4
374
EEf
493
350
6.65
1.90
136
7339
5
515
848
550
4.86
.883
138
7340
6
716
1410
950
4.21
• 443
141
7341
7
962
2160
1400
3-49
.249
144
7342
8
1 145
11
2829
1900
3-15
.166
147
7343
9
1301
•«
3588
2400
2.81
.117
149
7344
10
1472
4551
3000
2.47
.0823
149
7345
ii
1637
"
5503
3700
2.29
.0620
150
7346
12
1803
6545
4500
2.16
.0479
ISO
7347
13
1987
"
7976
5200
1.87
.0359
151
7348
4
383
EEE
493
350
6.65
1.90
138
7349
5
528
848
550
4-85
.882
140
7350
6
737
11
1410
950
4.20
.442
142
7351
7
991
2160
1400
3.47
.248
145
7352
8
H93
•
2829
1900
3.14
.165
149
7353
9
1373
««
3588
2400
2.81
.117
150
7354
10
1546
4551
3000
2.47
.0822
150
7355
II
1711
"
5503
3700
2.29
.0619
151
7356
12
1874
ff
6545
4500
2.16
.0479
151
7357
13
2060
"
7976
5200
1.87
.0359
151
1
130
Tubular Electric Line Pole Tables
Length of Pole, 28 Feet
Sections: 19 feet and 10 feet 6 inches
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
P
Load
for
deflec-
tion!)
L
Deflec-
tion for
loadL
D
Factor
R
Factor
m
7358
3
205
//
189
130
8.96
6.89
152
7359
4
285
352
220
6.45
2.93
148
7300
5
391
598
400
5.52
1.38
151
736l
6
514
"
932
600
4.41
• 735
153
7362
7
646
••
1339
900
3.96
• 440
156
7363
8
790
"
1845
1200
3-37
.281
157
7364
9
944
"
2454
I600
3-02
.189
158
7365
10
1126
"
3283
220O
2.79
.127
158
7366
II
1292
««
4054
27OO
2.51
.0931
160
7367
12
1421
"
4810
3200
2.30
.0720
160
7368
13
1558
5846
3900
2. II
.0541
159
7369
3
257
Ef
245
160
8.74
5.46
146
7370
4
365
468
300
6.87
2.29
141
7371
5
503
"
807
550
5.83
1. 06
144
7372
6
697
;• poj
1342
900
4-77
• 530
145
7373
7
922
••
2055
1400
4.19
.299
146
7374
8
1071
"
2691
1800
3-58
.199
149
7375
9
1226
"
3413
2300
3-22
.140
151
7376
10
1395
4329
2900
2.84
.0980
152
7377
II
1567
•«
5234
35oo
2.57
.0735
155
7378
12
1721
"
6226
4200
2.38
.0567
155
7379
13
1891
"
7587
5000
2.13
.0426
155
738o
3
276
EE
245
160
8.53
5-33
151
738i
4
393
11
468
300
6.63
2.21
147
7382
5
547
"
807
550
5-6i
1.02
ISO
7383
6
759
"
1342
900
4.63
.514
152
7384
7
1022
••
2055
1400
4,o6
.289
154
7385
8
1224
"
2691
1800
3.46
.192
158
7386
9
1381
"
3413
2300
3- II
.135
159
7387
10
1551
"
4329
2900
2.77
.0956
159
7388
ii
1716
«•
5234
35oo
2.52
.0720
160
7389
12
1874
"
6226
4200
2.34
• 0557
160
7390
13
2057
7587
5000
2.09
-0417
160
Tubular Electric Line Pole Tables 131
Length of Pole, 28 Feet
Sections: IQ feet, 7 feet, and 5 feet
Maxi-
Load
Deflec-
Number
Size
of
butt
Weight
Thick-
ness
mum
load
for
deflec-
tion D
tion for
loadL
Factor
Factor
P
L
D
R
m
7391
4
287
///
352
220
6.47
2.94
145
7392
5
391
598
400
5-52
1.38
148
7393
6
517
"
932
600
4.42
• 736
I5i
7394
7
653
1339
900
3-97
• 441
154
7395
8
803
44
1845
1200
3-38
.282
156
7396
9
962
••
2454
I6OO
3.02
.189
157
7397
10
1150
44
3283
2200
2.79
.127
157
7398
II
1319
44
4054
27OO
2.52
.0932
159
7399
12
1464
44
4810
3200
2.30
.0720
159
7400
13
1613
"
5846
3900
2. II
.0541
159
7401
4
367
Eff
468
300
6.87
2.29
138
7402
5
503
807
550
5.83
1.06
140
7403
6
700
"
1342
900
4-79
.532
142
7404
7
928
"
2055
1400
4.20
.300
144
7405
8
1084
"
2691
1800
3.60
.200
147
7406
9
1243
••
3413
2300
3.22
.140
ISO
7407
10
1420
"
4329
2900
2.84
.0981
151
7408
ii
1595
44
5234
35oo
2.58
.0736
154
7409
12
1764
"
6226
4200
2.38
.0567
154
7410
13
1945
"
7587
5000
2.13
.0426
155
7411
4
386
EEf
468
300
6.66
2.22
143
7412
5
532
807
550
5-67
1.03
145
7413
6
741
"
1342
900
4.64
.515
148
7414
7
995
"
2055
1400
4-05
.289
151
7415
8
1186
"
2691
1800
3.47
.193
155
74i6
9
1347
»
3413
2300
3-13
.136
156
7417
10
1523
41
4329
2900
2.78
.0957
156
7418
ii
1694
5234
35oo
2.52
.0720
158
7419
12
1866
44
6226
4200
2.34
.0557
159
7420
13
2056
"
7587
5000
2.09
.0418
159
7421
4
395
EEE
468
300
6.66
2.22
144
7422
5
546
44
807
550
5.67
1.03
147
7423
6
762
1342
900
4.64
.515
149
7424
7
1025
44
2055
1400
4.05
.289
152
7425
8
1234
2691
1800
3.46
.192
156
7426
9
1419
••
3413
2300
3 13
.136
158
7427
10
1597
44
4329
2900
2.77
.0956
157
7428
II
1768
44
5234
35oo
2.52
.0720
159
7429
12
1937
44
6226
4200
2.34
.0557
160
7430
13
2128
7587
5000
2.09
.0418
160
132
Tubular Electric Line Pole Tables
Length of Pole, 28 Feet
Sections: 21 feet, 5 feet, and 5 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
7431
4
294
fff
352
220
6.20
2.82
150
7432
5
399
598
4OO
5.36
1-34
152
7433
6
526
932
600
4-31
.718
155
7434
7
662
"
1339
900
3-90
433
156
7435
8
813
1845
1200
3.34
.278
158
7436
9
972
2454
l6oO
2.98
.186
159
7437
10
1163
"
3283
220O
2-75
.125
159
7438
ii
1330
4054
2700
2.49
.0921
160
7439
12
1472
"
4810
3200
2.29
-0715
161
7440
13
1623
5846
3900
2.09
.0537
I6i
7441
4
382
EM
468
300
6.48
2.16
144
7442
5
522
807
550
5-56
I.OI
146
7443
6
728
"
1342
900
4.56
.507
148
7444
7
966
"
2055
1400
4.02
.287
150
7445
8
1124
"
2691
1800
3.47
.193
152
7446
9
1283
«•
3413
2300
3-13
.136
154
7447
10
I46l
4329
2900
2.77
.0956
155
7448
ii
1634
"
5234
35oo
2.52
.0719
157
7449
12
1804
6226
4200
2.34
.0556
158
7450
13
1990
"
7587
5000
2.08
.0416
157
7451
4
396
EEf
468
300
6.39
2.13
148
7452
5
543
807
550
5.48
.996
ISO
7453
6
757
"
1342
900
4.51
.501
152
7454
7
1014
2055
1400
3.96
.283
154
7455
8
1196
"
2691
1800
3-42
.190
157
7456
9
1357
3413
2300
3-08
• 134
158
7457
10
1535
"
4329
2900
2.74
.0946
159
7458
ii
1705
5234
35oo
2.50
.0714
159
7459
12
1876
"
6226
4200
2.32
.0553
160
7460
13
2069
7587
5000
2.07
.0413
159
746i
4
405
EEE
468
300
6.39
2.13
ISO
7462
5
557
"
807
550
5-47
.995
151
7463
6
778
1342
900
4-50
.500
153
7464
7
1044
"
2055
1400
3.96
.283
156
7465
8
1244
"
2691
1800
3-42
.190
158
7466
9
1430
"
3413
2300
3-o8
.134
160
7467
10
1609
"
4329
2900
2.74
.0945
160
7468
ii
1779
11
5234
3500
2.50
.0713
160
7469
12
1947
"
6226
4200
2.32
.0552
161
7470
13
2142
7587
5000
2.07
.0413
160
Tubular Electric Line Pole Tables 133
Length of Pole, 29 Feet
Sections: 20 feet and 10 feet 6 inches
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
7471
3
212
//
180
120
9-48
7.90
160
7472
4
296
336
22O
7-37
3.35
156
7473
5
405
"
570
40O
6.32
1.58
159
7474
6
533
889
600
5.06
.843
161
7475
7
670
"
1277
850
4.30 1 .506
164
7476
8
819
"
1759
1200
3-88
323
165
• 7477
9
978
2340
I60O
3-47
.217
166
7478
10
1167
"
3130
2100
3-05
• 145
1 66
7479
ii
1337
••
3866
2600
2.78
.107
168
7480
12
1471
4587
3100
2.57
.0830
168
748i
13
1613
"
5574
37oo
2.31
.0623
167
7482
3
267
Ef
234
160
9.98
6.24
154
7483
4
38o
447
3oo
7.80
2.60
149
7484
5
523
"
769
500
6.05
1. 21
152
7485
6
725
1279
850
5-15
.606
153
7486
7
960
1959
1300
4-45
•342
154
7487
8
1115
"
2566
1700
3.88
.228
157
7488
9
1274
3254
2200
3-52
.160
159
7489
10
1450
; «bo8j
4127
2800
3.14
.112
1 60
7490
II
1627
4991
3300
2.79
.0844
163
7491
12
1787
: *?K>?.
5936
4000
2.60
.0651
164
7492
13
1963
7234
4800
2.34
.0488
163
7493
3
286
EE
234
160
9.78
6. ii
160
7494
4
408
447
300
7-59
2.53
155
7495
5
568
"
769
500
5-85
1.17
159
7496
6
787
1279
850
5-01
.589
160
7497
7
1060
«•
1959
1300
4-30
.331
163
7498
8
1267
"
2566
1700
3.76
.221
166
7499
9
1430
3254
220O
3-43
.156
167
7500
10
1605
"
4127
2800
3-08
.no
167
7501
II
1776
••
4991
3300
2.74
.0829
168
7502
12
1939
5936
4000
2.57
.0642
169
7503
13
2129
7234
4800
2.30
0480
167
134
Tubular Electric Line Pole Tables
Length of Pole, 29 Feet
Sections: 18 feet 6 inches, 7 feet, and 6 feet 6 inches
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadZ,
Factor
Factor
P
L
D
R
m
7504
4
291
///
336
220
7.74
3.52
147
7505
5
395
570
400
6.60
1.65
148
75o6
6
524
"
889
600
5-23
.872
153
7507
7
663
"
1277
850
4-41
.519
158
75o8
8
817
"
1759
1200
3.96
•330
160
7509
9
980
•«
2340
I600
3.54
.221
161
7Sio
10
H73
*f
3i3o
2IOO
3. ii
.148
162
751 1
ii
1348
'{
3866
2600
2.83
.109
164
7512
12
1500
"
4587
3100
2.6o
.0838
165
7513
13
1654
"
5574
3700
2.33
.0630
165
7514
4
368
Eff
447
300
8.40
2.8o
138
7515
5
504
769
500
6.45
1.29
139
75i6
6
702
11
1279
850
5.46
.642
143
7517
7
931
"
1959
1300
4.68
.360
146
75i8
8
1091
"
2566
1700
4-05
.238
ISO
7519
9
1254
••
3254
2200
3.65
.166
153
7520
10
1435
"
4127
2800
3.25
.116
155
7521
II
1616
"
4991
3300
2.86
.0866
158
7522
12
1792
"
5936
4000
2.66
.0665
159
7523
13
1978
"
7234
4800
2.40
.0501
160
7524
4
387
EEf
447
300
8.04
2.68
142
7525
5
534
"
769
500
6.15
1.23
144
7526
6
743
"
1279
850
5.23
.615
148
7527
7
998
"
1959
1300
4.46
.343
152
7528
8
1192
"
2566
1700
3.84
.226
157
7529
9
1358
3254
2200
3.50
.159
159
7530
10
1539
"
4127
2800
3-14
.112
160
7531
II
1715
"
4991
3300
2.78
.0842
162
7532
12
1894
"
5936
4000
2.60
.0649
164
7533
13
2088
"
7234
4800
2.34
.0487
164
7534
4
399
EEE
447
300
7.98
2.66
145
7535
5
551
"
769
500
6.!S
1.23
147
7536
6
770
"
1279
850
5.20
.612
151
7537
7
1037
11
1959
1300
4-43
• 341
155
7538
8
1255
"
2566
1700
3.83
.225
161
7539
9
1452
«•
3254
2200
3.48
.158
163
7540
10
1635
4127
2800
3.14
.112
163
7541
II
1811
"
4991
3300
2.77
.0839
165
7542
12
1986
"
5936
4000
2.59
.0648
166
7543
13
2182
7234
4800
2.33
.0486
166
Tubular Electric Line Pole Tables 135
Length of Pole, 29 Feet
Sections: 21 feet, 7 feet, and 4 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadZ,
Factor
Factor
P
L
D
R
m
7544
4
303
fff
336
220
7.24
3-29
158
7545
5
413
570
4OO
6.24
1.56
160
7546
6
544
11
889
600
S.oo
.833
163
7547
7
685
"
1277
850
4.26
.501
165
7548
8
841
1759
1200
3.85
.321
166
7549
9
1006
"
2340
I600
3.46
.216
167
7550
10
1 202
"
3130
2IOO
3-02
.144
166
7551
ii
1377
3866
2600
2.78
.107
168
7552
12
1523
41
4587
3IOO
2.56
.0827
169
7553
13
1676
"
5574
37oo
2.29
.0620
168
7554
4
391
Eff
447
300
7.59
2.53
I5i
7555
5
536
769
500
5-90
1.18
154
7556
6
746
"
1279
850
5-03
.592
155
7557
7
989
11
1959
1300
4.36
.335
157
7558
8
1152
"
2566
1700
3.8l
.224
159
7559
9
1317
»
3254
2200
3-48
.158
161
756o
10
1500
"
4127
2800
3- n
.in
162
7501
ii
1681
"
4991
3300
2.75
.0834
164
7562
12
1855
"
5936
4000
2.58
.0646
165
7563
13
2044
'*
7234
4800
2.32
.0483
164
7564
4
410
EEf
447
300
7-44
2.48
157
7565
5
566
11
769
500
5.8o
1.16
159
7566
6
787
"
1279
850
4-94
.581
161
7567
7
1057
"
1959
1300
4.26
.328
163
7568
8
1253
"
2566
1700
3-74
.220
1 66
7569
9
1421
3254
2200
3-41
.155
167
7570
10
1604
"
4127
2800
3.05
.109
167
7571
II
1781
4991
3300
2.72
.0824
168
7572
12
1956
"
5936
4000
2.56
.0639
109
7573
13
2154
"
7234
4800
2.29
.0477
168
7574
4
418
ERR
447
300
7-44
2.48
157
7575
5
577
"
769
500
5-75
1. 15
160
7576
6
804
"
1279
850
4-94
.581
161
7577
7
1080
41
1959
1300
4.26
.328
164
7578
8
1292
"
2566
1700
3-74
.220
167
7579
9
1479
«•
3254
2200
3.41
.155
168
758o
10
1663
4127
2800
3.05
.109
167
758i
ii
1840
"
4991
3300
2.72
.0824
168
7582
12
2013
"
5936
4OOO
2.56
.0639
169
7583
13
2213
7234
4800
2.29
.0478
168
136
Tubular Electric Line Pole Tables
Length of Pole, 30 Feet
Sections: 21 feet and 10 feet 6 inches
Number
Size
of
butt
Weight
Thick
ness
Maxi-
mum
load
P
Load
for
deflec-
tion D
L
Deflec-
tion for
loadL
D
Factor
R
Factor
m
7584
3
220
//
172
no
9-91
9.oi
168
7585
4
306
321
220
8.40
3-82
164
7586
5
420
545
350
6.30
i. 80
167
7587
6
552
849
55o
5.29
.962
170
7588
7
693
"
1 220
800
4.62
.578
172
7589
8
847
1681
IIOO
4.06
.369
173
7590
9
1012
"
2236
1500
3-72
248
174
7591
10
I2O7
2991
2OOO
3.32
.166
174
7592
ii
1383
»
3694
2500
3.08
.123
176
7593
12
1520
M
4383
290O
2.75
.0949
176
7594
13
1667
"
5326
3600
2.57
.0713
176
7595
3
277
Ef
223
ISO
10.6
7-09
162
7596
4
395
>t
427
280
8.26
2.95
157
7597
5
544
735
500
6.85
1-37
160
7598
6
754
"
1222
800
5.50
.688
161
7599
7
998
••
1872
I2OO
4.67
.389
163
7600
8
1158
"
2452
1600
4.16
.260
165
7601
9
1323
3110
2IOO
3-82
.182
167
7602
10
1505
\ "OG£
3944
26OO
3-33
.128
168
7603
ii
1687
«'
4769
3200
3-08
.0963
171
7604
12
1852
"
5672
3800
2.82
.0743
171
7605
13
2035
"
6913
4500
2.51
.0557
171
7606
3
297
EE
223
150
10.4
6.96
168
7607
4
423
427
280
8.06
2.88
163
7608
5
588
"
735
500
6.70
1-34
167
7609
6
816
1222
Soo
5-38
.672
168
7610
7
1098
«
1872
I2OO
4-54
.378
171
7611
8
1310
"
2452
I600
4-05
.253
174
7612
9
1478
"
3HO
2IOO
3-74
.178
175
7613
10
1660
"
3944
2600
3.28
.126
175
7614
II
1836
«
4769
3200
3-03
.0948
176
7615
12
2005
"
5672
3800
2.79
.0734
176
7616
13
22OI
6913
4500
2.47
.0549
175
Tubular Electric Line Pole Tables 137*
Length of Pole, 30 Feet
Sections: 18 feet 6 inches, g feet 6 inches, and 5 feet
Number
Size
of
butt
Weight
Thick
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
7617
4
301
///
321
220
8.98
408
156
7618
5
411
545
350
6.65
1.90
159
7619
o
544
"
849
550
5-50
I.OO
164
7620
7
688
"
1220
800
4.78
.597
167
7621
8
847
"
1681
IIOO
4.18
.380
169
7622
9
1016
2236
1500
3.8i
-254
170
7623
10
1214
"
2991
2000
3-42
.171
170
7624
II
1398
"
3694
2500
3-13
.125
173
7625
12
1553
4383
2900
2.79
.0963
174
7626
13
1709
•"c<>
5326
3600
2.61
.0724
173
7627
4
379
Eff
388
250
8.15
3.26
148
7628
5
520
723
5oo
7-45
1.49
ISO
7629
6
722
"
1222
800
5.96
• 745
153
7630
7
957
1872
1200
5-02
.418
155
7631
8
1 121
. r*^v
2452
1600
4.42
.276
159
7632
9
1290
«•
3HO
2IOO
4-03
.192
162
7633
10
1477
3944
2600
3-48
.134
163
7634
II
1666
"
4769
3200
3-20
.100
166
7635
12
1846
"
5672
3800
2.92
.0768
167
7636
13
2033
M
6913
45oo
2.60
.0577
166
7637
4
404
EEf
427
280
8.65
3-09
154
7638
5
560
735
500
7.05
1. 41
158
7639
6
778
1222
800
5.65
.706
160
7640
7
1048
"
1872
1200
4.72
• 393
164
7641
8
1259
2452
1600
4.14
.259
169
7642
9
1431
<•
3HO
2IOO
3.82
.182
170
7643
10
1618
"
3944
2600
3.35
.129
171
7644
II
1801
"
4769
3200
3.08
.0964
172
7645
12
1983
"
5672
3800
2.83
.0744
173
7646
13
2183
"
6913
4500
2.52
.0559
172
7647
4
414
EEE
427
280
8.62
3.o8
156
7648
5
573
"
735
500
7.05
1.41
159
7649
6
799
1222
800
5.64
• 70S
162
7650
7
1077
"
1872
1200
4.72
• 393
165
7651
8
1307
"
2452
I600
4.14
.259
170
7652
9
1503
»
3HO
2IOO
3.82
.182
172
7653
10
1692
"
3944
2600
3-33
.128
172
7654
II
1875
"
4769
3200
3.o8
.0963
173
7655
12
2054
"
5672
3800
2.83
.0744
174
7656
13
2256
6913
4500
2.52
-0559
173
138 Tubular Electric Line Pole Tables
Length of Pole, 30 Feet
Sections: 19 feet, 7 feet, and 7 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
7657
4
299
///
321
220
8.93
4.06
152
7658
5
406
545
350
6.65
1.90
154
7659
6
539
"
849
550
5.5o
1. 00
159
7660
7
682
1220
800
4-77
.596
164
7661
8
841
IpP?
1681
1 100
4-17
• 379
167
7662
9
1009
"
2236
1500
3.8i
.254
169
7663
10
1207
2991
2OOO
3-40
.170
169
7664
ii
1387
"
3694
2500
3-13
.125
171 -
7665
12
1545
4383
29OO
2.79
.0962
173
7666
13
1704
fSj
5326
3600
2.60
.0723
173
7667
4
379
Eff
408
280
9.04
3-23
143
7668
5
518
735
5oo
7-45
1.49
144
7669
6
721
"
1222
800
5.92
• 740
I48
7670
7
957
1872
I2OO
4.98
.415
151
7671
8
1 122
r" oo
2452
1000
4.38
.274
156
7672
9
1290
••
3HO
2100
4.01
.191
159
7673
10
1477
3944
26OO
3.48
.134
161
7674
ii
1663
"
4769
3200
3-18
.0994
164
7675
12
1845
5672
3800
2.91
.0765
167
7676
13
2036
"
6913
4500
2.58
.0574
166
7677
4
398
EEf
427
280
8.65
3-09
148
7678
5
548
735
500
7-15
1.43
148
7679
6
763
"
1222
800
5.67
.709
153
7680
7
1024
"
1872
1 200
4-74
• 395
157
7681
8
1224
"
2452
1600
4.16
.260
163
7682
9
1394
••
3HO
2100
3-84
.183
166
7683
10
1580
"
3944
26OO
3-35
.129
167
7684
ii
1762
"
4769
3200
3.09
.0966
169
7685
12
1947
5672
3800
2.83
.0746
172
7686
13
2147
"
6913
45oo
2.51
.0558
170
7687
4
4ii
EEE
427
280
8.60
3 07
151
7688
5
567
735
5oo
7-05
1.4*
153
7689
6
792
"
1222
800
5.63
.704
157
7690
7
1066
11
1872
1200
4.70
.392
161
7691
8
1291
"
2452
I60O
4-14
.259
167
7692
9
1495
«
3IIO
2100
3.82
.182
170
7693
10
1684
"
3944
2600
3-33
.128
171
7694
ii
1866
"
4769
3200
3.o8
.0962
172
7695
12
2046
"
5672
3800
2.82
.0743
173
7696
13
2248
6913
4500
2.51
.0557
173
Tubular Electric Line Pole Tables 139
Length of Pole, 30 Feet
Sections: 21 feet, 7 feet, and 5 feet
Maxi-
Load
Deflec-
Number
Size
of
butt
Weight
Thick-
ness
mum
load
for
deflec-
tion D
tion for
loadL
Factor
Factor
P
L
D
R
m
7697
4
309
///
321
220
8.40
3.82
162
7698
5
420
545
350
6.30
i. 80
164
7699
6
555
11
849
550
5-30
.964
167
7700
7
700
1220
800
4.62
• 578
170
77oi
8
860
"
1681
IIOO
4.07
• 370
172
7702
9
1030
««
2236
1500
3 74
.249
173
7703
10
1231
2991
2OOO
3-32
.166
173
7704
ii
1411
"
3694
2500
3.08
.123
175
7705
12
1563
"
4383
2900
2.75
.0949
175
7706
13
1722
"
5326
3600
2.57
.0713
175
7707
4
397
Eff
427
280
8.29
2.96
154
77o8
5
544
735
500
6.85
1.37
156
7709
6
757
41
1222
800
5-52
.690
159
7710
7
1004
"
1872
1200
4-67
.389
160
771 1
8
II7I
"
2452
1600
4.16
.260
164
7712
9
1340
••
3110
2IOO
3.84
.183
166
7713
10
1529
"
3944
2600
3-33
.128
167
7714
ii
1715
"
4769
3200
3.o8
.0964
170
7715
12
1895
5672
3800
2.82
.0743
170
7716
13
2089
11
6913
4500
2.51
.0557
170
7717
4
416
EEf
427
280
8.09
2.89
160
7718
5
573
735
500
6.70
1.34
162
7719
6
798
"
1222
800
5.38
.673
164
7720
7
1071
14
1872
1200
4-55
.379
167
7721
8
1272
"
2452
I600
4-05
.253
171
7722
9
1444
«•
3110
2IOO
3-74
.178
173
7723
10
1633
14
3944
2600
3-28
.126
173
7724
ii
1815
"
4769
3200
3-04
.0949
175
7725
12
1997
"
5672
3800
2.79
.0734
174
7726
13
2200
"
6913
4500
2.48
-0550
175
7727
4
425
EEE
427
280
8.06
2.88
161
7728
5
587
"
735
500
6.70
1.34
164
7729
6
819
"
1222
800
5-38
.673
166
7730
7
IIOI
"
1872
I20O
4-54
.378
169
7731
8
1320
"
2452
1600
4-05
.253
173
7732
9
1517
••
3110
2100
3-74
.178
174
7733
10
1707
11
3944
260O
3.28
.126
174
7734
ii
1889
"
4769
3200
3-03
.0948
175
7735
12
2068
"
5672
3800
2.79
.0734
175
7736
13
2272
6913
4500
2.48
.0550
175
140 Tubular Electric Line Pole Tables
Length of Pole, 31 Feet
Sections: 18 feet 6 inches, 10 feet 6 inches, and 5 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
load!.
Factor
Factor
P
L
D
R
m
7737
4
308
///
307
200
9.46
4-73
163
7738
5
421
522
350
7.70
2.20
166
7739
6
559
"
813
550
6.38
1.16
170
7740
7
707
1168
800
5-49
.686
174
7741
8
871
"
1609
IIOO
4.80
.436
176
7742
9
1045
"
2141
1400
4.09
.292
178
7743
10
1248
2864
1900
3-72
.196
178
7744
n
1438
"
3537
2400
3-43
.143
181
7745
12
1599
"
4196
2800
3-o8
.110
181
7746
13
1759
"
5ioo
3400
2.82
.0829
180
7747
4
386
Eff
352
220
8.38
3.8i
154
7748
5
531
657
450
7.83
1-74
157
7749
6
736
"
III5
750
6.50
.866
159
7750
7
976
"
1738
1 200
5-83
.486
161
7751
8
H45
"
2347
1600
5.12
.320
165
7752
9
1319
««
2977
2OOO
4.44
.222
168
7753
10
1511
"
3776
2500
3.88
.155
169
7754
II
1707
"
4566
3000
3-45
.115
173
7755
12
1891
"
5431
3600
3-i8
.0884
174
7756
13
2083
6618
4500
2.99
.0665
173
7757
4
415
EEf
409
280
IO.O
3-58
161
7758
5
575
"
704
450
7.38
1.64
164
7759
6
798
1170
800
6.51
.814
167
7760
7
1076
"
1792
1200
5-44
.453
171
7761
8
1297
2347
1600
4-75
-297
176
7762
9
1474
2977
20OO
4.18
.209
178
7763
10
1666
"
3776
2500
3.68
.147
178
7764
II
1856
"
4566
3000
3-30
.110
180
7765
12
2044
"
5431
3600
3-07
.0852
181
7766
13
2249
"
6618
4500
2.88
.0640
180
7767
4
424
EEE
409
280
IO.O
3.58
162
7768
5
588
704
450
7.34
1.63
166
7769
6
819
"
1170
800
6.51
.814
168
7770
7
1106
"
1792
I20O
5.42
• 452
172
7771
8
1345
"
2347
I6OO
4-75
.297
177
7772
9
1547
"
2977
2OOO
4.18
.209
179
7773
10
1740
"
3776
2500
3-68
.147
179
7774
n
1930
"
4566
3OOO
3-30
.no
181
7775
12
2115
"
5431
3600
3.07
.0852
182
7776
13
2321
6618
4500
2.88
.0640
180
Tubular Electric Line Pole Tables 141
Length of Pole, 31 Feet
Sections: 21 feet, 6 feet 6 inches, and 6 feet 6 inches
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
7777
4
314
///
307
200
8.88
4-44
164
7778
5
426
522
350
7-32
2.09
165
7779
6
564
"
813
550
6. ii
I. ii
170
778o
7
712
1168
800
5-33
.666
174
7781
8
877
"
1609
IIOO
4.68
.425
177
7782
9
1051
"
2141
1400
3-99
.285
178
7783
10
1257
2864
1900
3.63
.191
178
7784
II
1441
"
3537
2400
3-36
.140
180
7785
12
1601
"
4196
2800
3-05
.109
182
7786
13
1765
"
5100
3400
2.77
.0816
182
7787
4
402
Eff
409
280
9.69
3-46
155
7788
5
550
704
450
7-25
1.61
156
7789
6
766
11
1170
800
6.43
.804
160
7790
7
1016
1792
1200
5-42
• 452
163
7791
8
1188
.. '&_7p
2347
I600
4.82
.301
167
7792
9
1361
2977
2000
4.22
.211
170
7793
10
1555
"
3776
2500
3-70
.148
172
7794
ii
1746
«•
4566
3OOO
3-33
.III
175
7795
12
1933
"
5431
3600
3-07
.0854
176
7796
13
2133
6618
45oo
2.88
.0641
176
7797
4
420
EEf
409
280
9-41
3-36
159
7798
5
577
"
704
450
7.02
1.56
161
7799
6
804
"
1170
800
6.26
.782
165
7800
7
1079
"
1792
1 200
5-26
• 438
169
7801
8
1282
"
2347
1600
4.66
.291
174
7802
9
1458
•«
2977
2OOO
4.10
.205
176
7803
10
1651
"
3776
2500
3.63
.145
177
7804
ii
1838
"
4566
3000
3.27
.109
180
78os
12
2027
"
5431
3600
3-03
.0841
180
7806
13
2236
"
6618
4500
2.83
.0629
180
7807
4
432
EEE
409
280
9.38
3-35
163
7808
5
595
704
450
7.02
1.56
164
7809
6
831
"
1170
800
6.22
.778
168
7810
7
1117
11
1792
1 200
5-24
.437
172
7811
8
1344
"
2347
1600
4.64
.290
178
7812
9
1552
«
2977
2OOO
4.08
.204
180
7813
10
1747
"
3776
2500
3.60
.144
180
7814
ii
1934
"
4566
3000
3-27
.109
182
78iS
12
2I2O
"
5431
3600
3-02
.0840
182
7816
13
2330
6618
45oo
2.83
.0629
182
142
Tubular Electric Line Pole Tables
Length of Pole, 32 Feet
Sections: 18 feet 6 inches, 9 feet 6 inches, and 7 feet
Maxi-
Load
Deflec-
Number
Size
of
butt
Weight
Thick-
ness
mum
load
for
deflec-
tion D
tion for
loadL
Factor
Factor
P
L
D
R
m
7817
4
312
///
295
200
II. O
5.5o
165
7818
5
426
500
350
8.93
2.55
167
7819
6
566
"
780
500
6.70
1.34
173
7820
7
718
"
1120
750
5-92
.789
178
7821
8
885
"
1544
IOOO
5.00
.500
181
7822
9
1063
'«
2053
1400
4.68
• 334
182
7823
10
1272
"
2747
1800
4 03
.224
183
7824
ii
1466
"
3392
2300
3-75
.163
186
12
1634
"
4025
2700
3-40
.126
188
7826
13
1801
"
4891
3300
3 12
.0946
187
7827
4
390
Eff
323
220
9.86
4.48
155
7828
5
535
602
400
8.16
2.04
156
7829
6
743
11
1022
700
7.07
1. 01
160
7830
7
986
1593
IIOO
6.22
.565
164
7831
8
H59
"
2252
1500
5-55
• 370
1 68
7832
9
1337
"
2856
IQOO
4-86
.256
172
7833
10
1534
"
3622
2400
4-30
.179
174
7834
ii
1734
"
438o
2900
3.83
.132
178
7835
12
1927
"
5209
3500
3-54
.101
181
7836
13
2124
"
6348
4200
3.20
.0762
180
7837
4
416
EEf
392
250
10.5
4.19
160
7838
7839
i
575
800
«
675
1 122
450
750
8.60
7.10
1.91
.946
162
167
7840
7
1077
"
1719
IIOO
5-75
.523
171
7841
8
1297
"
2252
1500
5-13
• 342
178
7842
9
1478
«<
2856
1900
4-54
.239
181
7843
10
1675
"
3622
2400
4.06
.169
181
7844
ii
1869
"
4380
2900
3.65
.126
184
7845
12
2064
"
5209
3500
3-41
.0973
186
7846
13
2274
"
6348
4200
3-07
.0731
186
7847
4
429
ERE
392
250
10.4
4.17
164
7848
s
594
11
675
450
8.55
1.90
166
7849
6
829
"
1 122
750
7.06
.941
170
7850
7
1118
"
1719
IIOO
5.73
.521
175
7851
8
1364
"
2252
1500
S.io
• 340
182
7852
9
1579
••
2856
1900
4.52
.238
185
7853
10
1779
"
3622
2400
4-03
.168
185
7854
ii
1973
"
4380
2900
3.65
.126
187
7855
12
2164
"
5209
35oo
3-40
.0970
187
7856
13
2376
6348
4200
3-07
.0730
188
Tubular Electric Line Pole Tables 143
Length of Pole, 32 Feet
Sections: 21 feet, 7 feet, and 7 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
7857
4
320
///
295
200
10.2
5. ii
168
7858
5
435
500
350
8.44
2.41
170
7859
6
577
"
780
500
6.35
1.27
175
7860
7
729
"
1 120
750
5-71
.761
180
7861
8
898
"
1544
IOOO
4.85
.485
183
7862
9
1077
"
2053
1400
4-55
.325
185
7863
10
1288
2747
1800
3-92
.218
185
7864
ii
1478
"
3392
2300
3-68
.160
187
7865
12
1644
4025
2700
3-35
.124
190
7866
13
1813
"
4891
33oo
3-o6
.0928
189
7867
4
409
Eff
392
250
10. I
4.02
159
7868
5
559
675
450
8.37
1.86
* 160
7869
6
778
"
1 122
750
6.97
.929
164
7870
7
1033
1719
IIOO
5-74
.522
167
7871
8
1209
"
2252
1500
5-19
.346
172
7872
9
1387
<•
2856
1900
4.60
.242
175
7873
10
1586
3622
2400
4.08
.170
177
7874
ii
1783
"
4380
2900
3.68
.127
181
7875
12
1976
"
5209
35oo
3-42
.0976
184
7876
13
2181
"
6348
4200
3.07
.0732
183
7877
4
428
EEf
392
250
9.70
3.88
164
7878
5
589
675
450
8.10
i. 80
165
7879
6
820
"
1122
750
6.74
.898
109
7880
7
1 100
"
1719
IIOO
5-52
.502
174
7881
8
1310
11
2252
1500
5.oo
.333
179
7882
9
1491
•>
2856
1900
4-45
.234
182
7883
10
1690
"
3622
2400
3.96
.165
183
7884
ii
1882
"
4380
2900
3.6o
.124
185
788s
12
2078
"
5209
35oo
3-35
• 0957
188
7886
13
2291
11
6348
4200
3.oi
.0717
187
7887
4
441
EEE
392
250
9.65
3-86
167
7888
5
608
11
675
450
8.06
1.79
169
7889
6
849
"
1 122
750
6.70
.893
173
7890
7
1142
"
1719
IIOO
5-49
• 499
178
7891
8
1378
"
2252
1500
4-97
• 331
184
7892
9
1593
"
2856
1900
4-43
.233
186
7893
10
1793
"
3622
2400
3-94
.164
187
7894
ii
1986
"
4380
2900
3.6o
.124
188
7895
12
2177
11
5209
3500
3-34
.0955
189
7896
13
2393
6348
4200
3-01
.0716
189
144 Tubular Electric Line Pole Tables
Length of Pole, 32 Feet
Sections: 21 feet, 10 feet, and 4 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
load L
Factor
Factor
P
L
D
R
m
7897
4
326
///
295
200
10.14
5-07
175
7898
5
445
500
350
8.33
2.38
178
7899
6
588
780
500
6.30
1.26
182
7900
7
742
"
1120
750
5.67
.756
185
7901
8
912
1544
IOOO
4.83
.483
186
7902
9
1092
"
2053
1400
4-54
.324
188
7903
10
1304
"
2747
1800
3-91
.217
187
7904
II
1498
3392
2300
3.66
. 159 i 190
7905
12
1660
"
4025
2700
3-32
. 123 i 191
7906
13
1825
4891
3300
3-o6
.0927
191
790?
4
414
Eff
392
250
9-95
3-98
166
7908
5
569
675
450
8.24
1.83
169
7909
6
790
" .
1122
750
6.89
.918
171
7910
7
1046
1719
IIOO
5.69
.517
173
79"
8
1222
"00*
2252
1500
5.i6
• 344
176
7912
9
1403
«
2856
1900
4.56
.240
179
7913
10
1602
11
3622
2400
4.06
.169
180
7914
II
1803
"
4380
2900
3-65
.126,
184
7915
12
1991
5209
3500
3-41
.0974
185
7916
13
2193
6348
4200
3-07
.0731
185
7917
4
441
EEf
392
250
9 58
3.83
174
7918
5
611
"
675
450
7-97
1-77
177
7919
6
849
' **O£l
1 122
750
6.64
.885
180
7920
7
1142
"
1719
IIOO
5.46
.496
183
7921
8
1367
2252
1500
4-95
.330
187
7922
9
I55i
2856
1900
4-41
.232
188
7923
10
1750
"
3622
2400
3-94
.164
189
7924
II
1945
"
4380
2900
3-57
.123
190
7925
12
2136
5209
35oo
3-34
.0953
191
7926
13
2351
pooj
6348
4200
3-00
.0715
191
7927
4
449
EEE
392
250
9-58
3-83
174
7928
5
622
11
675
450
7-97
1.77
178
7929
6
866
"
1 122
750
6.64
.885
180
7930
7
1166
"
1719
IIOO
5.46
.496
183
7931
8
1406
"
2252
1500
4-95
.330
188
7932
9
1609
••
2856
1900
4.41
.232
189
7933
10
1809
"
3622
2400
3.94
.164
189
7934
II
2004
"
4380
2900
3.57
.123
190
7935
12
2193
"
5209
3500
3-34
.0953
191
7936
13
2409
6348
4200
3-00
.0715
191
Tubular Electric Line Pole Tables 145
Length of Pole, 33 Feet
Sections: 18 feet 6 inches, 10 feet 6 inches, and 7 feet
Number
Size
of
butt
Weight
Thick
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadZ,
Factor
Factor
P
L
D
R
m
7937
4
320
///
283
190
12.0
6.31
172
7938
5
437
481
300
8.73
2.91
174
7939
6
58o
"
749
500
7.60
1.52
180
7940
7
737
"
1076
700
6.28
.897
185
7941
8
909
"
1483
IOOO
5-68
.568
188
7942
9
1092
"
1973
1300
4-93
• 379
190
7943
10
1306
"
2639
1800
4-57
.254
190
7944
ii
1506
3259
2200
4-07
.185
193
7945
12
1680
"
3867
260O
3.69
.142
196
7946
13
1850
4699
3100
3-32
.107
195
7947
4
398
Eff
298
200
10.3
5-17
162
7948
5
546
556
350
8.23
2.35
163
7949
6
758
"
943
650
7-54
1.16
167
7950
7
1005
"
1470
IOOO
6.49
.649
170
7951
8
1183
| "oo>
2112
1400
5-94
.424
175
7952
9
1366
"
2744
1800
5-26
.292
179
7953
10
1568
"
3480
2300
4-69
.204
181
7954
ii
1775
"
4208
2800
4.20
.150
185
7955
12
1972
"
5005
3300
3.8o
• US
188
7956
13
2174
"
6099
4000
3-47
.0868
187
7957
4
426
EEf
377
250
12. 0
4.80
167
7958
5
590
649
450
9.8l
2.18
169
7959
6
820
1078
700
756
1. 08
174
7960
7
1106
"
1652
IIOO
6.55
.595
179
796i
8
1335
"
2163
1400
5-43
.388
185
7962
9
1521
2744
1800
4.88
.271
188
7963
IO
1724
348o
2300
4-39
.191
189
7964
II
1924
"
4208
2800
4.00
.143
192
7965
12
2125
"
5005
3300
3.63
.110
194
7966
13
2340
"
6099
4000
3-31
.0828
193
7967
4
439
EEE
377
250
12. 0
4-78
170
7968
5
609
"
649
450
9-77
2.17
173
7969
6
849
"
1078
700
7-49
1.07
177
7970
7
1147
"
1652
IIOO
6.52
• 593
182
7971
8
1402
"
2163
1400
5.40
.386
189
7972
9
1623
»
2744
1800
4.86
.270
192
7973
10
1827
"
3480
2300
4-39
.191
192
7974
ii
2027
"
4208
2800
4.00
.143
194
7975
12
2224
"
5005
3300
3.63
.no
195
7976
13
2441
6099
4000
3-31
.0827
IPS
146 Tubular Electric Line Pole Tables
Length of Pole, 33 Feet
Sections: 21 feet, 10 feet, and 5 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
ft
R
m
7977
4
332
///
283
190
II. 0
5-8o
179
7978
5
453
481
300
8.16
2.72
183
7979
6
599
"
749
500
7.20
1.44
187
7980
7
757
"
1076
700
6.01
.859
191
7981
8
931
"
1483
IOOO
5.48
• 548
193
7982
9
IH5
«
1973
1300
4-77
.367
194
7983
10
1333
11
2639
1800
4-43
.246
194
7984
II
1532
11
3259
2200
3.98
.181
197
7985
12
1700
11
3867
26OO
3.64
.140
198
7986
13
1871
pSlj
4699
3100
3-26
.105
198
7987
4
420
Eff
369
250
ii. 5
4-59
169
7988
5
576
if
649
450
9-50
2. II
173
7989
6
801
"
1078
700
7-35
1.05
175
7990
7
1061
"
1652
IIOO
6.52
.593
178
7991
8
1241
"
2163
1400
5-52
.394
182
7992
9
1426
2744
1800
4-93
.274
184
7993
10
1631
"
348o
2300
4-44
.193
186
7994
II
1837
4208
2800
4.03
.144
190
7995
12
2032
"
5005
3300
3-66
.III
191
7996
13
2238
: VP°C
6099
4000
3.32
.0830
191
7997
4
447
EEf
377
250
II. 0
4-39
177
7998
5
618
11
649
450
9.09
2.02
181
7999
6
860
"
1078
700
7.07
1. 01
184
8000
7
H57
"
1652
IIOO
6.22
.565
188
8001
8
1386
"
2163
1400
5-24
.374
193
8002
9
1574
«
2744
1800
4-73
.263
194
8003
10
1779
"
3480
2300
4.28
.186
195
8004
II
1979
"
4208
2800
3-92
.140
196
8005
12
2177
"
5005
3300
3.56
.108
197
8006
13
2396
j **9oe
6099
4000
3-24
.0809
196
8007
4
456
EEE
377
250
II. 0
4.38
178
8008
5
632
"
649
450
9.09
2.02
182
8009
6
881
1078
700
7.07
1. 01
185
8010
7
1187
"
1652
IIOO
6.20
.564
189
Son
8
1434
"
2163
1400
5.24
.374
194
8012
9
1647
2744
1800
4-73
.263
195
8013
10
1853
"
3480
2300
4.28
.186
196
8014
ii
2053
"
4208
2800
3-89
.139
197
8015
12
2248
"
5005
33oo
3.56
.108
198
8016
13
2469
6099
4000
3-23
.0808
197
Tubular Electric Line Pole Tables 147
Length of Pole, 34 Feet
Sections: 19 feet 6 inches, 10 feet 6 inches, and 7 feet
. Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
8017
4
331
///
273
180
12. 5
6.95
179
8018
5
451
462
300
9.66
3-22
182
8019
6
599
"
721
500
8.45
1.69
188
8020
7
760
44
1036
700
6.98
• 997
193
8021
8
938
"
1427
950
6.01
.633
196
8022
9
1126
M
1898
1300
5.49
.422
198
8023
10
1346
44
2539
1700
4.81
.283
198
8024
ii
1552
14
3136
2IOO
4-33
.206
2OI
8025
12
1730
44
3721
2500
3-98
.159
204
8026
13
1905
"
4522
3000
3.6o
.120
203
8027
4
413
Eff
298
200
II. 3
5-66
169
8028
5
566
u
556
350
9-03
2.58
170
8029
6
787
"
943
650
8.32
1.28
174
8030
7
1043
44
1470
IOOO
7-14
.714
178
8031
8
1226
44
2082
1400
6.57
.469
183
8032
9
1415
••
2640
1800
5.83
.324
187
8033
10
1623
44
3348
22OO
4-97
.226
189
8034
II
1835
"
4049
27OO
4-51
.167
193
8035
12
2038
4816
32OO
4.10
.128
195
8036
13
2246
"
5869
3900
3.76
.0965
195
8037
4
441
EEf
362
250
13-2
5-29
175
8038
5
610
"
624
400
9.64
2.41
177
8039
6
849
44
1038
700
8.33
1. 19
181
8040
7
1 144
1589
IIOO
7-27
.661
187
8041
8
1378
44
2082
1400
6.05
• 432
193
8042
9
1570
44
2640
1800
5-44
.302
196
8043
10
1778
44
3348
220O
4.69
.213
197
8044
ii
1984
44
4049
2700
4-32
.160
200
8045
12
2190
"
4816
3200
3-94
.123
201
8046
13
2412
44
5869
3900
3.6o
.0924
2OI
8047
4
454
EEE
362
250
13.2
5-27
178
8048
5
629
44
624
400
9.60
2.40
181
8049
6
878
44
1038
700
8.33
1. 19
185
8050
7
1185
"
1589
IIOO
7-24
.658
190
8051
8
1446
44
2082
1400
6. 02
• 430
197
8052
9
1671
««
2640
1800
5-42
.301
200
8oS3
10
1882
14
3348
220O
4.69
.213
200
8054
ii
2087
44
4049
2700
4-29
.159
203
8055
12
2289
44
4816
3200
3-94
.123
203
8056
13
2513
44
5869
3900
3-6o
.0923
203
1
148
Tubular Electric Line Pole Tables
Length of Pole, 34 Feet
Sections: 21 feet, 9 feet 6 inches, and 6 feet 6 inches
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor .
P
L
D
R
m
8057
4
336
///
273
180
12. 0
6.64
182
8058
5
459
462
300
9-30
3-10
185
8059
6
608
"
721
500
8.20
1.64
190
8060
7
769
11
1036
700
6.82
• 974
195
8061
8
947
"
1427
95o
5.89
.620
198
8062
9
1136
1898
1300
5.40
• 415
200
8063
10
1359
"
2539
1700
4.73
.278
200
8064
ii
1563
3136
2IOO
4.28
.204
2O2
8065
12
1738
"
3721
2500
3.93
.157
205
8066
13
1914
"
4522
3000
3 54
.118
2O4
8067
4
425
Eff
337
220
ii. 6
5-29
172
8068
5
582
ft
624
400
9.72
2.43
174
8069
6
810
"
1038
700
8.47
1. 21
178
8070
7
1073
'*
1589
1 100
7-47
.679
181
8071
8
1258
"
2082
1400
6.29
• 449
186
8072
9
1447
2640
1800
5-62
.312
189
8073
10
1657
"
3348
2200
4.82
.219
191
8074
ii
1867
"
4049
2700
4.40
.163
195
8075
12
2070
"
4816
3200
4.00
.125
197
8076
13
2282
"
5869
3900
3-67
.0940
196
8077
4
451
EEf
362
250
12.6
5-03
178
8078
5
622
"
624
400
9.24
2.31
181
8079
6
866
"
1038
700
8.05
1. 15
185
8080
7
1165
"
1589
1 100
7.06
.642
190
8081
8
1396
"
2082
1400
5-94
.424
196
8082
9
1588
»
2640
1800
5.36
.298
198
8083
10
1797
"
3348
22OO
4.62
.210
199
8084
ii
2002
"
4049
27OO
4.27
.158
201
8085
12
2208
"
4816
3200
3-90
.122
203
8086
13
2432
M
5869
39oo
3.56
.0913
203
8087
4
463
ERE
362
250
12.6
5-02
181
8088
5
640
"
624
400
9.20
2.30
184
8089
6
893
"
1038
700
8.05
I. IS
188
8090
7
1203
"
1589
1 100
7.05
.641
193
8091
8
1458
"
2082
1400
5.92
423
199
8092
9
1682
»
2640
1800
5.35
.297
202
8093
10
1894
"
3348
2200
4.60
.209
202
8094
ii
2098
"
4049
27OO
4.24
.157
204
8095
12
2300
"
4816
3200
3.90
.122
205
8096
13
2526
'*
5869
3900
3.56
.0912
204
1
Tubular Electric Line Pole Tables 149
Length of Pole, 35 Feet
Sections: 18 feet 6 inches, 10 feet, and 9 feet 6 inches
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
8097
4
331
///
258
170
14.2
8.33
179
8098
5
450
446
300
ii. 5
3.84
180
8099
6
600
695
450
8.91
1.98
187
8100
7
764
"
998
650
7-54
1.16
194
8101
8
945
1375
000
6.57
• 730
199
8102
9
1 137
««
1829
1 200
5-82
.485
201
8103
10
1360
2447
1600
5-20
• 325
2O2
8104
ii
1571
"
3022
2OOO
4.70
• 235
205
8105
12
1758
3586
240O
4-34
.181
209
8106
13
1939
"
4358
290O
3-94
.136
208
8 07
4
408
Eff
258
170
n. 8
6.96
168
8 08
5
559
482
300
9.48
3-i6
168
8 09
6
778
11
8i7
550
8.53
1.55
174
8 10
7
1032
"
1274
850
7-29
.858
178
8 II
8
1218
"
1830
1 200
6.67
.556
185
8 12
9
1410
«•
2522
1700
6.46
.380
189
8 13
10
1623
"
3227
2200
5-83
.265
192
8 14
ii
1839
"
3902
26OO
5-04
.194
197
8115
12
2051
4641
3100
4-59
.148
200
8116
13
2263
"
5656
3800
4.26
.112
199
8117
4
436
EEf
335
22O
14.1
6.42
172
8118
5
601
597
400
ii. 7
2.92
172
8119
6
837
"
IOOO
650
9-30
1.43
178
8120
7
1128
"
1532
IOOO
7.81
.781
184
8121
8
1363
"
2006
1300
6.53
.502
192
8122
9
1558
M
2544
1700
5-93
.349
196
8123
10
1771
"
3227
2200
5-41
.246
198
8124
ii
1981
3902
260O
4-76
.183
202
8125
12
2196
"
4641
3IOO
4-37
.141
2O4
8126
13
2421
5656
3800
4-03
.106
204
8127
4
453
EEE
335
22O
13-9
6.33
177
8128
5
627
"
001
400
ii. 5
2.87
• 179
8129
6
877
"
IOOO
650
9.17
1. 41
185
8130
7
1184
"
1532
IOOO
7-70
.770
191
8131
8
1455
2006
1300
6.44
.495
199
8132
9
1696
M
2544
1700
5.87
.345
204
8i33
10
1911
"
3227
2200
5-35
.243
205
8i34
II
2122
"
3902
2600
4-71
.181
208
8i35
12
2331
"
4641
3100
4-34
.140
208
8136
13
2559
5656
3800
3-99
.105
208
150
Tubular Electric Line Pole Tables
Length of Pole, 35 Feet
Sections: 21 feet, 10 feet, and 7 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
8137
4
343
///
263
180
13-6
7-54
187
8138
5
468
446
300
10.5
3-51
190
8i39
6
621
695
450
8.33
1.85
196
8140
7
786
"
998
650
7-15
I.IO
201
8141
8
969
1375
900
6.28
.698
204
8142
9
1162
t-"odi
1829
1200
5.6o
.467
206
8143
10
1390
"
2447
I600
S.oo
• 313
206
8144
ii
1600
3022
200O
4-58
.229
210
8145
12
1781
"
3586
2400
4.25
.177
213
8146
13
1962
4358
2900
3-86
.133
211
8i47
4
431
Eff
3io
200
12. 1
6.06
176
8148
5
592
it
578
400
II. I
2.77
178
8i49
6
822
" •
981
650
8.97
1.38
182
8150
7
1090
"
1529
IOOO
7-73
.773-
186
8151
8
1279
"
2006
1300
6.63
.510
191
8152
9
1473
•<
2544
1700
6.00
.353
195
8i53
10
1688
"
3227
220O
5-43
.247
197
8154
ii
1904
11
3902
2600
4.76
.183
2OI
8i5S
12
2113
"
4641
3100
4-37
.141
204
8156
13
2329
"
5656
3800
4-03
.106
203
8i57
4
459
EEf
349
22O
12.6
5-73
183
8158
5
634
601
400
10.5
2.62
185
8iS9
6
881
"
IOOO
650
8.52
I.3I
190
8160
7
1186
11
1532
IOOO
7.26
.726
195
8161
8
1424
"
2006
1300
6. 20
.477
202
8162
9
1621
«
2544
1700
5-70
.335
204
8163
10
1836
"
3227
2200
5-19
.236
205
8164
ii
2046
3902
2600
4.60
.177
208
8165
12
2258
"
4641
3100
4.25
.137
211
8166
13
2487
"
5656
3800
3-91
.103
209
8167
4
472
EEE
349
220
12.6
5.71
186
8168
5
653
"
601
400
10.4
2.6l
189
8169
6
911
"
IOOO
650
8.45
1.30
194
8170
7
1228
"
1532
IOOO
7-23
• 723
198
8171
8
1492
"
2006
1300
6.18
.475
205
8172
9
1723
••
2544
1700
5-66
.333
208
8i73
10
1940
"
3227
2200
5-17
.235
209
8174
ii
2150
"
3902
260O
4.60
.177
211
8i7S
12
2357
«
4641
3100
4.22
.136
212
8176
13
2589
5656
3800
3-88
.102
211
Tubular Electric Line Pole Tables 151
Length of Pole, 35 Feet
Sections: 18 feet 6 inches, 9 feet 6 inches, 6 feet 6 inches, and 5 feet
i " ~ ~~
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
8177
5
45i
////
446
300
n. 6
3-88
175
8178
6
598
695
45o
9.00
2.00
183
8i79
7
764
"
998
650
7-54
1.16
191
8180
8
949
"
1375
900
6.60
• 733
196 -
8181
9
1 147
1829
1200
5.84
.487
199
8182
10
1375
»
2447
I600
5-22
.326
200
8183
ii
1592
"
3022
2000
4-72
.236
204
8184
12
1784
"
3586
2400
4-34
.181
208
8185
13
1980
"
4358
2900
3-94
.136
207
8186
5
56o
Efff
482
300
9.60
3-20
164
8187
6
776
817
550
8.64
1.57
168
8188
7
1032
"
1274
850
7-34
.864
174
8189
8
1223
11
1830
1200
6.71
• 559
182
8190
9
1421
"
2522
1700
6.49
.382
187
8191
10
1638
••
3227
220O
5-83
.265
190
8192
ii
1860
"
3902
2600
5-04
.194
195
8193
12
2076
"
4641
3100
4-59
.148
198
8194
13 1 2304
5656
3900
4-37
.112
198
8i95
5
600
EEff
554
350
10.4
2.96
166
8196
6
832
1000
650
9-43
1-45
172
8197
7
1124
11
1532
IOOO
7-89
.789
179
8198
8
1360
"
2006
1300
6.58
.506
188
8199
9
1561
"
2544
1700
5-98
.352
193
8200
10
1778
«•
3227
2200
5-43
.247
195
8201
ii
1995
"
3902
2600
4.78
.184
200
8202
12
2214
"
4641
3100
4-37
.141
203
8203
13
2454
5656
3900
4-13
.106
203
8204
5
618
EEEf
601
4OO
ii. 6
2.90
172
8205
6
859
"
IOOO
650
9-23
1.42
178
8206
7
1162
1532
IOOO
7-75
• 775
185
8207
8
1423
"
2006
1300
6.47
.498
195
8208
9
i655
2544
1700
5.88
.346
2OI
8209
10
1874
•«
3227
22OO
5-37
.244
2O2
8210
ii
2091
"
3902
2600
4-73
.182
205
8211
12
2306
"
4641
3100
4-34
.140
207
8212
13
2548
"
5656
3900
4.10
.105
206
8213
5
627
EEEE
601
400
n. 6
2.90
174
8214
6
873
IOOO
650
9.23
1.42
180
8215
7
1183
"
1532
IOOO
7-75
• 775
187
8216
8
1452
"
2006
1300
6.46
.497
196
8217
9
1703
2544
1700
5.88
.346
202
8218
10
1947
«•
3227
2200
5-37
.244
203
8219
ii
2165
"
3902
2600
4-73
.182
206
8220
12
2380
"
4641
3IOO
4.34
.140
207
8221
13
2619
"
5656
3900
4.10
.105
207
152 Tubular Electric Line Pole Tables
Length of Pole, 36 Feet
Sections: 18 feet 6 inches, 10 feet 6 inches, and 10 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
8222
4
337
///
242
160
15.1
9-45
185
8223
5
459
430
280
12.2
4-35
185
8224
6
613
"
670
450
10. 1
2.24
193
8225
7
780
"
963
650
8.45
1.30
201
8226
8
966
"
1327
900
7.38
.820
205
8227
9
1162
««
1765
1200
6.53
• 544
208
8228
10
1391
2361
I60O
5-82
.364
209
8229
II
1608
"
2916
1900
5.00
.263
212
8230
12
1801
"
3460
2300
4 65
.202
216
8231
13
1987
"
4205
2800
4.26
.152
215
8232
4
415
Eff
242
160
12.7
7-95
174
8233
5
568
452
300
10.8
3.6o
174
8234
6
790
"
766
500
8.85
1.77
179
8235
7
1049
"
H95
800
7-79
• 974
184
8236
8
1240
"
1716
I10O
6.92
.629
191
8237
9
1436
"
2364
1600
6.88
• 430
196
8238
10
1654
"
3ii3
2100
6.26
.298
198
8239
ii
1876
"
3765
2500
5-45
.218
203
8240
12
2094
4478
30OO
4.98
.166
206
8241
13
2311
"
5457
3600
4-50
.125
205
8242
4
444
EEf
314
20O
14.6
7-29
177
8243
5
613
11
554
350
ii. 6
3-31
177
8244
6
852
965
650
10.5
1.62
. 183
8245
7
1149
"
1478
IOOO
8.81
.881
190
8246
8
1392
"
1935
1300
7-33
.564
198
8247
9
1592
2455
1600
6.27
.392
202
8248
10
1809
"
3H3
2100
5.8o
.276
205
8249
ii
2025
"
3765
2500
5.13
.205
208
8250
12
2246
"
4478
3000
4-71
.157
212
8251
13
2477
"
5457
3600
4.25
.118
210
8252
4
462
EEE
314
200
14.4
7-19
183
8253
5
640
"
58o
400
I3.o
3 25
184
8254
6
894
"
965
650
10 3
1-59
191
8255
7
1208
"
1478
IOOO
8.67
.867
197
8256
8
1488
"
1935
1300
7-23
.556
206
8257
9
1737
»
2455
1600
6.18
.386
211
8258
10
1957
"
3H3
2100
5-73
.273
212
8259
ii
2173
"
3765
2500
5.o8
.203
214
8260
12
2388
"
4478
3000
4.68
.156
216
8261
13
2622
5457
3600
4.25
.118
214
Tubular Electric Line Pole Tables 153
Length of Pole, 36 Feet
Sections: 19 feet, 9 feet 6 inches, 7 feet, and 5 feet
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
8262
5
462
ffff
430
280
12. 1
4-33
181
8263
6
613
670
450
10. 0
2.23
189
8264
7
783
44
963
650
8.45
1.30
197
8265
8
973
44
1327
900
7-34
.816
203
8266
9
H75
"
1765
1200
6.50
• 542
206
8267
10
1409
2361
1600
5.8i
.363
207
8268
ii
1631
44
2916
I9OO
S.oo
.263
211
8269
12
1829
44
346o
2300
4-65
.202
215
8270
13
2030
44
4205
2800
4.26
.152
214
8271
5
574
Efff
466
300
10.7
3-57
169
8272
6
796
14
791
550
9.63
1.75
174
8273
7
1059
44
1233
800
7-70
.963
180
8274
8
1254
1771
1200
7.46
.622
188
8275
9
1457
44
2440
1600
6.80
.425
194
8276
10
1679
"
3H3
2IOO
6.20
.295
197
8277
ii
1907
3765
2500
5.40
.216
2OI
8278
12
2129
44
4478
3000
4.95
.165
206
8279
13
2363
5457
3600
4.46
.124
204
8280
5
614
EEff
517
350
ii. 6
3-31
171
8281
6
852
964
650
10.5
1.62
177
8282
7
1150
"
1478
IOOO
8.80
.880
185
8283
8
1392
"
1935
1300
7-35
.565
194
8284
9
1597
1 '
2455
1600
6.27
• 392
199
8285
10
1820
••
3113
2IOO
5.8o
.276
2O2
8286
ii
2042
44
3765
250O
5 13
.205
206
8287
12
2267
44
4478
3000
4-71
.157
2IO
8288
13
2513
5457
3600
4.25
.118
209
8289
5
633
EEEf
58o
40O
13.0
3-24
178
8290
6
881
44
965
650
10.3
1.58
184
8291
7
1191
44
1478
IOOO
8.64
.864
192
8292
8
1459
1935
1300
7.22
.555
2O2
8293
9
1699
44
2455
1600
6.16
.385
208
8294
10
1923
44
3H3
2IOO
5 69
.271
209
8295
ii
2146
44
3765
2500
5-05
.202
212
8296
12
2366
44
4478
3000
4.68
.156
214
8297
13
2614
"
5457
3600
4.21
.117
213
8298
5
642
EEEE
58o
400
12.9
3-23
180
8299
6
895
44
965
650
10.3
1.58
186
8300
7
1212
44
1478
IOOO
8.64
.864
193
8301
8
1488
44
1935
1300
7.20
.554
203
8302
9
1747
"
2455
1600
6.16
.385
209
8303
10
1996
••
3H3
2100
5.69
.271
210
8304
ii
2220
44
3765
2500
5-05
.202
213
8305
12
2440
44
4478
3000
4.68
.156
215
8306
13
2685
44
5457
3600
4.21
.117
214
154
Tubular Electric Line Pole Tables
Length of Pole, 37 Feet
Sections: 19 feet, 10 feet 6 inches, and 10 feet 6 inches
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
8307
4
346
iff
235
160
16.8
10.5
191
8308
5
470
415
280
13-6
4.84
191
8309
6
628
648
450
II. 2
2.49
200
8310
7
799
"
930
600
8.70
1.45
207
8311
8
990
44
1282
850
7-73
.909
212
8312
9
1191
1705
IIOO
6.64
.604
215
8313
10
1426
"
2281
1500
6.06
.404
216
8314
II
1648
2817
1900
5-55
.292
219
8315
12
1846
3343
2200
4-93
.224
223
8316
13
2037
"
4062
270O
4-56
.169
222
8317
4
425
Eff
235
160
I4-I
8.82
180
8318
5
582
438
300
12.0
4.00
179
8319
6
810
44
743
500
9.80
1.96
185
8320
7
1075
1158
750
8.10
1. 08
190
8321
8
1271
"
1664
IIOO
7.68
.698
197
8322
9
1472
••
2292
1500
7-14
.476
202
8323
10
1696
"
3008
2000
6.62
.331
205
8324
ii
1923
44
3637
2400
5.8i
.242
209
8325
12
2147
14
4326
2900
5-34
.184
213
8326
13
2370
"
5272
35oo
4.87
.139
213
8327
4
454
EEf
305
200
16.2
8. II
183
8328
5
627
44
517
350
12.9
3-68
182
8329
6
872
44
932
600
10.8
i. 80
189
8330
- 7
1176
44
1428
950
9-30
• 979
195
8331
8
1423
44
1870
1200
7-54
.628
204
8332
9
1628
«•
2372
1600
6.98
.436
209
8333
10
1851
44
3008
2000
6.12
.306
211
8334
ii
2072
44
3637
2400
5.47
.228
215
8335
12
2299
44
4326
2900
5.08
.175
218
8336
13
2535
"
5272
35oo
4.59
.131
218
8337
4
474
EEE
305
200
16.0
7-98
189
8338
5
655
"
560
350
12.6
3.6l
190
8339
6
916
44
932
600
10.6
1.76
197
8340
7
1238
44
1428
950
9-15
.963
203
8341
8
1524
44
1870
1200
7-40
.617
213
8342
9
1780
««
2372
1600
6.86
.429
218
8343
10
2006
44
3008
2000
6.04
.302
219
8344
II
2228
44
3637
2400
5-40
.225
221
8345
12
2448
44
4326
2900
5-02
.173
223
8346
13
2688
5272
35oo
4.55
.130
223
Tubular Electric Line Pole Tables 155
Length of Pole, 38 Feet
Sections: 20 feet, 10 feet 6 inches, and 10 feet 6 inches
Number
Size
of
butt
Weight
Thick-
ness
Maxi-
mum
load
Load
for
deflec-
tion D
Deflec-
tion for
loadL
Factor
Factor
P
L
D
R
m
8347
4
356
///
235
160
18.2
II. 4
198
8348
5
485
"
402
280
14-7
5-25
108
8349
6
647
626
400
10.8
2.71
207
8350
7
823
"
900
600
9.48
1.58
215
8351
8
1018
"
1240
850
8.46
• 995
220
8352
9
1225
1649
1 100
7.28
.662
223
8353
10
1466
"
2206
1500
6.65
• 443
224
8354
ii
1693
2725
1800
5.78
.321
227
8355
12
1896
14
3233
2200
5-41
.246
231
8356
13
2092
3929
2600
4.84
.186
230
8357
4
440
Eff
235
160
15.2
9-47
186
8358
5
603
438
300
12.9
4-31
186
8359
6
839
"
743
500
10.6
2. II
192
8360
7
HI3
44
1158
750
8.78
1. 17
197
8361
8
1314
1664
1 100
8.33
.757
204
8362
9
IS2I
2292
1500
7-77
.518
2IO
8363
10
1750
44
2909
1900
6.84
.360
212
8364
II
1983
11
35i8
2300
6.07
.264
217
8365
12
2212
44
4184
2800
5.66
.202
221
8366
13
2442
"
5099
34oo
5-17
.152
220
8367
4
469
EEf
305
200
17-5
8.76
190
8368
5
647
"
517
350
14.0
3-99
189
8369
6
001
"
902
600
ii. 7
1.95
I96
8370
7
1214
41
1381
900
9.63
1.07
202
8371
8
1467
44
1808
1200
8.23
.686
212
8372
9
1676
•«
2294
1500
7.16
• 477
217
8373
10
1906
41
2909
1900
6.38
.336
219
8374
ii
2132
44
35i8
2300
5-75
.250
223
8375
12
2364
44
4184
2800
5.38
.192
226
8376
13
2608
"
5099
34oo
4-90
.144
226
8377
4
489
EEE
305
200
17-3
8.63
196
8378
5
676
44
542
350
13-7
3-91
197
8379
6
945
902
600
n-5
1.92
204
8380
7
1270
44
1381
900
9-45
1.05
211
8381
8
1567
"
1808
1200
8. II
.676
221
8382
9
1829
»
2294
1500
7-05
• 470
226
8383
10
2061
44
2909
1900
6.29
• 331
227
8384
ii
2288
44
35i8
2300
5.68
.247
229
8385
12
2514
44
4184
2800
5-32
.190
231
8386
13
2760
5099
3400
4.86
.143
231
156
Tubular Electric Line Pole Tables
Length of Pole, 39 Feet
Sections: 21 feet, 10 feet 6 inches, and 10 feet 6 inches
Maxi-
Load
Deflec-
Number
Size
of
butt
Weight
Thick-
ness
murn
load
for
deflec-
tion D
tion for
loadL
Factor
Factor
P
L
D
R
ra
8387
4
367
///
229
150
18.5
12.3
205
8388
5
500
389
250
14.2
5-69
206
8389
6
666
"
607
400
ii. 8
2.94
215
8390
7
846
"
871
600
10.3
1.72
223
8391
8
1047
"
1 201
800
8.72
1.09
228
8392
9
1259
»
1597
IIOO
7.95
.723
231
8393
10
1507
"
2136
1400
6.78
.484
232
8394
II
1739
"
2638
1800
6.34
• 352
235
8395
12
1946
"
3130
2IOO
5-67
.270
239
8396
13
2146
"
3804
25OO
5-08
.203
238
8397
4
455
Eff
235
160
16.3
10.2
193
8398
5
623
438
300
13-9
4.63
192
8399
6
867
il
743
500
II. 4
2.28
199
8400
7
II5I
1158
750
9-45
1.26
204
8401
8
1358
1664
IIOO
9.02
.820
212
8402
9
1570
••
2221
1500
8-43
.562
217
8403
10
1805
"
2817
1900
7-45
• 392
22O
8404
ii
2043
"
3406
2300
6.60
.287 ,
225
8405
12
2278
"
4052
2700
5-94
.220
229
8406
13
2514
4937
3300
5.48
.166
228
8407
4
484
EEf
305
200
18.9
9-45
197
8408
5
668
"
517
350
I5-I
4-31
196
8409
6
929
873
600
12.7
2.12
203
8410
7
1252
11
1337
900
10.4
1.16
211
8411
8
1510
"
1751
1 200
8.99
• 749
22O
8412
9
1725
"
2221
1500
7-83
.522
225
8413
10
1960
"
2817
1900
6.97
.367
227
8414
II
2192
"
3406
2300
6.28
.273
231
8415
12
2430
"
4052
2700
5.67
.210
234
8416
13
2680
"
4937
3300
5.21
.158
234
8417
4
504
EEE
305
200
18.6
9-32
203
8418
5
696
"
525
350
14.8
4.24
2O4
8419
6
973
"
873
600
12.5
2.08
212
8420
7
1314
"
1337
900
10.3
1. 14
218
8421
8
1611
11
1751
1200
8.87
.739
229
8422
9
1877
««
2221
1500
7-73
.515
234
8423
10
2116
11
2817
1900
6.90
.363
235
8424
ii
2348
"
3407
23OO
6.23
.271
237
8425
12
2579
"
4052
2700
5-64
.209
239
8426
13
2832
4937
33oo
5-18
.157
239
Tubular Electric Line Pole Tables 157
Length of Pole, 40 Feet
Sections: 21 feet, 10 feet, 7 feet, and 6 feet 6 inches
Maxi-
Load
r
Deflec-
Number
Size
of
butt
Weight
Thick-
ness
mum
load
lor
deflec-
tion D
tion for
loadZ,
Factor
Factor
P
L
D
R
nt
8427
5
SOS
////
377
250
16.2
6.47
202
8428
6
670
588
400
13-3
3-33
2IO
8429
7
856
"
844
550
10.6
1-93
221
8430
8
1064
1164
800
9.68
1. 21
228
8431
9
1286
"
1548
IOOO
8.05
.805
233
8432
10
1542
••
2070
1400
7-53
• 538
234
8433
ii
1786
"
2557
1700
6.63
• 390
239
8434
12
2001
3034
200O
5.98
• 299
243
8435
13
2225
"
3687
2500
5-63
.225
244
8436
5
629
Efff
413
280
14.9
5.33
188
8437
6
871
701
450
ii. 7
2.60
193
8438
7
1160
"
1092
750
10.7
1-43
201
8439
8
1374
"
1569
IOOO
9-23
.923
211
8440
9
1597
2153
1400
8.83
.631
218
8441
10
1841
««
2730
1800
7-88
.438
222
8442
ii
2090
44
3302
22OO
7.06
.321
228
8443
12
2333
"
3927
2600
6-37
• 245
233
8444
13
2593
44
4785
3200
5-89
.184
233
8445
5
67I
EEff
431
280
13-9
4.96
190
8446
6
930
803
550
13-3
2.42
195
8447
7
1256
44
1296
850
II. 2
1.32
205
8448
8
1519
14
1697
1 100
9.28
.844
217
8449
9
1745
"
2153
1400
8.18
.584
224
8450
10
1989
••
•2730
1800
7.38
.410
228
8451
ii
2232
"
3302
2200
6.71
305
233
8452
12
2478
44
3927
260O
6.08
234
237
8453
13
2751
"
4785
3200
5-6o
.175
237
8454
5
690
EEEf
509
350
16.9
4.84
196
8455
6
960
11
846
550
13-0
2.37
202
8456
7
1298
11
1296
850
II. 0
1.29
212
8457
8
1587
"
1697
IIOO
9-09
.826
225
8458
9
1846
44
2153
1400
8.02
.573
233
8459
10
2092
••
2730
1800
7.25
.403
235
8460
ii
2336
44
3302
220O
6.60
.300
239
8461
12
2578
44
3927
2600
6.01
.231
242
8462
13
2852
4785
3200
5-57
.174
242 1
8463
5
702
EEEE
509
350
16.9
4 83
1
2OO
8464
6
978
"
846
550
13-0
2.36
206
8465
7
1325
"
1296
850
II. 0
1.29
216
8466
8
1625
44
1697
IIOO
9.08
.825
228
8467
9
1909
"
2153
1400
8.01
• 572
236
8468
10
2187
««
2730
1800
7-25
.403
239
8469
ii
2432
14
3302
2200
6,60
.300
241
8470
12
2674
"
3927
26OO
6.01
.231
244
8471
13
2944
44
4785
3200
5-57
.174
243
158 Upset and Expanded Tubes
LAP-WELDED AND SEAMLESS TUBES UPSET AND
EXPANDED
Uses for Upset Tubes. Upset tubes are largely used for stay tubes
in marine-boiler work, but frequently tubes are upset for mechanical
purposes, and in such cases they come under the heading of "Tube
Specialties. " As the variations of upsets in the tube specialty line are
so numerous, they cannot be standardized the same as tubes upset for
boiler work.
Upsetting. The upsetting of tubes consists in increasing the thick-
ness of the wall of a tube at the ends, which increases its durability and
strength. This increased thickness can be placed either on the inside
or on the outside, or on both the inside and outside of the tube.
Method of Operation. The end of the tube is heated to a sufficient
heat and while hot is placed in a die, and, by means of a punch with a
shoulder on it, the end of the tube is stoved up, upset, or reinforced in
the thickness of the wall.
When heavy reinforcements or upsets are necessary, it may take from
three to four heats and operations to accomplish this, but light upsets
may be obtained in one heat and one operation. Often upsets are
asked for that are either very difficult or practically impossible to make,
and as a guide for ordering such tubes a set of tables has been prepared
showing the practical limits.
Standard Upsets. Table, pages 160-161, gives the advisable external
upset for the various diameters and thicknesses of tubes. By advisable
is meant the standard upset of a tube with a given diameter and thick-
ness (see Fig. 49).
Table, pages 160-161, gives the advisable internal upset for various
diameters and thicknesses of tubes. The rules covering the standard
external upset of tubes also apply to standard internal upsets, as per
Fig. 50.
Special Upsets. Any upsets less than that given in the table are
treated as standard upsets, and any upsets greater than those given in
the table are considered special upsets, as it requires more work and
operations to produce them than the standard advisable upsets.
Tubes Upset and Expanded. Page 159 shows illustrations of the
different kinds of upsets.
Fig. 49 shows a tube end upset on the outside, leaving the inside of
the tube straight.
Fig. 50 shows a tube end upset on the inside, leaving the outside of
the tube straight.
Fig. 51 shows a tube end expanded without any upset either on the
inside or outside.
Fig. 52 shows a tube end upset on the outside and then expanded.
Fig. 53 shows a tube with an internal and external upset.
Upset and Expanded Tubes 1
59
Upset and Expanded Tubes
:• ^ ' >'' WxmW/////yy//^^
Fig. 49. External Upset
%J^^^^
Fig. 50. Internal Upset
««f««««f««f««ff«««w««f«^
W»»»»»»»»»»»»M»»»»»»10r
Fig. 51. Expanded Without Any Upset
MMMMMMMMZfa
^^^^^^^^^^^^^
Fig. 52. External Upset and Expanded
Fig. 53. Internal and External Upset
160 Upsets for Lap-weld or Seamless Tubes
Advisable Internal Upsets for Lap-weld or Seamless Tubes
Thickness
External diameter of tubes
Inch
Nearest
B.W.G.
i%
I8/4
2
2V4
2%
2%
3
3V4
Internal diameter of upset
.134
.148
.165
.188
.203
.219
.238
.250
.281
.313
• 344
.375
.406
• 438
10
9
8
7
6
5
4
1.03
-98
• 92
.84
• 79
1.28
1.23
1. 17
1.09
1.04
.98
• 91
.87
.53
• 48
.42
• 34
.29
.23
.16
.12
1.02
.78
.73
.67
• 59
• 54
-48
• 41
• 37
.27
.15
2.03
1.98
.92
•84
• 79
• 73
.66
.62
• 52
.40
.29
2.28
2.23
2.17
2.09
2.04
1.98
I-9I
1.87
1.77
1.65
1.54
1-44
2.53
2.48
2.42
2.34
2.29
2.23
2.16
2.12
2. 02
1.90
1.79
1.69
1-58
1.46
2.78
2.73
2.67
2.59
2.54
2.48
2.41
2.37
2.27
2.15
2.04
1.94
1.83
1.71
Advisable External Upsets for Lap-weld or Seamless Tubes
Thickness
External diameter of tubes
|
Inch
Nearest
B.W.G.
iV2
i%
2
2V4
2y2
2%
3
3V4
External diameter of upset
;I34
.148
.165
.188
.203
.219
.238
.250
.281
.313
• 344
.375
.406
• 438
10
9
8
7
6
5
4
.70
.72
• 75
• 78
.80
.83
.86
.88
.92
• 97
.02
2.06
2. II
2.16
1-95
1.97
2.OO
2.03
2.05
2.08
2. II
2.13
2.17
2.22
2.27
2.31
2.36
2.41
2.20
2.22
2.25
2.28
2.30
2.33
2.36
2.38
2.42
2.47
2.52
2.56
2.61
2.66
2.45
2.47
2.50
2.53
2.55
2.58
2.61
2.63
2.67
2.72
2.77
2.81
2.86
2.91
2.70
2.72
2.75
2.78
2.80
2.83
2.86
2.88
2.92
2.97
3-02
3.06
3- II
3-16
2.95
2.97
3.oo
3-03
3-05
3.08
3-II
3-13
3-17
3-22
3-27
3-31
3.36
3-41
3-20
3-22
3-25
3-28
3-30
3-33
3.36
3-38
3-42
3-47
3-52
3.56
3-6l
3-66
3.45
3-47
3-50
3-53
3-55
3-58
3.6i
3.63
3.67
3-72
3.77
3.81
3.86
3-91
Diameters of upsets given are based on a length of upset 2^ inches long. Upset
on tubes heavier than specified and longer than zVz inches can be made, but will
require special attention. All dimensions are nominal. All dimensions given in
inches. For illustrations of tubes see Figs. 49 and 50, page 159.
Upsets for Lap- weld or Seamless Tubes 161
Advisable Internal Upsets for Lap-weld or Seamless Tubes (Concluded)
Thickness
External diameter of tubes
Inch
Nearest
B.W.G.
3V2
3%
4
4V4
4Y2
43/i 5
Internal diameter of upset
.134
.148
.165
.188
.203
.219
.238
.250
.281
• 313
• 344
.375
.406
.438
10
9
8
7
6
5
4
3.03
2.98
2.92
2.84
2.79
2.73
2.66
2.62
2.52
2.40
2.29
2.19
2.08
1.96
3-23
3-17
3-09
3-04
2.98
2.91
2.87
2.77
2.65
2.54
2.44
2.33
2.21
3-48
3-42
3-34
3-29
3.23
3-i6
3.12
3-02
2.90
2.79
2.69
2.58
2.46
3-73
3.67
3-59
3-54
3.48
3.41
3-37
3-27
3-15
3-04
2.94
2.83
3.98
3-92
3-84
3-79
3 73
3-66
3.62
3-52
3-40
3-29
3-19
4-23
4-17
4.09
4.04
3-98
3-91
3.87
3-77
3.65
3-54
4.42
4.34
4.29
4.23
4.16
4.12
4.02
3.90
Advisable External Upsets for Lap-weld or Seamless Tubes (Concluded)
Thickness
External diameter of tubes
Inch
Nearest
B.W.G.
3V2
38/4
4
4V4
4V2
4%
5
External diameter of upset
.134
.148
.165
.188
.203
.219
.238
.250
.281
.313
• 344
• 375
.406
.438
10
9
8
7
6
5
4
3-70
3-72
3-75
3-78
3.8o
3.83
3-86
3-88
3-92
3-97
4.02
4.06
4- II
4.16
3-97
4.OO
4-03
4-05
4.08
4. II
4-13
4-17
4.22
4-27
4-31
4.36
4-41
4.22
4-25
4.28
4-30
4-33
4.36
4-38
4.42
4-47
4-52
4.56
4.61
4.66
4.47
4.50
4.53
4.55
4-58
4.61
4.63
4.67
4-72
4-77
4.81
4.86
4-72
4-75
4.78
4.80
4-83
4.86
4.88
4-92
4-97
5-02
S.o6
4-97
S.oo
5-03
5-05
5.08
5- II
5.13
5.17
5-22
5.27
5-25
5-28
5-30
5-33
5.36
5.38
5-42
5-47
Diameters of upsets given are based on a length of upset 2% inches long. Upset
on tubes heavier than specified and longer than 2^5 inches can be made, but will
require special attention. All dimensions are nominal. All dimensions given in
inches. For illustrations of tubes see Figs. 49 and 50, page 159.
162
Pipe Bends
WROUGHT PIPE BENDS
The attached table gives the advisable radius and the least radius to
which pipe of standard thickness may be bent.
The radii given are as short as should be used to secure good results
and if they be reduced, the thickness of the pipe must be increased. As
the radius is decreased, however, it becomes more difficult to avoid
buckles.
For making bends, we suggest pipe as follows: —
Bends 12 inch and smaller to regular dimensions to be made of full-
weight pipe.
Bends 14, 15 and 16 inch outside diameter to be not less than % inch
thick.
Bends 18 inch outside diameter and larger to be not less than %6 inch
to V2 inch thick.
For offset bends try to make a straight length between the bends in
preference to the direct reverse bend. This is of advantage to the pipe
bender.
With the welded flanges there must be a short straight length of
pipe between the bend and the flange. On sizes under 4 inches this
should equal, at least,
one and a half diam-
eters. On sizes over
4 inches it should
equal, at least, one
diameter of the pipe.
In all cases it is bet-
ter if equal to two
diameters of straight
pipe.
Bent Tubes.
These are more dif-
ficult to bend than
standard weight pipe.
Try not to vary from
the advisable radius
given in the table.
With tubes it is fre-
quently necessary to
increase the thickness
over that of standard
boiler tubes in order
to bend them.
For illustration of
Pipe Bends see page
163.
Table of Radii for Wrought Pipe Bends
Pipe size
Inches
Advisable
radius — R
Inches
Minimum
radius — R
Inches
gft
15
10
3
18
12
3l/2
21
14
4
24
16
4Va
27
18
5
30
20
6
36
24
7
42
28
8
48
32
9
54
36
10
60
40
ii
66
44
12
72
48
13
84
60
14
90
68
IS
IOO
76
18 O.D.
125
90
20 O.D.
150
120
22 O.D.
165
132
24 O.D.
180
144
Pipe Bends
163
Wrought Pipe Bends
Single Offset U Bend Single Offset 90° Bend U Bend
164
Butted and Strapped Joints
BUTTED AND STRAPPED JOINTS — SINGLE AND
DOUBLE RIVETED
Fig. 54. Joint Flush Outside — Fig. 55. Joint Flush Outside-—
Single Riveted Double Riveted
Fig. 56. Joint Flush Inside —
Single Riveted
Fig. 57. Joint Flush Inside —
Double Riveted
This class of goods is special, and made to suit the conditions as indi-
cated by the customer's requirements. Since there seldom are two par-
allel cases, it is difficult to give any rule for these joints. They usually
take on quite different forms, according to the use to which applied.
In a general way it may be said they have been employed on pipe mostly
to piece out boiler flues, or to piece out pipes used as piles, masts, or
booms.
When used for flues, it is generally customary to put the strap on the
outside and then countersink the rivets on the outside, leaving the button
heads on the inside. The outside countersinking is done to avoid un-
necessary enlargement of the hole in the flue sheet. The end of the
flue is then expanded to fit this enlarged hole in the flue sheet. Since
the flue is connected to the tube sheet by single riveting, it is seldom
necessary, and always unadvisable, to double rivet because it is more
difficult to calk a double rivet seam satisfactorily.
Bump Joints
165
Strapped joints used for piles, etc., are usually so made that the rivet-
ing is secondary to the beam action of the strap. On piles the strap is
usually made several diameters long, and attached to the end of one of
the pieces by a few well-scattered rivets.
The connection between the sleeve and the second piece is made in
the field by means of patch bolts. For some uses where the joint section
is relied on mainly for its beam action or lateral stiffness, the sleeve is
inserted into each piece for a distance of about one-half to two diameters.
The sleeve is turned slightly tapered with its largest diameter at the
center, and the pipes are bored to match. After assembling, however,
a few patch bolts are placed about midway between the end of pipe and
the end of sleeve.
For the information of those who wish to use these joints, it may be
said that for short sleeves the thickness is usually from one and one-half
to twice the thickness of the pipe, and that for long sleeves, used for
strength as beams, the thickness is determined by the rules for strength
of beams.
The following rules may be used for figuring the riveting, spacing, etc.
Figs. 54 and 56
Single Riveted
D = i.sT + .i6inch
P = 2 D + .4 inch
A = 1.5 D + Vs inch
B= 1.5 D
Figs. 55 and 57
Double Riveted
D= 1.5 r + .i6 inch
P1== 3D + .78 inch
N=* 2 D + .4 inch
A =
B=i.5D.
BUMP JOINTS — SINGLE AND DOUBLE RIVETED
Fig. 58
Fig. 59
This joint has been largely used in the past for coupling two pieces
of boiler-flue together in order to make a flue longer than 2 1 feet. The
necessity for this practice has ceased as it is now possible to secure flues
up to 20 inches in diameter and 40 feet in length. This joint is also being
used extensively for long lines of large size pipe, say 20 to 30 inches in
166 Bump Joints
diameter, and for such lines it has the advantage of low cost in compari-
son with the high pressure it will carry, being serviceable for pressures
up to 500 pounds, when used on flues or pipe of the proper thickness,
and although it entails difficulty in assembling with lines buried in the
ground its advantages more than offset its disadvantages. Many of the
Pacific Coast Hydro Electric Developments have used this joint in this
manner with satisfaction and probably at less cost than if the pipe had
been connected by flanges welded to them, or other means.
This joint is not adapted to small sizes, say under 20 inches, because
of the difficulty of obtaining men who can work continuously inside of a
pipe less than 20 inches in diameter when riveting joints. For boiler-
flues it is practical, because of its accessibility in riveting to add 10 or
15 feet to a 1 2-inch tube.
The double riveted joint, Fig. 59, exhibits the spigot end as straight.
This form usually entails accurate sizing of the two parts for each joint
so that those identical pieces will be assembled in the field.
In order to make the jpints interchangeable in the erection and to
facilitate assembling and calking, it is advisable to expand the spigot end
on a slight taper for single riveted joints, as shown by Fig. 58. This
enables laying out the rivet holes accurately tor a gage before punching.
The tapered spigot can, of course, be applied to the double riveted joint,
Fig. 50-
Since the strain imposed by the pressure on the girth joint is one-half
of the strain imposed pn the longitudinal joint, it is evident that the
riveted girth joint need have only one-half of the strength of the welded
joint or longitudinal seam. Therefore with welded or seamless pipe it
is never necessary to use double riveted joints except in those locations
where the pipe above ground makes a bend, or where the pipe must act
as a beam and the joint is exposed to strains produced by flexure.
The following rule can be used for figuring the riveting, spacing, etc.:
Fig. 58 Fig. 59
Single Riveted Double Riveted
D = 1.5 T + .16 inch D = 1.5 T + .16 inch
P = 2D + .4 inch PI = 3 D + .78 inch
A = 1.5 D + y8 inch N = 2 D + .4 inch
B = 1.5 D A = 1.5 D + y8 inch
B= 1.5 D
Valves and Fittings 167
VALVES AND FITTINGS
It is the intention to present information in this section regarding
valves and fittings, which will be of value to all who use them.
Valves and fittings are designed to conform to the pipe connections
of the line in which they are used. Wrought pipe is usually connected
in one of three ways, screwed, flanged, or leaded joints.
Screwed. Pipe in sizes from l/s inch to 15 inches inclusive, is regu-
larly threaded on the ends, and is connected by means of threaded
couplings.
Flanged. Pipe in sizes i*4 inches and larger is frequently connected
by drilled flanges bolted together, the joint being made by a gasket
between the flange faces.
Flanges are attached to the pipe in a variety of ways. The most
common method for sizes of pipe from i^4 inches to 15 inches inclusive,
is by screwing them on the pipe. Many prefer peened flanges for pipe
larger than 6 inches. The peened flange is shrunk on the end of the
pipe, and the latter is then peened over or expanded into a recess in the
flange face, after which the ends of the pipe and the flange are sometimes
faced off in a lathe. Steel flanges are also welded to pipe and loose
flanges are used by flanging over the pipe ends. When flanges are called
for, and no method of attaching is stated, screwed flanges are always
furnished.
Leaded Joints. For water pipe which does not have to stand very
high pressures leaded joints are often used. The most common leaded
joints are the Converse Lock Joint* and the Matheson Joint. Converse
Joint is made by means of a special cast-iron coupling or hub which has a
groove on each end extending around just inside of the end of the coupling,
and two tee-shaped grooves on each end a short distance in from the circu-
lar groove. The pipe has two holes punched a short distance from the end
on opposite sides into which rivets are driven. In making up this joint, the
heads of the rivets slip into the tee-shaped slots of the hub, and the pipe
is turned slightly, thus holding the pipe from pulling out of the hub end-
wise. This joint is then made tight by pouring lead into the circular
slot and calking. The Matheson Jointt is another type of lead joint
used for water or gas.
Working Pressures. All valves and fittings are classified, as a rule,
under five general headings: low pressure, standard, medium pressure,
extra heavy, and hydraulic, which are almost universally understood to
represent the following working pressures:
Low Pressure — suitable for working steam pressures up to 25 pounds
per square inch.
Standard — suitable for working steam pressures up to 125 pounds per
square inch.
* See pages 84 and 108. f See pages 84 and 107.
168 Valves and Fittings
Medium Pressure — suitable for working steam pressures from 125
pounds to 175 pounds per square inch.
Extra Heavy — suitable for working steam pressures from 175 pounds
to 250 pounds per square inch.
Hydraulic — suitable for high pressure water up to 800 pounds pressure
per square inch.
Water Hammer. When selecting valves and fittings, the possibility
of shock or strain due to water hammer, in excess of the average working
pressure of the line or system, should be considered. Many valves and
fittings, installed where the working pressure under normal conditions
would be low, have failed because of a pressure due to water hammer.
This danger can be avoided by proper cushioning of the line (see
page 284).
Expansion and Contraction. Expansion and contraction should be
provided for in all installations, especially steam, by the use of an expan-
sion joint, expansion bend, or other approved device. For table of ex-
pansion and contraction, see page 347.
Thread Gage. All valves and fittings are regularly furnished, threaded
or tapped to the Briggs Standard Gage, which is the same as used for
pipe threads. The threading is accurate to gage within ordinary limits
of variation. (For article concerning Briggs Standard Threads see
page 208.)
Nipples. Nipples are made in all sizes from Vs inch to 12 inches in-
clusive, in all lengths, either black or galvanized, and regular right-hand
or right- and left-hand threads. (For table of nipples see pages 171-172.)
In the case of Long Screws or Tank Nipples, they should be made
of extra heavy pipe because there is less danger of crushing or splitting
them when screwing up.
Screwed Fittings — Malleable Iron. Malleable Iron Fittings are
made in Standard, Extra Heavy and Hydraulic.
The Standard Malleable Iron Fittings are made in both plain and
beaded.
The Plain Standard Malleable Iron Fittings are generally u? a for
low pressure gas and water, as in house plumbing and railing WOIK, and
the beaded is the standard steam, air, gas, or oil fitting.
The Beaded Fittings are made in sizes from VQ inch to 8 inches in-
clusive, and in 4 inches and smaller in nearly every useful combination
of openings. Sizes larger than 4 inches are not usually made reducing
except by means of bushing.
The Extra Heavy and Hydraulic Malleable Iron Fittings are usually
flat bead, or Banded, and Standard Malleable Iron Fittings with a flat
bead are also coming into use.
Screwed Fittings — Cast Iron. Cast-Iron Screwed Fittings are made
in Standard and Extra Heavy in sizes 1A inch to 12 inches inclusive.
However, it is not considered good practice to use screwed fittings of
any kind in sizes larger than 6 inches.
Valves and Fittings 169
Flanged Fittings. Flanged fittings are generally made only in sizes
2 inches and larger, and in four weights; namely, Low Pressure, Standard,
Extra Heavy, and Hydraulic. The flanges of the Low Pressure and
Standard are the same, with the exception of the flange thickness, which
is less on the low pressure. These flanges are known as the American
Society of Mechanical Engineers or Master Steam Fitters' Standard
(see page 176).
The flanges of Extra Heavy fittings are what is known as the Manu-
facturers' Standard, or that adopted by leading valve and fitting manu-
facturers in 1901.
There is no recognized standard for flanges in Hydraulic work.
Unions. Unions are usually classified under two headings, Nut
Unions and Flange Unions. The Nut Unions are commonly used in
sizes 2 inches and smaller and Flange Unions in sizes larger than 2 inches.
However, many manufacturers make Nut Unions as large as 4 inches
and Flange Unions smaller than 2 inches.
Nut Unions are made in Malleable Iron, Brass and Malleable Iron,
and all Brass. The all Malleable Iron Union (Lip Union) is the standard
Malleable Union of the trade and requires a gasket. The Brass and Mal-
leable Iron Union (known as the "Kewanee" Union) is a much better
union because no gasket is required, and there is no possibility of the parts
rusting together. The pipe end of the "Kewanee" Union which carries
an external thread, called the thread end, upon which the nut or ring
screws, is made of brass, and the other pipe end (called the bottom) and
nut or ring are made of Malleable Iron. The seat formed by the Brass
and Iron Pipe ends when brought together is truly spherical, and the
harder iron is sure to make a perfect joint with the softer brass.
When selecting a Brass and Malleable Union, one with inserted brass
pieces should be avoided. These inserts are generally rolled in, and
frequently become loose under varying expansion and contraction; or
when disconnection is attempted the nut and thread end are firmly
corroded together.
All Brass Unions are made with a spherical or conical seat, no gaskets
being required. The finished all Brass Union is often used where showy
work is desired, such as oil piping for engines, etc.
Flange Unions are made of both cast iron and malleable iron in three
weights. Standard, Extra Heavy, and Hydraulic.
Valves and Cocks. The most common means for regulating the flow
of fluids in pipes is by means of valves and cocks, the valves being pre-
ferred because of the easier operation and greater reliability. The com-
mon types of valves are Straightway or Gate, Globe, and Angle. While
the use of Globe Valves is still advised by some engineers, yet it is be-
coming more thoroughly appreciated every day that a straightway
valve should be preferred, for many reasons, in most installations. One
of the principal reasons for not using a globe valve is the resistance which
it offers to the flow of any fluid. It is considered that a globe valve at
its best offers 50 per cent more resistance to the flow of steam or other
170 Valves and Fittings
fluids than a right-angled elbow. There are, however, some kinds of
service where a globe valve is preferable, and many where an angle valve
is an absolute necessity.
Gate or Straightway Valves. Gate or Straightway Valves are made
in Low Pressure, Standard, Medium Pressure, Extra Heavy, and Hy-
draulic, in both brass and iron body. Gate Valves for superheated steam
have also been made of all iron or steel castings. Brass valves are regu-
larly made in sizes as large as 3 inches, and iron body Gate Valves are
regularly made as follows:
Low Pressure 12 inches to 48 inches inclusive.
Standard 2 inches to 30 inches inclusive.
Medium Pressure 2 inches to 18 inches inclusive.
Extra Heavy i^4 inches to 24 inches inclusive.
Hydraulic i% inches to 12 inches inclusive.
Globe and Angle Valves. Globe and Angle Valves are made in
Standard, Medium Pressure, Extra Heavy and Hydraulic, in both brass
and iron body, except Hydraulic, which are generally made in brass
only. Many manufacturers make a Globe and Angle Valve known as
Light Standard or Competition Valve, but it is not recommended for
any work except the lowest pressures, or where the valve will not be
often opened or closed.
Standard Brass Globe and Angle Valves are regularly made in sizes
VB inch to 4 inches inclusive, Medium Pressure Vi inch to 3 inches inclu-
sive, Extra Heavy ^ inch to 3 inches inclusive, and Hydraulic Vz inch
to 2 inches inclusive.
The Standard and Extra Heavy Iron Body Globe and Angle Valves
are regular^ made in sizes from 2 inches to 12 inches inclusive.
Check Valves. Check Valves are regularly made in Standard,
Medium Pressure, Extra Heavy and Hydraulic, in both brass and iron
body. The brass Check Valves are regularly made in sizes from Vs inch
to 4 inches inclusive, and the iron body Check Valves in sizes 2 inches
to 12 inches inclusive.
Cocks. Cocks are generally designated under two headings, Steam
and Gas, and are made in both brass and iron body. The brass are
regularly made in sizes from i/i inch to 3 inches inclusive, and the iron
body in sizes from V'z inch to 6 inches inclusive.
Blast Furnace Fittings. Under this heading may be classified
Tuyere Cocks, Tuyere Unions, and Universal Unions, which are very
common fittings in blast furnace piping, and are always made of brass
on account of the ease in disconnecting, greater reliability of metal,
and resistance to corrosion from the impurities in the water, such as
sulphuric acid.
NOTE. — A special catalogue, showing fittings, valves, etc., has been issued.
Pipe Nipples
171
Wrought Pipe Nipples — Black and Galvanized
Fig. 60
Fig. 6 1
Threaded Right Hand
Size
Length
Threads
per inch
(!)
o
|
C/D
Long
Extra long
1
Vs
%
l!/2
2
3
3V2
4
5
6
7
8
9
0
II
12
27
y4
7/8
iVfe
2
2y>
3
4
5
6
7
8
9
0
II
12
18
I
i!/2
2
2l/{.
3
3V2
4
5
6
7
8
9
o
II
12
18
%
1%
2
2y2
3
4
5
6
7
8
9
0
II
12
14
%
1%
2
21/2
3
3Ms
4
5
6
7
8
9
0
II
12
14
i
2
3
3y2
4
5
6
7
8
9
0
II
12
uy2
iy4
1%
2^2
3
3l/2
4
4y2
5
6
7
8
9
0
II
12
ny2
i%
1%
2y2
3
3y2
4
4y2
5
6
7
8
9
0
II
12
ny2
2
I8/4
2y2
3
3y2
4
4%
5
6
7
8
9
0
II 12
ii%
3
3
3
3y2
3*6
4
4
41/2
5
5
6
6
7
7
8
8
9
9
0
0
II
II
12
12
8andii!/2
8andiii/2
3%
2%
4
4%
5
5%
6
7
8
9
0
II
12
8
4
3
4
4y2
5
sy2
6
7
8
9
0
II
12
8
3
4
4y2
5
sy2
6
7
8
9
0
II
12
8
5
3%
5
sy2
6
6y^
7
8
9
0
II
12
8
6
3H
4^2
5
sV2
6
6y2
7
8
9
0
II
12
8
7
y
5
6
7
8
9
o
II
12
8
8
_]/
5
6
7
8
9
o
II
12
8
4
5
6
8
9
o
II
12
8
10
4
5
6
8
9
o
II
12
8
4
5
6
8
9
o
II
12
8
12
4
5
6
8
9
0
II
12
8
Assorted close and short nipples will always be shipped, unless otherwise
ordered.
Nipples also made from Extra Strong Pipe.
Nipples longer than 12 inches can be furnished when ordered.
Taper of threads is % inch diameter per foot length for all sizes.
Nipples larger than 3 inch pipe and longer than 12 inches are considered as cut
pipe and can be furnished when ordered.
2V2 inch and 3 inch nipples will be furnished 8 threads unless otherwise ordered.
All dimensions given in inches.
172
Pipe
Nipples
Wrought
Pipe Nipples — Black and Galvanized
•r
•
i
i
Fig. 62
Threaded Right and Left Hand
Length
Size
Threads
per inch
Short
Long
Extra long
y*
IV2
2 2^>
3 3y2 4
5 6
7 8
9 o
n
12
27
y*
I^2
2 2y2
3 3y2 4
5 6
7 8
9 o
II
12
18
I^2
2 2y2
3 3y2 4
5 6
7 8
9 o
n
12
18
%
iy2
2 21/2
3 3y2 4
5 6
7 8
9 o
n
12
14
%
2
2y2 3
3y2 4 ...
5 6
7 8
9 10
ii
12
14
i
2
2y2 3
3y2 4 ...
5 6
7 8
9 o
ii
12
ny2
!^4
2%
3 3y2
4 4y2 . . .
5 6
7 8
9 o
n
12
iy2
2$
3 3y2
4 4V2 . . .
5 6
7 8
9 o
n
12
ny2
2
2y2
3 3y2
4 4!/2 . . •
5 6
7 8
9 o
n
12
ny2
2%
3
31,2 4
4^2 5
... 6
7 8
9 °
TT
T?
8
3
3
3V2 4
4V2 5 ...
... 6
7 8
9 o
TT
T?
8
3y2
4
4^2 5
sy2 6
7 8
9 o
II
12
8
4
4
4y2 s
sy2 6
7 8
9 10
II
12
8
Nipples also made from Extra Strong Pipe.
Nipples longer than 12 inches can be furnished when ordered.
Nipples larger than 3-inch pipe and longer than 12 inches are considered aa
cut pipe and can be furnished when ordered.
Taper of threads is 8/
i inch diameter per foot length for all sizes.
All dimensions given
in inches.
Pipe Nipples
173
Wrought Pipe — Long Screw Nipples — Black and Galvanized
Fig. 63
Threaded Right Hand
Size
rl
a/0
y2
8/l
I
Tl/l
TVo
2
?Vo
3
W«>
4
Standard length . .
2%
3
3V2
4
4%
5
5%
6
7
8
8%
9
Threads per inch..
18
18
14
14
ny2
iiy2
11%
nV2
8
8
8
8
Nipples made from Extra Strong Pipe.
All dimensions given in inches.
Long screws, longer than Standard can be made.
In ordering special lengths always specify the length of thread desired.
Wrought Pipe Tank Nipples — Black and Galvanized
Fig. 64
Threaded Right Hand
Size . »
%
y*
9$
U
8/1
i
T1/1
TVo
2
2%
3
W-
4
Standard length..
6
6
6
6
6
6
6
6
6
7
8
8%
9
8
8
Threads per inch..
27
18
18
14
14
11%
n%
11%
"%
and
and
8
8
11%
11%
Nipples made from Extra Strong Pipe.
Nipples longer than Standard can be furnished when ordered.
All dimensions given in inches.
In ordering special lengths always specify the length of thread desired.
174
Casing Nipples
Wrought Casing Nipples
Fig. 65
Threaded Right Hand
Length
Size
Close
Short
Long
|
Extra long
3
2V2
3
3%
4
4V2
5
6
7
8
Q
10
TT
12
3V4
2%
4
4%
5
5V2
6
7
8
Q
TO
TT
12
3V2
2%
4
4%
5
5%
6
7
8
0
TO
II
12
3%
2%
4
4V2
5
sV2
6
7
8
9
10
II
12
4
3
4
Sft
5
sV2
6
7
8
0
TO
TT
12
4}4
3
4
45
5
SVa
6
7
8
9
10
II
12
tfi
3
4
4^
5
5%
6
7
8
9
10
II
12
4%
3
4.
4%
5
5%
6
7
8
9
IO
II
12
5
3
4
4%
S
5^
6
7
8
9
TO
II
12
58/l6
5
5V2
6
6V«
7
8
9
10
II
12
5%
6^4
S
5V2
6
6V2
V
7
7
8
8
9
9
IO
IO
II
II
12
12
6
7
'ft
9
IO
II
12
75 /
6
7
8
Q
IO
II
12
8*4
6
7
8
9
IO
II
12
8%
7
8
9
IO
II
12
9%
~f-t
8
9
IO
II
12
10%
7
8
9
10
II
12
Made from lightest weight Standard Boston Casing and same number of
threads per inch as shown on page 26, unless otherwise ordered.
Nipples longer than 12 inches can be furnished when ordered.
All dimensions given in inches.
Threaded Flanges 175
Extra Heavy Pipe Flanges (Threaded)
Suitable for 250 Pounds Working Steam Pressure
Adopted by a Conference of Manufacturers, June 28, 1901
Pipe size
Flange
Bolts
Weight
In-
Ex-
Out-
per
ternal
diam-
ternal
diam-
side
diam-
Thick-
ness
Length
Num-
ber
Size
Length
Circle
pair
eter
eter
eter
2
23/8
6V2
%
i%
4
%
3
S
15
2%
2%
7%
I
i%6
4
%
31/2
5%
21
3
3^2
81/4
i%
I%6
8
%
31/2
6%
28
m
4
9
I%6
i%
8
%
3V2
7V*
34
4
4%
10
1%
i%
8
%
4
7%
44
4Va
5
10%
I%6
I18/16
8
%
4
8V2
So
5
59/16
II
1%
1%
8
%
4
9%
56
6
6%
I2V2
iTAe
2
12
%
4l/2
105/8
72
7
7%
14
1%
2Vl6
12
%
4V2
HT/8
91
8
9
8%
9%
IS
16
i%
i%
a-
12
12
%
%
5
5
13
14
108
126
10
10%
17%
i%
2%
16
%
sV2
15%
155
II
n%
18%
2
2%
16
%
sy2
16%
186
12
12%
20
2
a%e
16
%
sV2
17%
209
13
14
22%
2%
21^16
20
7/8
6
20
288
14
rs
23%
2%6
ai%6
20
I
6
21
311
IS
16
25
2U
2%
2O
I
6
22V2
363
18
27
2%
3Vl6
24
I
6V2
24V2
423
20
29V2
2%
3^4
24
iVs
7
26%
515
22
311/2
2%
3Vl6
28
11/8
7
283/4
587
24
34
2%
3%
28
iVs
7V2
31%
713
All dimensions given in inches.
All weights given in pounds.
Weights specified do not include bolts and gaskets.
176 Threaded Flanges
Standard Pipe Flanges (Cast Iron, Threaded)
Adopted August, 1894, by a Committee of the Master Steam and Hot Water
Fitters' Association, a Committee of the American Society of Mechanical
Engineers, and the leading Valve and Fitting Manufacturers of the United
States.
Pipe size
Flange
Bolts
|l
xternal
ameter
Outside
diameter
Thick-
ness
Width of
Face
1
Size
Length
Circle
^£
W*
a
2
2%
6
%
2
4
% %
2
48/i
2%
2%
7
*%6
2%
4
% %
2V4
3
3%
m
3/4
2%
4
% %
2%
6 2
3%
4
8%
18/4e
2%
4
% %
2%
7
4
4%
9
15Ae
2%
4
% 8/4
28/4
7y2
4%
5
9%
1%6
2%
8
% 3/4
3
7%
5
5%0
10
15/16
2%
8
% 8/4
3
8%
6
6%
II
I
2%
8
% 8/4
3
9%
7
7%
12%
I%6
28/4
8
% 8/4
314
103/4
8
8%
13%
1%
28/4
8
% %
H8/4
9
9%
IS
1%
3
12
% 8/4
3V2
13%
10
10%
16
3
12
% %
3%
141/4
12
123/4
19
1%
3%
12
8/4 %
3%
17
13
14
21
1%
12
% I
4%
i88/4
14
15
15
16
23%
1%
f!
16
16
% I
% I
%
20
21%
18
25
i9/ie
3%
16
1%
48/4
22%
20
22
27%
Il%6
38/i
38/4
20
20
1%
5%
25
27%
24
31% 32
1% I7/8
38/4 4
2O
1%
29% 291/2
26
333/4 34%
1% 2
3% 4%
24
1%
58/4
31% 3i3/i
28
36 36%
I%6 2% 0
4 4%
28
!%
6
33% 34
30
38 38%
1% 2%
4 4%
28
%i%
61/4
35% 36
These flanges in the heavier bolting are used in general practice for pressures
up to 125 pounds per square inch. For greater pressures see table, page 175. of
extra heavy flanges adopted by a Conference of Manufacturers, June 28, 1901.
All dimensions given in inches.
Railings
HAND RAILINGS
177
The use of pipe and fittings for hand railings around area ways, on
stairs, for office enclosures with gates and for permanent ladders, is illus-
trated by the following set of cuts, which are typical of many installations
which might be made. The construction of hand railings of such
materials commends itself, first, on the ground of durability due to
material used; second, neatness of design and detail; third, safety due
to strength; and fourth, cheapness of construction. The illustrations
illustrate methods of assembling, which can be differentiated in a great
many ways, but which have been found successful and economical.
Regular railing fittings, such as shown by figures H-i64 to £[-172
inclusive, are furnished recessed, so that all short threads will be cov-
ered. Other railing fittings may be furnished in the same manner.
Fittings of special angles can also be furnished when required, at special
prices, but it is our experience that the regular patterns can be used in
almost all cases, regardless of the angles involved, either by bending the
pipe, as in Fig. 71, or by the use of extra fittings, as in Fig. 72.
The numbers on the illustrations with the letter "H" in front refer
to National Tube Company's catalogue H, issue 1909.
NOTE. All threads right-hand. Thread double length where indicated.
Numbers given refer to catalogue numbers.
178
Railings
/H.I
Fig. 67
NOTE. All threads right-hand. Thread double length where indicated.
Numbers given refer to catalogue numbers.
Fig. 68
NOTE. All threads right-hand. Thread double length where indicated.
Numbers given refer to catalogue numbers.
Railings
179
'& Fig. 69
NOTE. All threads right-hand. Numbers given refer to catalogue numbers.
Fig. 70
NOTE. Suitable for steps at 30° angle. All threads right-hand. Numbers
given refer to catalogue numbers.
180
Railings
Fig. 71
NOTE. Standard fittings used and pipes bent to suit any angle of steps. All
threads right-hand. Thread double length where indicated. Numbers given
refer to catalogue numbers.
Fig. 72
NOTE. Standard fittings are suitable for any angle of steps. All threads
right-hand. Thread double length where indicated. Numbers given refer to
catalogue numbers.
Railings
181
Fig. 73
NOTE. Standard fittings are suitable for any angle of steps. All threads
right-hand. Thread double length where indicated. Numbers given refer to
catalogue number.
Fig. 74
NOTE. Fittings marked "A" are bored to turn on pipes for hinges. All
threads right-hand. Thread double length where indicated. Numbers given
refer to catalogue number.
182
Railings
Fig- 75
NOTE. All threads right-hand. Thread double length where indicated.
Numbers given refer to catalogue number.
Fig. 76
NOTE. All threads right-hand. Thread double length where indicated.
Numbers given refer to catalogue numbers.
Pipe Ladders
183
o=
Fig. 77
Round Pipe Rungs
Round Pipe Runners
Fig. 78
Flat Bar Rungs
Round Pipe Runners
Typical Pipe Ladders
184
Pipe Ladders
Fig. 79
Round Pipe Rungs
Round Pipe Runners
Fig. 80
Square Pipe Rungs
Rectangular Pipe Runners
Typical Pipe Ladders
Pipe Ladders
185
=§
~l
'
•
©
e
©
©
©
©
©
©
©
©
:
c
Fig. 81
Square Pipe Rungs
Rectangular Pipe Runners
Fig. 82
Round Pipe Rungs
Rectangular Pipe Runners
Typical Pipe Ladders
186
Pipe Ladders
Fig. 83
Round Pipe Rungs
Round Pipe Runners
Fig. 84
Square Pipe Rungs
Square Pipe Runners
Typical Pipe Ladders
Working Barrels
187
WORKING BARRELS
The working barrels, sizes and weights of which are given in table
shown, are manufactured from specially made lap-welded pipe. The
steel from which these lap-welded pipes are made is of a special corn-
position with a view to obtaining a hard, smooth surface in the finished
working barrel.
The making of the working barrel from a lap- welded pipe is accom-
plished by a special process consisting of several cold-drawing oper-
ations. These cold-drawing operations make the inside surface of the
working barrel extremely smooth and bright; besides that it still fur-
ther hardens the surface of the working barrel, over and above the hard-
ness already established in the especially prepared lap-welded pipe.
This process of manufacturing working barrels makes them especially
adapted and suited for the hard service to which they are subjected in
the oil fields.
i...
Fig. 85
k-3«4">J
! Std.0il Well Tubing 11 J$th
H-iSM
>JMG Fig'86
3 WORKING BARREL
2^ StdLOU Well Tubing llj$th
ny&r' ^r°
li
Fig. 88
NOTE. All Working Barrels are threaded 14 threads per inch.
188
Seamless Cylinders
Table of Lengths and Weights of Working Barrels
1
2-inch Barrel
2^-inch Barrel
3-inch Barrel
4-inch Barrel
i
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bo
bo
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P
Ft.In.
Lbs.
Lbs.
Lbs.
Lbs.
Lbs.
Lbs.
Lbs.
Lbs.
Lbs.
Lbs.
Lbs.
Lbs.
4-0
29
2.5
3.5
3i
3-5
5
44
5.5
6.5
66
8
Q
4-6
34
35
48
72
5-o
37
38
53
78
5-6
4O
41
57
84
6-0
43
45
61
90
6-6
46
47
65
96
7-0
49
50
69
103
7-6
53
54
74
109
8-0
56
57
77
115
9-0
63
64
85
127
10-0
70
71
93
139
SEAMLESS CYLINDERS
National Tube Company manufactures seamless cylinders for a variety
of purposes: containers for oxygen, carbonic acid, air, etc. A wide range
of sizes is produced, varying from a few pounds in weight up to 1 8 and 20
inches in diameter with %-inch wall and 12 to 14 feet long.
The smaller cylinders are manufactured from a seamless hot-rolled
or cold-drawn tube, one end being forged to form the neck, and the
other end being closed in for the bottom.
The larger cylinders are made from a flat plate, cupped and hot- drawn
into a cylindrical shell. The closed end of the shell, remaining from the
cupping process, forms the bottom of the container; the open end is
forged to form the neck.
The material used for making cylinders is basic open-hearth steel of
analysis to give desired physical properties; low-medium, high-carbon
and nickel steels, also chrome-vanadium steels, are regularly furnished
when desired.
NOTE. See standard specifications for seamless cylinders.
Cylinder Heads
189
CYLINDER HEADS ; THEIR STRENGTH, ETC.
The ends of pipes or tubes may have heads put in or formed with them
in order to produce cylinders. Commercial considerations of quantity
of cylinders, cost of manufacture, handling, etc., affect the selection of
the design, often to greater extent than do engineering considerations.
A design that would be permissible and cheap on 10 ooo heads might
be of prohibitive cost on one head. The ordinary shapes of heads are
here shown:
Fig. 89
Fig. 90
Fig. 91
Fig. 92
. Fig. 93
Fig. 94
Fig. 95
Fig. 96
Fig. 97
Fig. 98
Fig. 99
Fig. 100
Fig. 101
Fig. 102
Fig. 103
190 Cylinder Heads
Figs. 89, 98, and 101 show "flat heads'' Fig. 89 shows the seamless
shape which is frequently used on cylinders of large diameters over 10
inches, when the cylinders are required to stand upright. Fig. 98 shows
a head welded in lap-weld pipe. Such is desirable at times because the
thick heads permit tapping for connections. When only a few cylinders
are wanted such heads are relatively cheap. Fig. 101 shows style of
welded heads used on annealing pots.
Figs. 90 and 91 show heads that are called "Round," or "Spherical" on
seamless cylinders, while Fig. 100 shows heads that are called "Bumped"
in the case of lap-weld cylinders. Bumped heads are brazed in. This
style of heads is used on cylinders that are not required to stand up-
right.
Figs. 92, 94, 95, 96, 97, 102, and 103 show styles of heads that are
applied to cylinders that are required to stand upright. Figs. 92, 94, and
95 are used on seamless cylinders up to lo-inch diameter. Figs. 96 and 97
may be used on any size of lap-weld cylinders. Fig. 102 is practically
restricted in use to small sizes and is frequently made tight by means
of hard or soft solder.
Fig. 93 shows what may be called the "Standard" neck, end, or head
used on all seamless cylinders.
Fig. 99 shows a "converged" form of ends, which are so formed in
order to prevent the fingers from slipping off when handling the cylin-
ders. This shape does not affect or increase the strength or security
of the heads to any calculable extent.
Thin heads that must be drilled and tapped usually require rein-
forcement at the holes. A common form of such is shown in Fig. 103,
which illustrates what is called a welded "boss" or "pop."
Figs. 90 and 91 show heads that are usually the consequent product
from the plates of which the cylinder is drawn, but many are produced
by a spinning operation from the material of the tubes, and so permits
a cylinder to be made from "plain-end" tube. Using lap- weld pipe this
shape may be made by swaging down to a shape somewhat like Fig. 95,
and then welding, or welding in a plug.
The strength of heads is usually determined, in the case of round, spher-
ical, or bumped heads (Figs. 90, 91, and 100), by the simple approximate
rule for spheres subjected to internal pressure: i.e.,
pD = 4 TS,
which is suitable in such cases, as pd = 2 ts is suitable for pipes. There-
fore, for one pressure and one fiber stress the thickness of a sphere would
be half the thickness of a cylinder of same diameter, or for equal thick-
ness the radius of the sphere would equal the diameter of the pipe. The
same rule may be applied to the shape per Figs. 93 and 95, but the
radius of curvature of such shape is usually determined by the swaging
process by which it is produced. That process also invariably thickens
the material toward the neck.
The cupped heads like Fig. 91, having the thickness of the plate from
which the tube is made, usually can stand having the head dished in,
without the head being weaker than the shell.
Cylinder Heads
191
The strength of welded dished heads (Figs. 96, 97, 99, and 102) is less
understood, but the marine-inspection laws usually allow them to carry
%o the pressure that may be put on bumped heads. Expressed other-
wise, the thickness of dished heads by such rules must be i% times
the thickness of bumped heads. Thus
pDl 2\ 5PD .5PR
2 — i j _ i _ _ .
45 \ 37 12 s 6s
Assume that steel of good welding quality may be stressed to s —
20 ooo pounds per square inch by test pressure = p; then an approxi-
mate solution gives the thickness of heads stated in the following table
for value of R and p (in inches and pounds per square inch). R = radius
of curvature of spherical dished heads.
Table of Thickness of Dished Heads
Radius
R
500
700
IOOO
Test pressure
1500
P
2OOO
25OO
3000
2
.042
.058
.083
.13
• 17
.21
.25
3
.063
.088
.13
.19
.25
• 31
.38
4
.083
.12
.17
.25
.33
.42
• 50
5
.10
.15
.21
.31
.42
• 52
.63
6
.13
.18
.25
.38
• 50
.63
• 75
8
.17
.23
.33
.50
.67
.83
I.O
10
.21
.29
.42
.63
.83
I.O
1-3
12
.25
.35
.50
•75
I.O
1.3
i.S
14
.29
.41
.58
.88
1.2
1.5
1.8
16
.33
• 47
.67
I.O
1.3
1-7
2.0
20
.42
.58
.83
1.3
1-7
2.1
2.5
24
.50
.70
I.O
1.5
2.O
2.5
3.0
30
-63
.88
1.3
1-9
2.5
3-1
3.8
N.B. — This rule indicates that it makes no difference what is the diameter
of pipe, provided it does not exceed twice the radius (/?) of the sphere. No
thicknesses are given for less test than 500 pounds because no lap-weld pipes
are made that will not stand such test.
The strength of fiat heads (Figs. 89, 98, and 101) is difficult to determine
analytically, but the usually accepted formula is that of Grashof derived
from the difficult "Theory of Elasticity." The formula is
r =
If we use pD = 2 ts for cylindrical wall of pipe, we may combine the two
rules, making p and s equal, and find that
T = 0.645
192 Shelby Seamless Steel Specialties
An approximate solution of this gives the thickness of head (in inches)
here tabulated.
Table of Thickness of Flat Heads
External
diam-
Thickness of pipe
eter of
pipe
C.J.* .125
.20
• 25
.375
• 50
• 75
2
.28 .32
• 41
.46
.56
.64
4
.46 .46
.58
.64
• 79
• 91
i.i
6
.59
• 71
• 79
.97
I.I
1.4
8
.73
.82
• 91
I.I
1.3
1.6
10
.85
• 91
I.O
1.3
1-4
1.8
12
.98
I.O
i.i
1-4
1.6
1-9
16
1.3
1.3
1.6
1.8
2.2
20
24
1.5
i 8
1.8
I 9
2.0
2 2
2.5
2 7
30
23
2.5
3.1
* C. J. refers to the set of thicknesses given on page 43 for Converse joint pipe.
For practical reasons it is not wise to attempt to weld less thickness of head in
any diameter than given in this table. The great thickness of flat heads renders
them advantageous for drilling and tapping connection holes.
SHELBY SEAMLESS STEEL SPECIALTIES
Shelby Seamless Steel Tubing is formed into special shapes to meet
special requirements, where hollow forgings can be used to advan-
tage to replace solid forgings requiring a boring operation, thus saving
machine work and material. Special shapes made from seamless tub-
ing have found a wide use, and new applications are constantly develop-
ing.
The homogeneous character of the material entering into a seamless
tube permits the working of the material into a great variety of intricate
shapes such as the requirements may demand.
By the cupping process, in which seamless articles are made by the
progressive cupping of a round plate, certain special shapes may be pro-
duced without first producing the cylindrical tube.
Special shapes of tubular sections are usually formed hot, and are
subject to certain variations of dimensions which are to be expected in
all hot-forged articles.
The aim is to produce the forgings with just sufficient allowances to
enable the user to finish them by machining to required dimensions
where accurate sizes are required. In some cases, however, special
shapes of uniform section are formed cold, in which case greater accuracy
in formed dimensions is the rule.
Shelby Seamless Steel Specialties
193
Automobile Specialties
The illustrations cover a few automobile specialties, in the shape of
axles. These axles are made from seamless tubing, of different material
to suit the requirements.
These specialties are formed by swaging, expanding and upsetting
either from hot-finished or cold-drawn tubing.
Fig, 104. Shelby Seamless Steel Front and Rear Axles
194
Shelby Seamless Steel Specialties
Cylinder Specialties
The illustrations below cover a few cylinder specialties, in the form
of various styles of valve protecting caps, and also boiler shells and
floats for feed water regulators, made partly direct by the cupping
process, and partly from tubing.
A B C D
Fig. 105. Various Styles of Valve Protecting Cap Used on
Carbonic Acid Gas Cylinders
2225.
Fig. 106. Boiler Shells
Fig. 107. Floats for Feed
Water Regulators
Cream Separator Specialties
The illustrations below cover a few cream separator specialties made
direct from plates.
Fig. 108. Cream Separator Forgings
Shelby Seamless Steel Specialties
195
Bent Specialties
The illustrations below cover a few bent specialties.
Fig. 109 Shelby Seamless Steel Tubes Bent
Miscellaneous Specialties
The illustrations below cover a few miscellaneous forgings, some of
which are made direct from plates, and others from tubing.
i
Forging for Shaft Bearing
Fig. no
Steel Cone
196
Shelby Seamless Steel Specialties
Angular Section Specialties
The illustrations below cover a few specialties in Angular section
tubing, mainly in the shape of socket wrenches.
Socket Wrench
Socket Wrench
Fig. in
Tapered Specialties
The illustrations below cover a few specialties of Taper Tubing.
These tubes are tapered by different methods, as the conditions may
call for.
Shelby Seamless Steel Tubing Tapered
Shelby Seamless Steel Tubing Tapered
Shelby Seamless Steel Tubing Tapered
Fig. 112
NOTE. We are prepared to furnish other specialties and will be glad to supply
full information on receipt of blue prints or sketches showing exactly what is
required.
Seamless Trolley Poles 197
SHELBY SEAMLESS COLD-DBA WN STEEL
TROLLEY POLES
Under normal conditions of service, a trolley pole is subjected to stress
as a beam rigidly secured at one end and loaded on the free end. This
condition of loading causes a maximum bending moment at the point of
support, which bending moment decreases uniformly to zero at the point
of applying the load. Abnormal conditions cause other stresses of un-
known magnitude, which can be provided against only by a judicious
increase in the strength of the pole over that required for the known
stresses.
The trolley pole of minimum weight, to resist the known stresses,
would have a maximum cross-sectional area at the trolley base or point
of support, with the cross section decreasing uniformly to nothing at
the harp. For practical reasons, such a theoretical pole is not desirable.
In the design of the Shelby poles, the theoretical requirement for mini-
mum weight has received careful consideration, while providing for the
unknown stresses and a practical form to suit the standard trolley bases
and harps.
The standard Shelby poles are made from 13 -gage material, as years
of practical experience have shown that a lighter gage may fail by
local injuries, and a heavier gage simply adds to the weight of the pole
without increasing its strength to a corresponding extent. The theo-
retical requirement for a pole of minimum weight points out a method
for increasing the strength of the pole without a proportionate increase
in the weight. This method consists in the use of a reinforcement at
the base end, and on the inside of the 13 -gage member. The length
of this reinforcement is varied, to suit the requirement as to strength,
up to a maximum which occurs when the length of the reinforcement
is such that the resistance to bending at the end of the reinforcement
is just equal to the resistance to bending at the trolley base.
The Shelby trolley pole is regularly manufactured in two designs, viz.:
Standard "A" and Standard "B."
In the Standard "A" pole, the reinforcement is only of sufficient
length to prevent deformation of the circular section by the stresses
caused by the service of the pole or by the clamp on the trolley base.
This design is suitable for all ordinary service, and makes the lightest
pole it is practicable to manufacture or use.
In the Standard "B" design, the reinforcement is of the maximum
length required by the condition of two points in the length of the pole
with equal resistance to bending. Speaking generally, the Standard
" pole will be 20 per cent heavier and 50 per cent stronger than the
Standard "A" pole. This design is intended to meet the most severe
service conditions.
Externally, the two designs are duplicates, the outside diameter being
inches, which, at a point 30 inches from the end of the pole, is re-
duced to i% inches, which diameter is again reduced to i inch for a
distance of 6 inches from the end of the pole. The ii^-inch diameter
198
Seamless Trolley Poles
merges into the i%-inch diameter, with fillets of large radii, and the
i%-inch diameter into the i-inch diameter, with a gradual taper 6 inches
long. The section i inch in diameter is reamed to a %-inch hole.
Special designs, varying in some or all particulars from the standard
designs, are made to meet special requirements.
Shelby trolley poles are made from a selected grade of basic open-
hearth steel of about 0.17 per cent carbon, low in phosphorus and
sulphur. Prior to the last cold-drawing operation, the material is given
a special heat treatment which leaves the grain in the finest condition.
The elastic limit of the material in the finished pole is from 60 ooo to
70 ooo pounds per square inch.
Recent improvements have been made in the methods of manufac-
ture, particularly in the method of inserting the reinforcement. As now
made, the reinforcement is integral with the body of the pole, which adds
materially to its efficiency.
The following table gives loads and deflections of various length poles
at the elastic limit:
Length, feet
Average weight,
pounds
Load carried at
end of pole at
elastic limit,
pounds
Deflection due to
load at elastic
limit and weight
of pole, inches
Standard" A1' Pole
12
13
14
15
18.4
20.3
22.3
24.3
48
44
40
36
13%
15%
17%
19%
Standard " B " Pole
12
13
14
15
22.7
24.7
26.7
28.7
75
69
62
55
22Y2
36%
30
33
Properties of Shelby Seamless Tubing 199
PROPERTIES OF SHELBY SEAMLESS TUBING
Outside Diameter, Surface, and Volume or Displacement
Outside surface
Lineal
External volume or displace-
Outside
per lineal foot
feet per
Per lineal foot
diameter.
square
Inches
Square
inches
Square
feet
foot out-
side sur-
face
Cubic
inches
Cubic
feet
United
States
gallons
4
18.85
.1309
7.639
2.356
.0014
.0102
%
23.56
.1636
6. 112
3.682
.0021
.0159
8/4
28.27
.1963
5.093
5-301
.0031
.0229
%
32.99
.2291
4.365
7.216
.0042
.0312
I
37-70
.2618
3.820
9.425
.0055
.0408
iVs
42.41
.2945
3.395
11-93
.0069
.0516
IV4
47-12
.3272
3.056
14-73
.0085
.0637
1%
51-84
.3600
2.778
17.82
.0103
.0771
iV2
56.55
.3927
2.546
21.21
.0123
.0918
1%
65.97
.4581
2.183
28.86
.0167
.1249
2
75-40
.5236
1.910
37-70
.0218
.1632
2H
84.82
.5890
1.698
47-71
.0276
.2065
2%
94-25
.6545
.528
58.90
.0341
.2550
2%
103.67
.7199
.389
71.27
.0412
.3085
3
113.10
.7854
.273
84.82
.0491
.3672
3V4
122.52
.8508
.175
99-55
.0576
.4309
3V2
I3L95
.9163
.091
115-45
.0668
.4998
38/4
I4L37
-9817
.019
132.54
.0767
• 5737
4
150.80
1.0472
.955
150.80
.0873
.6528
4V4
160.22
1.1126
.899
170.24
.0985
.7369
*H
169.65
1.1781
.849
190.85
.1104
.8262
48/4
179-07
I • 2435
.804
212.65
.1231
.9205
5
188.50
1.3090
.764
235 • 62
.1364
I.020O
5V4
197.91
1.3744
.728
259-77
.1503
I . 1245
5V2
207.35
1-4399
.694
285 . 10
.1650
1.2342
53/4
216.76
1-5053
.664
3ii.6l
.1803
1.3489
6
226 . 20
1.5708
.637
339-29
.1963
1.4688
200 Properties of Shelby Seamless Tubing
Sectional Area of Wall in Square Inches
Outside
diam.
Inches
Thickness in gage and fractions of an inch
22
B.W.G.
20
B.W.G.
18
B.W.G.
He
%2
Vs
%2
%6
%
%
8/4
%
X
iVs
1%
1%
iVa
1%
2
2V4
2%
2%
3H
1
k
4%
4%
L
s$
5%
6
.04152
.05251
.06351
.07451
.08550
.09650
.1075
.05113
.06487
.07862
.09236
.1061
.1199
.1336
.1473
.1611
.06943
.08867
.1079
.1272
.1464
.1656
.1849
.2041
.2234
.0859
.1104
.1350
.1595
.1841
.2086
.2332
.2577
.2823
• 3313
.3804
.4295
.4786
.5277
.1197
.1565
.1933
.2301
.2669
.3037
• 3405
• 3774
.4142
.4878
.5614
.6351
.7087
.7823
8560
.1473
.1963
.2454
.2945
.3436
.3927
.4418
.4909
.5400
.6381
.7363
.8345
.9327
1.031
T29
.2915
.3528
.4142
• 4755
.5369
.5983
.6596
.7823
.9050
1.028
1.150
1.273
1.396
I.5I9
1.641
1.764
1.887
2.010
2.132
2.255
2.378
2.501
2.623
2.746
2.868
.3313
.4050
• 4786
• 5522
.6259
.6995
• 7731
.9204
i. 068
.215
.362
.509
.657
.804
.951
.098
2.246
2.393
2.540
2.688
2.835
2.983
3.129
3-277
.3.424
.9296
1.003
.227
.325
.424
.522
Capacity in Cubic Inches per Lineal Foot
V2
%
8/4
7/8
i
1%
a*
i%
2
(4i
3
k
3MS
38/4
k
4H
4%
SV4
5V2
S?/4
6
1.858
3.051
4-539
6.322
8.399
10.770
13.436
1.743
2.903
4.358
6.107
8^151
10.490
13.123
16.051
19.273
1.523
2.618
4.007
5.690
7.668
9.941
12.508
15-37
18.53
1.325
2.356
3-682
5.301
7.216
9.425
H.93
14-73
17.82
24.89
33.13
42.56
53.16
64.94
.920
1.804
2.982
4-455
6.222
8.283
IO.64
13.29
16.24
23.01
30.96
40.09
50.40
61.89
74-55
88.39
103.41
.589
1.325
2.356
3.682
5-301
7.216
9.425
H.93
14-73
21.21
28.86
37-70
47-71
58.90
71.27
84.82
99-55
115 45
1.804
2.982
4-455
6.222
8.283
IO.64
13.29
19.48
26.84
35.38
45-10
56.00
68.07
81.33
95.76
ill 37
1-325
2.356
3-682
5-301
7.216
9.425
11-93
17.82
24.89
33-13
42.56
53.16
64.94
77-90
92.04
107-35
123.85
I4L52
160.37
180.40
201.60
223.99
247-55
272.28
208.20
132.54
128.15
146.12
165.26
185.59
207.09
229.76
253 62
278.65
.304 87
Properties of Shelby Seamless Tubing 201
Sectional Area of Wall in Square Inches
Outside
Thickness in fractions of an inch
diam.
Inches
7/32
V4
5/16
%
V2
%
%
%
I
%
• 4510
i
.5369
.5890
1%
.6228
.6872
.7087
.7854
.92O4
1.031
i%
.7946
.8836
1.043
1.178
fft
.8805
.9817
1.166
1.325
1.571
.052
I.I78
1.411
1.620
1.963
2
.224
1.374
1.657
1.914
2.356
2.700
2*4
.396
I.57I
1.902
2.209
2.749
3.I9I
2*£
.568
1.767
2.148
2.503 3.142
3-682
2%
.740
1.963
2.393
2.798
3-534
4.172
3
• 911
2.160
2.638
3-093
3.927
4.663
5-301
5.841
6.283
3V4
.083
2.356
2.884
3.387
4.320
5.IS4 5.890
6.529
7.069
2.255
2.553
3.129
3-682
4.712
5-645
6.480
7.2l6
7-854
3%
2.427
2.749
3-375
3.976
5.105
6.136
7.069
7.903
8.639
4
2.599
2.945
3.620
4.271
5.498
6.627
7-658
8-590
9-425
4V4
2.770
3.142
3.866
4.565
5.890
7.118
8.247
9.278
IO.2IO
41/2
2.942
3.338
4. in
4.860
6.283
7.609
8.836
9 965
10.996
48/4
3.H4
3-534
4-357
5-154
6.676
8.099
9.425
10.652
II.78I
5
3-286
3-731
4.602
5-449
7.069
8.590
10.014
11.339
12.566
5*4
3-458
3.927
4.848
5-744
7.462
9.082
10.603
12.029
13.352
sV2
3.629
4-123
5-093
6.038
7-854
9-572
11.192
12.714
14.137
5%
3.8oi
4.320
5-338
6.332
8.246
10.063
11.781
13.401
14.922
6
3-973
4.5i6
5.583
6.626
8.639
10.553 1 12. 370
14.088
15.708
Capacity in Cubic Inches per Lineal Foot
n
I
1.804
I
I
2.982
2.356
1
1*6
4-455
3-682
1*4
6.222
5-301
3-682
2.356
i%
8.283
7.216
5-301
3-682
1*^2
10.64
9.425
7.216
5-301
2.356J
i%
16.24
14-73
11.93
9.425
5-301
2
23-01
21.21
17.82
14-73
9.425
5-301
2*4
30.96
28.86
24.89
21.21
14-73
9.425
2*;2
40.09
37-70
33.13
28.86
21.21
14-73
2%
50.40
47.71
42.56
37-70
28.86
21.21
3
61.89
58.90
53.16
47-71
37-70
28.86
21.21
14-73
9-425
3*4
74-55
71.27
64-94
58.90
47-71
37.70
28.86
21.21
14 73
3V2
88.39
84.82
77-90
71.27
58.90
47-71
37.70
28.86! 21.21
38/4
103.41
99 55
92.04
84.82
71.27
58.90
47-71
37.70 28 86
4
119.61
115-45
107-35
99-55
84.82 71.27
58.90
47-71
37-70
4V4
136.99
132.54
123.85
115-45
99-55 84.82
71.27
58.90
47-71
155-55
150.80
141.52
132.54
115-45 99-55
84.82
71 .'27
58.90
48/4
175.28
170.24
160.37
150.80
132.54 115-45
99-55
84.82
71.27
5
196.19
190.85
180.40
170.24
150.80
132.54
115-45
99-55
84.82
5*4
218.28
212.65
201.60
190.85
170.24
150.80
132.54
115-45
99-55
5*&
24L55
235.62
223.99
212.65
190.85
170.24
150.80
132.54
115-45
5%
265.99
259.78
247-55
235.62
212.65
190.85
170.24
150.80
132.54
6
291.61
285 . 10
272.28
259 78
235 62
212.65
190.85
170.24
TSO 80
202 Properties of Shelby Seamless Tubing
Capacity in Cubic Feet per Lineal Foot
Outside
diarn.
Inches
Thickness in gage and fractions of an inch
22
B.W.G.
20
B.W.G.
18
B.W.G.
Vl6
%2
y8
%2
3/16
%
%
8/4
%
I
iVs
IH
1%
iV2
I3/4
2
2}i
2%
2%
k
3V2
33/4
4
4V4
4V2
43/4
5V4
%
6
.00108
.00177
.00263
.00366
.00486
.00623
.00778
.OOIOI
.00168
.00252
.00353
.00472
.00607
.00759
.00929
.01115
.00088
.00151
.00232
.00329
.00444
.00575
.00724
.00889
.01072
.00077
.00136
.00213
.00307
.00418
.00545
.00690
.00852
.01031
.01440
.01917
.02463
.03076
.03758
.00053
.00104
.00173
.00258
.00360
.00479
.00616
.00769
.00940
.01332
.01792
.02320
.02917
.03581
.04314
.05115
.05985
.00034
.00077
.00136
.00213
.00307
.00418
.00545
.00690
.00852
.01227
.01670
.02182
.02761
.03409
.04125
.04909
.05761
.06681
.07670
.00104
.00173
.00258
.00360
.00479
.00616
.00769
.01127
.01553
.02047
.02610
.03241
.03939
.04706
-05542
.06445
.07416
.08456
.09564
. 10740
.11984
. 13297
. 14677
.16126
. 17643
.00077
. 00136
.00213
.00307
.00418
.00545
.00690
.01031
.01440
.01917
.02463
.03076
.03758
.04508
.05326
.06213
.07167
.08190
.09281
. 10440
.11667
. 12962
. 14326
. 15757
. 17257
Capacity in U. S. Gallons per Lineal Foot
%
%
%
%
i
i%
m
i%
m
I8/4
2
2V4
1
&
3V2
33/4
4
4%
4V2
48/4
5
5V4
sV2
5%
.0080
.0132
.0197
.0274
.0364
.0467
.0582
.0075
.0126
.0189
.0264
-0353
.0454
.0568
.0695
.0834
.0066
.0113
-0173
.0246
.0332
.0430
.0541
.0665
.0802
.0057
.0102
.0159
.0229
.0312
.0408
.0516
.0637
.0771
.1077
.1434
.1842
.2301
.2811
.0040
.0078
.0129
.0193
.0269
.0359
.0461
.0575
.0703
.0996
.1340
.1736
.2182
.2679
.3227
.3827
• 4477
.0025
.0057
.0102
.0159
.0229
.0312
.0408
.0516
.0637
.0918
.1249
.1632
.2065
.2550
.3085
.3672
.4309
.4998
.5737
.0078
.0129
.0193
.0269
.0359
.0461
.0575
.0843
.1162
.1532
.1952
.2424
.2947
.3521
.4145
.4821
.5548
.6326
.7154
.8034
.8965
.9946
1.0979
I . 2063
I.3I98
.0057
.0102
• 0159
.0229
.0312
.0408
.0516
.0771
.1077
.1434
.1842
.2301
.2811
.3372
.3984
4647
.5361
.6126
.6942
.7809
.8727
.9696
1.0716
I . 1787
1.2909
Properties of Shelby Seamless Tubing 203
Capacity in Cubic Feet per Lineal Foot
Outside
Thickness in fractions of an inch
diam.
Inches
%2
V4
5/16
%
V2
% 1 8/4
%
I
V-2
%
.00104
I
.00173
.00136
iys
.00258
.00213
lV4
.00360
.00307
.O02I3
.00136
1%
.00479
.00418
.00307
.00213
.00616
•00545
.OO4l8
.00307
.00136
1%
.00940
.00852
.00690
.00545
.00307
2
.01332
.01227
.01031
.00852
.00545
.00307
2^4.
.01792
.01670
.OI44O
.01227
00852
.00545
2^2
.02320
.02182
.01917
.01670
.01227
.00852
2%
.02917
.02761
.02463
.02182
.01670
.01227
3
.03581
.03409
.03076
.02761
.02182
.01670
.01227
.00852
.00545
3H
.04314
.04125
.03758
.03409
.02761
.02182
. 01670
.01227
.00852
31/!'
.05115
.04909
.04508
.04125
.03409
.02761
.02182
.01670
.01227
3%
.05985
.05761
.05326
.04909
.04125
.03409
.02761
.02182
.01670
4
.06922
.06681
.06213
.05761
.04909
.04125
.03409
.02761
.02182
.07928
.07670
.07167
.06681
.05761
.04909
.04125
.03409
.02761
4*/2
.09002
.08727
.O8I90
. 07670
.06681
.05761
.04909
.04125
.03409
43A
. 10143
.00852
.09281
.08727
.07670
.06681
.05761
.04909
.04125
5
.11354 .11045
. 10440
.09852
.08727
.07670
.06681
.05761
.04909
.12632 .12306
.11667
.11045
.09852
.08727
.07670
.06681
.05761
sV2
.13978 .13635
. 12962
. 12306
.11045.
.09852
.08727
.07670
.06681
53/i
.15393 .15033
. 14326
. 13635
. 12306
.11045
.09852
.08727
.07670
6
.16876! .16499
.15757
• 15033
. 13635
. 12306
.11045
.09852
.08727
Capacity in U. S. Gallons per Lineal Foot
V2
8/4
.0078
I
.0129
.0102
j_y#
.0193
.0159
i*4
.0269
.0229
.0159
.0102
i%
.0359
.0312
.0229
.0159
1^2
.0461
.0408
.0312
.0229
.0102
1%
.0703
.0637
.0516
.0408
.0229
2
.0996
.0918
.0771
.0637
.0408
.0229
2^
.1340
.1249
.1077
.0918
.0637
.0408
2-Vii
.1736
.1632
• 1434
.1249
.0918
.0637
2%
.2182
.2065
.1842
.1632
.1249
.0918
3
.2679
.2550
.2301
.2065
.1632
.1249
.0918
.0637
.0408
3V4
.3227
.3085
.2811
.2550
.2065
.1632
.1249
.0918
.0637
.3827
.3672
• 3372
.3085
.2550
.2065
.1632
.1249
.0918
3SA
• 4477
.4309
.3984
.3672
.3085
.2550
.2065
.1632
.1249
4
.5178
.4998
.4647
• 4309
.3672
.3085
.2550
.2065
.1632
4^4
• 5930
.5737
.536i
.4998
• 4309
.3672
.3085
.2550
.2065
4%
.6734
.6528
.6126
.5737
.4998
.4309
.3672
.3085
.2550
48/4
.7588
.7369
.6942
.6528
• 5737
.4998
• 4309
.3672
.3085
5
.8493
.8262
.7809
.7369
.6528
• 5737
.4998
• 4300
.3672
34
• 9449
.9205
.8727
.8262
.7369
.6528
• 5737
.4998
.4309
1-0457
1.0200
.9696
.9205
.8262
.7369
.6528
.5737
.4998
53/!
I.I5I5
1.1246
1.0716
1.0200
.9205
.8262
.7369
.6528
-5737
6
I . 2624
I 2342
i . 1787
I 1246
I O2OO
.9205
.8262
7369
6528
204 Properties of Shelby Seamless Tubing
Moment of Inertia, I, for Neutral Axis through Center of Section
Outside
diam.
Inches
Thickness in gage and fractions of an inch.
22
B.W.G.
20
B.W.G.
18
B.W.G.
M6
%S
Vs
%2
%6
%
%
8/4
%
I
x%
ife
1%
x%
1 i%
2
2V4
2*£
£
$
4
4U
4V2
4%
1%
§S
6
.00116
.00234
.00414
.00669
.01011
.01453
.02008
.00139
.00283
.00504
.00816
.01237
.01782
.02467
.03309
.04324
.00179
.00370
.00666
.01088
.01659
. 02402
.03339
•04493
.05885
.00210
.00442
.00804
.01324
.O203I
.02954
.O4I2I
.05562
.07304
.Il8l
.1787
.2571
3557
4767
.00260
.00569
.01062
.01781
.02769
.04071
.05728
.07785
.1028
.1678
.2556
.3698
.5137
.6909
.9047
1. 159
1.456
.00288
.00652
.01246
.02128
.03356
.04985
.07075
.09683
.1287
.2119
.3250
.4727
.6594
.8899
1.169
1.500
1.890
2.341
2.859
.01373
.02386
.03812
.05724
.08192
.1129
.1509
.2508
.3873
.5663
• 7935
1.075
I.4I5
1.822
2.299
2.853
3-490
4.216
5-035
5-955
6.980
8. 117
9-371
10.75
12.26
.01456
.02571
.04l6o
.06310
.09107
.1264
.1699
.2849
• 4431
.6514
.9165
1.246
1.645
2.123
2.685
3.338
4.092
4-947
5.917
7.005
8.219
9.566
11.05
12.69
14.48
Section Modulus, Z, for Neutral Axis through Center of Section
£5
%
%
%
i
iVs
i%
i%
m
i%
2
2%
2V2
2%
k
3tt
3%
4V4
4V2
48/i
5V4
sV2
5%
6
.00461
.00750
.0111
.0153
.0202
.0258
.0321
.00556
.00906
.0134
.0187
.0247
• 0317
.0395
.0481
• 0577
.00714
.0119
.0178
.0249
.0332
.0427
.0534
.0653
.0785
.00839
.0142
.0214
.0303
.0406
.0525
.0659
.0809
.0974
.1350
.1787
.2286
.2845
.346?
.01040
.0182
.0283
.0407
• 0554
.0724
.0917
.1132
.1371
.1918
.2556
.3287
.4110
.5024
.6031
.7130
.8321
.0115
.0209
.0332
.0486
.0671
.0886
.1132
.1408
.1716
.2422
.3250
.4201
.5275
.6472
• 7791
.9233
1.080
1.249
1.430
.0366
• 0545
.0762
.1018
.1311
.1642
.2012
.2866
.3873
.5034
.6348
.7815
.9436
1. 121
I.3I4
1.522
1-745
1.984
2.238
2.507
2.792
3.092
3.408
3.738
4.085
.0388
.0588
.0832
.1122
.1457
.1838
.2265
.3256
• 4431
• 5790
• 7332
• 9059
1.097
I 306
1-534
1.780
2.046
2.328
2.630
2.949
3-288
3 644
4.019
4 413
4.825
Properties of Shelby Seamless Tubing 205
Moment of Inertia, I, for Neutral Axis through Center of Section
Outside
Thickness in fractions of an inch
diam.
Inches
7/82
tt
%6
%
y2
%
8/4
%
I
¥2
3/4
7/8
.02698
I
.04417
.04602
1%
.06766
.07114
m
.09845 .1043
.1124
.1168
i%
.1375 I .1467
.1599
.1680
i'%
.1859
.1994
.2197
.2330
.2454
1%:
.3147 .3405
.3818
.4H3
.4449
2
.4928
.5369
.6099
.6656
.7363
.7699
2^x4
.7283 ! .7978
-9I58
1. 010
1.138
1.209
2^>
1.029
I.I32
I.3H
1-457
1.669
1.798
2%
1.404
1.549
1. 806
2.022
2.347
2.559
3
i. 860
2.059
2.414
2.718
3.I9I
3.516
3.728
3-856
3.927
3V4
2.405
2.669
3.146
3-559
4.218
4.691
5.016
5.228
5-357
m
3-048
3-390
4-013
4-559
5-449
6.108
6.581
6.906
7.118
33/i
3-797
4.231
5-026
5-731
6.900
7-790
8-449
8.922
9-247
4
4.660
5-200
6.197
7.090
8.590
9-759
10.65
II. 31
11.78
4V4
5.644
6.308
7-539
8.649
10.54
12.04
13-21
14.10
14.76
4V2
6.759
7.563
9.061
10.42
12.76
14.65
16.15
17-32
18.21
43/4
8. on
8.974
10.78
12.42
15.28
17.62
19.51
21.01
22.18
5
9.409
10.55
12.70
14.66
i8.ii
20.97
23.31
25.20
26.70
5&
10.96
12.30
14.83
17.16
21.27
24.72
27.58
29.92
31.81
sy2
12.68
14.24
17.19
19-93
24-79
28.90
32.35
35-21
37-55
53/4
14.56
16.37
19-79
22.98
28.67
33-53
37.64 141.09
43-95
6
16.63
18.70
22.65
26.33
32.94
38.63
43-49 !47-6o
51.05
Section Modulus, Z, for Neutral Axis through Center of Section
%
.0617
i
.0883
.0920
^Vs
.1203
.1265
iVi
.1575
.1669
.1798
.1869
i%
.2001
.2134
.2326
.2443
iV2
.2479
.2659
.2930
.3106
.3272
I3/4
• 3597
.3892
.4363
.4701
.5084
2
.4928
.5369
.6099
.6656
.7363
.7699
2V4
.6474
.7090
.8140
.8974
I.OI2
1.075
.8234
.9057
1.049
1.166
1. 335
1.438
2%
I.O2I
1.127
I.3I4
I.47I
1.707
1.861
3
1.240
1.372
1.610
1.812
2.127
2.344
2.485
2.571
2.618
3V4
1.480
1.643
1.936
2.190
2.596
2.887
3-087
3-217
3-295
1.742
1-937
2.293
2.605
3.114
3-490
3.760
3.946
4.067
33/!
2.O25
2.256
2.680
3-057
3-680
4-155
4.5o6
4.758
4-932
4
2.330
2.6oo
3-099
3-545
4-295
4.880
5.324
5.654
5.891
4&
2.656
2.968
3.548
4.070
4-959
5-665
6.215
6.634
6.944
3-004
3.36i
4.027
4.632
5.672
6.512
7-179
7.698
8.094
4%
3-373
3-778
4-537
5.230
6.434
7.420
8.216
8.847
9-340
5V4
3.764
4.176
4.220
4-687
5.078
5-650
5-866
6.538
7-245
8.105
8.389
9.419
9-325
10.508
10.081
11.400
10.681
I2.I2O
sV2
4 609
5.178
6.252
7-247
9.014
10.510
11.764
12.804
13-655
53/4
5-064
5.693
6.885
7 993
9-972
11.663
13.094
14.293
15-288
6
5 541
6.233
7 549
8.775
10.979
12.876
14.496
15.867
17-017
206 Properties of Shelby Seamless Tubing
Radius of Gyration, R, for Neutral Axis through Center of Section
Outside
diam.
Inches
Thickness in gage and fractions of an inch
22
B.W.G.
20
B.W.G.
18
B.W.G.
Vie
8/32
%
%2
8/10
%
%
8/4
%
I
iVs
IV4
18/8
2
2%
2V2
2%
3
3V4
3V2
38/4
k
4V2
48/4
y
5%
6
.1672
.2113
.2555
.2996
• 3438
.3880
.4322
.1649
.2090
.2531
.2972
.3414
.3856
.4297
.4739
.5181
.1604
.2044
.2484
.2925
.3367
.3808
.4250
.4691
.5133
.1563
.2001
.2441
.2881
• 3322
.3763
.4204
.4646
.5087
• 5970
.6854
• 7737
.8621
• 9504
.1474
.1907
.2344
.2782
.3221
.3661
.4101
• 4542
.4983
.5865
.6748
.7631
.8513
• 9397
1.028
1.116
1.205
.1398
.1822
.2253
.2688
.3125
.3563
.4002
.4441
.4881
.5762
.6644
.7526
.8409
.9291
.017
.106
.194
.282
• 371
.2171
.2601
.3034
.3469
.3906
• 4344
.4783
.5662
.6542
.7423
.8305
.9187
.007
.095
.183
.272
.360
.448
• 537
.625
.713
.802
.890
• 979
.067
.2096
.2519
.2948
.3380
.3815
.4250
.4688
.5564
.6442
• 7322
.8203
.9084
.9966
.085
•173
.261
•350
.438
.526
.614
• 703
.791
-879
.968
.056
Inside Surface in Square Feet per Lineal Foot
¥2
%
8/4
%
I
m
m
i%
i%
18/4
2
2V4
2V2
2%
3
3%
3%
38/4
4
4%
4V2
48/4
sV,
1
6
.1102
.1490
.1817
. .2144
.2471
.2799
.3126
.1120
.1453
.1780
.2107
.2435
.2762
.3089
.3416
.3744
.1052
.1380
.1707
.2034
.2361
.2689
.3016
.3343
.3670
.0982
.1309
.1636
.1963
.2291
.2618
.2945
.3272
.3600
.4254
.4909
.5563
.6218
.6872
.0818
.1145
.1473
.1800
.2127
.2454
.2782
.3109
.3436
.4091
.4745
• 5400
.6054
.6709
.7363
.8018
.8672
.0654
.0982
.1309
.1636
.1963
.2291
.2618
.2945
.3272
.3927
.4581
.5236
.5890
.6545
.7199
.7854
.8508
.9163
.9817
• 1145
• 1473
.1800
.2127
.2454
.2782
.3109
.3763
.4418
.5072
.5727
.6381
.7036
.7690
.8345
.8999
.9654
.0308
.0963
.1617
.2272
.2926
.3581
.4235
.4800
.0982
• 1309
.1636
.1963
.2291
.2618
.2945
.3600
.4254
.4909
.5563
.6218
.6872
-7527
.8181
.8836
.9490
.0145
.0799
.1454
.2108
.2763
-34I7
.4072
.4726
Properties of Shelby Seamless Tubing 207
Radius of Gyration, R, for Neutral Axis through Center of Section
Outside
Thickness in fractions of an inch
diam.
Inches
7/32
#
5/16
%
§
5/8
%
7/8
I
%
3/4
7/8
.2446
I
.2868
.2795
T-Ys
.3296
.3217
m
.3727
.3644
• 3494
.3366
i%
.4l6o
.4075
.3916
.3776
1^2
.4595
.4507
• 4341
.4193
• 3953
1%.
.5469
.5376
.5201
.5039
.476o
2
.6345
.6250
.6068
.5896
.5590
• 5340
2Y±
.7223
.7126
.6939
.6760
.6435
.6156
2V2
.8102
.8004
.7813
.7629
.7289
.6988
2%
.8983
.8883
.8688
.8501
.8149
.7831
3
.9864
.9763
.9566
• 9375
.9014
.8683
.8385
.8125
.7906
3^4
.074
.064
.044
.025
.9882
• 9540
.9228
.8949
.8705
.163
.152
.132
.113
.075
.O4O
.008
.9783
• 9520
3%
.251
.241
.220
.201
.163
.127
.093
.063
.035
4
• 339
.329
.308
.288
.250
.214
.179
.147
.118
4V4
.427
.417
.396
.376
.338
.301
.266
.233
.202
4V2
.516
.505
.485
.464
.425
.388
.352
.318
.287
48/4
.604
• 593
• 573
• 552
.513
.475
.439
.405
• 372
5
.692
.682
.661
.641
.601
.563
.526
.491
• 458
5V4
.780
• 770
• 749
.729
.689
.650
.613
• 577
• 544
.869
.858
.837
.817
• 777
.738
.700
.664
.630
s4i
• 957
• 947
.926
• 90S
.865
.825
.788
• 751
.716
6
.045
.035
.014
.993
• 953
.913
.875
.838
.803
Inside Surface in Square Feet per Lineal Foot
%
%
.1145
i
• 1473
.1309
!^8
.1800
.1636
IV4
.2127
.1963
.1636
.1309
1%
.2454
.2291
.1963
.1636
1-^2
.2782
.2618
.2291
.1963
.1309
1 44
.3436
.3272
.2945
.2618
.1963
2
.4091
.3927
.3600
.3272
.2618
.1963
2%
.4745
.4581
.4254
.3927
.3272
.2618
2V2
• 5400
.5236
.4909
.4581
.3927
.3272
23/4
.6054
.5890
.5563
.5236
.4581
.3927
3
.6709
.6545
.6218
.5890
.5236
.4581
.3927
.3272
.2618
3^4
.7363
.7199
.6872
.6545
.5890
.5236
.4581
.3927
.3272
3V2
.8018
.7854
.7527
.7199
.6545
.5890
.5236
.4581
.3927
38/4
.8672
.8508
.8181
.7854
.7199
.6545
.5890
.5236
.4581
4
• 9327
.9163
.8836
.8508
.7854
.7199
.6545
.5890
.5236
4V4
.9981
.9817
.9490
.9163
.8508
.7854
.7199
.6545
.5890
4V2
1.0636
1.0472
I. 0145
.9817
.9163
.8508
.7854
.7199
.6545
43/4
.1290
.1126
.0799
.0472
.9817
.9163
.8508
.7854
.7199
5
• 1945
.1781
.1454
.1126
.0472
.9817
.9163
.8508
.7854
5V4
• 2599
.2435
.2108
.1781
.1126
1.0472
.9817
.9163
.8508
5%
.3254
.3090
.2763
.2435
.1781
1.1126
1.0472
.9817
.9163
58/4
.3908
• 3744
.3417
.3090
.2435
1.1781
1.1126
1.0472
.9817
6
4563
. 4399
. 4072 . 3744
.3090
1.2435
1.1781
1.1126
1.0472
208
Briggs' Standard
BRIGGS9 STANDARD
The nominal sizes of pipe 10 inches and under, and the pitches of the
threads, were for the most part established in the British tube (called
"pipe" in America) trade between 1820 and 1840. The sizes are desig-
nated roughly, according to their internal diameters.
Robert Briggs, about 1862, while Superintendent of the Pascal Iron
Works, formulated the nominal dimensions of pipe up to and including
10 inches. These dimensions have been broadly spread and are widely
known as "Briggs' Standard." They are as follows:
The nominal and outside diameters and pitch of thread, for sizes
10 inches and under, are given in the table of Standard Pipe, page 22,
of this book.
The thread has an angle of 60° and is slightly rounded off at top and
0.8
bottom so that the total height (depth), H = • — , where n is the number
of threads per inch.
increases roughly with the diameter, but
The pitch of the threads [ -
\ni
in an arbitrary and irregular manner. It would be advantageous to
change the pitches except for the fact that they are now firmly estab-
lished.
The conically threaded ends of pipe are cut at a taper of %-mch
diameter per foot of length (i.e., i in 32 to the axis of the pipe). (See
Fig. 113.)
VVV\AAAAAAZI>T"'
Fig. 113
The thread is perfect for a distance (L) from the end of the pipe,
outside diameter
expressed by the rule, L = — — ; where D
in inches. Then come two threads, perfect at the root or bottom,
but imperfect at the top, and then come three or four threads imperfect
at both top and bottom. These last do not enter into the joint at all,
but are incident to the process of cutting the threads.
The thickness of the pipe under the root of the thread at the end of
the pipe equals T — 0.0175 D+ 0.025 inch.
The Physical Properties of Carbonic Acid 209
The above notes on Briggs' Standard were taken from Paper No. 1842,
"American Practice in Warming Buildings by Steam," presented before
the British Institute of Civil Engineers by Robert Briggs, member of the
Institute. It is contained in the Institute Proceedings, Vol. LXXI, Session
1882-83, Part I. The substance of that paper is quoted quite fully in
the report of the Committee on Standard Pipe and Pipe Threads to the
American Society of Mechanical Engineers at the seventh annual meeting
and is published in Vol. VIII, Paper No. 226, of their proceedings. The
report was accepted by the American Society, December 29, 1886.
Briggs' Standard was adopted by the manufacturers of wrought-iron
pipe and boiler tubes, October 27, 1886, and indorsed by the Manu-
facturers' Association of Brass and Iron, Steam, Gas and Water Work,
December 8, 1886; except that the outside diameter of 9-inch pipe was
changed to 9.625 inches.
By trade usage, the above rules have been extended to take in sizes
up to 15 inches inclusive, except that the standard thickness is 0.375
inch, with the outside diameters given on page 22. Pipes larger than
15 inches, nominal size, are known by their outside diameter. The
dimensions have also been extended to Extra Strong and Double Extra
Strong Pipe, by holding the outside diameter and allowing the inside
diameter to decrease according to increase in thickness. See page 25
for Extra and Double Extra Strong Pipe.
National Tube Company threads its pipe to conform to the Briggs'
Standard Gages as made by the Pratt & Whitney Company of Hart-
ford, Conn., U. S. A.
The following table gives the depth of different pipe and casing
threads:
8 threads per inch 100 inch
10 threads per inch 080 inch
i iy2 threads per inch 0696 inch
1 2 threads per inch 0667 inch
14 threads per inch 0571 inch
18 threads per inch 0444 inch
27 threads per inch 0296 ipch
THE PHYSICAL PROPERTIES OF CARBONIC ACID
In a paper presented before the American Society of Mechanical
Engineers (December, 1908) by Prof. R. T. Stewart, of the University
of Pittsburgh, is given the most recent information on "The Physical
Properties of Carbonic Acid and the Conditions of Its Economic Storage
for Transportation. " The necessity for accurate data on this subject
was at that time so apparent that arrangements were made with Professor
Stewart to make a special study of all the data available, and to make
such experiments as were required in order to supply a sound basis for
the design, manufacture and filling of carbonic acid cylinders. The
results of this investigation may be found in the above article.
The tables and charts given in this paper furnish the data necessary
in investigating the strength and safety of existing carbonic acid cylinders
and the design of new cylinders on a safe and economical basis. The
210 Holding-Power of Boiler Tubes
value of these tables will be apparent when it is considered that each
of these cylinders becomes, when charged, a reservoir of stored energy,
which would in all probability cause loss of both life and property should
rupture occur.
It is impracticable in a short space to give an abstract which would
be sufficiently complete, nor is this necessary, as the complete data is
available to all who are interested. The scope of Professor Stewart's
paper may be judged from the following extract from the introduction:
"In Part One of this paper the tables and charts show the physical
properties of pure carbon dioxide and are based upon three things:
First, the average of the values obtained by Lord Rayleigh and by
Leduc for the weight in grams of one liter of purified and dried carbon
dioxide, CO2, under standard conditions; second, the adjusted results
which carbon dioxide differs in its physical actions from the laws of a
perfect gas; and, third, the direct application of certain fundamental
physical relations and of mathematical and graphical analyses.
"In Part Two is given the results of the author's experiments on
commercial carbonic acid contained in commercial steel cylinders.
"In Part Three is given a rational method of designing commercial
carbonic acid cylinders."
HOLDING-POWER OF BOILER-TUBES EXPANDED
INTO TUBE SHEETS
(Kent's Mechanical Engineers' Pocket Book.)
Experiments by Chief Engineer W. H. Shock, U. S. N., on brass
tubes 2l/2 inches diameter, expanded into plates %-inch thick, gave
results ranging from 5850 to 46 coo pounds. Out of 48 tests, 5 gave
figures under 10 coo pounds, 12 between 10 ooo and 20,000 pounds,
1 8 between 20000 and 30000 pounds, 10 between 30000 and 40000
pounds, and 3 over 40 ooo pounds.
Experiments by Yarrow & Co., on steel tubes, 2 to 2% inches diameter,
gave results similarly varying, ranging from 7900 to 41 715 pounds,
the majority ranging from 20 ooo to 30 ooo pounds. In 15 experiments
on 4- and 5-inch tubes the strain ranged from 20 720 to 68 040 pounds.
Beading the tube does not necessarily give increased resistance, as some
of the lower figures were obtained with beaded tubes. (See paper on
Rules Governing the Construction of Steam Boilers, Trans. Engineering
Congress, Section G, Chicago, 1893).
The Slipping Point of Rolled Boiler-tube Joints
(O. P. Hood and G. L. Christensen, Trans. A. S. M. E., 1908.)
When a tube has started from its original seat, the fit may be no
longer continuous at all points and a leak may result, although the
ultimate holding power of the tube may not be impaired. A small
movement of the tube under stress is then the preliminary to a possible
leak, and it is of interest to know at what stress this slipping begins.
As results of a series of experiments with tube sheets of from M? inch
to i inch in thickness, and with straight and tapered tube seats, the
Thermal Expansion of Iron and Steel Tubes 211
authors found that the slipping point of a 3 -inch i2-gage Shelby cold-
drawn tube rolled into a straight, smooth machined hole in a i-inch
sheet occurs with a pull of about 7000 pounds. The frictional resistance
of such tubes is about 750 pounds per square inch of tube-bearing area
in sheets % inch and i inch thick.
Various degrees of rolling do not greatly affect the point of initial
slip, and for higher resistances to initial slip other resistance than friction
must be depended upon. Cutting a 10 pitch square thread in the seat,
about o.oi inch deep, will raise the slipping point to three or four times
that in a smooth hole. In one test this thread was made 0.015 inch
deep in a sheet i inch thick, giving an abutting area of about 1.4 square
inches and a resistance to initial slip of 45 ooo pounds. The elastic
limit of the tube was reached at about 34 ooo pounds.
Where tubes give trouble from slipping and are required to carry an
unusual load, the slipping point can be easily raised by serrating the
tube seat by rolling with an ordinary flue expander, the rolls of which
are grooved about 0.007 inch deep and 10 grooves to the inch. One
tube thus serrated had its slipping point raised between three and four
times its usual value.
THERMAL EXPANSION OF IRON AND
STEEL TUBES
A number of samples of the various metals used in the manufacture
of seamless and welded tubes were recently submitted to the Bureau of
Standards, Washington, D. C., for determinations of the coefficients
of expansion within the range of temperatures common to boiler practice.
The mean coefficient of expansion (a) of these materials between o° C.
and 200° C. was found to be:
Charcoal iron
Chemical analyses
(«)
Carbon
Phos-
phorus
Man-
ganese
Sulphur
Trace
.07
.12
.049
.132
.0145
Trace
.40
.51
.020
.052
.035
.00001235
.00001258
.00001239
Bessemer steel
Seamless O. H. steel
(hot finished)
The length of a tube at / degrees Centigrade is:
Lt = Lo (i + at).
The report of this investigation -remarks:
"As might have been expected from the known behavior of metals,
nearly all the specimens appeared to expand faster at higher than at
low temperatures. The measurements indicate that, throughout the
range from o° C. to 200° C., the values of the coefficients (a) might
increase from as much as about i .3 per cent, less than to about as much
as 1.3 per cent, greater than the values given in the above table."
212 Strength of Tubes Under Internal Fluid Pressure
STRENGTH OF TUBES, PIPES, AND CYLINDERS
UNDER INTERNAL FLUID PRESSURE
In order to arrive at some definite conclusion as to what formula or
formulae should be used for calculating the strength of tubes, pipes,
and cylinders subjected to internal fluid pressure, the different published
formulae have been investigated and compared. These are five in num-
ber; namely, the Common Formula, and those by Barlow, Lame, Clava-
rino, and Birnie.
These formulas have been put into the simplest form for application
to tubes, pipes, and cylinders, and are reduced to a common notation
for the sake of making an easy comparison. The notation used is as
follows:
Di = outside diameter in inches;
Di = inside diameter in inches;
/ = thickness of wall in inches;
p = internal gage pressure, or difference between internal and
external fluid pressures, in pounds per square inch;
/= fiber stress in the wall in pounds per square inch.
The formulae here given are for the usual conditions of practice,
namely, where the external pressure is atmospheric and the internal
pressure is expressed as gage pressure. They are also applicable to
cases where the external pressure is not excessive by taking p as the
difference between the internal and external pressures.
In all that follows it is assumed that the length of the tube or pipe
relative to its diameter is sufficiently great to eliminate the influence
of end support tending to prevent ruptu -e.
Nature of Stress in a Tube Wall. An internal fluid pressure may
give rise (i) to a circumferential stress within the wall of a tube or
pipe, or (2) to both a circumferential and a longitudinal stress acting
jointly. In either case the tube wall is under radial compressive stress,
as indicated by the arrows, Figs. 114 and 115.
Fig. 114
Fig. 114 illustrates a tube with frictionless plungers fitted into its ends,
the plungers being kept in place by the external forces, P, P, which
exactly balance the internal fluid pressure tending to force them outward.
In this case the tube wall is subjected only to the internal forces shown
as acting at right angles to its inner surface. It is obvious that these
Strength of Tubes Under Internal Fluid Pressure 213
forces can give rise to radial and circumferential stresses only in the tube
wall. The value of the circumferential stress, ft, in pounds per square
inch, is ~ ~
ft=PD^D-2=^f (I)
Fig. 115
Fig. 115 illustrates the ordinary case of a tube or pipe with both ends
closed. In this case the tube wall, as in Fig. 114, is subjected to the cir-
cumferential stress, ft, along with the radial stress, and at the same time
is subjected to the longitudinal stress, /j. The longitudinal stress is
caused by the internal fluid pressure tending to force the attached heads
outward and expressed in pounds per square inch is
(2)
When the thickness of wall, /, is relatively small with respect to the
diameter, the longitudinal stress becomes approximately
in
or one-half the corresponding circumferential stress.
Common Formula. This is the formula generally found in books
on mechanics. It is based on the condition that the tube wall is sub-
jected to circumferential stress only (Fig. 114), and assumes (i) that
the material of the tube wall is devoid of elasticity, and (2) that the
stress is the same on all the circumferential fibers from the innermost
to the outermost. These assumptions are only approximately true for
tubes of comparatively thin walls, and are greatly in error for tubes
having very thick walls.
Using the notation as given above, the formula is
(4)
t = 2L. P=2fL. t=lDt. t=iDi
f 2 ZV P 2J D2' ~ 2 2 f J~ 2 2 t
Referring to the curves, Figs. 116 and 1 17, it will be seen that the Com-
mon Formula gives quite close results for comparatively thin walls when
used for the conditions shown in Fig. 114, for which Birnie's Formula
is theoretically correct. The error increases as the thickness of wall
becomes relatively greater, reaching ten per cent for a thickness ratio,
214 Strength of Tubes Under Internal Fluid Pressure
— , of about 0.05. For thick walls the error is great; for example, when
L>\
t p
— equals 0.25 the value of — is about one hundred per cent in error.
It should be observed when applying the Common Formula to this
case that the error is always on the side of danger.
For the conditions shown in Fig. 115, that is, when the tube is sub-
jected to the stresses due to an internal fluid pressure acting jointly on
the tube wall and its closed ends, for which Clavarino's Formula is theo-
retically correct, the curves show for a thickness ratio, — , less than 0.07,
Di
that the Common Formula errs on the side of safety, the greatest error
being about twelve per cent; while for thickness ratios greater than
0.07 the error is on the side of danger, reaching ten per cent for a thick-
ness ratio of o.i and about one hundred per cent 'for a ratio of 0.25.
Barlow's Formula. This formula assumes (i) that because of the
elasticity of the material, the different circumferential fibers will have
their diameters increased in such a manner as to keep the area of cross-
section constant, and (2) that the length of the tube is unaltered by
the internal fluid pressure. As neither of these assumptions is theo-
retically correct, this formula can give only approximately correct
results. Using the notation given above, this formula is
It should be observed that while Barlow's Formula is similar in form
to the Common Formula, it gives results that are quite different when
applied to tubes, pipes, and cylinders having walls of considerable
thickness. This is due to the fact that Barlow's Formula is expressed
in terms of the outside diameter, Di, whereas the Common Formula
is expressed in terms of the inside diameter, Z>2.
Referring to the curves, Figs. 116 and 117, it will be seen that Barlow's
Formula gives quite close results when used for the condition shown in
Fig. 114, for which Birnie's Formula is theoretically correct. The curves
show for the entire practical range of thickness ratios that the error in
values of -, for this case, does not exceed three per cent, the error
throughout the whole practical range being on the side of safety. This,
then, is the best of the simple theoretical formulae for application to
the case illustrated in Fig. 114.
For the conditions shown in Fig. 115, namely, when the tube is sub-
jected to the stresses due to an internal fluid pressure acting jointly on
the tube wall and its closed ends, for which Clavarino's Formula is theo-
retically correct, the curves show that Barlow's Formula gives values
of - whose errors range from fifteen per cent for tubes, pipes, and cylin-
ders having thin walls to ten per cent for those having thick walls, the
error being on the side of safety for all practical thickness ratios.
Strength of Tubes Under Internal Fluid Pressure 215
Lame's Formula. This formula is meant to apply to the conditions
shown in Fig. 115. Each material particle of the tube wall is supposed to
be subjected to the radial compression, and the circumferential and longi-
tudinal tensions due to an internal fluid pressure acting jointly on the
tube wall and its closed ends; and the material of the tube wall is
supposed to be elastic under these actions. Lame's Formula, however,
ignores the "Coefficient of Lateral Contraction," known as "Poisson's
Ratio," and consequently is not theoretically correct.
Using the notation as given above, this formula is
p DS-DJ Di*-D*f n
Referring to the curves, Figs. 116 and 117, it will be seen that Lame's
Formula, which is meant to apply to the conditions for which Clava-
rino's Formula is theoretically correct, gives for thickness ratios, — ,
less than 0.15, an error on the side of safety, the error having a maxi-
mum value of about fourteen per cent when — - equals o.oi. For thick-
D\
ness ratios greater than 0.15 the error is on the side of danger, reaching
ten per cent for a ratio of about 0.23.
Clavarino's Formula. In this formula, as in Lame's Formula, each
material particle of the tube wall is supposed to be subjected to the
radial compression and the circumferential and longitudinal tensions
due to an internal fluid pressure acting jointly on the tube wall and its
closed ends; and the material is supposed to be elastic under these
actions. Unlike Lame's Formula, however, this formula expresses the
true stresses in the tube wall as based upon the " Coefficient of Lateral
Contraction," known as "Poisson's Ratio," and is consequently theo-
retically correct for the conditions shown in Fig. 115, providing the
stress on the most strained fiber does not exceed the elastic limit of
the material.
Using the notation given above and assuming the value of the "Co-
efficient of Lateral Contraction, " for tube steel to be 0.3, this formula is
p ...xoW-ZW). p^jjjj$j^ Di
iU-
iof-i3P
This theoretically correct formula for the conditions shown in Fig. 115
has the disadvantage that it is difficult to apply directly in making
calculations. In order to remove this difficulty the table on page 220
has been prepared, by means of which any desired calculation can be as
216 Strength of Tubes Under Internal Fluid Pressure
readily made by Clavarino's Formula as by any of the simpler formulae.
The entries of this table are the values in Clavarino's Formula of the
factor
It will be observed that these factors are tabulated for thickness
ratios, — , from o.oi to 0.3, advancing by thousandths. Thus for a
Di
wall thickness, t, of 0.25 inch and an outside diameter, Di, of ten inches,
the thickness ratio, — , would be 0.25 divided by 10, or 0.025. The
Di
required factor corresponding to this thickness ratio is 0.0587 and is
found in the column headed 0.005 opposite 0.02 in column one. Simi-
larly for an outside diameter of four inches and a wall thickness of 0.5
inch, the thickness ratio would be 0.125 and the corresponding internal
pressure factor is 0.2869.
If we designate the value of any tabular factor by k, then it is obvious
that Clavarino's Formula may be written
(8)
This table is well adapted to the ready solution of problems involving
the strength and safety of a tube, pipe, or cylinder which is subjected to
the stresses due to an internal fluid pressure acting jointly on its wall
and closed ends, as illustrated in Fig. 115.
Problem i. Required the safe working fluid pressure p, Fig. 115, when
the outside diameter, Di, equals four inches; thickness of wall, /, equals
0.5 inch; and the working fiber stress of the steel,/, equals 10 ooo pounds.
Solution, (i) The thickness ratio, — , equals 0.125; (2) the corre-
D\
spending tabular factor, k, is found from the table, page 220, to be
0.2869; and (3) the required safe working fluid pressure, p, equals kf
(equation 8), or 0.2869 times 10 ooo, or 2869 pounds per square inch.
Problem 2. Required the fiber stress, /, in the wall of a cylinder, Fig. 115,
when the outside diameter, D\, equals 5.5 inches; the thickness of wall,
t, equals 0.25 inch; and the working fluid pressure, p, equals 1500 pounds
per square inch.
Solution, (i) The thickness ratio, — -, equals 0.045; (2) the corre-
Di
spending tabular factor, k, is found from table on page 220, to be 0.1054;
and (3) the required fiber stress, /, equals - (equation 8), or 1500 divided
by 0.1054, or 14 200 pounds per square inch.
Problem 3. Required the thickness of wall, t, Fig. 115, when the outside
diameter, Di, equals eight inches; the working fiber stress of the steel,
Strength of Tubes Under Internal Fluid Pressure 217
/, equals 15 ooo pounds per square inch; and the working fluid pressure,
p, equals 2000 pounds per square inch.
P
Solution, (i) The factor, k, equals ~ (equation 8) or 2000 divided by
15 ooo or 0.133; (2) the value of the thickness ratio, — -, corresponding
D\
to this value of k is found from the table on page 220 to be 0.057; and
(3) the required thickness will result from multiplying this thickness
ratio, — , by the outside diameter, Di, or 0.057 times 8 equals 0.456 inch.
Di
NOTE. When the inside diameter, Dz', the internal pressure, p;
and the working fiber stress, /, are given and it is required to find the
thickness of wall, t: proceed by finding first the value of the outside
diameter, D\, by means of equation (7), after which the required thick-
ness may be had by taking one-half the difference of the outside and
inside diameters, or
Di - D2 .
t = • (9)
2
Birnie's Formula. This formula is based upon the conditions illus-
trated in Fig. 1 14. In its derivation, precisely the same assumptions
are made as for Clavarino's Formula with the single exception that the
longitudinal stress, fi, due to the internal fluid pressure acting upon
attached heads is assumed not to exist. Birnie's Formula consequently
is theoretically correct for tubes, pipes, and cylinders that are sub-
jected to an internal fluid pressure in such a manner as not to give rise
to longitudinal stress in the wall; provided the stress on the most
strained fiber does not exceed the elastic limit of the material.
Using the same notation as before and assuming the value of the
"Coefficient of Lateral Contraction" for steel to be 0.3, this formula
p io(Di2-Z)22) _io(£i2-Z)22) / IQ/+ 7 P .
2
°f~I3p (10)
iof+7P
Birnie's Formula, like Clavarino's Formula, has the disadvantage of
being difficult to apply directly in making calculations. In order to
remove this difficulty the table on page 221 has been prepared, the
entries being the values in Birnie's Formula of the factor
This table is used in a manner precisely similar to the table of factors
for Clavarino's Formula. See explanation and solution of problems
on page 216.
218 Strength of Tubes Under Internal Fluid Pressure
Comparis
.22
.21
.20
.19
.18
.1 7
•£*M6
$ .15
K
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LJ
m
C .13
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id
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CO
£ .09
CL
-.08
to
^ .07
<
> .06
.05
.04
.03
.02
.01
0
on of Internal Fluid Pressure Formulae for Tubes, Pipes and
Cylinders
/ /
/
//
//
/ /
'/,'
' //
/
//
' /
/ t
/ /
/'
/,
/ //
/
^/x
'V
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/,
'///
///,
t/
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'///
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•//-
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I
7_
E FOR CLAVARINO'S FORMULA
Z FOR BIRNIE'S FORMULA
= FOR COMMON FORMULA
E FOR LAME'S FORMULA
E FOR BARLOW'S FORMULA
CURV
CURV
CURV
//
/
/
/
/
.01 .02 .03 .04 .05 .06 .07 .08 .09 .10
VALUES OF THICKNESS DIVIDED BY OUTSIDE DIAMETER,^
Fig. 116
Strength of Tubes Under Internal Fluid Pressure 219
Comparh
.75
.70
.65
^.60
U)
t-
m
E .55
.50
.45
5 .40
.35
.30
.25
.20
>on of Internal Fluid Pressure Formulae for Tubes, Pipes and
Cylinders (Concluded)
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
/
x/
/
/
X.
/
1
/
/
/
/'
,/
1
/
/
/
,^
j
/
/ y
k/
/s
/
/
/
/
/
//
//
/
/
//i
//
/
i
i
/
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/ \
//
/
//
//
/y
/
/
'/ /
/.'
/
/
/ ,
//
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1 ' /y
E FOR CLAVARINO'S FORMULA
E FOR BIRNIE'8 FORMULA .
E FOR COMMON FORMULA
E FOR LAME'S FORMULA
— CURV
-- CURV
- CURV
/
//,
Y
im
//
25
^UnVCi . wr. wr,r,wv. » . wr....wwr.
m
•x
'/
10 .12 .14 .16 .18 .20 .22 .24 .26 .28 .30
VALUES OF THICKNESS DIVIDED BY OUTSIDE DIAMETER,^}
Fig. 117
220 Strength of Tubes Under Internal Fluid Pressure
Internal Fluid Pressure Factors, k, for Conditions shown in Fig. 115
[Calculated by Clavarino's Formula, assuming for steel a "Coefficient of
Lateral Contraction" (Poisson's Ratio) equal 0.3.]
Rule. Divide thickness of tube or pipe by its outside diameter, both being
expressed in inches, then multiply the tabular value corresponding to this quo-
tient by the working fiber stress in pounds per square inch. The result will
be the safe internal pressure in pounds per square inch.
For further use of table, see page 216.
t/Dl
.OOO
.001
.002
.003
.004
.005
.006
.007
.008
.009
.01
.0235
.0259
.0282
.0306
.0329
.0352
.0376
• 0399
• 0423
.0446
.02
.0470
• 0493
.0517
.0540
.0564
• 0587
.0610
.0634
• 0657
.0681
.03
.0704
.0727
.0751
.0774
.0797
.0821
.0844
.0867
.0891
.0914
.04
• 0937
.0961
.0984
.1007
.1031
• 1054
.1077
.IIOO
.1123
.1147
• 05
.1170
• 1193
.I2l6
• 1239
.1263
.1286
.1309
.1332
• 1355
• 1378
.06
.1401
.1424
.1448
.1471
.1494
.1517
.1540
.1563
. 1586
.1609
.07
.1632
.1655
.1678
.1700
• 1723
.1746
.1709
.1792
.1815
.1838
.08
.1861
.1883
.1906
.1929
.1952
.1974
.1997
.2020
.2043
.2065
.09
.2088
.2111
.2133
.2156
.2178
.2201
.2223
.2246
.2269
.2291
.10
.2314
.2336
.2358
. 2381
.2403
•2425
.2448
.2470
• 2493
.2515
.11
.2537
• 2559
. 2582
.2604
.2626
.2648
.2670
.2692
.2715
•2737
.12
• 2759
.2781
.2803
.2825
• 2847
.2869
.2890
.2912
• 2934
.2956
.13
.2978
.300O
.3022
• 3043
.3065
.3087
.3108
• 3130
.3152
• 3173
• 14
-3I9S
.3216
-3238
• 3259
.3281
•3302
. 3323
•3345
• 3366
.3388
• 15
• 3409
• 3430
• 3451
•3472
• 3494
•3515
.3536
• 3557
• 3578
•3599
.16
.3620
.3641
.3662
.3683
•3704
•3724
.3745
.3766
.3787
.3808
.17
.3828
.3849
.3869
.3890
• 3910
• 3931
-3951
• 3972
•3992
• 4013
.18
• 4033
• 4053
.4073
.4094
.4114
• 4134
• 4154
• 4174
.4194
.4214
-19
• 4234
• 4254
.4274
.4294
-4314
•4333
• 4353
• 4373
•4393
.4412
.20
.4432
•4452
• 4471
• 4490
• 4510
• 4529
• 4548
.4568
.4587
.4606
.21
.4626
.4645
.4664
.4683
• 4702
• 4721
• 4740
• 4758
• 4777
.4706
.22
.4815
.4834
.4852
.4871
.4889
.4908
.4926
• 4945
.4964
.4982
•23
.5001
.5019
• 5037
• 5055
• 5073
.5091
.5109
• 5127
.5145
• 5163
.24
.5181
•5199
.5216
.5234
.5252
• 5269
• 5287
.5304
• 5322
• 5340
•25
• 5357
• 5374
• 5391
.5408
.5426
• 5443
• 546o
.5477
• 5494
• 5511
.26
.5528
• 5545
.556l
• 5578
• 5594
.5611
.5628
.5644
.5661
• 5677
-27
.5694
• 5710
.5726
• 5742
• 5758
-5774
.5790
.5806
.5822
• 5838
28
.5854
.5870
.5885
• 5901
.5916
• 5932
• 5947
. 5963
.5978
•5994
.29
.6009
.6024
.6039
.6054
.6069
.6084
.6099
.6114
.6129
• 6l43
• 30
.6158
.6173
.6187
.6201
.6216
• 6230
.6244
.6259
.6273
.6287
Strength of Tubes Under Internal Fluid Pressure 221
Internal Fluid Pressure Factors, k, for Conditions shown in Fig. 114
[Calculated by Birnie's Formula, assuming for steel a "Coefficient of Lateral
Contraction" (Poisson's Ratio) equal 0.3.]
Rule. Divide thickness of tube or pipe by its outside diameter, both being
expressed in inches, then multiply the tabular value corresponding to this quo-
tient by the working fiber stress in pounds per square inch. The result will
be the safe internal pressure in pounds per square inch.
For further use of table, see page 217.
t/D1
.000
.001
.002
.003
.004
.005
.006
.007
.008
.009
.01
.0201
.0221
.O24I
.0261
.0282
.0302
.0322
.0342
.0363
.0383
.02
.0403
.0423
.0444
.0464
.0485
• 0505
• 0525
.0546
.0566
.0586
.0.3
.0607
.0627
.0648
.0668
.0689
.0709
.0730
.0750
.0771
.0791
.04
0812
.0832
.0853
.0873
.0894
.0915
0935
.0956
.0976
.0997
.05
.1018
.1038
.1059
.1080
.IIOO
.1121
.1142
.1163
.1183
.1204
.06
.1225
.1245
.1266
.1287
. 1308
• 1329
• 1349
.1370
- 1391
.1412
.07
•1433
• 1453
• 1474
• 1495
.1516
• 1537
.1558
.1579
• 1599
.1620
.08
.1641
.1662
.1683
.1704
• 1725
.1746
.1767
.1787
.1808
.1829
.09
.1850
.1871
.1892
.1913
.1934
• 1955
.1976
.1997
.2018
.2039
.10
.2059
.2080
.2101
.2122
.2143
.2164
.2185
.2206
.2227
.2248
.11
.2269
.2290
.2311
.2332
.2353
.2374
.2395
.2416
• 2437
.2457
.12
.2478
2499
.2520
.2541
.2562
.2583
.2604
.2625
.2646
.2667
.13
.2688
.2708
.2729
.2750
.2771
.2792
.2813
.2834
.2854
.2875
.14
.2896
2917
.2938
•2959
.2979
.3000
.3021
.3042
.3062
. 3083
.15
• 3104
.3125
.3145
.3166
.3187
.3208
.3228
.3249
.3270
.3290
.16
• 3311
• 3332
•3352
.3373
• 3393
.3414
.3434
• 3455
.3476
.3496
.17
• 3517
.3537
• 3558
• 3578
.3598
.3619
.3639
.3660
.3680
.3700
.18
.3721
• 3741
• 376T
.3782
.3802
.3822
.3842
.3863
.3883
.3903
• 19
.3923
• 3943
.3963
.3983
.4003
.4024
• 4044
.4064
.4084
.4104
.20
4124
.4144
•4163
.4183
.4203
• 4223
.4243
.4262
.4282
• 4302
.21
.4322
• 4341
.4361
.438o
.4400
.4419
-4439
• 4459
.4478
.4498
.22
.4517
.4536
.4556
• 4575
• 4594
.4613
.4633
.4652
.4671
.4690
.23
.4710
.4729
• 4748
.4767
.4785
.4804
.4823
.4842
.4861
.4880
.24
.4899
.4918
.4936
• 4955
• 4973
• 4992
• 5010
.5029
.5048
.5066
.25
.5085
.5103
• 5121
-5I39
.5157
.5176
• 5194
.5212
.5230
.5248
.26
.5266
.5284
• 5302
• 5320
.5338
• 5355
.5373
• 5391
.5409
.5427
.27
• 5444
.5462
.5479
• 5496
.5514
• 5531
.5548
.5566
.5583
.5600
.28
.5617
.5634
.5651
.5668
• 5685
.5702
.5718
.5735
• 5752
.5769
.29
.5786
.5802
.5818
.5835
.5851
.5867
.5884
• 5900
.5916
.5933
.30
• 5949
.5965
.5981
.5996
.6012
.6028
.6044
.6059
.6075
.6091
222 Strength of Tubes to Resist Internal Fluid Pressures
Strength of Commercial Tubes, Pipes and Cylinders
to Resist Internal Fluid Pressures
In the preceding portion of this chapter there appears a full statement
of the basis of each of the five theoretical formulae for the strength of
tubes, pipes, and cylinders when subjected to internal fluid pressures,
together with a comparison of results obtained by their use. One or
other of these formulae, taken apparently at random, has often been
used without sufficient understanding of their application to practical
conditions. It is the purpose of what follows to illustrate the proper
application of these formulae making use of the results of hydrostatic
tests recently made on commercial pipes at one of the mills of the
National Tube Company.
Yield Point Tests on Commercial Pipe. Tests were made under
Clavarino's condition, Fig. 115, on 195 specimens of lo-inch and 279
specimens of 1 2-inch lap- welded steel pipes, all of which were made up
into cylinders with heads welded to the pipe. The hydrostatic pressure
was raised until the yield point of the material was reached. The unit
stresses on the most strained fibers were then calculated by means of
Clavarino's formula, the pipes having been measured by micrometer,
before welding in the head, to determine the least thickness of wall.
The average results of the yield points of the most strained fibers of
the material constituting these pipes when compared with the average
yield point of tensile test specimens cut from about 400 similar pipes
may be summarized as follows:
Outside diameter of pipe, inches 10.00 12.00
Least thickness of wall, inch .172 . 164
Hydrostatic pressure at yield point, pounds
per square inch 1 435 i 195
Yield point by Clavarino's formula, pounds
per square inch 35 600 37 100
Yield point, average of tensile tests, pounds
per square inch 37 00° 37 00°
Apparent error in yield point by Clavarino's
formula -3-8% +0.3%
This summary of the average results of 474 tests is a very satisfactory
confirmation of the accuracy of Clavarino's Formula when applied to
commercial steel pipes for the conditions under which the formula
theoretically applies.
Other tests show that when the heads are attached to the pipe, as
m Fig. 115, it lengthens upon application of an internal fluid pressure,
and that when the heads are held independently, as in Fig. 1 14, it shortens
in accord respectively with the assumptions which constitute the basis
of Clavarino's and Birnie's formulae regarding change of length under
internal fluid pressure.
Applicability of Clavarino's and Birnie's Formulae. The above
summary of results of tests on pipes shows that Clavarino's formula
is applicable to commercial wrought steel pipe for the condition shown in
Strength of Tubes to Resist Internal Fluid Pressures 223
Fig. 115, when the yield point of the most strained fiber is not exceeded
and the least thickness of wall is accurately known.
Tests made at the Watertown Arsenal in 1892-3-4-7 and 1902 on
sections of steel guns show that Birnie's formula for the condition
shown in Fig. 114, when applied up to the elastic limit of the most
strained fiber, gives results which agree with the results of direct tests
that are within the ordinary range of experimental error. These Water-
town Arsenal tests were all made on tubes the material and dimensions
of which were uniform to a degree obtainable only by boring and turn-
ing from forgings of the choicest portion of selected ingots.
It is apparent that any variation below the nominal or average value
in strength of material, thickness of wall and efficiency of joint in welded
pipe, or above the nominal in diameter, will give results which err on
the side of danger when making use of either Clavarino's or Birnie's
formulae. These formulae then should be restricted in their use to cer-
tain classes of seamless tubes and cylinders and to critical examinations
of ordinary tubes, pipes and cylinders, when exact results are desired
and sufficiently accurate data are available.
For all ordinary calculations of strength of commercial tubes, pipes
and cylinders Barlow's simple approximate formula is preferable.
Bursting Tests of Commercial Tubes and Pipes. The tables,
pages 225-226, show the average results of several hundred tests of
commercial tubes and pipes, all of which were burst by hydrostatic
pressure at one of the mills of the National Tube Company.
Of the steel tubes and pipes, 95 per cent was made by this Company,
while 86 per cent of the wrought iron pipe tested was obtained by
purchase in the open market.
The average ultimate tensile strength of pipe steel is 57 ooo pounds
per square inch, whether taken in the direction of rolling or trans-
versely thereto, while that of the seamless steel tested is 60 ooo pounds
per square inch. No tensile tests were made of the material of the
wrought iron pipes.
An examination of these tables will lead to the following general
conclusions:
1. In commercial welded pipe the variations in thickness of wall,
perfection of weld, etc., give rise to variations in bursting strength of
sufficient magnitude to render unnecessary any consideration of Clava-
rino's or Birnie's condition of head support as shown in Figs. 115 and
114, respectively.
2. The relative strengths of steel pipes and tubes, when using Barlow's
Formula and basing the calculations on average diameter, thickness of
wall and ultimate tensile strength of material, are as follows: For butt-
welded steel pipe, 73 per cent; for lap- welded steel pipe, 92 per cent;
and for seamless steel tubes, approximately 100 per cent.
In steel pipe, then, the strength of the butt-weld is about 80 per cent
of that of the lap-weld.
3. The relative strengths of wrought iron and steel pipe, from the
accompanying tables, are as follows: Butt- welded wrought-iron pipe is
224 Strength of Tubes to Resist Internal Fluid Pressures
70 per cent as strong as similar butt- welded steel pipe; and lap- welded
wrought iron pipe is 60 per cent as strong as similar lap-welded steel
pipe.
Applicability of Barlow's Formula. Of the five formulae con-
sidered in this chapter that by Barlow is the best suited for all ordinary
calculations pertaining to the bursting strength of commercial tubes,
pipes and cylinders.
The theoretical error on the side of safety resulting from its use will
generally not exceed the actual combined error on the side of danger
when using either Birnie's or Clavarino's formula due to the ordinary
range of variation in the thickness of wall, strength of the material,
etc., when applied to the ordinary commercial product.
This is true, at least up to the yield point of the material, for any
ratio of thickness of wall to outside diameter less than three-tenths.
In this respect Barlow's formula is very superior to the common approxi-
mate formula which gives errors that are absurdly large on the side of
danger for very thick walls. See Fig. 117.
For certain classes of seamless tubes and cylinders and for critical
examinations of welded pipe, where the least thickness of wall, yield
point of material, etc., are known with accuracy, and close results are
desired, see Clavarino's formula and Birnie's equations (7) and (10).
For all ordinary calculations pertaining to the bursting strength of
commercial tubes, pipes and cylinders use Barlow's Formula, which is
Where D = outside diameter, inches;
/ = average thickness of wall, inches;
p = internal fluid pressure, pounds per square inch;
/= working or safe fiber stress, pounds per square inch.
When n = safety factor as based on ultimate strength then
/= 40 ooo In for butt- welded steel pipe;
= 50 ooo/n for lap-welded steel pipe;
= 60 ooo/n for seamless steel tubes;
= 28 ooo/n for wrought iron pipe.
These average values of / are based upon the accompanying tables
of bursting tests of commercial tubes and pipes. They are intended
for substitution in Barlow's Formula in case more exact data for the
working fiber stress are not at hand.
Strength of Tubes to Resist Internal Fluid Pressures 225
Bursting Tests of Commercial Tubes and Pipes
(Tests made by National Tube Company.)
£ £
•* w
Bursting pressures
G
.0
£
* c3 —
«*-, ""*>
"* +*
.SH^
pounds per square
£
J^W c
OJ J3
- a
« *
inch
G
%
"S-QO
Class of
Size
G-Sn «3
nf^0*
g
a
8
-g
a? w*w
material
ffj
'§2-g
fc w-g
i g
« 3
fe o>
•8
G
% <8"£
0.3
> 5?
OJ
> •*-» o
2 a
Z «•
<
*,
g
<ri
s
m
< w-
r vs
10
•405
.066
11840
17320
14 266
("
i
44 oi I
Standard pipe
•^4
10
•540
.085
8830
14680
12 2O6
c
i
38645
Standard pipe
%
IO
•675
.088
5850
13030
10330
c
i
39272
Standard pipe
%
10
.840
.101
11380
16 310
14038
(2
0
58163
Standard pipe
1
IO
.050
.109
7150
9 ISO
8 020
^
0
38657
Standard pipe
i
10
.315
.131
45oo
8800
6990
^
0
35085
Standard pipe
1
JV4
IO
.660
.139
4400
73oo
5808
^
0
34603
Standard pipe
|
*Vi
IS
.660
.140
55oo
11900
7 700
C
I
45215
Redrawn
3 "
ri4
IO
.900
.143
3000
6 loo
4960
c
0
33031
Standard pipe
.Q
2
II
2.375
.149
3830
6060
4951
c
0
40485
Standard pipe
|
2V2
IO
2.875
.198
43io
5740
5 134
c
0
37351
Standard pipe
T3
3
10
3-500
.204
4650
6370
5398
c
0
46234
Standard pipe
j§
1*4
IO
1. 660
.180
7910
14280
10514
c
0
48922
Extra strong
C/3
2
10
2.375
.213
7250
8940
8238
c
0
45935
Extra strong
2
IO
2.375
.220
6160
8 920
7661
^
0
41347
Extra strong
2
10
2.375
.445
8500
18314
14992
c
0
40023
XX strong
General average
41686
2
10
2.375
.155
4890
7940
6645
c
I
50962
Standard pipe
2
10
2.375
.182
4860
10060
736i
c
0
47889
Standard pipe
3
IO
3-500
.210
3830
8200
6368
c
7
5356o
Standard pipe
*d
4
10
4-500
.232
4810
568o
5 249
c
I
51462
Standard pipe
T)
5
IO
5.563
.258
3410
5260
4538
c
I
48882
Standard pipe
13
6
5
6.625
• 275
2450
5210
4088
c
0
49286
Standard pipe
i
6
5
6.625
.275
3170
476o
3666
B
0
44106
Standard pipe
3 <
IO
5
10.750
• 349
356o
4730
4290
c
I
66080
Standard pipe
1
IO
5
10.750
• 347
2770
3940
3396
B
2
52692
Standard pipe
1
2
IO
2.375
.218
2500
9870
7909
C
0
43254
Extra strong
<B
2
IO
2.0OO
.108
Sioo
6560
6062
C
7
55607
Boiler tubes
CO
3
IO
3.000
.112
3220
4860
3967
C
I
52957
Boiler tubes
4
5
4.000
.135
3640
4070
3840
C
2
56978
Boiler tubes
4
5
4.000
.136
3720
4040
3914
B
I
57440
Boiler tubes
I
General average
52225
. r 2
10
2.000
.098
5420
6590! 6052
C
10
6i53o
Boiler tubes
J,gJ 3
10
3.000
.112
3940
4730 4272
C
10
57075
Boiler tubes
6
4.000
.134
4160
4440 43i8
C
6
64450
Boiler tubes
•^co"* i 4
4
4.000
.134
4250
4440] 4328
B
4
64488
Boiler tubes
CO ^
General average
61886
f!^4
10
1. 660
.136
2880
6290
5283
C
3
32126
Standard pipe
1%
10.
1.660
.136
3640
5680
4891
c
I
29817
Standard pipe
2
10
2.375
.156
2930
4250
3687
c
2
28051
Standard pipe
1%
10
i. 660
.188
2770
7330
5895
c
I
26678
Extra strong
General average
29168
1 .*S ( 2
10
2.375
.152
2400
3940
3213
c
j
25122
Standard pipe
« rt 2 1 2
10
2.375
.207
5530
7120
6349
c
8
36461
Extra strong
^^ 1 '
General average
30792
The column marked "See note below" gives the number burst by failure of
material not at weld.
C — Clavarino conditions, Fig. 115.
B — Birnie conditions, Fig. 114.
226 Strength of Tubes to Resist Internal Fluid Pressures
Strength of Weld of Commercial Tubes and Pipes
(Selected from Preceding Table of Bursting Tests.)
Size
Number
burst in
•nrol r\ *
Average
fiber stress
by Barlow's
Class of
material
weld
formula
Steel — Butt-welded
Vs
9
43938
Standard pipe
•Vi
9
37 777
Standard pipe
%
9
38954
Standard pipe
i£
0
58 163
Standard pipe
SA
o
38657
Standard pipe
i
0
35085
Standard pipe
J-V4
o
34603
Standard pipe
1^4.
4
45 643
Redrawn
1^/2
10
33031
Standard pipe
2
II
40485
Standard pipe
3
10
IO
37351
46234
Standard pipe
Standard pipe
2
10
10
48922
45935
Extra strong
Extra strong
2
10
41 347
Extra strong
2
10
40023
XX strong
Gen. average
41 634
Steel — Lap-welded
2
9
50052
Standard pipe
2
10
47889
Standard pipe
3
3
54510
Standard pipe
4
9
51019
Standard pipe
5
9
48852
Standard pipe
6
IO
47026
Standard pipe
IO
7
59537
Standard pipe
2
10
43254
Extra strong
2
3
56933
Boiler tubes
3
9
51 98o
Boiler tubes
4
7 57 521
Boiler tubes
Gen. average
51688
Iron — Butt-welded
lU
7
31 136
Standard pipe
9
30680
Standard pipe
2
8
27323
Standard pipe
!^4
9
27073
Extra strong
Gen. average
29053
Iron — Lap-welded
2
9
24581
Standard pipe
2
2
34340
Extra strong
Gen. average
29 461
* These only are included in averages.
Collapsing Pressures 227
COLLAPSING PRESSURES
Until recently Sir Wm. Fairbairn's classic experiments on tubes sub-
jected to external fluid pressure were the basis of the rules for collapse.
The results of his tests on 40 odd tubes made up of riveted sheets
soldered tight were transmitted to the Royal Society in 1858. As
might be expected, conclusions and formulae based on tests of such
tubes could hardly be expected to apply to modern welded tubes with
any approach to accuracy.
In view of the urgent need for experimental data of a highly reliable
character on which a formula for collapsing strength could be based,
Prof. R. T. Stewart, Dean of the Mechanical Engineering Department
of the University of Pittsburgh, was authorized to plan and direct a
series of experiments on full-sized tubing up to twenty feet in length,
which work was carried out at the National Department of National
Tube Company, at McKeesport, Pa., occupying the time of from one
to six men continuously for a period of four years.
A full report of the details of these experiments will be found in
Professor Stewart's paper presented before the American Society of
Mechanical Engineers, May, 1906. The general scope of the tests and
conclusions arrived at are described in an abstract of this paper as
follows:
Series One. This series of tests was made on tubes that were
S% inches outside diameter, for all of the different commercial thick-
nesses of wall, and in lengths of 2^, 5, 10, 15 and 20 feet between
transverse joints tending to hold the tube to a circular form. The
chief purpose of this series was to furnish data for determining which
of the existing formulae, if any, were applicable to modern lap-welded
steel tubes, especially when used in comparatively long lengths, such as
well casing, boiler tubes and long, plain flues.
Series Two. This series of tests was made on single lengths of 20
feet between end connections tending to hold the tube to a circular
form. Seven sizes, from 3 to 10 inches outside diameter, and in all the
commercial thicknesses obtainable, were tested. The chief purpose of
these tests was to obtain, for commercial tubes, the manner in which the
collapsing pressure of a tube is related to both the diameter and thickness
of the wall.
Inapplicability of Previously Published Formulae. Preparatory
to entering upon the research all existing published formulae that could
be found were collected, and, after the completion of Series One, were
tested as to their applicability to modern steel tubes. Among the
formulae thus tested were two each by Fairbairn, Unwin, Wehage and
Clark, and one each by Nystrom, Grashof, Love, Belpaire, and the Board
of Trade (British), all of which, with possibly two exceptions, appear to
be based upon Fairbairn's experiments made upon tubes wholly unlike
the modern product. Without exception, all of these formulae, when thus
tested, proved to be inapplicable to the wide range of conditions found
228 Collapsing Pressures
in modern practice. As an illustration of this, the very first tube tested
in connection with this research failed under a pressure that exceeded
by about 300 per cent, that calculated by means of Fairbairn's formula.
Results of Research. The principal conclusions to be drawn from
the results of this research may be briefly stated as follows:
1. The length of tube, between transverse joints tending to hold it
to a circular form, has no practical influence upon the collapsing pressure
of a commercial lap-welded steel tube so long as this length is not less
than about six times the diameter of the tube.
2. The formulae, as based upon the research, for the collapsing pressures
of modern lap-welded Bessemer steel tubes, are as follows:
P = 86 670^ - 1386 (B)
P = 50 210 ooo - (G)
where P = collapsing pressure, pounds per square inch;
D = outside diameter of tube in inches;
/ = thickness of wall in inches.
Formula (B) is for values of P greater than 581 pounds per square
inch, or for values of — greater than 0.023, while formula (G) is for
values less than these.
These formulae, while strictly correct for tubes that are 20 feet in
length between transverse joints tending to hold them to a circular form,
are at the same time substantially correct for all lengths greater than
about six diameters. They have been tested for seven sizes, ranging
from 3 to 10 inches outside diameter, in all obtainable thicknesses of
wall, and are known to be correct for this range.
For the convenience of those who wish to apply these formulae to prac-
tice, a table (pages 232-243) has been calculated, giving the collapsing
pressures of tubes from i to 12% inches, outside diameter.
When applying these formulae and tables to practice it should be
remembered that a suitable factor of safety should be applied. The
selection of a proper safety factor in any particular case should be left
to the judgment of one who is quite familiar with the conditions under
which the tube is to be used.
Ordinarily a safety factor of five is sufficient when the stresses due to
actions other than a constant fluid pressure are more or less trivial.
In case there are repeated fluctuations of the fluid pressure, vibration,
shock, internal strain due to unequal heating, etc., then a larger safety
factor of from six to twelve or more should be used, depending upon the
severity of these actions.
3. The apparent fiber stress under which the different tubes failed
varied from about 7000 pounds for the relatively thinnest to 35 ooo
pounds per square inch for the relatively thickest walls. Since the
average yield point of the material was 37 ooo and the tensile strength
58 ooo pounds per square inch, it would appear that the strength of a
Collapsing Pressures
229
tube subjected to a fluid collapsing pressure is not dependent alone
upon either the elastic limit or the ultimate strength of the material
constituting it.
Marine law fixes the thickness of tubes that may be used subject
to external or collapsing pressure, on Merchant (not Naval) Marine
Vessels. The following is taken from the "Rules and Regulations pre-
scribed by the Board of Supervising Inspectors of the Steamboat Inspec-
tion Service of the Department of Commerce and Labor, U. S. A., as
amended January, 1912."
From page 32, paragraph 15: Working pressures and corresponding
minimum thicknesses of wall for long, plain, lap-welded and seamless
steel flues, 7 to 18 inches diameter, subjected to external pressure only,
shall be determined by the following table and formula:
Working pressure in pounds per square inch
Outside
diameter
100 120
140
160
180
200
220
of flue
1
Thickness of flue in inches. Safety factor, 5
Inches
7
• 152
.160
.168
.177
.185
.193
.2OI
8
.174
.183
• 193
.202
.211
.220
.229
9
.196
.206
.217
.227
-237
.248
.258
10
.218
.229
.241
.252
.264
.275
.287
ii
.239
.252
.265
.277
.290
.303
.316
12
.261
• 275
.289
.303
.317
.330
.344
13
.283
.298
• 313
-328
• 343
.358
• 373
14
.301
.320
• 337
• 353
.369
.385
.402
15
• 323
• 343
.361
.378
.396
• 413
• 430
16
• 344
.366
.385
.404
.422
.440
• 459
17
.366
.389
.409
.429
.448
.468
.488
18
.387
.412
• 433
• 454
.475
.496
.516
Thicknesses in this table were calculated by formula:
where
86 670
j) _ outside diameter of flue in inches;
T = thickness of wall in inches;
P = working pressure in pounds per square inch;
F = factor of safety.
This formula is applicable to lengths greater than six diameters of
flue, to working pressures greater than 100 pounds, to outside diameters
of from 7 to 1 8 inches and to temperatures less than 650° F.
From page 34, paragraph 16: Lap-welded and seamless tubes, used
in boilers whose construction was commenced after June 30, 1910,
having a thickness of material according to their respective diameters,
shall be allowed a working pressure as prescribed in the following table,
provided they are deemed safe by the inspectors. Where heavier
material is used, pressure may be allowed as prescribed in formula of
paragraph 15, given above. Any length of tube is allowable.
230
Collapsing Pressures
Outside
diameter
Thickness of
material
Maximum
pressure
allowed
Inches
Inch
Pounds
2 .095
427
2*4 .095
380
21/2
.109
392
2%
• .109
356
3
.109
327
M
.120
332
3V2
.120
308
3%
.120
282
4
.134
303
m
.134
238
5
.148
235
6
.165
199
Comparison of Collapse and Column Formulae. To connect these
collapse tests with the known properties of material under compression,
consider their relation to the supporting power of columns as pointed
out in 1876 by Prof. W. C. Unwin* Consider a short portion of the pipe,
say, one inch long. The thickness bears a relation to the radius of gyra-
tion and the circumference a relation to the length of a column whose
ends are "fixed." Expressed in symbols, these relations are
f-..SpJ
By this rule can be computed the value of — that corresponds to —
D K
of any column tested. The pressure (P) corresponding to the support-
Pi Pi
ing power — of a column is obtained by putting — = S in the rule
S D A A
— *» — . By these rules a diagram, Fig. 118, has been constructed from
tests of columns. The diagram is plotted to show the relation between
collapsing pressure and ratio of thickness to diameter. It is evident
from this diagram that collapsing pressure can be calculated either from
tests of columns or directly from tests of collapse.
The heavy full line is by formulae (B) and (G), page 228. The solid
dots are from Christie's tests on fixed end columns. The circles are
from Watertown tests on pipe columns. The dot and dash line is from
Christie's tests of columns of steel having 0.12 per cent. Carbon and the
dotted line from Christie's tests of columns of steel having 0.36 per cent.
Carbon. The last two indicate what increase in collapsing pressure
may be expected from the use of high strength steel.
The change in the direction of the lines (from column tests), which
starts at about ^= o.io, indicates that the straight line formula for
* Proc. Ins. Civ. Engrs., Vol. 46, p. 225.
Collapsing Pressures 231
collapse should not be extrapolated far outside the range of experiments
on which it was based. This diagram indicates the remarkable con-
firmation that column tests lend to the results of these collapse tests.
1
/
HARD STEEL
C-06 ~>
/
/
SOFT STEEL/
Csa'12 /^4''
^
/
//f
'S
z
' s/
u
cc 7 000
/
' s6
/
/
< 7,oo
W 5,000
£ 4,000
CO
CO 3,000
UI
cc
C
a.
0
1 1.000
a.
3 70°
o
500
400
300
200
100
.C
Prof. \\
that used
formula f
empirical
mula, beir
formula, £
umns and
s
•/
c /•
/
/,•'
-
~j
'/
«
/,
'/
f£
fr
i
f:
• WROUGHT
O STEEL PIPE
ION COL
COLUMN
IMNS
\
I
i
jj
ir
!
I
//
J
./
1 .02 .C
r. E. Lilly, * pro
in obtaining a
or collapse, P =
and based on 1
ig derived by the
;ives another con
the colla-pse of ti
*
3 .04 .05 .07
RATIO J
Fig. 118
:eeding by a p
column formu
80000
.10 .20 .30 .40.50
ft
rocess of reasoning similar to
la, has derived the following
, in which the constants are
rt's collapse tests. This for-
lat is used to obtain a column
ti the supporting power of col-
Cngrs.
/ 1000 \ t )
'rofessor Stewa
same process t
nection betwee
ibes.
Tish Ins. of Civ.
232 Collapsing Pressures
Collapsing Pressures — Pounds per Square Inch
(Based on Professor Stewart's Formulae B and G.)
Formula
P = 86 670 t/D- 1386 (B). P= 50 210 ooo (t/D)* (G).
Where P — collapsing pressure in pounds per square inch;
D = outside diameter of tube in inches; / = thickness of wall in inches.
Thick-
ness
Outside diameter— Inches
1. 000
1.050
1. 125
1.250
I.3I5
1-375
I.50O
i. 660
.01
.02
.03
.04
.05
.06 •
.07
.08
.09
.10
.11
.12
.13
.14
.15
.16
.17
.18
.19
.20
.21
.22
.23
.24
.25
.26
•27
.28
.29
.30
• 31
•32
.33
.34
.35
• 36
• 37
.38
.39
.40
.41
• 42
.43
• 44
•45
.46
• 47
.48
.49
402
i 214
2081
2948
3814
4681
5548
6414
7 281
8 148
9014
9881
10 748
ii 615
12 481
13348
14 215
I508I
15948
I68I5
I768I
18548
I94I5
20 282
21 148
22015
22 882
23748
24615
347
I 090
I 916
2741
3567
4392
5217
6043
6868
7694
8519
9345
10 170
IQ995
ii 821
12 646
13472
14297
15 123
15948
16773
17599
18424
19250
20075
20901
21 726
22551
23377
24 2O2
282
925
1696
2466
3236
4007
4777
5548
6318
7088
7859
8629
9400
10 170
10 940
II 711
12 481.
13252
14 O22
14792
15563
16333
17104
17874
l8644
I94I5
20185
20 956
21 726
22 496
206
694
1387
2081
2774
3468
4 161
4854
5548
6 241
6934
7628
8321
9014
9708
10 401
II 094
11788
12 481
T3i75
13868
14561
15255
15948
16 641
17335
18028
18 721
I94I5
20 108
20 802
21495
22 l88
22 882
23575
24 268
596
I 250
1909
2568
3228
3887
4546
5205
5864
6523
7 182
7841
8500
9 159
9818
10478
ii 137
ii 796
12455
13114
13773
14432
15091
15750
16409
17068
17728
18387
19 046
19705
20364
21 023
21 682
• 22 341
23 ooo
521
I 135
1766
2396
3026
3657
4287
4917
5548
6178
6808
7439
8069
8699
9330
9960
10590
II 221
II85I
12 481
13 112
13742
14372
15003
'5633
16 263
16893
17524
18154
18784
I94I5
20045
20675
21 306
21 936
402
925
I 503
2081
2659
3236
3814
4392
4970
5548
6 125
6703
7 281
7859
8437
9014
9592
10 170
10 748
II 326
II 903
12 481
13059
13637
I42I5
14792
15370
r|948
1 6 526
17104
17681
18259
18837
I94I5
19993
i 747
2 269
2791
3313
3835
4357
4879
5401
5923
6446
6968
7490
8012
8534
9056
9578
IO IOO
10 622
II 145
II 667
12 189
12 711
13233
13755
14277
14799
15321
15844
16366
16888
17410
17932
18976
Collapsing Pressures 233
Collapsing Pressures — Pounds per Square Inch (Continued)
(Based on Professor Stewart's Formulae B and G.)
Formula
P= 86 670 t/D- 1386 (B). P =50 2 10 ooo (t/D)* (G).
Where P= collapsing pressure in pounds per square inch;
D = outside diameter of tube in inches; / = thickness of wall in inches.
Outside diameter — Inches
Thick-
ness
1.750
1.875
1.900
2. OOO
2.250
2.375
2.500
.01
.02
.03
.04
.05
.06
1586
1387
1351
I 214
925
804
694
.07
2081
I 850
1807
I 647
i 310
I 169
I 041
.08
2576
2 312
2 263
2081
1696
1533
1387
.09
3071
2774
2719
2514
2081
1898
I 734
.10
3567
3236
3176
2948
2466
2 263
2081
.11
4062
3699
3632
3381
2851
2628
2427
.12
4557
4 161
4088
3814
3236
2993
2774
•13
5052
4623
4544
4248
3 622
3358
3 121
• 14
5548
5085
5 ooo
4681
4007
3723
3468
• IS
6043
5548
5456
5 H4
4392
4088
3814
.16
6538
6 oio
5913
5548
4777
4453
4 161
• I?
7033
6472
6369
598i
5 162
4818
4508
.18
7529
6934
6825
6414
5548
5183
4854
.19
8024
7397
7281
6848
5933
5548
5201
.20
8519
7859
7 737
7 281
6318
5913
5548
.21
9014
8 321
8 193
7714
6703
6277
5894
.22
95io
8783
8649
8 148
7088
6642
6 241
.23
10005
9246
9 106
8581
7474
7007
6588
.24
10 500
9708
9 562
9014
7859
7372
6934
.25
10995
10 170
0018
9448
8244
7737
7281
.26
II 491
10632
0474
9881
8629
8 102
7628
.27
II 986
11094
0930
10314
9014
8467
7974
.28
12 481
II 557
1386
10748
9400
8832
8321
.29
12976
12 019
1843
ii 181
9785
9 197
8668
.30
13 472
I248I
12299
ii 615
10 170
9562
9014
• 31
13967
12943
12 755
12048
10555
9927
936i
• 32
14462
13406
13 211
12 48l
10940
10 292
9708
.33
14957
13868
13667
12915
ii 326
10657
10054
• 34
15453
14330
14 123
13348
II 711
II O2I
10 401
• 35
15948
14792
I458o
13781
12 096
II386
10748
.36
16443
I52S5
15036
14215
12 48l
II 751
ii 094
.37
16939
I57I7
15492
14648
12866
12 Il6
ii 44i
.38
17434
16 179
15948
15081
13252
12 481
11788
.39
17929
16 641
16 404
15515
13637
12 846
12 135
.40
18424
17104
16860
15948
14022
I32II
12481
.41
16381
14 407
13 576
12 828
• 42
16 815
14 792
13 941
13 175
• 43
17 248
15 178
14 306
13 521
• 44
17681
15 563
14 671
13868
• 45
15 036
14 215
.46
15 401
14 56l
• 47
.48
.49
234 Collapsing Pressures
Collapsing Pressures — Pounds per Square Inch (Continued)
(Based on Professor Stewart's Formulae B and G.)
Formula
P= 86 670 t/D- 1386 (B). P= 50 210 ooo (t/DF (G).
Where P— collapsing pressure in pounds per square inch;
D = outside diameter of tube in inches; / = thickness of wall in inches.
Outside diameter — Inches
Thick-
ness
2.750
2.875
3-OOO
3.250
3-500
3.750
4.000
.01
.02
.03
.04
.05
.06
521
.07
820
.08
i 135
.09
1450
1327
I 214
I OI4
843
.10
1766
I 629
1503
I 28l
i 090
.11
2081
I 930
I 792
I 547
1338
.12
2396
2 232
2081
I 814
i 586
1387
1214
.13
2711
2533
2370
2081
1833
1619
1431
.14
3026
2834
2 659
2347
2081
1850
1647
.15
3341
3 136
2948
2 614
2328
2081
1864
.16
3657
3437
3236
2881
2576
2312
2081
17
3972
3739
3525
3148
2824
2543
2297
.18
4287
4040
3814
3414
3071
2774
2514
.19
4 602
4342
4 103
3681
3319
3005
2731
.20
4917
4643
4392
3947
3567
3236
2948
.21
5232
4945
4681
4 214
3814
3468
3164
.22
5548
5246
4970
4481
4 062
3699
338i
.23
5863
5548
5259
4748
4309
3930
3598
.24
6178
5849
5548
5014
4557
4161
3814
.25
6493
6 151
5836
5 281
4805
4392
4031
.26
6808
6452
6 125
5548
5052
4623
4248
.27
7 123
6753
6414
5814
53oo
4854
4464
.28
7439
7055
6703
6081
5548
5085
4681
.29
7754
7356
6992
6348
5795
5316
4898
.30
8069
7658
7 281
6614
6043
5548
5H4
.31
8384
7959
7570
6881
6 290
5779
5331
.32
8699
8261
7859
7148
6538
6010
5548
.33
9014
8562
8 148
7414
6786
6241
5764
.34
9330
8864
8437
7681
7033
6472
5981
.35
9645
9 165
8726
7948
7 281
6703
6198
.36
9960
9467
9014
8214
7529
6934
6414
.37
10275
9768
9303
8481
7776
7105
6631
.38
10590
10070
9592
8748
8024
7397
6848
• 39
10905
10371
9881
9014
8272
7628
7064
.40
II 221
10 672
10 170
9 281
8519
7759
7281
.41
H536
10974
10459
9548
8767
8090
7498
.42
II85I
II 275
10748
9814
9014
8321
7714
.43
I2I66
II 577
II 037
10 08 1
9 262
8552
7931
• 44
12 481
II 878
II 326
10348
9 5io
8783
8148
.45
12796
12 180
II 615
10 615
9757
9014
8364
.46
13 H2
12 481
11903
10 88 1
10 005
9246
8581
«47
12 783
12 192
ii 148
10 253
9477
8798
.48
13 084
12 481
II 414
10 500
9708
9014
.49
13386
12 770
ii 681
10 748
9939
9231
Collapsing Pressures 235
Collapsing Pressures — Pounds per Square Inch (Continued)
(Based on Professor Stewart's Formulae B and G.)
Formula
P = 86 670 t/D- 1386 . . . . (B). P = 50 210 ooo (///>)» (G).
Where P= collapsing pressure in pounds per square inch;
D = outside diameter of tube in inches; / = thickness of wall in inches.
Thick-
ness
Outside diameter — Inches
2.750
2.875
3 ooo
3.250
3.500
3-750
4.000
• So
.51
• 52
.53
.54
$
.57
.58
.59
.60
.61
.62
.63
.64
1
-67
.68
.69
.70
• 71
.72
.73
• 74
• 75
.76
• 77
• 78
.79
.80
.81
.82
.83
.84
.85
.86
.87
.88
.89
.90
• 9i
.92
• 93
.94
• 95
.96
• 97
.98
.99
1. 00
13687
13988
14290
I459I
14893
I5I94
15496
13059
13348
13637
13926
14 215
14503
14792
ii 948
12 215
12 481
12748
I30I5
13 281
13548
0995
I 243
I 491
I 738
1986
2234
2 481
2729
2976
13224
13472
10 170
10 401
10 632
10863
II 094
II 326
II 557
II 788
12 019
12 250
12 481
12 712
12943
I3I75
13406
9448
9664
9881
0098
0314
0531
o 748
0964
I 181
1398
I 615
I 831
2048
12 265
12 481
236 Collapsing Pressures
Collapsing Pressures — Pounds per Square Inch (Continued)
(Based on Professor Stewart's Formulae B and G.)
Formula
P= 86 670//D- 1386 (B). P= 50 210000 (//£)» (G).
Where P= collapsing pressure in pounds per square inch;
D = outside diameter of tube in inches; / = thickness of wall in inches.
Outside diameter — Inches
Thick-
ness
4.250
4.500
4-750
S.ooo
5.250
5 5oo
5.563
.01
.02
.03
.04
.05
.06
.07
.08
.09
.10
.11
.12
1061
925
.13
1265
1118
986
867
760
663
.14
1469
1310
1169
1041
925
820
795
.15
1673
1503
1351
1214
IOOO
978
951
.16
1877
1696
1533
1387
1255
1 135
1107
.17
2081
1888
1716
1561
1420
1293
1263
.18
2285
2081
1898
1734
1586
1450
1418
.19
2489
2273
2081
1907
1751
1608
1574
.20
2693
2466
2263
2081
1916
1766
1730
.21
2897
2659
2446
2254
2081
1923
1886
.22
3100
2851
2628
2427
2246
2081
.2042
•23
3304
3044
2811
2601
2411
2238
2197
.24
35o8
3236
2993
2774
2576
2396
2353
.25
3712
3429
3176
2948
2741
2554
2509
.26
39i6
3622
3358
3121
2906
2711
2665
.27
4120
3814
3540
3294
3071
2869
2821
.28
4324
4007
3723
3468
3236
3026
2976
.29
4528
4199
3905
3641
3401
3184
3132
• 30
4732
4392
4088
3814
3567
3341
3288
.31
4936
4585
4270
3988
3732
3499
3444
• 32
5140
4777
4453
4161
3897
3657
3600
.33
5344
4970
4635
4334
4062
3814
3755
• 34
5548
5162
4818
4508
4227
3972
391 1
• 35
5752
5355
5000
4681
4392
4129
4067
.36
5955
5548
5183
4854
4557
4287
4223
• 37
6i59
5740
5365
5028
4722
4445
4378
.38
6363
5933
5548
5201
4887
4602
4534
.39
6567
6125
5730
5374
5052
476o
4690
.40
6771
6318
5913
5548
5217
4917
4846
.41
6975
6511
6095
5721
5383
5075
5002
.42
7179
6703
6277
5894
5548
5232
5157
• 43
7383
6896
6460
6068
5713
5390
5313
.44
7587
7088
6642
6241
5878
5548
5469
• 45
7791
7281
6825
6414
6043
5705
5625
.46
7995
7474
7007
6588
6208
5863
578i
.47
8199
7666
7190
6761
6373
6020
5936
.48
8403
7859
7372
6934
6538
6178
6092
.49
8607
8051
7555
7108
6703
6336
6248
Collapsing Pressures 237
Collapsing Pressures — Pounds per Square Inch (Continued)
(Based on Professor Stewart's Formulae B and G.)
Formulas,
P= S667ot/D- 1386 (B). P=so2ioooo(//Z))3 (G).
Where P= collapsing pressure in pounds per square inch;
D = outside diameter of tube in inches; t = thickness of wall in inches.
Thick-
ness
Outside diameter — Inches
4.250
4.500
4-750
5.000
5.250
5-500
5.563
.50
.51
• 52
• 53
.54
.55
.56
.57
-58
.59
.60
.61
.62
.63
.64
.65
.66
.67
.68
.69
.70
• 71
.72
.73
• 74
.75
.76
• 77
.78
.79
.80
.81
.82
.83
.84
.85
.86
.87
.88
.89
.90
• 91
• 92
• 93
.94
•95
.96
• 97
.98
.99
i 1. 00
I
8810
9014
9 218
9422
9 626
9830
10034
10238
10 442
10 646
10850
ii 054
ii 258
ii 462
11665
8244
8437
8629
8822
9014
9207
9 400
9592
9785
9977
o 170
0363
0555
0748
0940
II 133
II 326
II 518
II 711
7 737
7920
8 102
8285
8467
8649
8832
9014
9 197
9379
9562
9 744
9927
o 109
o 292
0474
0657
0839
II 022
7 281
7454
7628
7801
7974
8 148
8321
8 494
8668
8841
9014
9 188
936i
9534
9708
9881
0054
o 228
o 401
0574
0748
o 921
6868
7033
7 198
7364
7529
7694
7859
8024
8 189
8354
8519
8684
8849
9014
9 179
9345
95io
9675
9840
10 005
10 170
IQ335
6493
6651
6808
6966
7123
7281
7439
7596
7754
7911
8069
8226
8384
8542
8699
8857
9014
9172
9330
9487
9645
9802
6404
6560
6715
6871
7027
7183
7339
7494
7650
7806
7962
8118
8273
8429
8585
8741
8897
9052
9208
9364
9520
9676
9831
9987
10143
10299
238 Collapsing Pressures
Collapsing Pressures — Pounds per Square Inch (Continued)
(Based on Professor Stewart's Formulae B and G.)
Formula
P= 86 670 t/D- 1386 (B). P= 50 210 ooo (//D)3 (G).
Where P = collapsing pressure in pounds per square inch;
D = outside diameter of tube in inches; t = thickness of wall in inches.
Thick-
Outside diameter — Inches
ness
6.000
6.500
6.625
7.000
7-500
7.625
8 ooo
.01
.02
.03
.04
.05
.06
• 07
.08
.09
.10
.11
.12
.13
.14
636
502
.15
78i
614
583
494
402
382
331
.16
925
747
707
600
488
464
402
• 17
1070
881
838
719
585
556
482
.18
1214
1014
969
843
694
660
572
.19
1359
1147
1 100
966
810
774
672
.20
1503
1281
1230
1090
925
887
781
.21
1647
1414
1361
1214
1041
1001
889
.22
1792
1547
1492
1338
1156
IH5
997
.23
1936
1681
1623
. 1462
1272
1228
1106
.24
2081
1814
1754
1586
1387
1342
1214
.25
2225
1947
1885
1709
1503
1456
1322
.26
2370
2081
2015
1833
1619
1569
I43i
.27
2514
2214
2146
1957
1734
1683
1539
.28
2659
2347
2277
2081
1850
1797
1647
.29
2803
2481
2408
2205
1965
1910
1756
• 30
2948
2614
2539
2328
2081
2024
1864
• 31
3092
2747
2670
2452
2196
2138
1972
• 32
3236
2881
2800
2576
2312
2251
2081
• 33
338i
3014
2931
2700
2427
2365
2189
• 34
3525
3148
3062
2824
2543
2479
2297
• 35
3670
3281
3193
2948
2659
2592
2406
.36
3814
3414
3324
3071
2774
2706
2514
• 37
3959
3548
3454
3195
2890
2820
2622
.38
4103
368i
3585
3319
3005
2933
2731
• 39
4248
3814
37i6
3443
3121
3047
2839
.40
4392
3948
3847
3567
3236
3i6l
2948
.41
4536
4081
3978
3690
3352
3274
3056
.42
4681
4214
4109
3814
3468
3388
3164
•43
4825
4348
4239
3938
3583
3502
3273
.44
4970
4481
4370
4062
3699
36i5
3381
. -45
5H4
4614
4501
4186
38i4
3729
3489
.46
5259
4748
4632
4309
3930
3843
3598
• 47
5403
4881
4763
4433
4045
3956
37o6
.48
5548
5014
4894
4557
4161
4070
3814
• 49
5692
5148
5024
4681
4276
4184
3923
Collapsing Pressures 239
Collapsing Pressures — Pounds per Square Inch (Continued)
(Based on Professor Stewart's Formulae B and G.)
Formula
P= 86 670 //Z>- 1386 (B). P= 50 210 ooo (t/D)* (G).
Where P = collapsing pressure in pounds per square inch ;
D = outside diameter of tube in inches; t = thickness of wall in inches.
Thick-
ness
Outside diameter — Inches
6. ooo
6.500
6.625
7.000
7-500
7-625
8.000
• So
.51
.52
• 53
.54
• 55
-56
• 57
.58
• 59
.60
.61
.62
.63
.64
.65
.66
.67
.68
.69
.70
• 71
• 72
.73
• 74
.75
• 76
• 77
.78
• 79
1
.81
.82
.83
.84
.85
.86
.87
.88
.89
.90
.91
• 92
• 93
.94
.95
.96
.97
.98
• 99
I.OO
5837
598i
6125
6270
6414
6559
6703
6848
6992
7137
7281
7425
7570
7714
7859
8003
8148
8292
8437
8581
8726
8870
9014
9159
9303
9448
5281
5414
5548
5681
5814
5948
6081
6214
6348
6481
6614
6748
6881
7014
7148
7281
7414
7548
7681
7814
7948
8081
8214
8348
8481
8614
5155
5286
5417
5548
5678
5809
5940
6071
6202
6333
6463
6594
6725
6856
6987
7117
7248
7379
75io
7641
7772
7902
8033
8164
8295
8426
8557
8687
8818
8949
9080
9211
9341
9472
9603
9734
9865
9996
4805
4929
5052
5176
5300
5424
5548
5671
5795
5919
6043
6167
6290
6414
6538
6662
6786
6910
7033
7157
7281
7405
7529
7652
7776
7900
8024
8148
8272
8395
8519
8643
8767
8891
9014
9138
9262
9386
4392
4508
4623
4739
4854
4970
5085
5201
5316
5432
5548
5663
5779
5894
6010
6125
6241
6357
6472
6588
6703
6819
6934
7050
7165
7281
7397
7512
7628
7743
7859
7974
8090
8205
8321
8437
8552
8668
4297
44i I
4525
4638
4752
4866
4979
5093
5207
5320
5434
5548
566i
5775
5889
6002
6116
6230
6343
6457
6571
6684
6798
6912
7025
7139
7253
7366
748o
7594
7707
7821
7935
8048
8162
8276
8389
8503
8617
4031
4139
4248
4356
4464
4573
4681
4789
4898
5006
5H4
5223
5331
5439
5548
5656
5764
5873
598l
6089
6198
6306
6414
6523
6631
6739
6848
6956
7064
7173
7281
7389
7498
7606
7714
7823
7931
8039
8148
240 Collapsing Pressures
Collapsing Pressures — Pounds per Square Inch (Continued)
(Based on Professor Stewart's Formulae B and G.)
Formula
P= 86 670//.D- 1386 (B). P=502ioooo(//Z))3 (G) .
Where P= collapsing pressure in pounds per square inch;
D = outside diameter of tube in inches; t = thickness of wall in inches.
Thick-
Outside diameter — Inches
ness
8.500
8.625
9.000
9.500
9.625
10.000
10.500
.01
.02
.03
.04
.05
.06
.07
.08
.09
.10
.11
.12
.13
.14
• IS
276
.16
335
320
282
240
230
.17
402
385
338
288
277
247
213
.18
477
456
402
341
328
293
253
.19
56l
537
472
402
386
344
297
.20
653
624
551
468
450
402
347
.21
755
724
636
542
521
465
402
.22
857
825
733
621
600
535
. 462
.23
959
925
829
712
685
611
528
• 24
1061
1026
925
804
775
694
600
•25
1163
1126
1022
895
865
78i
678
.26
1265
1227
1118
986
955
867
760
.27
1367
1327
1214
1077
1045
954
843
.28
1469
1428
1310
1168
1 135
1041
925
.29
I57i
1528
1407
1260
1225
1127
1008
• 30
1673
1629
1503
1351
1315
1214
1090
• 31
1775
1729
1599
1442
1405
1301
H73
.32
1877
1830
1696
1495
1387
1255
• 33
1979
1930
1792
1625
1586
1474
1338
.34
2081
2031
1888
1716
1676
1561
1420
• 35
2183
2131
1985
1807
1766
1647
1503
.36
2285
2232
2081
1898
1856
1734
1586
.37
2387
2332
2177
1990
1946
1821
1668
.38
2489
2433
2273
2081
2036
1907
1751
• 39
2591
2533
2370
2172
2126
1994
1833
• 40
2693
2633
2466
2263
2216
2081 I 1916
.41
2795
2734
2562
2355
2306
2167
1998
.42
2897
2834
2659
2446
2396
2254
2081
• 43
2998
2935
2755
2537
2486
2341
2163
.44
3100
3035
2851
2628
2576
2427
2246
• 45
3202
3136
2948
2719
2666
2514
2328
.46
3304
3236
3044
2811
2756
2601
2411
• 47
34o6
3337
3140
2902
2846
2687
2494
.48
3508
3437
3236
2993
2936
2774
2576
.49
3610
3538
3333
3084
3026
2861
2659 1
1
Collapsing Pressures 241
Collapsing Pressures — Pounds per Square Inch (Continued)
(Based on Professor Stewart's Formulae B and G.)
Formula
P=8667o//Z>-i386 (B). P= 50 210000 (//Z>)» (G).
Where P = collapsing pressure in pounds per square inch;
D = outside diameter of tube in inches; / = thickness of wall in inches.
Outside diameter — Inches
Thick-
ness
8.500
8.625
9.000
9.500
9.625
10.000
10.500
• 50
3712
3638
3429
3176
3116
2948
2741
• 51
3814
3739
3525
3267
3206
3034
2824
• 52
39i6
3839
3622
3358
3296
3121
2906
• 53
4018
3940
3718
3449
3386
3208 i 2989
• 54
4120
4040
3814
3541
3477
3294 1 3071
• 55
4222
4141
39io
3632
3567
338i
3154
.56
4324
4241
4007
3723
3657
3468
3236
.57
4426
4342
4103
3814
3747
3554
3319
.58
4528
4442
4199
3905
3837
3641
3401
.59
4630
4543
4296
3997
3927
3728
3484
.60
4732
4643
4392
4088
4017
38i4
3567
.61
4834
4744
4488
4179
4107
3901
3649
.62
4936
4844
4585
4270
4197
3988
3732
.63
5038
4945
4681
4362
4287
4074
3814
.64
5140
5045
4777 •
4453
4377
4161
3897
.65
5242
5146
4873
4544
4467
4248
3979
.66
5344
5246
4970
4635
4557
4334
4062
-67
5446
5347
5066
4727
4647
4421
4144
.68
5548
5447
5162
4818
4737
4508
4227
.69
5650
5548
5259
4909
4827
4594
4309
.70
5752
5648
5355 i 5ooo
4917
4681
4392
• 71
5853
5749
5451 ! 5091
5007
4768
4475
• 72
5955
5849
5548
5i83
5097
4854
4557
• 73
6057
5950
5644
5274
5187
4941
4640
• 74
6i59
6050
5740
5365
5277
5028
4722
• 75
6261
6151
5836
5456
5368
5114
4805
• 76
6363
6251
5933
5548
5458
5201
4887
• 77
6465
6351
6029
5639
5548
5288
4970
• 78
6567
6452
6125
5730
5638
5374
5052
• 79
6669
6552
6222
5821
5728
546i
5135
.80
6771
6653
6318
5913
5818
5548
5217
.81
6873
6753
6414
6004
5908
5634
53oo
.82
6975
6854
6511
6095
5998
5721
5383
.83
7077
6954
6607
6186
6088
58o8
5465
.84
7179
7055
6703
6277
6178
5894
5548
• 85
7281
7155
6799
6369
6268
598i
5630
.86
7383
7256
6896
6460
6358
6068
5713
.87
7485
7356
6992
6551
6448
6i54
5795
.88
7587
7457
7088
6642
6538
6241
5878
.89
6734
6628
6328
5960
.00
6825
6718
6414
6043
.91
6916
6808
6501
6125
.92
7007
6898
6588
6208
• 93
7099
6988
6674
6290
• 94
7190
7078
6761
6373
• 95
7281
7168
6848
6456
.96
7372
7258
6934
6538
• 97
7464
7349
7021
6621
.98
7555
7439
7108
6703
• 99
7646
7529
7194
6786
I.OO
7737
7619
7281
6868
242 Collapsing Pressures
Collapsing Pressures — Pounds per Square Inch (Continued)
(Based on Professor Stewart's Formulae B and G.)
Formula
P = 86 670 t/D- 1386 (B). P=so 210000 (t/D)* (G).
Where P= collapsing pressure in pounds per square inch;
D = outside diameter of tube in inches; t = thickness of wall in inches.
Thick-
Outside diameter — Inches
ness
10.750
II.OOO
11.500
11.750
12.000
12.500
12.750
.01
.02
.03
.04
.05
.06
.07
.08
.09
.10
.11
.12
• 13
.14
.15
.16
• I?
.18
236
220
192
180
170
150
141
.19
277
259
226
212
199
176
166
.20
323
302
264
248
232
206
194
.21
374
349
3o6
287
269
238
224
.22
430
402
351
329
309
274
258
.23
492
459
402
377
353
313
295
.24
559
522
456
428
402
355
335
.25
630
589
5i6
484
454
402
379
.26
710
663
58o
544
511
452
426
• 27
791
741
649 .
609
572
506
477
.28
871
820
724
679
636
564
532
.29
952
899
800
753
709
625
591
.30
1033
978
875
827
781
694
653
.31
IH3
1057
950
901
853
763
721
.32
1194
H35
1026 974
925
833
789
.33
1275
1214
noi | 1048
997
902
857
• 34
1355
1293
1176 ! 1122
1070
971
925
• 35
1436
1372
1252
1196
1142
1041
993
.36
1516
I45o
1327
1269
1214
IIIO
1061
• 37
1597
1529
1403
1343
1286
1 179
1129
• 38
1678
1608
1478
1417
1359
1249
1 197
.39
1758
1687
1553
1491
1431
1318
1265
.40
1839
1766
1629
1564
1503
1387
1333
.41
1920
1844
1704
1638
1575
1457
1401
.42
200O
1923
1779
1712
1647
1526
1469
.43
2081
2O02
1855
1786
1720
1595
1537
.44
2161
2081
1930
1860
1792
1665
1605
• 45
2242
2l6o
2205
1933
1864
1734
1673
.46
2323
2238
2081
2007
1936
1803
1741
.47
2403
2317
2156
2081
2009
1873
1809
.48
2484
2396
2232
2155
2081
1942
1877
• 49
2565
2475
2307
2228
2153
201 1
I94'5
Collapsing Pressures 243
Collapsing Pressures — Pounds per Square Inch (Concluded)
(Based on Professor Stewart's Formulae B and G.)
Formula
P=86 670 t/D- 1386 (B). P= 50 210 ooo (t/D}» (G).
Where P= collapsing pressure in pounds per square inch;
D = outside diameter of tube in inches; I = thickness of wall in inches.
Outside diameter — Inches
Thick-
ness
10.750
11.000
11.500
H.750
12.000
12.500
12.750
• So
2645
2554
2382
2302
2225
2081
2013
.51
2726
2632
2458
2376
2297
2150
2081
• 52
2806
2711
2533
2450
2370
2219
2149
• 53
2887
2790
2608
2523
2442
2289
2217
.54
2968
2869
2684
2597
2514
2358
2285
.55
3048
2947
2759
2671
2586
2427
2353
-56
3129
3026
2834
2745
2659
2497
2421
• 57
3210
3io5
2910
2818
2731
2566
2489
• 58
3290
3184
2985
2892
2803
2635
2557
.59
3371
3263
3061
2966
2875
2705
2625
.60
3451
3341
3136
3040
2948
2774
2693
.61
3532
3420
321 1
3H3
3020
2843
2761
.62
3613
3499
3287
3i87
3092
2913
2829
.63
3693
3578
3362
3261
3164
2982
2897
-64
3774
3657
3437
3335
3236
3052
2964
.65
3855
3735
3513
3409
3309
3121
3032
.66
3935
3814
3588
3482
3381
3190
3100
.67
4016
3893
3663
3556
3453
3260
3168
.68
4096
3972
3739
3630
3525
3329
3236
.69
4177
4051
38i4
3704
3598
3398
3304
.70
4258
4129
3890
3777
3670
3468
3372
• 7i
4338
4208
3965
3851
3742
3537
3440
• 72
4419
4287
4040
3925
38i4
3606
3508
-73
4499
4366
4116
3999
3886
3676
3576
• 74
458o
4445
4191
4072
3959
3745
3644
• 75
4661
4523
4266
4146
4031
3814
3712
.76
4741
4602
4342
4220
4103
3884
378o
• 77
4822
4681
4417
4294
4175
3953
3848
.78
4903
476o
4492
4367
4248
4022
3916
• 79
4983
4838
4568
4441
4320
4092
3984
.80
5064
4917
4643
4515
4392
4161
4052
.81
5144
4996
4719
4589
4464
4230
4120
.82
5225
5075
4794
4662
4536
4300
4188
.83
5306
5154
4869
4736
4609
4369
4256
.84
5386
5232
4945
4810
4681
4438
4324
.85
5467
5311
5020
4884
4753
45o8
4392
.86
5548
5390
5095
4958
4825
4577
4460
.87
5628
5469
5171
5031
4898
4646
4528
.88
5709
5548
5246
5105
4970
4716
4596
.89
5789
5626
5322
5179
5042
4785
4664
.90
5870
5705
5397
5253
5114
4854
4732
-91
5951
5784
5472
5326
5186
4924
4800
•92
6031
5863
5548
5400
5259
4993
4868
• 93
6112
5942
5623
5474
5331
5062
4936
.94
6i93
6020
5698
5548
5403
5132
5004
• 95
6273
6099
5774
5621
5475
5201
5072
-96
6354
6178
5849
5695
5548
5270
5140
• 97
6434
6257
5924
5769
5620
5340
5208
• 98
6515
6336
6000
5843
5692
5409
5276
-99
6506
6414
6075
59i6
5764
5478
5344
I.OO
6676
6493
6151
5990
5836
5548
5412
244 Pipe Columns
PIPE COLUMNS
Those parts of a structure that resist thrust or compressive stress are
known as columns or struts. Except when comparatively quite short,
columns and struts tend to fail by lateral bending or buckling. While
apparently similar in this respect to beams, the real stresses in a loaded
column are, however, of such an obscure nature that no satisfactory
theoretical formula has yet been produced for columns of the propor-
tions commonly used in practice. The only really useful formulae for
columns and struts are those based directly upon experimental data.
Radius of Gyration. The radius of gyration is the property of the
cross-section of a column that determines its strength. The relation
of the radius of gyration, R, to the moment of inertia, /, and area of
cross-section, A, is such that it equals the square root of the quotient
resulting from dividing the former by the latter, or R = v 7 H- A .
Slenderness Ratio. The strength of a column or strut is most easily
expressed in terms of its slenderness ratio, which is the length divided
by the least radius of gyration, — , both being stated in inches.
R
Strength of Columns. The strength of a column or strut depends
(i) upon the manner in which the ends are connected to the rest of the
structure, whether fixed in direction, hinged, etc., and upon the placing
of the loading, whether axial or eccentric; (2) upon the slenderness
L
ratio, — ; (3) upon the area of cross-section, A; and (4) upon the pltysi-
R
cal properties of the material.
Tables of Safe Loads for Pipe Columns. The tables, pages 245
to 249, give the safe loads in tons of 2000 pounds for Standard, Extra
Strong, and Double Extra Strong Pipe, computed by the formulae of
the New York and Chicago Building Laws.
According to the New York Building Code, the allowable compressive
stress per square inch for steel columns with flat ends is given by the
formula S = 15 200 — 58 — , where L is the length of the column and
R
R is the least radius of gyration, both in inches. It further states that
no column shall be used whose unsupported length is greater than 120
times its least radius of gyration.
According to the Chicago Building Ordinances the allowable com-
pressive stress per square inch for steel columns shall be determined
by the formula S = 16 ooo — 70 — , with a maximum allowable stress
R
of 14 ooo pounds per square inch. The length of column is limited to
120 times the least radius of gyration, except in the case of struts for
wind bracing, in which case the limit is 150 times the least radius of
gyration.
Pipe Columns
245
Standard Pipe Columns
(Loads in tons of 2000 pounds, based on New York Building Code.)
S = 15 200 - 58 L/R.
S = allowable compressive stress for steel, pounds per square inch;
L = length of column in inches;
R = least radius of gyration in inches.
Length,
feet
Size of pipe
2 2V2 3 1 3Va 1 4 4V2 1 S 6 7
Thickness
.154
.203
216
.226
•237
.247
.258
.280
.301
40
36
33
30
27
24
22
20
18
16
14
13
12
II
10
9
8
6
5
19.16
21-95
24-74
27 53
13-87
16.47
19.06
21.66
2
5
8
0
ii. 16
13-55
15.15
16.74
9-7
II. 2
12.7
14.3
30 32
8.02
9-49
10.95
12.42
23-39
25.12
32.18
34-04
35.90
37.76
39.62
40.55
41.48
42.41
43-34
44-27
45-20
46.13
47.06
47-99
6.41
7.81
9.20
10. 60
6.27
7.61
8.27
8-94
18.34
19-93
21.52
22.32
23.12
23.91
24.71
25-51
26.30
27.10
27.90
28.69
26.85
28.58
30.31
31-17
32.04
32.90
33-77
34.63
35-50
36.36
37-23
38.09
15-83
17-35
18.11
18.88
19.64
20.40
21.17
21.93
22.69
23-45
24.22
4.19
4.81
5-44
6.07
6.69
13.88
14.61
15-34
16.07
16.81
17-54
18.27
19.00
19-73
20.46
ii
ii
12
13
14
14
15
16
16
• 30
-99
.69
•39
.09
.78
.48
.18
.88
2.94
3-42
9.61
10.27
10.94
II. 60
12.27
12.94
I3.6o
3-89
4-37
7-32
7-94
8.57
9.20
9.82
4.84
5-32
5-79
Length,
feet
Size of pipe
8 | 9 1 10
II 12 | 13 | 14 15
Thickness
.322
• 342
.365
-375
• 375
• 375
.375
-375
40
36
33
30
27
24
22
20
18
16
14
13
12
II
10
9
8
6
5
24.04
28.02
31.00
33-99
33-53
37.76
40.93
45.38
55-49
60.12
63-60
67.08
70.55
74-03
76.35
78.67
80.99
83.30
85.62
86.78
87.94
89.10
90.26
91.42
92 . 57
93-73
94.89
96.05
64.44
69.07
72.55
76.03
79-51
82.98
85.30
87.62
89.94
92.26
94-57
95-73
96.89
98.05
99-21
100.37
101.53
102 . 69
103.85
105.00
75.63
80.26
83.74
87.22
90.69
94-17
96.49
98.81
101 . 13
103 . 45
105 76
106 . 92
108.08
109.24
110.40
111.56
112.72
113.88
115.04
116 20
84.58
89.21
92.69
96.17
99.65
03.12
05-44
07.76
10.08
12.40
14.72
15-88
17-03
18.19
19-35
20.51
21.67
22.83
23-99
25 . 15
93-53
98.17
101 . 64
105.12
108.60
112.08
114.40
116.71
119.03
121.35
123.67
124 83
125 99
127 15
128.31
129 47
130.62
131.78
132.94
134 - 10
49.90
53.28
56.66
60.05
63.43
65.69
67.94
70.20
72.46
74-71
75-84
76.97
78.10
79-22
80.35
81.48
82.61
83-74
84.86
44.10
36.97
39.96
41-95
43-94
45-93
47-92
49-90
50.90
51.89
52.89
53-88
54.88
55-87
56.87
57-86
58.86
47-27
50.44
52.55
54-66
56.78
58.89
61.01
62.06
63-12
64.18
65-23
66.29
67.35
68.40
69.46
70.52
NOTE. — Loads
L/R greater than
above or to the left of the zigzag line correspond to values of
120.
246
Pipe Columns
Standard Pipe Columns (Concluded)
(Loads in tons of 2000 pounds, based on Chicago Building Ordinances.)
S = 16000- ?oL/R.
S — allowable compressive stress for steel, pounds per square inch ;
L = length of column in inches; R — least radius of gyration in inches;
Maximum allowable compressive stress = 14 ooo pounds per square inch.
Length,
feet
Size of pipe
2 2Ya 3 3% 1 4 1 4% 1 S 6 | 7
Thickness
.154
.203
.216
.226
.237
.247
.258
.280
.301
40
36
33
30
27
24
22
20
18
16
14
13
12
ii
IO
9
8
7
6
5
15.00
18.37
21.73
25 10
IO.20
13-33
16.46
19.60
8.43
11.32
13-24
15.16
7.41
9-25
11.09
12.94
28.47
5-96
7-73
9-50
11.26
21.68
23-77
25.86
27-95
30.04
31.08
32.12
33-17
34-21
35-26
36.30
37-34
38.39
39-07
30.71
32.96
35-20
37-45
39.69
40.81
41-94
43.o6
44-iS
45-30
46.43
47-55
48.48
48.48
4.60
6.28
7-97
9-65
17.09
19.01
20.93
21.90
22.86
23.82
24-78
25-74
26.71
27.67
28.63
29-59
*3'o6
3.8i
4-57
5-32
6.08
4.96
6.57
7-37
8.18
14.78
16.62
17-54
18.46
19.38
20.30
21.22
22.14
23.06
23.98
24.90
13-03
13-91
14.79
15-68
16.56
17-44
18.33
19.21
20.09
20.98
2.29
2.86
10.49
11.33
12.18
13.02
13-86
14.70
15-54
16.38
17.23
8.98
9.78
10.59
H.39
12.20
13.00
I3.8I
3-44
4.01
6.83
7-59
8.34
9.10
9.86
4.58
5.16
5-73
Length,
feet
Size of pipe
8 | 9 10 ii | 12 | 13 I • 14 15
Thickness
.322
• 342
.365
• 375
• 375
.375
• 375
• 375
40
36
33
30
27
24
22
20
18
16
14
13
12
II
10
9
8
6
S
19.16
23.96
27-57
31.17
28.77
33.87
37-70
40.81
51
.26
60.68
66.27
70.47
74.67
78.86
83-06
85.86
88.65
91-45
94-25
97-05
98-45
99-85
101 . 24
102.05
102.05
102.05
102.05
102.05
102.05
72.45
78.05
82.25
86.44
90.64
94.84
97.64
100.43
103.23
106.03
108.83
110.23
111.62
I 2.36
I 2.36
i 2.36
I 2.36
I 2.36
I 2.36
i 2.36
81.88
87.47
91.67
95-87
100.06
104 . 26
107.06
109.86
112.65
115-45
118.25
119-65
120.61
120.61
120.61
120.61
120.61
120.61
120.61
120 . 6l
91.30
96.89
01.09
05.29
09.49
13-68
16.48
19.28
22.08
24.88
27.67
28.85
28.85
28.85
28.85
28.85
28.85
28.85
128.85
128.85
46.26
50.34
54-43
58.51
62.59
65.32
68.04
70.76
73.48
76.21
77-57
78.93
80.29
81.65
83.01
83.36
83-36
83.36
83.36
56.85
61.05
65.24
69.44
73.64
76.43
79-23
82.03
84.83
87.62
89.02
90.42
91.82
93-22
93.81
93.81
93.81
93.81
93.81
41-53
34-77
38.37
40.78
43-18
45-58
47.98
50.38
51.58
52.78
53-99
55-19
56.39
57-59
58.79
58.79
58.79
45-35
49-iS
51-73
54.28
56.83
59.38
6i.93
63.21
64.49
65.76
67.04
68.31
69.59
69.82
69.82
69.82
NOTE. — Loads above or to the left of the zigzag line correspond to values of
L/R greater than 120.
Pipe Columns
247
Extra Strong Pipe Columns
(Loads in tons of 2000 pounds, based on New York Building Code.)
5= 15 200- 58 L/R.
S = allowable compressive stress for steel, pounds per square inch;
L = length of column in inches;
R = least radius of gyration in inches.
Length,
feet
Size of pipe
2 21/2 1 3 1 3V2 1 4 4Va I 5 1 6 .7
Thickness
.218
.276 | .300
.318
• 337
.355
• 375
.432
.500
40
36
33
30
27
24
22
2O
18
16
14
13
12
II
IO
9
8
6
5
19.90
23.90
27.90
31.89
29-53
34.16
38.79
43-42
0
9
8
7
15-22
18.69
21.01
23-32
I3-I
15-2
17-4
19- 1
48.04
51.13
54-21
57-30
60.38
63.47
65.01
66.55
68.09
69.64
71.18
72.72
74.26
75.8o
77-35
10.65
12.72
14.80
16.88
34.56
37-23
8.36
10.32
12.28
14.24
25.63
27-95
30.26
31.42
32.57
33-73
34-89
36.04
37-20
38.35
39-51
40.67
39.89
42.56
45-22
46.55
47.89
49-22
50.55
51.88
53-22
54-55
55-88
57-21
8.14
9-99
10.91
11.84
21.86
24-05
25.14
26.24
27-33
28.43
29-52
30.61
31-71
32.80
33-90
"z'.&s
4-52
5-25
6.09
6.94
18.95
19.99
21.03
22.07
23.11
24.15
25.19
26.23
27.26
28.30
15.22
16.20
17.18
18.16
19.14
20.12
21. IO
22.08
23 06
7-79
8.64
12.76
13.68
I4.6l
15-53
16.46
17.38
18.30
5-19
5.86
9-49
10.34
11.19
12.03
12.88
6.53
7.20
7-87
Length,
feet
Size of pipe
8 9 I 10 | II 12 | 13 14 15
Thickness
.500
.500
.500
.500
.500
-500
.500
.500
40
36
33
30
27
24
22
20
18
16
.14
13
12
II
10
9
8
6
5
35-27
41.44
46.07
50.70
47-18
53.36
57-99
60.59
72.52
78.70
83.33
87.97
92.6o
97-23
100.32
103.41
106 . 50
109-59
112.68
114.22
115-77
117-31
118.86
120.40
121.95
123-49
125.04
126.58
84.45
90.63
95.26
99-90
104-53
109.17
112.25
115-34
118.43
121.52
124.61
126.16
127.70
129.25
130.79
132.34
133-88
135-43
136.97
138.52
99.36
105-54
IIO.I8
114.81
119-45
124.08
127.17
130.26
133-35
136.44
139-53
141.08
142.62
I44-I7
145.71
147.26
148.80
150.35
151.89
153-44
111.29
117-47
122. II
126.75
I3L38
136.02
139.11
142.20
145.29
148.38
151.47
I53-OI
154.56
156.10
157.65
159.19
160.74
162 . 29
163.83
165.38
123-23
129.41
134-04
138.68
143-32
147-95
151.04
154 • 13
157-22
160.31
163-41
164.95
166.50
168.04
169.59
I7LI3
172.68
174-22
175-77
177.31
66.77
71.40
62.62
76.04
80.67
85.30
88.39
91.48
94-57
97-66
100.74
IO2 . 29
103.83
105.38
106.92
108.47
IIO.OI
111.56
113.10
114.64
55-33
59.96
63.05
66.13
69.22
72.31
75-39
76.94
78.48
80.02
81.56
83.11
84-65
86.19
87.74
89.28
67.25
71.88
74-97
78.06
81.15
84.23
87.32
88.87
90.41
91-95
93-50
95-04
96.58
98.13
99.67
IOI . 22
NOTE. — Loads
L/R greater than
above or to the left of the zigzag line correspond to values of
1 20.
248
Pipe Columns
Extra Strong Pipe Columns (Concluded)
(Loads in tons of 2000 pounds, based on Chicago Building Ordinances.)
S = 16000 — ^oL/R.
S = allowable compressive stress for steel, pounds per square inch;
L = length of column in inches; R = least radius of gyration in inches;
Maximum allowable compressive stress =14 ooo pounds per square inch.
Length,
feet
Size of pipe
2 2i/2 | 3 1 3% I 4 4V2 i 5 I 6 7
Thickness
.218
.276
.300
.318
• 337
• 355
• 375
• 432
.500
40
36
33
30
27
24
22
2O
18
16
14
13
12
II
10
9
8
7
6
5
"*
22.52
28.11
33.69
39 28
14.16
18-99
23.81
28.64
II. 21
15-39
18.19
20.98
9-74
12.38
15.02
17.66
44 86
7.68
10.19
12.69
15.20
31.86
35-07
38.29
4i.5i
44-72
46.33
47-94
49 55
5I.I6
52.76
54-37
55-98
57-59
58.83
48.58
52.31
56.03
59-75
63-48
65.34
67.20
69.06
70.92
72.78
74.64
76.51
78.34
78.34
6.29
8.52
9-64
10.75
5.78
8.14
10.51
12.87
23-77
26.56
29-35
30.75
32.15
33-54
34-94
36.33
37-73
39-12
40.52
41-92
20.31
22.95
24.27
25.59
26.91
28.23
29 55
30.88
32.20
33-52
34.84
2.91
3-72
3.69
4-71
5-74
6.76
7-79
17.71
18.96
20.22
21.47
22.72
23.98
25-23
26.48
27.74
28.99
14.06
15-24
16.42
17.60
18.79
19-97
21.15
22.33
23.52
11.87
12.98
14.09
15.21
16.32
17-44
18.55
4-53
5-34
8.81
9-83
10.86
11.88
12.91
6.15
6.96
7-77
Length,
feet
Size of pipe
8 | 9 10 ii | 12 13 | 14 | 15
Thickness
.500
.500
.500
.500
.500
.500
.500
• 500
40
36
33
30
27
24
22
20
18
16
14
13
12
II
10
9
8
6
5
27.60
35-05
40.64
46.23
40.14
47-59
53-18
54-25
66.80
74.26
79-85
85-45
91.04
96.63
100.36
104.09
107.82
ill. 54
115.27
117.14
119.00
120.87
122.73
123.70
123.70
123.70
123.70
123-70
79.36
86.82
92.41
98.00
103.60
109 19
112.92
II6.65
120.38
124.11
127.84
129.70
131.56
133-43
134.70
134-70
134.70
134.70
134-70
134 • 70
95.o6
102 . 52
io8.ii
113.70
119.30
124.89
128 . 62
132.35
136.08
I39-8I
143-54
145-40
147.27
148.44
148 . 44
148.44
148.44
148.44
148.44
148.44
107.62
115.08
120.67
126.27
131.86
137-45
141 . 18
144-91
148 . 64
152.37
156.10
157-97
159-44
159-44
159-44
159-44
159-44
159-44
159-44
159-44
120.18
127.64
133.23
138.83
144.42
150.02
153-75
157.48
161.21
164.94
1 68. 67
170.43
170-43
170.43
170.43
170.43
170.43
170.43
170.43
170.43
61.71
67.30
72.89
78.48
84-07
87.80
91-53
95.26
98.98
02.71
04.58
06.44
08.30
0.17
2.03
2.70
2.70
2.70
2.70
58-77
51-81
57-40
61.13
64.85
68.58
72.30
76.03
77-89
79-75
81.61
83-48
85-34
87.20
89.06
89.34
89.34
64.36
69.95
73.68
77-40
81.13
84.86
88.58
90.45
92.31
94-17
96.04
97-90
99.76
100.33
100.33
100.33
NOTE. — Loads above or to the left of the zigzag line correspond to values of
L/R greater than 120.
Pipe Columns 249
Double Extra Strong Pipe Columns
(Loads in tons of 2000 pounds, based on New York Building Code.)
S = 15 200- 58 L/R.
S = allowable compressive stress for steel, pounds per square inch;
L = length of column in inches; R = least radius of gyration in inches.
Length,
feet
Size of pipe
2 2% 3 1 ZV-2 4 1 4% 5 6 7 8
Thickness
.436
.552
.600
.636
.674
•710 -750
.864
-875
.875
54-36
65 . 12
73-18
&I. 25
40
36
33
30
27
24
22
2O
18
16
14
13
12
II
IO
9
8
7
6
5
31.65
39-58
47-51
55-43
60.72
44.42
52.47
60.52
68.57
24-32
31.19
35-77
40.36
44-94
89-32
97-38
102.76
108.14
II3-5I
II8.89
124.27
126.96
129.65
132.33
135-02
137-71
140.40
143-09
145.78
148.47
20.74
25.07
29.40
33-74
38.07
76.62
81.99
87.35
92.72
98.09
03-45
06.14
08.82
11.50
14.19
16.87
19-55
22.24
124.92
127.60
5-72
7-03
8.35
9.66
7-37
9-03
10.69
12.35
14.01
15.67
12.47
16.11
17-93
19-74
21.56
12.43
16.30
20. 16
24-03
25.96
16.41
20.52
24.62
28.73
32-83
66.00
71.28
76.57
81.85
84.50
87.14
89.78
92.42
95.o6
97.71
100.35
102.99
105-63
49-52
54."
56.40
58.69
60.98
63.27
65.56
67-85
70.15
72.44
74-73
42.40
44-57
46.73
48.90
5i.o6
53-23
55-40
57.56
59-73
61.89
34.89
27.89
29.83
31.76
33.69
35.62
37.56
39-49
41.42
36.94
38.99
41.04
43-10
45.15
47.20
49-25
51-31
23.38
25.19
27.01
28.83
30.64
32.46
17-33
18.99
20.65
22.31
10.98
12.29
13.61
Double Extra Strong Pipe Columns (Concluded)
(Loads in tons of 2000 pounds, based on Chicago Building Ordinances.)
5 = 1 6 ooo - 70 L/R. (S, L, R, same as above.)
Maximum allowable compressive stress = 14 ooo pounds per square inch.
40
36
33
30
27
24
22
20
18
16
14
13
12
II
IO
9
8
6
5
31-86
41-57
51-29
6i.oa
40.04
53.61
63.35
73.08
82.82 :
92.55
99-04 .
105.53
112.02
IlS.51
125.00
128.25
131.49
134-74
137.98
141.23
144-47
147.72
149.13
149.13
19.87
29-43
39-00
48.57
54-94
16.05
24-35
29.88
35-41
40.94
13.81
19-04
24.27
29.50
34-73
70.72
77-19
83.67
90.15
96.63
103.10
106.34
109.58
112.82
116.06
119.29
122.53
125-77
129.01
129.89
10.31
15.27
20.22
25.17
30.13
7-13
H.79
16.46
21.12
23-45J
61.32
67.70
74.08
80.46
83.64
86.83
90.02
93-21
96.40
99-59
102.78
105-97
109.15
8.65
13.03
15.22
17.42
19.61
46.47
52.00
54.77
57-54
60.30
63.07
65-83
68.60
71.36
74-13
76.89
'3178
5-37
6.96
_L55
10.13
11.72
13.31
4-1?
6.17
8.18
10.18
12. 18
14 19
39-95
42.57
45-18
47-80
50.41
53-02
55.64
58.25
60.87
63-48
32.6l
35.08
37.56
40.04
42.52
44-99
47-47
49-95
52.42
25.78
28.12
30.45
32.78
35.ii
37-45
39.78
42.11
21.80
24.00
26.19
28.38
30.57
32.77
16.19
18.20
20.20
22.21
NOTE. — Loads above or to the left of the zigzag line correspond to values of
L/R greater than 120.
250 Mechanical Properties of Solid and Tubular Beams
MECHANICAL PROPERTIES OF SOLID AND TUBU-
LAR BEAMS
All those parts of a structure, such as a simple lever, an automobile
axle, or a trolley pole, which have to resist bending actions are known
as beams.
The bending actions upon a beam give rise to both stresses and defor-
mations, whose precise nature will of course depend upon the manner of
support and the nature of the loading. These will be treated, in what
follows, for straight solid and tubular beams having a uniform cross
section throughout their lengths.
Tensile and Compressive Stresses in Beams. The principal
stresses in a loaded beam are tension and compression. These are
illustrated in Fig. 119 for the case of a
beam supported at the ends and loaded
at the middle. In this case the lower
longitudinal fibers are subjected to
tensile stress, while the upper fibers
are subjected to compressive stress.
The former will, therefore, lengthen and
the latter shorten to an extent that
will depend upon the amount of the
loading. Within the elastic limit of
the material the lengthening or shortening of any fiber is directly pro-
portional to its distance from the neutral surface, JJ.
For steel, and other similar elastic materials not stressed beyond the
elastic limit, the neutral surface, JJ, will always pass through the centers
of gravity of the different cross sections. This neutral surface will of
course always divide the beam longitudinally into two parts, one of
which is subjected to tensile stress and the other to compressive stress.
The stresses on the individual fibers of a loaded beam are proportional
to their distances from the neutral surface, when all stresses are less
than the elastic limit of the material. There is of course no stress upon
the fibers lying in the neutral surface, this being the place where the
stress passes from tension on one side to compression on the other.
While selecting a value for the working fiber stress, when applying
the formulae given in the table, pages 258 to 263, of the Properties of
Solid and Tubular Beams, it should be remembered (i) that the fiber
of a beam that is subjected to the greatest stress is the one that lies at
the greatest distance from the neutral surface, and (2) that this most
remote fiber in practice should never be stressed beyond a certain frac-
tion of the elastic limit of the material, the value of the fraction depend-
ing upon the nature and frequency of the loading. See pages 268 to 270.
Shearing Stress in Beams. Every beam when loaded is subjected
to a transverse stress that tends to shear the beam across, as illustrated
at section YY of Fig. 120. The vertical shear, s, for any section of a
beam is the algebraic sum of all the external vertical forces on either
Shearing Stress in Beams
251
side of that section, upward forces, or reactions, being considered as posi-
tive, and downward forces or loads as negative to the left of the section.
To the right of the section the algebraic signs
are reversed. When s is positive, as at sec-
tion YY, Fig. 1 20, the part of the beam to the
left of the section tends to slide upward with
respect to the part to the right, and when
s is negative the left-hand part tends to slide
downward with respect to the right-hand
part.
In most cases the shearing action may be
ignored for steel beams, especially for those
having comparatively bulky cross sections,
such as tubes with sufficiently thick walls rel-
ative to their diameters. When, however,
the beam is very short, or the loading is
quite close to a support, or the web is com-
paratively thin, then the shearing stress may
become of equal or even greater importance
Fig. 1 20
than the tension or compression in the beam, in which case it should
be taken into consideration.
In the table, pages 258 to 263, of the Properties of Solid and Tubular
Beams, the maximum numerical values of the shearing stress will be
found tabulated for the different kinds of beam support and loading.
The locations of these maximum shears are also given.
Elastic Curve. Since the materials of which beams are constructed
are more or less elastic, a beam under load will assume a curved form.
The nature of this curve will of
course depend upon the manner of
support and loading.
Fig. 121 shows in a general way
the curved form assumed by a beam
that is fixed at one end, supported at
the other, and loaded at the middle
point of its length. The curved line
JJ assumed by the neutral axis of
the beam, the material not being
stiessed beyond the elastic limit, is known as the elastic curve. This
curve is of the greatest importance in the theoretical discussion of beams.
Elastic Deflection of Beams. The greatest departure of the elastic
curve of a loaded beam from the position of the neutral surface when the
beam is in an unloaded condition is known as the elastic deflection of
the beam. This is shown as d in Fig. 121, and is also represented by the
same letter in the different formulae of the table, pages 258 to 263, of
the Properties of Solid and Tubular Beams. It is to be understood, of
course, that these formulae apply only to beams of uniform cross section
and when the most strained fiber of the beam is not stressed beyond the
elastic limit of the material.
Fig. 121
252 Reactions of Supports
Reactions of Supports. Two kinds of external forces act upon a
beam. These are the loads which tend to move the beam bodily down-
ward and the reactions of the supports which oppose this tendency.
Thus, in Fig. 122, the load P acting down-
ward, because of the rigidity of the beam,
will be carried to the supports, and will
rest upon them jointly. The portion of
the load, in this case, carried by the
1 T left support, will be — —P- The reaction
»— * I
1 J offered by that support, then, will be
Ui IU2 Ui = —j— P, and similarly that carried by
the right-hand support will be Uz = - P.
It is a fundamental principle of mechanics that the sum of the reac-
tions must equal the sum of the loading, or, in the case of the simple
beam shown in Fig. 122, Ui + Uz — P-
In the table of the Properties of Solid and Tubular Beams, pages 258
to 263, the reactions, designated by U, are given for the different kinds
of support and loading, and are expressed in the same unit as the loading.
It should be noted that these formulae assume that the reactions act
in directions that are parallel to the action of the loading, that is to say,
in Fig. 122, the forces Ui, Uz, and P all act in parallel directions.
When a simple beam is subjected at the same time to both uniform and
concentrated loads, the reaction may be obtained by taking the sum of the
respective reactions due to the uniform load and to each concentrated load.
Bending Moment. The chief action of the external forces upon a
beam is most easily expressed as a bending moment, which is the ten-
dency of the external forces to produce rotation of the beam around
any of its sections. Thus, in
Fig. 123, the force P, acting down-
ward at the free end, will tend to
cause a bodily rotation of the beam
in a downward direction about the
section KK, at the fixed end. .
This tendency to rotate is
measured by the force, P, multi-
plied by the lever arm, I, the result, FiS- I23
PI, being the bending moment at
the section KK. Similarly, the bending moment at any other section
YY will be Px. A bending moment is commonly expressed in inch
pounds, the lever arm being stated in inches and the force in pounds.
Considering the portion of a beam that lies to the left of any section,
bending moments that tend to cause rotation in a clockwise direction
are taken as positive, while those that tend to cause rotation in the
opposite direction are taken as negative. For that portion that lies
to the right of any section, bending moments that tend to cause rotation
Bending Moment and Resisting Moment
253
Fig. 124
in a clockwise direction are negative, while those that tend to cause
rotation in the opposite direction are positive.
The bending moment at any section of a beam is equal to the algebraic
sum of the moments of all the external forces on either side of that section.
In case the force P does not act in a direction at right angles to the
beam, then the lever arm is to be taken as the perpendicular or shortest
distance from the section considered ...j.
to the line of action of the force.
Thus, in Fig. 124, the lever arm is
x = I sin a for the fixed end of the
inclined beam, and the corresponding
bending moment will be PI sin a, a
being the angle that the line of action
of the loading, or other force, makes
with the axis of the beam.
The bending moments of the table
of the Properties of Solid and Tubu-
lar Beams, pages 258 to 263, are ex-
pressed in inch pounds, and assume that the direction of loading is at
right angles to the direction of the beam when in its unloaded condition.
Resisting Moment. The strength of a beam to resist bending action
is known as its resisting moment. Thus, in Fig. 125, which represents
a beam fixed at one end and loaded at the other, the external force P
will evidently give rise to stresses that are held in equilibrium by the
internal forces shown. These internal resisting forces, shown in this
case for section KK, are due to the tensile
strength of the material of the beam ly-
ing above the neutral surface JJ, and to
the compressive strength of the material
lying below JJ. The beam in this case
tends to rotate downward about the cen-
ter of gravity of the section KK, and this
tendency is precisely counteracted by
the internal forces shown. It is evident
that the bending moment PI, Fig. 125,
must equal the sum of the individual
moments of each of the internal resisting
forces shown, all lever arms being measured from the center of gravity
of section KK In works on mechanics it is shown that this sum, or the
total resisting moment, is, for steel not stressed beyond the elastic limit,
Mr = /Z=/-> (i)
y
where M r = resisting moment in inch pounds;
/ = stress on farthest fiber from neutral surface JJ, in pounds
per square inch;
/ = moment of inertia of cross section;
y = distance of farthest fiber from neutral surface JJ;
Z = section modulus = I/y.
Fig. 125
254 Strength of Beams
Moment of Inertia, JT, and Section Modulus, Z. These are the prop-
erties of the cross section that determine respectively the elasticity and
strength of beams. By referring to the table of the Properties of Solid
and Tubular Beams, pages 258 to 263, it will be observed that every deflec-
tion formula contains as a factor the reciprocal of the moment of inertia of
cross section, /, and that every formula for the strength of beams contains
as a factor the section modulus, Z. Other things being equal, then, the
stiffness of beams will be proportional to their moments of inertia of cross
section, while the strengths will be proportional to their section moduli.
These two properties of the cross sections of beams are, therefore, of
the greatest importance in the practical application of mechanics to
all parts of structures that are subjected to bending actions. The
relation of these two properties is such that the value of the section
modulus can be obtained by dividing the corresponding moment of inertia
by the distance of the farthest fiber from the neutral axis, or
ZJ- <„
y
These properties of the cross section of pipe can be obtained from the
table of properties, pages 58 to 65. For Seamless Tubing see tables, pages
204 and 205. For other sizes use table, pages 424 to 459. For the prop-
erties of cross sections other than circular see tables, pages 264 to 267.
Strength of Beams. In order that a beam for any kind of support
and loading may have sufficient strength, the following conditions must
be satisfied:
1. The resisting moment due to the internal longitudinal stresses
at any section must equal the bending moment at that section due to
the external forces, or /
fZ=f-=M. (3)
2. The resisting shear due to the internal transverse stresses at any
section must equal the transverse shear at that section due to the
external forces, or fsA = S, (4)
where M = bending moment in inch pounds;
/ = moment of inertia of cross section;
Z = section modulus;
y =» distance from farthest fiber to neutral axis in inches;
A = area of cross section in square inches;
/= safe working fiber stress in pounds per square inch;
fs = safe working shearing stress in pounds per square inch;
S = shearing force in pounds.
Comparative Strength of Beams. The strength of a beam is
measured by the load that it can carry when the most strained fiber is
stressed to the safe working strength of the material. An examination
of the beam formulae, pages 258 to 263, will show, for well-proportioned
beams, where the tendency to shear, crimp, or buckle is kept subordinate,
that the strength of beams for any kind of support and loading will vary
(i) directly as the safe working fiber stress of the material, fs, (2) directly
as the section modulus, Z, and (3) inversely as the length of beam, /.
Strength, Stiffness and Weight of Beams
255
It is apparent, then, that for similar beams of given material, length,
and weight, the one which has the greatest section modulus, Z, will be
the strongest. For example, the strength of a tubular beam which is
4 inches diameter by Y2 inch wall, as compared with that of a similar
solid round beam of the same length, weight, and manner of support
and loading, will be as follows: The weight of the tubular beam is i8.6g
pounds per foot. From the table, page 429, the diameter of a solid
round beam of the same weight is found to be 2.65 inches. The respec-
tive section moduli are, then, 4.30 and 1.83. This tubular beam will,
then, be theoretically 2.4 times as strong as a similar solid round beam
of the same length and weight.
It should be remembered that for extreme cases, where beams tend to
fail by shearing, crimping, or lateral buckling, the above simple relations
do not strictly apply. For well-proportioned beams, however, these
laws apply with sufficient accuracy for practical purposes, irrespective
of the manner of support and loading.
Comparative Stiffness of Beams. The stiffness of a beam is indi-
cated by the load that it can carry with a given deflection. An exami-
nation of the beam formulae, pages 258 to 263, will show that the stiffness
of a beam, when stressed within the elastic limit of the material, for
any kind of support and loading, varies (i) directly as the modulus of
elasticity of the material, E, (2) directly as the moment of inertia of
cross section, /, and (3) inversely as the cube of the length of beam, I3.
Other things being equal, then, the stiffness of beams is directly
proportional to their moments of inertia of cross section, /. For exam-
ple, the above tubular beam, whose strength was shown to be 2.4 times
that of a similar solid round beam of the same length, weight, and manner
of support and loading, will be found to be 3.5 times as stiff, since their
respective moments of inertia of cross section are as 8.59 to 2.42.
Sections Giving Minimum Weight of Beams fora Given Strength or
Stiffness. For material, such as steel, which has practically the same phys-
ical properties in tension as in compression, the most economical forms
of beam cross section are as follows:
•i. For vertical loading only, that is
to say, for loading in a single direction,
a beam of given length will have a mini-
mum weight for a given strength or stiff-
ness when it has the "I" section shown
in Fig. 126. This form of cross section x_
permits of the most advantageous dispo-
sition of the material to resist stress for
loading in a single direction, because for
this condition both the moments of in-
ertia of cross section, 7, and the section
modulus, Z, can be made a maximum.
When designing beams of this character it should be remembered,
however, that sufficient material must be put in the web to resist the
greatest shear, and that the width of the flange in compression must be
- — X
Fig. 126
256
Properties of Solid and Tubular Beams
sufficient to prevent lateral buckling. Sufficient material must also be
put into the web to prevent crushing or buckling of the web underneath
the loading and at the supports.
2. For vertical and horizontal loading, that is to say, for loading in
two directions at right angles to each other, a beam of given length will
have a minimum weight for a given
strength or stiffness when it has the
hollow rectangular section shown
in Fig. 127. This form of cross sec-
tion permits of the most advanta-
geous disposition of the material to
resist stresses, for the conditions as-
sumed, since, for this form of beam,
the moments of inertia, I, and the
section moduli, Z, for a given sec-
X-
h
__
Fig. 127
tional area, can be made a maxi-
Fig. 128
mum for both the vertical and horizontal bending actions. When these
two actions are equal the cross section should of course be a hollow square.
3. For equal loading in any direction, a beam of given length will have
a minimum weight for a given strength or stiffness when it has the tubu-
lar section shown in Fig. 128. The ordinary tubular form of beam per-
mits of the most advantageous
disposition of the material to
resist stresses for the conditions
assumed, since for the circular
section the moment of inertia of
cross section, /, and the section
modulus, Z, can be made a max-
imum for loading in all direc-
tions around the beam.
It is evident that the cylindri-
cal tubular beam will approximate closely to a hollow square beam with
respect to strength and stiffness for equal loading in directions at right
angles to each other; also, that the hollow oval section will give results
approximating closely to those of the hollow rectangular section, Fig. 127.
TABLE OF THE MECHANICAL PROPERTIES OP
SOLID AND TUBULAR BEAMS OF
UNIFORM CROSS SECTION
This table of the mechanical properties of beams is based upon the
assumptions: (i) that the beam is straight when in its unloaded condition;
(2) that it has a uniform cross section from end to end; and (3) that the
directions of the loading and reactions lie in the same plane and are at
right angles to the axis of the beam when in its unloaded condition.
All the formulae contained in this table of the properties of beams have
been calculated anew, because it was desired to eliminate any errors
and misprints in the data on beams as found in the different standard
works on mechanics.
Properties of Solid and Tubular Beams 257
Notation. In this table of the mechanical properties of beams the
following notation is used:
A = area of cross section of beam in square inches. For a hollow, or tu-
bular beam, the area of the actual wall cross section must be used.
D = diameter of a solid round beam, in inches, or the outside diameter
of a tubular beam.
d = greatest deflection of a beam, in inches, or the greatest deviation
from straightness when the beam is subjected to a given loading.
E — modulus of elasticity of the material in pounds. The value of E
is approximately 29 ooo ooo for steel tubing, as obtained by ex-
periments on long tubular beams.
/ = fiber stress in pounds per square inch on the most strained fiber of
the beam.
f9 = shearing stress in pounds per square inch of cross section of the
beam.
/ = moment of inertia of cross section of the beam.
Values of / for pipe can be obtained from the table of properties,
pages 58 to 65. For Seamless Tubing see table, pages 204 and
205. For other sizes use table, pages 424 to 459. For sections
that are not round see table, pages 264 to 267.
/ = polar moment of inertia. For circular sections: J = 2 I.
I = length of beam in inches.
M = bending moment in inch pounds due to the loading on the beam.
The greatest value of M and its location, for each style of beam
support and loading, is tabulated to the left and shown on the
moment diagram to the right, immediately underneath the
figure of the beam.
Mr = resisting moment of the beam cross section in inch pounds = fZ.
P = pressure in pounds due to a load or force acting at right angles to
the axis of a beam.
R = radius of gyration of cross section in inches = v / -=- A .
Values of R for pipe can be obtained from the table of prop-
erties, pages 58 to 65. For Seamless Tubing see table, pages
206 and 207. For other sizes see table, pages 424 to 459. For
sections that are not round see table, pages 264 to 267.
S, Si, Sz = vertical shearing forces in pounds acting on the beam, due
to the loading.
U, Ui, Uz = reactions of the supports of a beam in pounds.
W — weight of a beam in pounds per lineal inch, also weight of a uni-
formly distributed load in pounds per lineal inch.
y = distance from neutral axis of beam to the most distant fiber in
inches. Values of y for tubular beams are given in the table,
pages 424 to 459.
Z = section modulus, or / -5- y.
Values of Z for pipe are given in the table of properties, pages
58 to 65. For Seamless Tubing see table, pages 204 and 205.
For other sizes calculate from the corresponding values of /
and y, in the table, pages 424 to 459. For sections that are not
round see table, pages 264 to 267.
258 Properties of Solid and Tubular Beams
Properties of Solid and Tubular Beams
i Greatest bending moment, at K PI
1
2 Greatest fiber stress, at K — or —
/ Z
7 Greatest safe load — or —
"~- — 3!
PI
A. Section modulus (2) —
p
p/3 m
5. Greatest deflection, at J — — or — — -
P/3
6 Moment of inertia (7) . . . ...
M ^^^^'
3 Ed
\
7. Load in terms of deflection — — •
I. Beam fixed at one end
and loaded at the other.
o Greatest shear from J to K. . . . P
Wl2
i Greatest bending moment at K.
fe-^,
2
Wfty Wl2
2 Greatest fiber stress, at K .... or
2/ 2Z
*. Greatest safe load — — or ^—
ly I
Wl2
A. Section modulus (2) —
f-""'"-"^
Wl* fP
o till 4 Eij
Wl*
M ^^^
8 Ed
II. Beam fixed at one end
and uniformly loaded.
8. Fiber stress in terms of deflection. . . . - — —
/2
Properties of Solid and Tubular Beams 259
Properties of Solid and Tubular Beams (Continued)
PI
i. Greatest bending moment, at K —
4
2. Greatest fiber stress, at K — - or —
4/ 4Z
3 Greatest safe load . — or —
k; J
Ji J l«
P
Ui U2
^^^ |M\^
ly I
PI
4 Section modulus (Z~) : —
4/
p/3 m
5. Greatest deflection, at K . . or —
48 El 12 Ey
PP
48 Ed
7. Load in terms of deflection - — - —
l
III. Beam supported at
both ends and loaded
at the middle.
P
p
9 Greatest shear, Ji to J2 ~
2
p
10 Reactions . . U \ = I/j == ~
2
i. Greatest bending moment, at K —
j^ _,. »___„ ^ |
8
WPy WP
2. Greatest fiber stress, at K or
87 8 Z
8 f. I 8 fZ
3 Greatest safe load — ^~ or — —
^"2"1K
Ui U2
/^^ IM^^X^
ly I
Wlz
4 Section modulus (Z) . . •
&/
<? TF/4 «: #2
5. Greatest deflection, at K, or ~^—
384 El 48 Ey
384 Ed
i j
5 I3
8. Fiber stress in terms of deflection. . —
5^2
Wl
Q Greatest shear at ends of beam —
IV. Beam supported at
both ends and uni-
formly loaded.
Wl
10 Reactions U\ = U% := —
2
260 Properties of Solid and Tubular Beams
Properties of Solid and Tubular Beams (Continued)
i. Greatest bending moment, K to K Pb
2. Greatest fiber stress, K to K —- or — -
1 <L
•? Greatest safe load — or — •
L. , '
J ^ ~~^j
U&JK ^^n
1 p p I
by b
Pb
4 Section modulus (Z) —
5. Greatest deflection (f I2 - b2) or
6 El
J-V-v
6. Moment of inertia (/)...... (f P- V)
/M MK
sH i
LJs,
V. Beam supported at
both ends, with two
equal symmetrical loads.
STTIKar atroiae III torme rvf Aaflf*f*tir\n - - -^
9. Greatest shear, from each end to load P
10. Reactions U\ = U% — P
i. Greatest bending moment, K to K Pbi
2. Greatest fiber stress, K to K. . . ^ or ^
fi fz,
3 Greatest safe load — or —
r~ ^-^^^1
biy &i
4 Section modulus (Z) — -
-Ckj^, K ^d\ ^/r^Ni^
*u&j»- *^cL
p p
U! U2
5 Greatest deflection ... </, = Pb^ Or ^~
8 El 8 Ey
d*= -^ (3 »!- 4 *i2) or -^- (3 /6i~ 4 ^2)
6 El 6Ey
6. Moment of inertia (/) — — or
&Edi
^7(3^i-4^2)
6£a2
7. Load in terms ( S Eldi 6 EIdz
\ M M / !
\ / I
i ns,
s,U
VI. Beam supported sym-
metrically, with two
equal end loads.
of deflection, ( M22 &i(3^i-4*i2)
8. Fiber stress in ( 8 Eydi 6 Eyd2
terms of deflection, ( b£ ^ (3^1-4i12)
9. Greatest shear, from each end to support, P
10. Reactions V\ = U% = P
Properties of Solid and Tubular Beams 261
Properties of Solid and Tubular Beams
(Continued)
bend.n ient at K Phb*
Jl;
(.
S
V
2
Pbib*y P0i&2
2. Greatest fiber stress, at K. . . — — — or — — -
3. Greatest safe load or
Ji p L
/y& ^^^--^
5. Greatest ( _W|. ^3 W* / - W» or
deflection ( 27 /£/
27 Ey
r~i L
27 / hd
II. Beam supported at
both ends and loaded
at any point of its
length.
0102V302(2/-02)3
10 Reactions .... U\ = — — (/^ =
>st bendin moment at K A P/
I
^
V
,
J
J
3 P/y 3 P/
2. Greatest fiber stress, at K -— or — ;
i67 i6Z
i6/7 i6/Z
3 Greatest safe load — — or — * —
ri^r^^
p
(
240 £7 45 Ey
P/3 \/5
^ \
/^
240 Ed
7 Load in terms of deflection ... d
[II. Beam fixed at one
end, supported at the
other, and loaded at
the middle.
8. Fiber stress in terms of deflection, **
9 Greatest shear at K . . . . . y^ P
10. Reaction V ' = ^ P
262 Properties of Solid and Tubular Beams
Properties of Solid and Tubular Beams (Continued)
i. Greatest bending moment, at K, Pbfo 2
2/2
2. Greatest fiber ( Pbib%y(l-\-bz) Pbib%(l-{-bz)
stress at K, \ 2PI zPZ
G fid 2/^7 2^Z
b]b^y(l-\- 62) bib2(l-\-b%)
4. Section modulus (Z) •
•/ffi, < I — — *•{ .
U
5. Greatest deflection, — ;— - I/ ' • or
6 El T 2 / + 62
;
P
s,
IX. Beam fixed at one
end, supported at the
other, and loaded at any
point of its length.
9. Greatest shear from K to load, — (623 — 3 b2P)
2/3
10. Reaction U = — (2 /3 — 3 62/2 -j- £>23)
2 /3
WP
i. Greatest bending moment, at K
8
2. Greatest fiber stress at K — — or — •
ly I
4. Section modulus (Z) .
U
of
r -i-A-'tS^SA Wl* W
5. Greatest deflection. . . .0054 — or .0432 —
Wfi
6. Moment of inertia (7) 0054 —
"Y
Ed
/3
8. Fiber stress in terms of deflection . . 23.15 -~
9. Greatest shear, at K f Wl
X. Beam fixed at one
end, supported at the
other, and uniformly
loaded.
xo. Reaction U = f Wl
Properties of Solid and Tubular Beams 263
Properties of Solid and Tubular Beams (Concluded)
PI
i. Greatest bending moment, at K —
Ply PI
81 8Z
3. Greatest safe load — — or •
qk %
ly I
PI
4. Section modulus (Z) . .
8/
5. Greatest deflection or — - —
192 El 24 Ey
P/3
6. Moment of inertia (7)
*V \|M
192 Ed
T T mrJ in fnrmc nf Anflnrtinn 1.Q2 till ,
Is,
I3
8. Fiber stress hi terms of deflection. . . — — -d
P
9. Greatest shear, K to K J p
XI. Beam fixed at both
ends and loaded at the
middle.
Wl2
i. Greatest bending moment, at K
12
2. Greatest fiber stress, at K — * or
12 / 12 Z
3. Greatest safe load — *• or — —
ly I
Wft
4. Section modulus (Z) -L^-
I
384 £7 32£y
6 Moment of inertia (7) -
384 Ed
7. Load in terms of deflection 384 £7 d
XII. Beam fixed at both
ends and uniformly
loaded.
8. Fiber stress in terms of deflection. . . — -d
9. Greatest shear, at K. \ Wl
264 Properties of Beam and Column Sections
Properties of Beam and Column Sections
A — Area of Section. / = Moment of Inertia.
W = Weight in pounds per foot, based on weight Z = Section Modulus,
of cubic inch of steel = 0.2833 pound. R— Radius of Gyration.
i
A=bh
2 4 = &i^i — £>2//2
= 2(b1+h1-2t)t
\ W = *Mb,ki - bM
j W = 3-4bh
% I T 1 AZ.3
T * m Ta on
\-)L Z = i 6&2
H3
12 = 0.2887 ^
Frirn =6.8(61+^-2/)/
h %L SK*&
f 'j! |~| I = T2 (&i^i3- M23)
'LjfeU 7 w - b*h*
6h,
R= VI + A
3
A=P
4 A = b? -b£
= 4(bi - t) t
$ W = *.AfW - 6,2)
| W — 3-4 62
/ = A64
i p" f | « 13.6(61-0*
M 1-
li- 1 ^^ | / = 1 2 (*14 ~ *24)
^-6-*j * Z = i&»
£ = 0.2887 &
l^-Vi
z:|f^?j
U = 0.2887 V6i2 + 62z
5
X" .4 — J2
y =0.7071 6 # = 0.28876
6 ^ = 6^ - 622
= 4(6i-/)<
/°^A:"vpr=3-4(ii2~ft22)
*a|r^Jt- " I3'6(&1 ~ ° '
^^^^^r /mA0i4-v)
/^^x/ /*i4 — ^24\
V z = 0.1179 ( . )
y- 0.7071 6, &»
R = 0.2887 A/6i2 + 622
Properties of Beam and Column Sections
265
Properties of Beam and Column Sections (Continued)
A = Area of Section. / = Moment of Inertia.
W = Weight in pounds per foot, based on weight Z = Section Modulus.
of cubic inch of steel = 0.2833 pound. R= Radius of Gyration.
0.2041 h
A=* 0.7854 D2
I = 0.049 1 D*
Z = 0.09821)3
i -t)t
266
Properties of Beam and Column Sections
Properties of Beam and Column Sections (Continued)
A = Area of Section. 7 = Moment of Inertia.
W '= Weight in pounds per foot, based on weight Z = Section Modulus.
of cubic inch of steel = 0.2833 pound. R= Radius of Gyration.
Note that position of axis through center of these sections affects the Section
Modulus only.
A = 0.866 D%
Zaa =0.1042 D3
Zbb = o. 1 203 D3
0.8284 Z?2
R = 0.257 D
Zaa =0.101 1 03
Z66 = 0.1095 £>3
0.4142 Z)
0.54120
15
= 0.866 D^
- 0.7854 ^22
= 0.0806 DJ
18
A = 0.8284 Z?!2
- 0.7854 Da2
=0.0430 Z?i2+
3.1416 (ZV-0*
= 2.816 Z>i2
- 2.670 Z)22
=0.1463 Z> i2
+io.68(ZV-0/
Z«a=O.IOII013
/D24\
-0.0907^— j
Z66= 0.1095 Pi3
-— ©
Properties of Beam and Column Sections
267
Properties of Beam and Column Sections (Concluded)
A = Area of Section.
R = Radius of Gyration.
/ = Moment of Inertia.
Z = Section Modulus.
26 27 A = bihi _
28
Let 7 be the Moment of Inertia of a
cross-section with respect to an axis
through its center of gravity, and 1\
the corresponding moment with re-
spect to a parallel axis at a distance k
from the first.
Also let A be the area of cross-
section.
Then h = I
268 Safety Factors
SAFETY FACTORS AND SAFE WORKING FIBER
STRESSES
Each member of a mechanical structure should be capable of resisting
the greatest straining action to which it can ordinarily be subjected when
in use. The designer should, therefore, consider under what conditions
the straining actions are greatest. When these actions are of a variable
character, it is of the utmost importance to take into consideration the
effects of this variation upon the endurance of the material. For
example, a member may fail under a straining action that causes stresses
which fluctuate, or which alternate repeatedly from tension to compres-
sion, when the same straining action would be successfully resisted under
the conditions of steady loading.
Margin of Security. It is apparent that the working load on
a member of a mechanical structure should be less than the calculated
breaking load for that member, in order to allow for inaccuracies, dete-
rioration, and probable contingencies, and thus provide a margin of
security. It is customary, therefore, to design a member so that
either (i) the statical breaking load, or (2) the load that causes the most
strained fiber of the material to just reach its elastic limit, shall be a
number of times the working load. This number is called the safety
factor. Thus, in the first case, if the statical breaking strength were
12 ooo pounds and the working load upon it 2000 pounds, then the
safety factor would be 12 ooo divided by 2000, or 6. In the second case,
if the statical load that causes the most strained fiber of the member
to just reach the elastic limit of the material were 6000 pounds and the
working load upon it 2000 pounds, then the safety factor on this basis
would be 3.
The elastic and ultimate strengths of the materials under static load-
ing can be easily obtained. The strength, therefore, under an assumed
steady loading, of any member of a mechanical structure can ordinarily
be calculated with sufficient accuracy. But the proper safety factor
to use under a given set of actual working conditions, involving ac-
tions of a more or less variable or uncertain character, can be arrived
at in most cases only as the result of long experience, or by tedious
experiment.
Safety Factor for Static Loading. For static loading, which can
be estimated with a reasonable degree of exactness, a safety factor of
2, as based upon the elastic limit of the material, will ordinarily be
found sufficient. By " static loading " is here meant one that causes a
permanent and unvarying straining action.
Safety Factors for Variable Loading. In the absence of more
precise data, the following formula, based upon the notable tests on the
fatigue of steel under repeated loading, by Wohler and Spangenberg,
and the later tests by Bauschinger and at the Watertown Arsenal, may
Safety Factors 269
be used in finding the proper safety factor to use for variable loading
of an indefinite number of repetitions:
>«\
(i)
Or, assuming a safety factor of 2 for static loading, as based upon
the elastic limit of the material,
F2=4~~' (2)
where Pi = safety factor under static loading;
Fz = corresponding safety factor under a loading that varies re-
peatedly between the limits Pi and P2j
Pi = greatest pressure due to the variable loading, to be taken
as plus ( +) if causing tension, and minus ( — ) if causing
compression in the most strained fiber of the member;
Pz = least pressure due to the variable loading, to be taken as
plus ( +) if causing tension, and minus ( — ) if causing com-
pression in the most strained fiber of the member.
This formula is general in its application to an indefinitely great
number of repetitions of loading with a known variation of stress. When
the loading is of such a character as to cause the stress on the most
strained fiber to alternate from tension to compression, care must be
taken to give to Pi and Pz their proper algebraic signs. When Pz is
zero, or when the variable stress on the most strained fiber is either con-
stantly tension or compression, then the algebraic signs of Pi and Pi
will be the same and may therefore be ignored.
The following special cases are of frequent occurrence:
i. For a loading that causes an indefinite number of reversals of stress,
that is to say, when the alternating tension and compression on the most
strained fiber of a member are equal, then Pz = -Pi and equation (i)
becomes
Or, assuming a safety factor of 2 for static loading, as based upon the
elastic limit of the material,
Fz = 6. (4)
This shows for sudden reversals of stress, indefinitely repeated between
equal limits of tension and compression, that the safety factor used
should be three times that for static loading under otherwise similar
conditions.
2. For a loading that causes stresses that alternate indefinitely
between zero and a fixed value, Pz = o, and equation (i) becomes
270 Safe Working Fiber Stresses
Or, assuming a safety factor of 2 for static loading, as based upon the
elastic limit of the material,
F2 = 4. (6)
This shows, for a suddenly applied loading indefinitely repeated, that
the safety factor used should be twice that for static loading under
otherwise similar conditions.
3. For a steadily applied loading Pz will of course equal Pi, and
equation (i) becomes F2 = (2 - i) Fi = Fi which shows that formula (i)
is correct at its inferior limit.
Safe Working Fiber Stresses. Since for any given material the
working fiber stresses for the different conditions of variable loading are
inversely proportional to the corresponding safety factors, it is apparent
that formula (i) may be put into the following form:
(7)
where, in addition to the notation as used above, /i = working fiber
stress under static loading, in pounds per square inch, and /z => corre-
sponding working fiber stress under a loading that varies repeatedly
between the limits Pi and PI.
This formula is general in its application, care being taken to give to
Pi and Pi their proper algebraic signs, as fully explained in connection
with formula (i) above.
The following are important special cases of this formula:
i. For a loading that causes an indefinite number of reversals of stress,
the alternating tension and compression on the most strained fiber being
equal, Pz = —Pi, and equation (7) becomes
/2 = - = -1/, (8)
Or, the safe working fiber stress under this condition is one-third of that
under similar static loading.
2. For a loading that causes stresses that alternate indefinitely
between zero and a fixed value, whether tension or compression, Pz = o,
and equation (7) becomes
liiif <«>
Or, the safe working fiber stress under this condition is one-half of that
under similar static loading.
Water 271
WATER
Properties PAGE
Weight 272
Volume 272
Pressure 273
Ice and Snow. . .
274
Specific Heat 275
Compressibility 275
Boiler Incrustation and Corrosion 275
Flow in Pipes
Fundamental Ideas 277
Quantity Discharged 278
Mean Velocity of Flow 280
Approximate Formula 280
Kutter's Formula 281
Darcy's Formula 282
Williams & Hazen's Exponential Formula 283
Effect of Curves and Valves 283
Hydraulic Grade Line 284
Air-bound Pipes 284
Water Hammer 284
Flow in House Service Pipes 285
Loss of Head by Friction , 286
Cox's Formula for Friction 289
Measurement of Flowing Water
Piezometer 291
Pitot Tube 291
Maximum and Mean Velocity in Pipes 292
Venturi Meter 292
Discharge of Pumping Engines 293
Miner's Inch 294
Water Power
Power of a Fall of Water-Efficiency 297
Horse Power of a Running Stream 297
Current Motors 298
Bernoulli's Theorem 298
Horse Power of Water Heads 299
Tables
Gallons and Cubic Feet 300
Contents of Pipes and Cylinders 301
Cylindrical Vessels, Tanks, etc , 302
Weight of Water in Pipes , 303
Barrels in Cylindrical Tanks 304
Capacity of Rectangular Tanks 305
Relative Discharge Capacity of Pipes 306
Pressure in Equivalent Heads of Water and Mercury 310
Conversion Table 311
Hydraulic Equivalents 312
272
Water
WATER
Water is composed
of two gases,
hydrogen and
oxygen, in the ratio
of two volumes of the former to one
of the latter. It is never found
pure in nature, owing
to the readiness with
which
it absorbs impurities
from the air and soil
Water boils under
atmospheric pressure (14.7
pounds at sea level) at 212°, passing off as steam.
Its
greatest density
is at 39.1° F., when it weighs 62.425
pounds per cubic foot.
Weight of Water per Cubic Foot at Different Temperatures
$
Ms
&
III
&
Ms
¥
$
&
t-i ..
Sl|
§ £
•5.2 1
§ 1
*§.a |
S §
i
) SH §
i
0 §
"§•£ o
H •*•*
'55*2 ft
£-)-*->
°a>*^ ft
HIS
*3 ft
H
£H 4->
'Jo^ ft
^ o
£o
N
0
£o
32
62.42
ISO
61.18
260
58.55
380
54
36
500
48.7
40
62.42
160
60.98
270
58.26
390
53-94
48.1
So
62.41
170
60.77
280
57.96
4<
X)
53
5
520
47-6
60
62.37
180
60.55
290
57.65
410
53-0
530
47-0
TO
62.31
190
60.32
300
57-33
420
52
6
540
46.3
80
62.23
200
60.12
3io
57.00
4
JO
52
2
550
45-6
90
62.13
210
59-88
320
56.66
440
Si
7
56o
44-9
IOO
62.02
212
59.83
330
56.30
450
51.2
570
44-1
1 10
61.89
220
59 63
340
55-94
460
50.7
58o
43-3
120
61.74
230
59-37
350
55-57
470
So
2
590
42.6
130
61.56
240
59.li
360
55-18
4*
to
49
7
600
41.8
140
61.37
250
58.83
370
54.78
490
49
2
Volume of Water
Cent.
Fahr.
Volume
5 Cent.
Fahr.
Volume
Cent.
Fahr.
Volume
4°
39-1°
.ooooc
35°
95°
.00586
70°
158°
.02241
5
.00001
40
104
I
.007
67
75
i
67
.02548
10
So
.00025
45
H3
.00967
80
176
.02872
IS
59
.00083
So
122
.01186
85
185
.03213
20
68
.00171
55
131
.01423
90
194
.03570
25
77
.00286
1 60
I4C
MA
78
95
2
•03
.03943
30
86
.00425
65
149
.01951
IOO
212
.04332
Water Pressure 273
WATER PRESSURE
(From Kent's Mechanical Engineers' Pocket Book.)
Comparison of Heads of Water in Feet with Pressures in
Various Units
One foot of water at 39.1° F. = 62.425 pounds per square foot;
One foot of water at 39.1° F. = 0.4335 pound per square inch;
One foot of water at 39.1° F. = 0.0295 atmosphere;
One foot of water at 39.1° F. = 0.8826 inch of mercury at 30° F.;
One foot of water at 39.1° F. = 773-3 j feet °f df at 32° K and atmosPheric
/ pressure;
One pound on the square foot, at 39.1° F. = 0.01602 foot of water;
One pound on the square inch, at 39.1° F. = 2.307 feet of water;
One atmosphere of 29.922 inches of mercury =33.9 feet of water;
One inch of mercury at 32° F = 1.133 feet of water;
One foot of air at 32° F. and i atmosphere = 0.001293 foot of water;
One foot of average sea-water = 1.026 feet of pure water;
One foot of water at 62° F = 62.355 pounds per square foot;
One foot of water at 62° F = 0.43302 pound per square inch;
One inch of water at 62° F. = 0.5774 ounce = 0.036085 pound per square inch;
One pound of water on the square inch at
62° F = 2.3094 feet of water;
One ounce of water on the square inch at
62° F = 1.732 inches of water.
Pressure of Water Due to Its Weight. The pressure of still water
in pounds per square inch against the sides of any pipe, channel, or
vessel of any shape whatever is due solely to the "head" or height of the
level surface of the water above the point at which the pressure is con-
sidered, and is equal to 0.43302 pound per square inch for every foot
of head, or 62.355 pounds per square foot for every foot of head (at
62° F.).
The pressure per square inch is equal in all directions, downwards,
upwards, or sideways, and is independent of the shape or size of the
containing vessel.
The pressure against a vertical surface, as a retaining-wall, at any
point, is in direct ratio to the head above that point, increasing from o
at the level surface, to a maximum at the bottom. The total pressure
against a vertical strip of a unit's breadth increases as the area of a
right-angled triangle whose perpendicular represents the height of the
strip and whose base represents the pressure on a unit of surface at the
bottom; that is, it increases as the square of the depth. The sum of all
the horizontal pressures is represented by the area of the triangle, and
the resultant of this sum is equal to this sum exerted at a point one-third
of the height from the bottom. (The center of gravity of the area of a
triangle is one-third of its height.)
The horizontal pressure is the same if the surface is inclined instead of
vertical.
The amount of pressure on the interior walls of a pipe has no appre-
ciable effect upon the amount of flow.
274
Water Pressure
Pressure in Pounds per Square Inch for Different Heads of Water
(At 62'
F., i foot head = 0.433 pound per square inch; 0.433 X 144 = 62.352
pounds per cubic foot.)
Head,
feet
0
i
2
3
4
5
6
7
8
9
0
0.433
0.866
1.299
1.732
2.165
2.598
3.031
3.464
3.897
10
4-330
4.763
5.196
5-629
6.062
6.495
6.928
7.36i
7-794
8.227
20
8.660
9-093
9.526
9-959
10.392
10.825
11.258
11.691
12.124
12.557
30
12.990
13.423
13.856
14.289
14.722
15.155
15.588
16.021
16.454
16.887
40
17.320
17-753
18.186
18.619
19.052
19.485
19.918
20.351
20.784
21.217
50
21 . 650
22.083
22.516
22.949
23.382
23.815
24.248
24.681
25.114
25-547
60
25.980
26.413
26.846
27.279
27.712
28.145
28.578
29.011
29.444
29.877
70
30.310
30.743
31.176
31.609
32.042
32.475
32.908
33-341
33-774
34-207
80
34.640
35-073
35.5o6
35-939
36.372
36.805
37.238
37.671
38.104
38.537
90
38.970
39.403
39.836
40.269
40.702
41 • 135
41.568
42.001
42.434
42.867
Head in Feet of Water, Corresponding to Pressures in Pounds
per Square Inch
(i pound
per square inch = 2.30947 feet head; i atmosphere = 14.7 pounds
per square inch = 33.94 feet head.)
Pres-
o
sure,
I
2
3
4
5
6
7
8
9
Ibs.
o
2.309
4.619
6.928
9.238
11.547
13.857
16.166
18.476
20 . 785
10
23.0947
25.404
27.714
30.023
32.333
34.642
36.952
39.261
41.570
43.88o
20
4
6.1894
48.499
50.8o8
53-118
55.427
57-737
60.046
62.356
64.665
66.975
30
69.2841
71.594
73.903
76.213
78.522
80.831
83.141
85.450
87.760
90.069
40
92.3788
94-688
96.998
99.307
101.62
103-93
106 . 24
108.55
110.85
II3.I6
50
II
5-4735
117.78
120.09
122.40
124.71
127.02
129-33
131 . 64
133-95
136 . 26
60
138.5682
140.88
143.19
145.50
147.81
150.12
152.42
154-73
157.04
159 35
70
161 . 6629
163.97
166.28
168.59
170.90
173-21
175.52
177.83
180.14
182.45
80
184.7576
187.07
189.38
191.69
194.00
196.31
198.61
200.92
203.23
205.54
90
207.8523
210.16
212.47
214.78
217.09
219.40
221.71
224.02
226.33
228.64
Ice and Snow. (From Clark.) i cubic foot of ice at 32° F. weighs
57.50 pounds; i pound of ice at 32° F. has a volume of 0.0174 cubic
foot =
30.067 cubic inches. *
Relative volume of ice to water at 32° F., 1.0855, the expansion in
passing into the solid state being 8.55 per cent. Specific gravity of
ice = 0.922, water at 62° F. being i.
At high pressures the melting-point of ice is lower than 32° F., being
at the
rate of 0.0133° F. for each additional atmosphere of pressure.
Specific heat of ice is 0.504, that of water being i.
i cubic foot of fresh snow, according to humidity of atmosphere,
weighs
5 pounds to 12 pounds, i cubic foot of snow moistened and
compacted by rain weighs 15 pounds to 50 pounds (Trautwine).
Boiler Incrustation and Corrosion
275
Specific Heat of Water
(From Marks and Davis's Steam Tables.)
fc
o
fc
O
fc
y
*j
o
£
o
fe
o
c8
tC+j
w
c£^
od
0)
S-s
<8
OH 40
o
t£ .»->
<8
£-8
g,
11
g,
'o ^
O
i
ilS
&
u
g,
11
g,
£1
0>
Q
co
Q
CO
1
en
1
CO
Q
CO
P
CO
20
.0168
120
0.9974
220
.007
320
.035
420
.072
520
.123
30
.0098
130
0.9979
230
.009
330
.038
430
.077
530
.128
40
.0045
140
0.9986
24O
.012
340
.041
440
.082
540
.134
50
.0012
ISO
0.9994
250
.015
350
.045
450
.086
55o
.140
60
.9990
160
I.OO02
260
.018
360
.048
460
.091
560
.146
70
• 9977
170
I. 0010
270
.021
370
.052
470
.096
57o
.152
80
.9970
180
I.OOI9
280
.023
380
.056
480
.101
580
.158
90
.9967
190
1.0029
290
.026
390
.060
490
.106
590
.165
IOO
0.9967
200
1.0039
3oo
.029
400
.064
500
.112
600
1.172
no
0.9970
210
1.0050
3io
.032
410
.068
5io
.117
Compressibility of Water. Water is very slightly compressible.
Its compressibility is from 0.000040 to 0.000051 for one atmosphere,
decreasing with increase of temperature. For each foot of pressure,
distilled water will be diminished in volume 0.0000015 to 0.0000013.
Water is so incompressible that even at a depth of a mile, a cubic foot
of water will weigh only about half a pound more than at the surface.
BOILER INCRUSTATION AND CORROSION
Water, from natural sources, as a rule contains more or less carbon
dioxide, which holds in solution carbonates of lime and magnesia. On
boiling the water the carbon dioxide is driven out, and the lime and
magnesium in solution are thrown down in the form of a white or
grayish mud, that may be easily removed from the boiler by thorough
washing. The presence of other impurities, such as organic matter or
sulphate of lime, is likely to make the deposit hard and adhering.
Sulphate of lime is more soluble in cold than in hot water, and is
entirely thrown down at a temperature of 280° Fahrenheit. It forms a
hard and adhering s.cale and has a bad effect upon scales and deposits,
composed chiefly of carbonates. The bad effect of deposits from water
containing calcium sulphate is much ameliorated by introducing car-
bonate of soda or soda-ash into the boiler with the feed-water. The
result is to give a deposit of calcium carbonate in the form of a fine
white powder, which must be washed or swept out, and sodium sulphate
in solution, which must be blown out from time to time.
A deposition may arise from the settling of clay and other matter
held in suspension in the water. In water otherwise free from impurities
this matter commonly deposits in the form of a soft mud that may be
easily removed from the boiler. In conjunction, however, with other
impurities, as, for example, sulphate of lime, it may form an adhesive
276
Boiler Incrustation and Corrosion
scale, in which case it is usually best to free the feed-water from sus-
pended matter by nitration.
In some cases chemical treatment, either internally or externally,
should be resorted to. This is especially the case with feed-waters
containing much free acid, in which case the free acid should be neu-
tralized by chemical treatment, preferably before entering the boiler.
If more than 100 parts per 100 ooo of total solid residue be present in
the water, it will ordinarily cause trouble from scale, and should be con-
demned for use in the boiler unless a better supply be unobtainable.
Scale reduces the efficiency of the heating surface by detracting from
the conducting quality of the metal and is apt to cause overheating or
burning of the metal, or even bulging of the plates that are subjected to
the intense heat of the furnace. Grease, owing to its adhesive nature,
may, by collecting impurities contained in the water, become sufficiently
heavy to sink. In this condition it is apt to attach itself to a plate or
pipe near the furnace, and may, owing to its nonconducting qualities,
cause serious overheating, resulting in burning, bulging, or even blowing
out.
If water contains more than 5 parts per 100 ooo of free sulphuric or
nitric acid, serious corrosion will ensue, not only in boiler plates, but
also in tubes, pipes, cylinders and other parts with which the steam
comes in contact.
Animal and vegetable oils and greases decompose into fatty acids
when subjected to the temperature of high-pressure steam. Because
of this their presence in a high-pressure steam engine or boiler will cause
serious corrosion.
Tabular View
Troublesome substance
Trouble
Remedy or palliation
Sediment, mud, clay, etc.
Incrustation.
Filtration; bio wing off.
Readily soluble salts.
Incrustation.
Blowing off.
Bicarbonates of lime,)
Incrustation.
( Heating feed. Addition of
caustic soda, lime or mag-
magnesia, iron. J
( nesia, etc.
Sulphate of lime.
Incrustation.
( Addition of carbonate of
\ soda, barium chloride, etc.
Chloride and sulphate of )
Corrosion.
{Addition of carbonate of
j • 4.
magnesium. )
soda, etc.
Carbonate of soda in )
large amounts. )
Priming.
{Addition of barium chloride,
etc.
Acid (in mine waters).
Corrosion.
Alkali.
Dissolved carbonic acid )
j i
Corrosion.
! Heating feed. Addition of
caustic soda, slaked lime,
and oxygen.
etc.
Grease (from condensed )
Corrosion.
( Slaked lime and filtering.
I Carbonate of soda.
steam) . )
( Substitute mineral oil.
Organic matter (sewage).
Corrosion.
( Precipitate with alum or
\ ferric chloride and filter.
Flow of Water in Pipes 277
Experiments have shown that pure water, into which air has been
forced, on heating causes corrosion.
Highly heated surfaces in contact with water containing common salt
corrode and pit rapidly. The sides of the furnace, the tube plates and
the hottest tubes suffer most.
It is clear, then, that feed-water, free from solids, combined or in sus-
pension, organic matter, acids of all kinds, and air, would be best for
the life of boilers.
In cases where water containing large amounts of total solid residue
is necessarily used, a heavy petroleum oil, free from tar or wax, which
is not acted upon by acids or alkalies, not having sufficient wax in it to
cause saponification, and which has a vaporizing-point at nearly 600° F.,
will give the best results in preventing boiler-scale. Its action is to
form a thin, greasy film over the boiler linings, protecting them largely
from the action of acids in the water and greasing the sediment which is
formed, thus preventing the formation of scale and keeping the solid
residue from the evaporation of the water in such a plastic suspended
condition that it can be easily ejected from the boiler by the process
of "blowing off." If the water is not blown off sufficiently often, this
sediment forms into a "putty" that will necessitate cleaning the boilers.
Practical experience is decidedly in favor of water purification, both
from the standpoint of preserving the life of the boiler and for the best
efficiency in operation. Air in solution, if allowed to enter the boiler,
will accelerate corrosion more than any other cause, hence water heaters
should be used with open feed and careful regulation of the temperature,
which should always be about 190° F.
FLOW OF WATER IN PIPES
The quantity of water discharged through a pipe depends on the
head. If the discharge occurs freely into the air, this head is the differ-
ence in level between the surface of the water in the reservoir and the
center of the discharge end of the pipe; if the lower end of the pipe is
submerged, the head is the difference in elevation between the two
water levels. The discharge for a given diameter depends also upon
the length of the pipe, upon the character of its interior surface as to
smoothness and upon the number and sharpness of its bends.
The head, instead of being an actual distance between levels, may be
caused by pressure, as by pumping, in which case the head is calculated
as a vertical distance corresponding to the pressure, i pound per square
inch being equal to 2.309 feet head, or i foot head being equal to a
pressure of 0.433 pound per square inch.
The total head operating to cause flow is divided into three parts:
(i) The velocity head, which is the height through which a body must
fall in a vacuum to acquire the velocity with which the water flows in
the pipe. This is equal to v* -4- 2 g, in which v is the velocity in feet
per second, and 2 g = 64.32; (2) The entry head, which is required to
overcome the resistance to entrance to the pipe. With sharp-edged
278 Flow of Water in Pipes
entrance the entry head equals about one-half of the velocity head;
with smooth, rounded entrance the entry head is inappreciable; (3) The
friction head, due to the frictional resistance to flow in the pipe.
In ordinary cases of pipes of considerable length the sum of the entry
and velocity heads scarcely.. exceeds one foot; in the case of long pipes
with low heads it is so small that it may be neglected.
When the flow becomes steady, the pipe is entirely filled throughout
its length, and hence the mean velocity at any section is the same as
that at the end, when the size is uniform. This velocity is found to
decrease as the length of the pipe increases, other things being equal,
and becomes very small for great lengths, which shows that nearly all
the head has been lost in overcoming the resistances. The length of
the pipe is measured along its axis, following all the curves, if there be
any. The velocity considered is the mean velocity, which is equal to
the discharge divided by the area of the cross section of the pipe. The
actual velocities in the cross section are greater than this mean velocity
near the center and less than it near the interior surface of the pipe.
The object of the discussion of flow in pipes is to enable the discharge
which will occur under given conditions to be determined, or to ascertain
the proper size which a pipe should have in order to deliver a given dis-
charge. The subject cannot, however, be developed with the definite-
ness which characterizes the flow from orifices and weirs, partly because
the condition of the interior surface of the pipe greatly modifies the dis-
charge, partly because of the lack of experimental data, and partly on
account of defective theoretical knowledge regarding the laws of flow.
In orifices and weirs errors of two or three per cent may be regarded as
large with careful work; in pipes such errors are common, and are gen-
erally exceeded in most practical investigations.
It fortunately happens, however, that in most cases of the design of
systems of pipes errors of five and ten per cent are not important, al-
though they are of course to be avoided if possible, or, if not avoided,
they should occur on the side of safety.
Quantity of Water Discharged
The quantity of water which flows through a pipe is the product of
the area of its cross section and the mean velocity of flow. That is,
Q = av,
in which Q is the quantity discharged in cubic feet per second, a is the
area in square feet and v is the velocity in feet per second.
For U. S. gallons per second multiply by 7 . 4805
For U. S. gallons per minute multiply by 448. 83
For U. S. gallons per hour multiply by 26929. 9
For U. S. gallons per 24 hours multiply by 646317.
The diagram, page 279, gives the discharge in gallons per minute,
when the velocity in the pipe line is known.
Quantity of Water Discharged
279
r— 150000
—looooo Chart for Flow of Water in Wrought Pipe
^ 90000
If any two of the three factors represented by the
scales are known, the third may be found by passing a
— eoooo straight line through these quantities on their respective
^-50000 scales. This line will intersect the third scale at the
0,5—1
L_ 4oooo number representing the desired factor.
Example. For 4000 gallons per minute with 12 inch
0.6—
;— 30000 PiPe» velocity = 11.4 feet per second.
0.7—
E 25000
0.8—
- — 20000
0.9—
•
1
15000
r72
-
10000
-60
1.5-
9000
-48
8000
-42
~
7000
—36
2
6000
0
; 5000
-30 0
O
2.J
k^° I
-24
-
3~
sooo^i
-20 g a!
E >\
—18 I {[]
3.5—
r- 2500 w ^->.
-16 Z JJJ
-
2000 -5 ^"^V^
-14 Z Z
-
E § ^
<*nf i
B'*~
— 1500 <
a
-1<>S5.
- •
I
6
1000
-8 S ^\
7
900
Q. ^sv.
^•^
800
R ^^^
8
700
^Vx_^
g ~
600
— 5 \
10_I
BOO
^^v^
— 4
_I
2 400
-i
r — soo
— 3
16-r
E— 260
-2-2-
"^
^ 200
-2
20^
~— 150
*J
100
: — 90
70
60
' 50
280
Flow of Water in Pipes
Mean Velocity of Flow
The velocity of flow, depending as it does to such a great extent upon
the condition of the interior surface of the pipe, is difficult to compute.
Below are given the formulae most generally accepted. In the solution
of any problem a comparison of the results obtained by the use of these
formulae is advisable. There are so many conditions affecting the flow
of water that all hydraulic formulae give only approximations to accu-
rate results.
Approximate Formula (Trautwine). To find the velocity of water
discharged from a pipe line, knowing the head, length and inside diameter,
use the following formula:
in which v = approximate mean velocity in feet per second;
m = coefficient from table below;
D = diameter of pipe in feet;
h = total head in feet;
L = total length of line in feet.
Values of Coefficient "m"
Diameter of pipe
Diameter of pipe
Feet
Inches
m
Feet
Inches
m
O.I
1.2
23
1-5
18
53
0.2
2.4
30
2.0
24
57
0.3
3-6
34
2.5
30
60
0.4
4-8
37
3-0
36
62
0.5
6.0
39
3-5
42
64
0.6
7.2
42
4.0
48
66
0.7
8.4
44
S.o
60
68
0.8
9-6
46
6.0
72
70
0.9
10.8
47
7.0
84
72
I.O
12.0
48
10. 0
120
77
The above coefficients are averages deduced from a large number of
experiments. In most cases of pipes carefully laid and in fair condition,
they should give results within 5 to 10 per cent of the truth.
Example: Given the head, h = 50 feet, the length, L = 5280 feet,
and the diameter, D = 2 feet; to find the velocity and quantity of
discharge.
The value of the coefficient m from the table when D = 2 feet is
Kutter's Formula 281
Substituting these values in the formula, we get:
i -
— — = 57 X 0.136 = 7-752 feet per sec.
To find the discharge in cubic feet per second, multiply this velocity
by the area of cross section of the pipe in square feet.
Thus, 3-1416 X (i)2 X 7-752 = 24.35 cubic feet per second.
Since there are 7.48 gallons in a cubic foot, the discharge in gallons
per second = 24.35 X 7.48 = 182.1.
The above formula is only an approximation, since the flow is modified
by bends, joints, incrustations, etc. Wrought pipes are smoother than
cast-iron ones, thereby presenting less friction and less encouragement
for deposits; and, being in longer lengths, the number of joints is re-
duced, thus lessening the undesirable effects of eddy currents.
Kutter's Formula. This formula, although originally designed for
open channels, can be used in the case of long pipes with low heads. It
is the joint production of two eminent Swiss engineers, E. Ganguillet
and W. R. Kutter, and is, properly speaking, a formula for finding the
coemcient C in the well-known Chezy formula:
in which
v = mean velocity in feet per second;
r = mean hydraulic radius in feet;
s = slope = head -r- length, measured in a straight line
from end to end.
The mean hydraulic radius is the area of wet cross-section divided by
the wet perimeter, which for pipes running full, or exactly half full, is
equal to one-quarter of the diameter.
According to Kutter the value of this coefficient C is
0.00281 1.811
41.6 + - + - •
^ s n
in which s is the slope, r is the mean hydraulic radius in feet and n is
the " coefficient of roughness. " The value of n varies from .010 for very
smooth pipes to .015 for pipes in a very poor condition. For ordinary
wrought pipe .012 can be used. For clean steel riveted pipe .015 can be
used.
The following table gives values of the coefficient C as obtained by
Kutter's formula for different slopes, hydraulic radii and degrees of
roughness.
282 Darcy's Formula
Table of Coefficient " C "
Coeffi-
cient
" n "
Hydraulic radius in r feet
.1
• 15
.2
• 3
.4
.6
.8
I.O
I 5
2 O
3 o
Slope s =.0004
.009
.010
.on
.012
104
89
78
69
116
IOI
90
80
126
1 10
97
87
138
120
107
96
148
129
115
104
157
140
126
H3
166
148
133
121
172
154
138
125
183
164
148
135
190
170
154
141
199
179
162
149
.013
.015
.017
62
50
43
71
59
So
78
65
54
87
73
62
94
79
68
103
87
75
1 10
93
81
"5
98
85
124
106
93
130
112
98
138
119
105
Slope 5 =.0010
.009
.010
.Oil
.012
no
94
83
73
121
105
92
82
129
113
99
89
141
124
109
98
ISO
131
117
105
161
142
127
H5
I69
ISO
134
122
175
155
139
127
184
165
149
136
191
171
155
142
199
179
163
149
.013
.015
.017
65
54
45
74
61
51
81
66
57
89
74
63
96
80
69
104
88
76
III
94
82
116
99
86
124
108
93
130
112
98
138
119
105
Slope 5 =.0100
.009
.010
.Oil
.012
no
95
83
74
122
105
93
83
130
114
100
90
143
125
III
100
151
133
119
107
162
143
129
116
170
151
135
123
175
156
141
128
185
165
149'
136
191
171
155
142
199
179
162
149
.013
.015
.017
66
2
75
62
52
81
67
57
90
76
64
98
82
70
106
90
77
112
95
82
H7
99
87
125
107
94
130
112
99
138
H9
105
For slopes steeper than .01 per unit of length, = 52.8 feet per mile,
C remains practically the same as at that slope. But the velocity (being
C X Vrs) of course continues to increase as the slope becomes steeper.
Darcy's Formula. The simplest form of Darcy's formula is
C& = Ds,
in which v is the velocity in feet per second, D is the diameter of the pipe
in feet, s is the slope and C is a coefficient, varying with the diameter
and roughness of the pipe. For cast-iron pipe and wrought pipes of the
same roughness, the values of C are given below. For rough pipe
Darcy doubled the coefficient.
Williams and Hazen's Formula
283
Values of "C" in Darcy's Formula
Diameter,
inches
Rough pipe
Smooth pipe
3
4
6
8
0.00080
0.00076
0.00072
0.00068
0.00040
0.00038
0.00036
0.00034
10
12
14
16
0.00066
0.00066
0.00065
0.00064
0.00033
0.00033
0.000325
0.00032
24
30
36
48
0.00064
0.00063
0.00062
0.00062
0.00032
0.000315
0.00031
0.00031
Williams and Hazen's Exponential Formula. From Chezy's
formula, v = C VW, it would appear that the velocity varies as the
square root of the head; this is not true, however, for C is not a constant,
but a variable depending upon the roughness of the pipe and upon the
hydraulic radius and the slope. Hazen and Williams, as a result of a
study of the best records of experiments and plotting them on logarithmic
ruled paper, found an exponential formula v = O0-63^-54, in which the
coefficient C is practically independent of the diameter and the slope,
and varies only with the condition of the surface. In order to equalize
the numerical value of C to that of the C in the Chezy formula, at a
slope of o.ooi, they added the factor o.ooi-°-04 to the formula, so that
the working formula of Hazen and Williams is
The value of C varies to a great extent, depending on the condition
of the interior of the pipe. A fair value for iron or steel pipe is C = 100.
Computations of the exponential formula are made by logarithms or by
the Hazen- Williams hydraulic slide rule.
Effect of Curves and Valves (American Civil Engineers' Pocket
Book). The effect of curvature is to increase the loss of head. This
increased loss is partly due to the cross currents and eddies set up in
the bend, but also to the changes of velocity along the stream lines and
increased friction along the walls of the channels, due to increased
velocities over part of the circumference. The loss of head due to a
curve may be stated in terms of the velocity head or, better, in terms of
the equivalent length of straight pipe which would give the same loss
as the curve. Experiments upon the loss of head in pipes show the
radius of the curve of minimum resistance for a right-angled bend to be
about three diameters of the pipe. For six-inch pipe the loss due to
such a curve is about the same as that in eight feet of straight pipe,
and for a thirty-inch pipe about the same as that in forty feet of straight
284 Water Hammer
pipe. For intermediate sizes the loss may be expected to fall between
these limits and to vary approximately as the diameter.
The losses due to valves in pipe lines have been investigated with
accuracy in only a few instances. From these experiments it appears
that a fully open gate valve in a pipe causes a loss of head corresponding
to about six oliameters of length of the pipe.
Hydraulic Grade-line. In a straight tube of uniform diameter
throughout, running full and discharging freely into the air, the hydrau-
lic grade-line is a straight line drawn from the discharge end to a point
immediately over the entry end of the pipe, and at a depth below the
surface equal to the entry and velocity heads (Trautwine) .
In a pipe leading from a reservoir, no part of its length should be above
the hydraulic grade-line.
Air-bound Pipes. A pipe is said to be air-bound when, in conse-
quence of air being entrapped at the high points of vertical curves in
the line, water will not flow out of the pipe, although the supply is
higher than the outlet. The remedy is to provide cocks or valves at
the high points, through which the air may be discharged. The valve
may be made automatic by means of a float.
Water Hammer. When a valve in a pipe is closed while the water
is flowing, the velocity of the water behind the valve is retarded and a
dynamic pressure is produced. When the valve is closed quickly this
dynamic pressure may be much greater than that due to the static
pressure, and it is then called "water hammer" or "water ram." This
action is dangerous and causes in many cases fracture of the pipe. It
is provided against by arrangements which prevent a rapid closing of
the valve. The formulae for the pressure produced by this shock are
ID
p= 0.027 - - po + pi, (i)
£ = 63 a - po + pi, (2)
where po = the static pressure when there is no flow, pi = the static pressure
when the flow is in progress, p = the maximum dynamic pressure due to
the water hammer in excess over the pressure po, v = the velocity in feet
per second, / = length of pipe back from the valve in feet, and / = time
of closing of valve in seconds. The pressures in the formulae are expressed
in pounds per square inch. Formula (i) is to be used when / is greater
than 0.000428 / and formula (2) when / is equal to or less than this.
From the first of these formulae the value of / when p = o is found
to be fc
/ = O.O27 -
Po- pi
which is the time of valve closing in order that there may be no water
hammer. To prevent the effects of water hammer, it is customary to
arrange valves so that they cannot be closed very quickly, and the last
formula furnishes the means of estimating the time required in order
that no excess of dynamic pressure over the static pressure po may occur.
Flow of Water in House-Service Pipes 285
Flow of Water in House-service Pipes
(Thomson Meter Company.)
Pressure
Discharge in cubic feet per minute
Condition
pounds
Nominal internal diameter of pipe (inches)
of discharge
per
square
inch
V'2
%
%
I
i%
2
3
4
6
30
1. 10
1.92
3-01
6.13
16.58
33.34
88.16
173.85
444.63
Through 35
40
1.27
2.22
3.48
7.08
19.14
38.50
101.80
200.75
513.42
feet of
So
1.42
2.48
3.89
7.92
21.40
43-04
113.82
224.44
574-02
service
60
1.56
2.71
4.26
8.67
23-44
47-15
124.68
245.87
628.81
pipe, no
back
75
1.74
3-03
4-77
9-70
26.21
52.71
139.39
274.89
703.03
pressure.
IOO
130
2.01
2.29
3-50
3-99
5-50
6.28
11.20
12.77
30.27
34-51
60.87
69.40
160.96
183.52
317.41
361.91
811.79
925.58
30
0.66
1.16
1.84
3.78
10.40
21.30
58.19
118.13
317.23
Through
40
o.77
1.34
2.12
4.36
12.01
24.59
67.19
136.41
366.30
100 feet
50
0.86
1.50
2.37
4.88
13-43
27.50
75-13
152.51
409.54
of service
60
o.94
1.65
2.60
5-34
14.71
30.12
82.30
167.06
448.63
pipe, no
i-i
back
75
1.05
1.84
2.91
5-97
16.45
33-68
92.01
186.78
501.58
pressure.
IOO
1.22
2.13
3.36
6.90
18.99
38.89
106.24
215.68
579.18
130
1.39
2.42
3.83
7.86
21.66
44-34
121.14
245.91
660.36
Through
100 feet
of service
pipe and
30
40
50
60
0.55
0.66
o.75
0.83
0.96
I. IS
1.31
1.45
1.52
1.81
2.06
2.29
3- ii
3-72
4-24
4-70
8.57
10.24
11.67
12.94
17-55
20.95
23-87
26.48
47-90
57-20
65.18
72.28
97.17
116.01
132.20
146.61
260.56
3H.09
354-49
393.13
15 feet
vertical
75
IOO
o.94
1. 10
1.64
1.92
2.59
3-02
5-32
6.21
14.64
17.10
29.96
35-00
81.79
95-55
165.90
193.82
444.85
519.72
rise.
130
1.26
2.20
3.48
7-14
19.66
40.23
109.82
222.75
597-31
Through
ico feet
of service
pipe and
30
40
50
60
o.44
0.55
0.65
o.73
o.77
0.97
1. 14
1.28
1.22
1.53
1-79
2. 02
2.50
3.15
3.69
4-15
6.80
8.68
10. 16
H.45
14.11
17-79
20.82
23-47
38.63
48.68
56.98
64.22
78.54
98.98
115.87
130.59
2H.54
266.59
312.08
351.73
30 feet
vertical
rise.
75
IOO
130
0.84
I.OO
1. 15
1.47
1.74
2. 02
2.32
2.75
3.19
4-77
5.65
6.55
I3-I5
15.58
18.07
26.95
31-93
37-02
73.76
87.38
101.33
149-99
177.67
206.04
403.98
478.55
554.96
286 Loss of Head in Pipe by Friction
Loss of Head in Pipe by Friction
(Pelton Water Wheel Company.)
The following table shows the loss of head by friction in each 100 feet
in length of different diameters of pipe, when discharging the tabulated
quantities of water per minute:
v — velocity in feet per second;
H = loss of head by friction in feet;
Q = discharge in cubic feet per minute.
V
Inside diameter of pipe in inches
6
7
8
9
IO
II
H
Q
H
Q
H
Q
H
Q
H
Q
H
Q
2.0
2.2
2.4
2.6
• 39
.46
.54
.63
23.5
25.9
28.2
30.6
.33
.40
.46
.54
32.0
35-3
38.5
41-7
• 30
.35
• 41
• 47
41.9
46.1
50.2
54.4
.26
• 31
.36
.42
53.o
58.3
63.6
68.9
\2\
.32
.37
65-4
72.
78.5
85.1
.21
.25
.29
.34
79.
87.
95-
103.
2.8
3.o
3.2
3.4
.72
.81
.91
1.02
32.9
35-3
37-7
40.0
.61
.69
• 78
.87
44-9
48.1
5L3
54-5
• 54
.61
.68
.76
58.6
62.8
67.0
71.2
.48
• 54
.60
.68
74-2
79-5
84.8
90.1
.43
.48
• 54
.61
91.6
98.2
105.
in.
• 39
..44
.49
.55
in.
119.
127.
134.
3.6
3.8
4-0
4.2
1. 13
1.25
1.37
1.49
42.4
44-7
47-1
49-5
• 96
.07
.17
.28
57-7
60.9
64.1
67.3
.84
• 93
1. 02
1. 12
75.4
79-6
83-7
87.9
• 75
• 83
.91
.99
95-4
101.
106.
in.
.67
• 74
.82
.89
118.
124.
131-
137-
.61
.68
• 74
.81
142.
150.
158.
166.
4.4
4-6
4-8
5.o
1.62
1.76
1.90
2.05
51.8
54.1
56.5
58.9
.39
• 51
.63
1.76
70-5
73-7
76.9
80.2
1.22
• 32
• 43
.54
92.1
96.3
oo.o
05.
.08
• 17
• 27
• 37
116.
122.
127.
132.
• 97
.05
.14
.23
144.
150.
157.
163.
.88
.96
.04
.12
174.
182.
190.
198.
5.2
5-4
5.6
5.8
2.21
2.37
2.53
2.70
61.2
63.6
65.9
68.3
1.89
2.03
2.17
2.31
83.3
86.6
89.8
93-0
.65
• 77
-89
.01
09.
13.
17.
21.
• 47
!68
i. 80
138.
143.
I48.
154-
• 32
.41
• 51
1.61
170.
177.
183.
190.
.20
.28
.37
.46
206.
214.
222.
229.
6.0
2.87
70.7
82.4
2.46
3.26
96.2
[12.0
.15
.85
125.
146.
1.92
2.52
159-
185.
1.71
2.28
196.
229.
.56
.07
237-
277.
V
12
13
14
15
16
18
H
Q
H
Q
H
Q
H
Q
H
Q
H
Q
2.0
2.2
2.4
2 6
.19?
.273
.315
94-
103-
113-
122.
.183
.216
.252
.290
no.
121.
133-
144.
.169
.200
.234
.270
128.
141.
154.
167.
.158
.187
.218
.252
147.
162.
176.
191.
.147
.175
.205
.236
167.
184.
201.
218.
.132
.156
.182
.210
212.
233.
254-
275
2.8
3.o
3.2
3.4
.36c
.407
• 45^
.Sic
132.
141.
I5L
160.
.332
.375
.422
.471
156.
166.
177-
188.
.308
• 349
.392
• 438
179-
192.
205.
218.
.288
.325
.366
.408
206.
221.
235-
250.
.270
.306
.343
-383
234-
251.
268.
284.
.240
.271
.305
.339
297.
318.
339-
36o.
Loss of Head in Pipe by Friction 287
Loss of Head in Pipe by Friction (Continued)
Inside diameter of pipe in inches
V
12
13
14
15
16
18
H
Q
H
Q
H
Q
H
Q
H
Q
H
Q
3.6
.566
169.
.522
199.
.485
231.
.452
265.
.425
301.
.377
382.
3-8
.624
179.
.576
210.
• 535
243.
.499
280.
.468
318.
.416
403.
4.0
.685
188.
.632
221.
.587
256.
.548
294.
• 513
335.
.456
424.
4-2
.749
198.
.691
232.
.641
269.
.598
309.
.561
352.
• 499
445.
4-4
.815
207.
• 751
243-
.698
282.
.651
324.
.611
368.
.542
466.
4-6
.883
217.
.815
254-
• 757
295.
.707
339-
.662
385.
.588
488.
4-8
-954
226.
.881
265.
.818
308.
.763
353-
• 715
402.
.636
509.
5-0
1.028
235-
.949
276.
.881
321.
.822
368.
.770
419.
.685
530.
5-2
1.104
245.
.020
287.
.947
333.
.883
383.
.828
435-
• 736
551.
5-4
1.183
254-
.092
298.
1.014
346.
-947
397-
.888
452.
.788
572.
5-6
1.26
264.
.167
309.
1.083
359-
I. Oil
412.
• 949
469-
.843
594-
5-8
1.34
273-
.245
321.
1. 155
372.
1.078
427.
i. on
486.
.899
615.
6.0
1-43
283.
• 325
332.
1.229
385.
1.148
442.
1.076
502.
• 957
636.
7.0
1.91
330.
• 75
307-
1.630
449-
1.520
515.
1.430
586.
1.270
742-
V
20
22
24
26
28
30
H
Q
H
Q
H
Q
H
Q
H
Q
H
Q
2.0
.119
262.
.108
316.
.098
377-
.091
442.
.084
513.
.079
589.
2.2
.140
288.
.127
348.
.116
414.
.108
486.
.099
564.
.093
648.
2-4
.164
314.
.149
380.
.136
452.
.126
531.
.116
616.
.109
707.
2.6
.189
340.
.171
412.
.157
490.
.145
575-
.134
667.
.126
766.
2.8
.216
366.
.195
443.
.180
528.
.165
619.
.153
718.
.144
824.
3.o
• 245
393-
.222
475.
.204
565.
.188
663.
.174
770.
.163
883.
3-2
.275
419-
.249
507.
.229
603.
.211
708.
.195
821.
.182
942.
3.4
.306
445-
.278
538.
.255
641.
.235
752.
.218
872.
.204
1001.
3-6
.339
471-
.308
570.
.283
678.
.261
796.
.242
923.
.226
1060.
3-8
.374
497-
.340
601.
.312
716.
.288
840.
.267
973.
.249
1119.
4-0
.410
523.
.373
633.
.342
754-
.315
885.
.293
1026.
.273
1178.
4.2
.449
550.
.408
665.
.374
79L
.345
929.
.320
1077.
.299
1237.
4-4
.488
576.
.444
697.
.407
829.
.375
973.
• 348
1129.
• 325
1296.
4.6
.529
602.
.482
728.
• 441
867.
.407
1017.
• 378
1180.
.353
1355.
4-8
.572
628.
.521
760.
.476
90S.
.440
1062.
.409
1231.
.381
1414.
5.0
.617
654.
.561
792.
513
942.
.474
1106.
• 440
1283.
.411
1472.
5-2
.662
680.
.602
823.
• 552
980.
.510
1150.
.473
1334 -
.441
1531.
5-4
.710
707.
645
855.
.591
1018.
.546
H94.
.507'
1385.
.473
1590.
5.6
• 758
733.
.690
887.
.632
1055-
.583
1239.
• 542
1437-
.506
1649.
5.8
.809
759.
.735
918.
.674
1093-
.622
1283.
.578
1488.
540
1708.
6.0
.861
785.
.782
950.
.717
H3I.
.662
1327.
.615
1539-
.574
1767.
7-0
1. 143
916.
1.040
1109.
• 953
1319.
.879
1548.
.817
1796.
.762
2061.
288
Loss of Head in Pipe by Friction
Loss of Head in Pipe by Friction (Concluded)
V
2.0
2.2
2.4
2.6
Inside diameter of pipe in inches
33
36
39
42
45
48
H
.073
.085
.100
.115
Q
H
Q
H
.061
.072
.084
.097
Q
H
Q
H
Q
1325.
1456.
1590.
1721.
H
Q
712.
785.
855.
927.
.066
.078
.091
.104
848.
933-
1018.
IIOO.
995-
1094.
1194-
1294.
.057
.067
.079
.090
1155.
1270.
1385.
1500.
.053
.063
• 073
.084
.050
.059
.069
.079
1508.
1658.
1809.
1960.
2.8
3.0
3.2
3.4
.131
.148
.167
.186
IOOO.
1070.
1140.
1210.
.119
.135
.152
.169
1188.
1273.
1367.
1442.
.in
.125
.141
.157
1394-
1492.
1591.
1690.
.103
.117
.131
.146
1617.
1730.
1845.
1961.
.096
.109
.122
.136
1855.
1987.
2I2O.
2250.
.090
.102
.115
.128
21 10.
2260.
2410.
2560.
3.6
3-8
4.o
4.2
.206
.226
.248
.270
1282.
1355-
1425.
1495-
.188
.207
.228
.249
1527.
1612.
1697.
1782.
.174
.191
.210
.229
1790.
1891.
1990.
2091.
.162
.178
.195
.213
2079.
2190.
2310.
2422.
.151
.166
.182
.198
2382.
2515.
2650.
2780.
.142
.156
.171
.186
2715.
2865.
3016.
3165.
4-4
4-6
4.8
S.o
.295
.321
.346
.374
1568.
1640.
I7IO.
1780.
.271
.294
.318
.342
1866.
1951.
2036.
2121.
.250
.271
.293
.316
2190.
2290.
2389.
2490.
.232
.252
.270
• 294
2540.
2658.
2770.
2885.
.216
.235
.254
.273
2910.
3045.
3180.
3310.
.203
.220
.238
.256
3318.
3470.
3619.
3770.
5.2
5-4
5.6
5.8
.403
• 430
• 453
• 495
1852.
1922.
1995-
2065.
.368
.394
.421
.450
2206.
2291.
2376.
2460.
• 342
.364
.393
.419
2590.
2689.
2790.
2886.
.317
.338
.374
.389
3000.
3II5-
3230.
3348.
.296
.315
.340
.363
3442.
3578.
37io.
3840.
.278
.295
.319
.340
3920.
4071.
4222.
4373.
6.0
7.o
.520
.693
2I4O.
2495-
• 479
.636
2545.
2968.
.441
.586
2986.
3484.
.408
.545
346i.
4030.
.382
.509
3970.
4638.
.358
.476
4524.
5277.
The above table is based on Cox's reconstruction of Weisbach's
formula, using the denominator 1000 instead of 1200, to be on the safe
side, allowing 20% for the loss of head due to the laps and rivet -heads
in the pipe. Cox's formula, using the denominator 1 200, is given below.
Example. Given 200 feet head and 600 feet of n-inch pipe, carry-
ing 119 cubic feet of water per minute. To find the effective head: In
right-hand column, under n-inch pipe, find 119 cubic feet; opposite this
will be found the loss by friction in 100 feet of length for this amount
of water, which is 0.44. Multiply this by the number of hundred feet
of pipe, which is 6, and we have 2.64 feet, which is the loss of head.
Therefore the effective head is 200— 2.64= 197.36.
Explanation. The loss of head by friction in a pipe depends not
only upon diameter and length, but upon the quantity of water passed
through it. The head or pressure is what would be indicated by a
pressure-gage attached to the pipe near the outlet. Readings of gage
should be taken while the water is flowing from the nozzle.
To reduce heads in feet to pressure in pounds multiply by 0.433. To
reduce pounds pressure to feet multiply by 2.309.
Cox's Formula 289
Cox's Formula. (Kent's Mec
Weisbach's formula for loss of heac
pipes is as follows:
Friction-head = ( o.oi;
hanical Engineers' Pocket Book.)
I caused by the friction of water in
0.01716^ / • v*
Vv / 5-367 <*'
where / = length of pipe in feet;
v = velocity of the water in feet per second;
d — diameter of pipe in inches.
William Cox (Amer. Mach., Dec
which gives almost identical results
H = friction-head in f(
. 28, 1893) gives a sim
pier formula
d)
d 1200
He gives a table by i
once obtained when v is
Hd 4 z)2 + 5 v — 2
(2)
I
neans of w'
known, anc
Values of -
1200
lich the val
vice versa.
1200
1 200
v
0.0
O.I
0.2
0.3
0.4
i
2
3
4
.00583
.02000
.04083
.06833
.00695
.02178
.04328
.07145
.00813
.02363
.04580
.07463
.00938
.02555
.04838
.07788
.01070
.02753
.05103
.08120
6
8
. 10250
. 14333
.19083
.24500
. 10628
. 14778
. 19595
. 25078
. 11013
. 15230
.20113
.25663
.11405
.15688
.20638
.26255
.11803
. 16153
.21170
.26853
9
10
ii
12
.30583
.37333
.44750
.52833
.31228
.38045
.45528
.53678
.31880
.38763
.46313
.54530
.32538
•39488
.47105
.55388
.33203
.40220
.47903
.56253
13
14
IS
16
.61583
.71000
.81083
.91833
.62495
. 71978
.82128
.92945
.63413
.72963
.83180
.94063
.64338
•73955
.84238
.95188
.65270
.74953
.85303
.96320
17
18
19
20
1.03250
I. 15333
1.28083
1.41500
1.04428
I . 16578
I • 29395
I . 42878
1.05613
I . 17830
I.307I3
1.44263
1.06805
1.19088
1.32038
1.45655
1.08003
1.20353
1.33370
1.47053
21
1.55583
1.57028
1.58480
1.59938
1.61403
290
Cox's Formula
V
0.5
0.6
0.7
0.8
0.9
I
.01208
.01353
.01505
.01663
.01828
2
.02958
.03170
.03388
.03613
.03845
3
.05375
.05653
.05938
.06230
.06528
4
.08458
.08803
.09155
.09513
.09878
5
.12208
. 12620
. 13038
. 13463
. 13895
6
. 16625
. 17103
.17588
. 18080
. 18578
7
.21708
.22253
.22805
. 22363
.23928
8
.27458
.28070
.28688
.29313
.29945
9
.33875
.34553
.35238
•35930
.36628
10
.40958
.41703
.42455
-432I3
•43978
ii
.48708
.49520
.50338
.51163
.51995
12
.57125
.58003
.58888
.5978o
.60678
13
.66208
.67153
.68105
.69063
.70028
14
.75958
.76970
•77988
.79013
.80045
IS
.86375
.87453
.88538
.89630
.90728
16
.97458
.98603
•99755
1.00913
1.02078
17
1.09208
I . 10420
1.11638
i . 12863
i . 14095
18
i . 21625
I . 22903
1.24188
i . 25480
I . 26778
19
1.34708
1.36053
1.37405
1.38763
I . 40128
20
1.48458
I . 49870
1.51288
i • 52713
I.54I45
21
i . 62875
I - 64353
i 65838
i 67330
i 68828
The use of the formula and table is illustrated as follows:
Given a pipe 5 inches diameter and 1000 feet long, with 49 feet head,
what will the discharge be?
If the velocity v is known in feet per second, the discharge is 0.32725
dzv cubic foot per minute.
-D , x 4 a2 + 5 0 - 2 Hd 49 X 5
By equation (2) we have = — = — — = 0.245;
1200 / 1000
whence, by table, v = real velocity = 8 feet per second.
The discharge in cubic feet per minute, if v is velocity in feet per
second and d diameter in inches, is 0.32725 dzv, whence, discharge =
0.32725 X 25 X 8 = 65.45 cubic feet per minute.
The velocity due to the head, if there were no friction, is 8.025 V H
= 56.175 feet per second, and the discharge at that velocity would be
0.32725 X 25 X 56.175 = 460 cubic feet per minute.
Suppose it is required to deliver this amount, 460 cubic feet, at a
velocity of 2 feet per second; what diameter of pipe of the same length
and under the same head will be required and what will be the loss of
head by friction?
d = diameter = \ — — = \ — ; — = V 703 = 26.5 inches.
vX 0.32725
2 X 0.32725
Having now the diameter, the velocity, and the discharge, the friction-
head is calculated by equation (i) and use of the table; thus,
H--
- X 0.02 =
- = 0.75 foot,
s 1200 26.5 " 26.5
thus leaving 49 — 0.75 = say 48 feet effective head applicable to power-
producing purposes.
Measurement of Flowing Water 291
MEASUREMENT OF FLOWING WATER
(From Kent's Mechanical Engineers' Pocket Book.)
Piezometer. If a vertical or oblique tube be inserted into a pipe con-
taining water under pressure, the water will rise in the former, and the
vertical height to which it rises will be the head producing the pressure
at the point where the tube is attached. Such a tube is called a piezom-
eter or pressure measure. If the water in the piezometer falls below
its proper level it shows that the pressure in the main pipe has been
reduced by an obstruction between the piezometer and the reservoir.
If the water rises above its proper level it indicates that the pressure
there has been increased by an obstruction beyond the piezometer.
If we imagine a pipe full of water to be provided with a number of
piezometers, then a line joining the tops of the columns of water in them
is the hydraulic grade-line.
Pitot Tube. The Pitot tube is used for measuring the velocity of
fluids in motion. It has been used with great success in measuring the
flow of natural gas. (S. W. Robinson, Report Ohio Geol. Survey, 1890.)
(See also Van Nostrand's Mag., Vol. XXXV.) It is simply a tube so
bent that a short leg extends into the current of fluid flowing from a
tube, with the plane of the entering orifice opposed at right angles to
the direction of the current. The pressure caused by the impact of
the current is transmitted through the tube to a pressure-gage of any
kind, such as a column of water or of mercury, or a Bourdon spring-
gage. From the pressure thus indicated and the known density and
temperature of the flowing fluid is obtained the head corresponding to
the pressure, and from this the velocity. In a modification of the Pitot
tube described by Professor Robinson, there are two tubes inserted into
the pipe conveying the gas, one of which has the plane of the orifice at
right angles to the current, to receive the static pressure plus the pressure
due to impact; the other has the plane of its orifice parallel to the current
so as to receive the static pressure only. These tubes are connected to
the legs of a U tube partly filled with mercury, which then registers the
difference in pressure in the two tubes, from which the velocity may
be calculated. Comparative tests of Pitot tubes with gas-meters, for
measurement of the flow of natural gas, have shown an agreement within
3%.
It appears from experiments made by W. M. White, described in a
paper before the Louisiana Eng'g Socy., 1901, by Williams, Hubbell and
Fenkel (Trans. A. S. C. E., 1901), and by W. B. Gregory (Trans. A. S.
M. E., 1903), that in the formula for the Pitot tube, V = c V2 gH, in
which V is the velocity of the current in feet per second, H the head in
feet of the fluid corresponding to the pressure measured by the tube,
and c an experimental coefficient, c = i when the plane at the point of
the tube is exactly at right angles with the direction of the current, and
when the static pressure is correctly measured. The total pressure
produced by a jet striking an extended plane surface at right angles to
292 Measurement of Flowing Water
it, and escaping parallel to the plate, equals twice the product of the
area of the jet into the pressure calculated from the "head due to the
yt v2
velocity," and for this case H = 2 X — , instead of — ; but as found
2g 2g
in White's experiments the maximum pressure at the point on the plate
V2
exactly opposite the jet corresponds to h = — . Experiments made
2 g
with four different shapes of nozzles placed under the center of a falling
stream of water showed that the pressure produced was capable of sus-
taining a column of water almost exactly equal to the height of the falling
water.
Tests by J. A. Knesche (Indust. Eng'g, Nov., 1909), in which a Pitot
tube was inserted in a 4-inch water pipe, gave C = about 0.77 for veloci-
ties of 2.5 to 8 feet per second, and smaller values for lower velocities.
He holds that the coefficient of a tube should be determined by experi-
ment before its readings can be considered accurate.
Maximum and Mean Velocities in Pipes. Williams, Hubbell and
Fenkel (Trans. A. S. C. E., 1901) found a ratio of 0.84 between the
mean and the maximum velocities of water flowing in closed circular
conduits, under normal conditions, at ordinary velocities; whereby
observations of velocity taken at the center under such conditions, with
a properly rated Pitot tube, may be relied on to give results within
3% of correctness.
The Venturi Meter, invented by Clemens Herschel, and described
in a pamphlet issued by the Builders' Iron Foundry of Providence, R. I.,
is named for Venturi, who first called attention, in 1796, to the relation
between the velocities and pressures of fluids when flowing through
converging and diverging tubes. It consists of two parts, — the tube,
through which the water flows, and the recorder, which registers the
quantity of water that passes through the tube. The tube takes the
shape of two truncated cones joined in their smallest diameters by a
short throat-piece. At the up-stream end and at the throat there are
pressure-chambers, at which points the pressures are taken.
The action of the tube is based on that property which causes the
small section of a gently expanding frustum of a cone to receive, with-
out material resultant loss of head, as much water at the smallest diam-
eter as is discharged at the large end, and on that further property
which causes the pressure of the water flowing through the throat to be
less, by virtue of its greater velocity, than the pressure at the up-stream
end of the tube, each pressure being at the same time a function of the
velocity at that point and of the hydrostatic pressure which would
obtain were the water motionless within the pipe.
The recorder is connected with the tube by pressure-pipes which lead
to it from the chambers surrounding the up-stream end and the throat
of the tube. It may be placed in any convenient position within
1000 feet of the meter. It is operated by a weight and clockwork. The
difference of pressure or head at the entrance and at the throat of the
Measurement by Venturi Tubes 293
meter is balanced in the recorder by the difference of level in two columns
of mercury in cylindrical receivers, one within the other. The inner
carries a float, the position of which is indicative of the quantity of water
flowing through the tube. By its rise and fall the float varies the time
of contact between an integrating drum and the counters by which the
successive readings are registered.
There is no limit to the sizes of the meters nor the quantity of water
that may be measured. Meters with 24-inch, 36-inch, 48-inch, and
even 2o-foot tubes can be readily made.
Measurement by Venturi Tubes (Trans. A. S. C. E., Nov., 1887,
and Jan., 1888). Mr. Herschel recommends the use of a Venturi tube,
inserted in the force main of the pumping engine, for determining the
quantity of water discharged. Such a tube applied to a 24-inch main
has a total length of about 20 feet. At a distance of 4 feet from the
end nearest the engine the inside diameter of the tube is contracted to
a throat having a diameter of about 8 inches. A pressure gage is attached
to each of two chambers, the one surrounding and communicating with
the entrance or main pipe, the other with the throat. According to
experiments made upon two tubes of this kind, one 4 inches in diameter
at the throat and 12 inches at the entrance, and the other about 36
inches in diameter at the throat and 9 feet at its entrance, the quantity
of water which passes through the tube is very nearly the theoretical
discharge through an opening having an area equal to that of the throat,
and a velocity which is that due to the difference in head shown by the
two gages. Mr. Herschel states that the coefficient for these two widely
varying sizes of tubes, and for a wide range of velocity through the pipe,
was found to be within 2%, either way, of 98%. In other words, the
quantity of water flowing through the tube per second is expressed within
two per cent by the formula W = 0.98 A V 2 gh, in which A is the
area of the throat of the tube, h the head, in feet, corresponding to the
difference in the pressure of the water entering the tube and that found
at the throat, and g =32.16.
Measurement of Discharge of Pumping Engines by Means of
Nozzles (Trans. A. S. M. E., Vol. XII, 575). The measurement of
water by computation from its discharge through orifices, or through
the nozzles of fire hose, furnishes a means of determining the quantity
of water delivered by a pumping engine, which can be applied without
much difficulty. John R. Freeman (Trans. A. S. C. E., Nov., 1889)
describes a series of experiments covering a wide range of pressures and
sizes, and the results show that the coefficient of discharge for a smooth
nozzle of ordinary good form was within one-half of i%, either way,
of .977; the diameter of the nozzle being accurately calipered, and the
pressures being determined by means of an accurate gage attached to a
suitable piezometer at the base of the play-pipe.
In order to use this method for determining the quantity of water
discharged by a pumping engine, it would be necessary to provide a
pressure-box to which the water would be conducted, and attach to the
294 The Miner's Inch
box as many nozzles as would be required to carry off the water. Accord-
ing to Mr. Freeman's estimate, four i^-inch nozzles, thus connected,
with a pressure of 80 pounds per square inch, would discharge the full
capacity of a 2V£-million engine. He also suggests the use of a port-
able apparatus with a single opening for discharge, consisting essentially
of a Siamese nozzle, so-called, the water being carried to it by three or
more lines of fire hose.
To insure reliability for these measurements, it is necessary that the
shut-off valve in the force-main, or the several shut-off valves, should be
tight, so that all the water discharged by the engine may pass through
the nozzles.
THE MINER'S INCH
(From Merriman's Treatise on Hydraulics.)
The miner's inch may be roughly defined to be the quantity of water
which will flow from a vertical standard orifice one inch square, when
the head on the center of the orifice is 6l/2 inches. The coefficient of
discharge is about 0.623, and accordingly the actual discharge from the
orifice in cubic feet per second is
.
q = - X 0.623 X 8.02 i/ — = 0.0255,
and the discharge in one minute is 60X0.0255=1.53 cubic feet.
The mean value of one miner's inch is therefore about 1.5 cubic feet per
minute.
The actual value of the miner's inch, however, differs considerably
in different localities. Bowie states that in different counties of Cali-
fornia it ranges from 1.20 to 1.76 cubic feet per minute The reason
for these variations is due to the fact that when water is bought for
mining or irrigating purposes, a much larger quantity than one miner's
inch is required, and hence larger orifices than one square inch are
needed. Thus at Smartsville, a vertical orifice or module, 4 inches deep
and 250 inches long, with a head of 7 inches above the top edge, is said to
furnish 1000 miner's inches. Again at Columbia Hill, a module 12 inches
deep and 12% inches wide, with a head of 6 inches above the upper edge,
is said to furnish 200 miner's inches. In Montana the customary method
of measurement is through a vertical rectangle, one inch deep, with a
head on the center of the orifice of 4 inches, and the number of miner's
niches is said to be the same as the number of linear inches in the rec-
tangle; thus under the given head an orifice one inch deep and 60 inches
long would furnish 60 miner's inches. The discharge of this is said to
be about 1.25 cubic feet per minute, or 75 cubic feet per hour.
The following are the values of the miner's inch in different parts
of the Unites States. In California and Montana it is established by
law that 40 miner's inches shall be the equivalent of one cubic foot per
second, and in Colorado 38.4 miner's inches is the equivalent. In
The Miner's Inch 295
other States and Territories there is no legal value, but by common
agreement 50 miner's inches is the equivalent of one cubic foot per
second in Arizona, Idaho, Nevada, and Utah; this makes the miner's
inch equal to 1.2 cubic feet per minute.
A module is an orifice which is used in selling water, and which under
a constant head is to furnish a given number of miner's inches, or a
given quantity per second. The size and proportions of modules vary
greatly in different localities, but in all cases the important feature to
be observed is that the head should be maintained nearly constant in
order that the consumer may receive the amount of water for which
he bargains and no more.
The simplest method of maintaining a constant head is by placing
the module in a chamber which is provided with a gate that regulates
the entrance of water from the main reservoir or canal. This gate is
raised or lowered by an inspector once or twice a day so as to keep the
surface of the water in the chamber at a given mark. This plan is a
costly one, on account of the wages of the inspector, except in works
where many modules are used and where a daily inspection is necessary
in any event, and it is not well adapted to cases where there are frequent
and considerable fluctuations in the surface of the water in the feeding
canal.
Numerous methods have been devised to secure a constant head by
automatic appliances; for instance, the gate which admits water into
the chamber may be made to rise and fall by means of a float upon the
surface; the module itself may be made to decrease in size when the
water rises, and to increase when it falls, by a gate or by a tapering plug
which moves in and out and whose motion is controlled by a float.
These self-acting contrivances, however, are liable to get out of order,
and require to be inspected more or less frequently. Another method
is to have the water flow over the crest of a weir as soon as it reaches
a certain height.
The use of the miner's inch, or of a module, as a standard for selling
water, is awkward and confusing, and for the sake of uniformity it
is greatly to be desired that water should always be bought and sold
by the cubic foot per second. Only in this way can comparison readily
be made, and the consumer be sure of obtaining exact value for his
money.
The cut, Fig. 129, shows the form of measuring-box ordinarily used,
and the following table gives the discharge in cubic feet per minute
of a miner's inch of water, as measured under the various heads and
different lengths and heights of apertures used in California.
296
The Miner's Inch
Fig. 129. Miner's Inch Measuring Box
Miner's Inch Measurements
(Pelton Water Wheel Company.)
Length of
opening
in inches
Opening 2 inches high
Opening 4 inches high
Head to
center,
5 inches
Head to
center,
6 inches
Head to
center,
7 inches
Head to
center,
5 inches
Head to
center,
6 inches
Head to
center,
7 inches
Cubic feet
Cubic feet
Cubic feet
Cubic feet
Cubic feet
Cubic feet
4
-348
• 473
.589
.320 .450
1-570
6
• 355
.480
.596
.336
.470
1-595
8
.359
.484
.600
• 344
.481
.608
10
.361
.485
.602
• 349
.487
.615
12
.363
• 487
.604
• 352
• 491
.620
14
.364
.488
.604
• 354
• 494
.623
16
.365
.489
.605
.356
.496
.626
18
.365
.489
.606
• 357
.498
.628
20
.365
.490
.606
• 359
• 499
.630
22
.366
.490
.607
• 359
.500
.631
24
.366
• 490
.607
.360
.501
.632
26
.366
• 490
.607
.361
.502
.633
28
.367
.491
.607
.361
• 503
.634
30
.367
• 491
.608
.362
.503
.635
40
.367
.492
.608
.363
.505
.637
50
.368
• 493
.609
.364
.507
.639
60
.368
• 493
.609
.365
.508
.640
70
.368
• 493
.609
.365
.508
.641
80
.368
• 493
.609
.366
.509
.641
90
.369
• 493
.610
.366
• 509
.641
100
1.369
1.494
1.610
1.366
1.509
1.642
Water Power 297
WATEE POWER
(From Kent's Mechanical Engineers' Pocket Book.)
Power of a Fall of Water — Efficiency. The gross power of a
fall of water is the product of the weight of water discharged in a unit
of time into the total head, i.e., the difference of vertical elevation of
the upper surface of the water at the points where the fall in question
begins and ends. The term "head" used in connection with water-
wheels is the difference in height from the surface of the water in the
wheel-pit to the surface in the penstock when the wheel is running.
If Q = cubic feet of water discharged per second, D = weight of a
cubic foot of water = 62.36 pounds at 60° F., H = total head in feet;
then
DQH = gross power in foot-pounds per second,
and
DQH -r- 550 = 0.1134 QH = gross horse-power.
If Q' is taken in cubic feet per minute,
33000
A water-wheel or motor of any kind cannot utilize the whole of the
head H, since there are losses of head at both the entrance to and the
exit from the wheel. There are also losses of energy due to friction of
the water in its passage through the wheel. The ratio of the power
developed by the wheel to the gross power of the fall is the efficiency of
O'H
the wheel. For 75% efficiency, net horse-power = 0.00142 Q'H = — — •
706
A head of water can be made use of in one or other of the following
ways, viz.:
First. By its weight, as in the water-balance and in the overshot
wheel.
Second. By its pressure, as in turbines and in the hydraulic engine,
hydraulic press, crane, etc.
Third. By its impulse, as in the undershot wheel, and in the Pelton
wheel.
Fourth. By a combination of the above.
Horse-power of a Running Stream. The gross horse-power is
H.P. = QHX 62.36-;- 550= o.i 134 QH, in which Q is the discharge
in cubic feet per second actually impinging on the float or bucket, and
tf iP
H = theoretical head due to the velocity of the stream = — = - — »
2 g 644
in which v is the velocity in feet per second. If Q' be taken in cubic
feet per minute H.P. = 0.00189 Q'H .
Thus, if the floats of an undershot wheel driven by a current alone
be 5 feet X i foot, and the velocity of stream =210 feet per minute,
298 Bernoulli's Theorem
or sV2 feet per second, of which the theoretical head is 0.19 feet, Q =
5 square feetx 210= 1050 cubic feet per minute; H.P. = 1050X0.19
X 0.00189 = 0.377 H.P.
The wheels would realize only about 0.4 of this power, on account of
friction and slip, or 0.151 H.P., or about 0.03 H.P. per square foot of
float, which is equivalent to 33 square feet of float per H.P.
Current Motors. A current motor could only utilize the whole
power of a running stream if it could take all the velocity out of the
water, so that it would leave the floats or buckets with no velocity at
all; or in other words, it would require the backing up of the whole
volume of the stream until the actual head was equivalent to the theo-
retical head due to the velocity of the stream. As but a small fraction
of the velocity of the stream can be taken up by a current motor, its
efficiency is very small. Current motors may be used to obtain small
amounts of power from large streams, but for large powers they are not
practicable.
Bernoulli's Theorem. Energy of Water Flowing in a Tube.
The head due to the velocity is — ; the head due to the pressure is - J
2 g W
the head due to actual height above the datum plane is h feet. The
tf f
total head is the sum of these = \-h + - , in feet, in which v =
2 g W
velocity in feet per second, /= pressure in pounds per square foot,
w= weight of i cubic foot of water = 62.36 pounds. If p = pressure
in pounds per square inch - = 2.309 p. If a constant quantity of water
w
is flowing through a tube in a given time, the velocity varying at differ-
ent points on account of changes in the diameter, the energy remains
constant (loss by friction excepted) and the sum of the three heads is
constant, the pressure head increasing as the velocity decreases, and
vice versa. This principle is known as "Bernoulli's Theorem."
In hydraulic transmission the velocity and the height above datum
are usually small compared with the pressure-head. The work or energy
of a given quantity of water under pressure— its volume in cubic feet
X its pressure in pounds per square foot; or if Q = quantity in cubic
feet per second, and p = pressure in pounds per square inch, W =
144 pQ and the H.P. = *44 ^ = 0.2618 pQ.
55°
Water Power Tables 299
Table for Calculating the Horse-power of Water Heads
(Pelton Water Wheel Company.)
The following table gives the horse-power of i cubic foot of water
per minute under heads from i up to 2100 feet.
Heads
in feet
Horse-
power
Heads
in feet
Horse-
power
Heads
in feet
Horse-
power
Heads
in feet
Horse-
power
i
20
30
40
.0016098
.032196
.048294
.064392
220
230
240
250
.354156
.370254
.386352
.402450
430
440
450
460
.692214
.708312
.724410
.740508
1050
1 100
1150
1200
1.690290
1.770780
1.851270
1.931760
So
60
70
80
.080490
.096588
.112686
. 128784
260
270
280
290
.418548
.434646
.450744
.466842
470
480
490
500
.756606
.772704
.788802
.804900
1250
1300
1350
1400
2.012250
2.092740
2.173230
2.253720
90
100
no
120
. 144882
. 160980
. 177078
• I93I76
300
3io
320
330
. 482940
.499038
.515136
.531234
520
540
• 560
58o
.837096
.869292
.901488
.933684
1450
1500
1550
1600
2.334210
2.414700
2.495190
2.57568o
130
140
ISO
160
. 209274
. 225372
. 241470
.257568
340
350
360
370
.547332
.563430
.579528
.595626
600
650
700
750
.965880
1.046370
i . 126860
1.207350
1650
1700
1750
1800
2.656170
2.736660
2.817150
2.897640
170
180
190
200
210
.273666
.289764
.305862
.321960
.338058
380
390
400
410
.420
.611724
.627822
. 643920
.660018
.676116
800
850
900
950
IOOO
1.287840
1.368330
i . 448820
1.529310
1.609800
1850
1900
1950
2000
2100
2.978130
3.058620
3.I39HO
3.219600
3.380580
When the Exact Head is Found hi Above Table
Example; Have loo-foot head and 50 cubic feet of water per minute.
How many horse-power?
By reference to the above table the horse-power of each cubic foot
under zoo-foot head will be found to be .16098. This amount multi-
plied by the number of cubic feet per minute, 50, will give 8.05 horse-
power.
When Exact Head is Not Found in Table
Take the horse-power of i cubic foot per minute under i-foot head,
and multiply by the number of cubic feet available, and then by the
number of feet head. The product will be the required horse-power.
Note; The above table is based upon an efficiency of 85 per cent.
300 Gallons' and Cubic Feet
Gallons and Cubic Feet
United States Gallons in a Given Number of Cubic Feet
(i cubic foot = 7.480519 U. S. gallons; i gallon = 231 cubic inches = 0.13368056
cubic foot.)
Cubic feet
Gallons
Cubic feet
Gallons
Cubic feet
Gallons
O.I
0.75
50
374-0
8000
59844.2
0.2
1.50
60
448.8
9 ooo
67324.7
0.3
2.24
70
523-6
10 OOO
74805.2
0.4
2.99
80
598.4
20 000
149 610.4
o.S
3-74
90
673.2
30 ooo
224 415.6
0.6
4-49
100
748.1
40 ooo
299 220.8
0.7
5-24
200
i 496.1
50 ooo
374025.9
0.8
5.98
300
2244.2
60 ooo
448 831 . 1
0.9
6.73
400
2992.2
70000
523 636.3
I
7.48
500
3740.3
80 ooo
598441.5
2
14.96
600
4488.3
90000
673246.7
3
22.44
700
5236.4
IOOOOO
748051.9
4
29.92
800
5984.4
2OOOOO
I 496 103.8
5
37-40
900
6732.5
300000
2 244 155.7
6
44-88
IOOO
7480.5
400000
2 992 207.6
7
52.36
2OOO
14 961.0
500 ooo
3740259.5
8
59.84
3000
22 441 . 6
600000
44883H.4
9
67.32
4000
29922.1
700 ooo
5 236363.3
10
74-81
5000
37402.6
800000
5 984415.2
20
149-6
6000
44883.1
900000
6732467.1
30
224.4
7000
52363.6
I OOO OOO
7480519.0
40
299.2
Cubic Feet in a Given Number of Gallons
Gallons
Cubic feet
Gallons
Cubic feet
Gallons
Cubic feet
i
.134
I OOO
I33-68I
I OOO OOO
133 680.6
2
.267
2 000
267.361
2 OOO OOO
•267 361.1
3
.401
3000
401.042
3 ooo ooo
401041.7
4
.535
4 ooo
534-722
4 ooo ooo
534722.2
5
.668
5000
668.403
5 ooo ooo
668 402.8
6
.802
6 ooo
802.083
6 ooo ooo
802083.4
7
.936
7000
935 764
7 ooo ooo
935 763.9
8
1.069
8000
I 069 . 444
8 ooo ooo
1069444.5
9
1.203
9 ooo
I 203.125
9 ooo ooo
I 203 125.0
10
1.337
10 000
I 336.806
10 OOO 000
i 336805.6
Cubic Feet per Second, Gallons in 24 Hours, etc.
Cubic feet per second %0 i T • 5472 2 . 2280
Cubic feet per minute.... i 60 92.834 133.681
U. S. gallons per minute. 7.480519 448.83 694.444 i ooo
U. S. gallons per 24 hours 10 771-95 646 317 I ooo ooo i 440 ooo
Pounds of water (at 62° F. )
per mi
nute .... 62 355
3741-3 5788.65 8335.65
Contents of Pipes and Cylinders 301
Contents in Cubic Feet and United States Gallons of Pipes and Cylinders
of Various Inside Diameters and One Foot in Length
(i gallon = 231 cubic inches, i cubic foot = 7.4805 gallons.)
b
For i ft. in length
j.
For i ft. in length
*j
For i ft. in length
* 1
Cubic
•§ a!
Cubic
1LJ
Cubic
wl
rt 3
feet.also
U. S.
S'a!
feet, also
U. S.
8;S*S
rt 2
feet, also
U. S.
3 f
area in
square
gallons
p
area in
square
gallons
5 '
area in
square
gallons
feet
feet
feet
%
.0003
.0025
- 63/4
.2485
1.859
19
1.969
14-73
5/4e
.0005
.0040
7
.2673
1.999
191/2
2.074
I5-5I
%
.0008
.0057
7i/4
.2867
2.145
20
2.182
16.32
%e
.0010
.0078
7V2
.3068
2.295
201/2
2.292
17.15
%
.0014
.0102
7%
.3276
2.450
21
2.405
17-99
9/16
.0017
.0129
8
• 3491
2.611
2iy2
2.521
18.86
%
.0021
.0159
81/4
• 3712
2.777
22
2.640
19-75
!Vl6
.0026
.0193
81/2
• 3941
2.948
221/2
2.761
20.66
3/4
.0031
.0230
8%
.4176
3-125
23
2.885
21.58
13/16
.0036
.0269
9
.4418
3.305
23V2
3-012
22.53
7/8
.0042
.0312
9}4
.4667
3-491
24
3.142
23.50
15/16
.0048
.0359
9V2
.4922
3-682
25
3 409
25.50
I
.0055
.0408
93/4
.5185
3.879
26
3-687
27.58
1%
.0085
.0638
10
.5454
4.080
27
3.976
29-74
iV2
.0123
.0918
ioV4
• 5730
4.286
28
4.276
31-99
1%
.0167
.1249
ioV2
.6013
4.498
29
4.587
34-31
2
.0218
.1632
103/4
.6303
4-715
30
4.909
36.72
44
.0276
.2066
II
.6600
4-937
31
5-241
39-21
2V2
.0341
.2550
Hl/4
.6903
5.164
32
5.585
41.78
23/4
.0412
.3085
nV2
.7213
5.396
33
5-940
44-43
3
.0491
.3672
H3/4
• 7530
5.633
34
6.305
47-16
3V4
.0576
.4309
12
.7854
5.875
35
6.681
49.98
3V2
.0668
.4998
I2V2
.8522
6.375
36
7.069
52.88
33/4
.0767
-5738
13
.9218
6.895
37
7.467
55-86
4
.0873
.6528
I3V2
.9940
7.436
38
7.876
58.92
4V4
.0985
.7369
14
1.069
7-997
39
8.296
62.06
4%
.1104
.8263
I4V2
1. 147
8.578
40
8.727
65-28
48/4
.1231
.9206
15
1.227
9.180
41
9.168
68.58
5
.1364
1. 020
isV2
1.310
9.801
42
9.621
71.97
5H
.1503
.125
16
1.396
10.44
43
10.085
75-44
sV2
.1650
.234
i<%
1.485
II. II
44
10.559
78.99
53/4
.1803
.349
17
1.576
11.79
45
11.045
82.62
6
.1963
.469
I7V2
1.670
12.49
46
11.541
86.33
6V4
.2131
• 594
18
1.767
13.22
47
12.048
90.13
6V2
.2304
.724
I8VX2
1.867
13.96
48
12.566
94.00
To find the capacity of pipes greater than the largest given in the table,
look in the table for a pipe of one-half the given size, and multiply its
capacity by 4; or one of one-third its size, and multiply its capacity
by 9, etc.
To find the weight of water in any of the given sizes, multiply the
capacity in cubic feet by 62 1 or the capacity in gallons by 8j, or, if
a more accurate result is required, by the weight of a cubic foot of water
at the actual temperature in the pipe.
Given the dimensions of a cylinder in inches, to find its capacity in
U. S. gallons: Square the diameter, multiply by the length and by
0.0034. If d = diameter, / = length, gal
d2 X 0.7854 X I
.0034 dn.
231
If D and L are in feet, gallons = 5.875 DZL.
302 Cylindrical Vessels
Cylindrical Vessels, Tanks and Cisterns
Diameter in Ft. and Ins., Area in Sq. Ft. and Capacity in U. S. Gals, for i Ft. in Depth
(i gallon = 231 cubic inches = i cubic £001/7.4805 = 0.13368 cubic foot.)
Diam-
Area,
Gallons,
Diam-
Area,
Gallons,
Diam-
Area, Gallons,
eter,
square
i foot
eter,
square
i foot
eter,
square i foot
ft. in.
feet
depth
ft. in.
feet
depth
ft. in.
feet
depth
o
.785
5.87
5 8
25.22
188.66
19 o
283.53
2120.9
i
.922
6.89
5 9
25-97
194.25
19 3
291.04
2177.1 '
2
.069
8.00
5 10
26.73
199-92
19 6
298.65
2234.0
3
.227
9.18
5 ii
27-49
205.67
19 9
306.35
2291.7
4
.396
10.44
6 o
28.27
211.51
20 0
314.16
2350.1
5
.576
i-i . 79
6 3
30.68
229.50
20 3
322.06
2409.2
6
.767
13.22
6 6
33.18
248.23
20 6
330.06
2469.1
7
1.969
14-73
6 9
35-78
267.69
20 9
338.16
2529.6
8
2.182
16.32
7 o
38.48
287.88
21 0
346.36
2591-0
9
2.405
17-99
7 3
41.28
308.81
21 3
354-66
2653-0
10
2.640
19-75
7 6
44-18
330.48
21 6
363.05
2715.8
II
2.885
21.58
7 9
47-17
352.88
21 9
371-54
2779-3
o
3.142
23.50
8 o
50.27
376.01
22 0
380.13
2843.6
2 I
3.409
25.50
8 3
53.46
399,88
22 3
388.82
2908.6
2 2
3-687
27.58
8 6
56.75
424.48
22 6
397-6.1
2974-3
2 3
3.976
29-74
8 9
60.13
449.82
22 9
406.49
3040.8
2 4
4.276
31-99
9 o
63.62
475.89
23 o
415.48
3108.0
2 5
4.587
34-31
9 3
67.20
502.70
23 3
424.56
3175.9
2 6
4.909
36.72
9 6
70.88
530.24
23 6
433-74
3244.6
2 7
5.241
39-21
9 9
74.66
558.51
23 9
443-01
3314.0
2 8
5.585
41.78
10 O
78.54
587.52
24 o
452.39
3384.1
2 9
5-940
44-43
10 3
82.52
617.26
24 3
461.86
3455-0
2 10
6.305
47-16
10 6
86.59
647.74
24 6
471-44
3526.6
2 II
6.681
49.98
10 9
90.76
678.95
24 9
481.11
3598.9
3 o
7.069
52.88
II 0
95-03
710.90
25 o
490.87
3672.0
3 i
7.467
55.86
ii 3
99-40
743-58
25 3
500.74
3745-8
3 2
7.876
58.92
ii 6
103.87
776.99
25 6
510.71
3820.3
3 3
8.296
62.06
II 9
108.43
811.14
25 9
520.77
3895.6
3 4
8.727
65-28
12 0
113.10
846.03
26 o
530.93
3971.6
3 5
9.168
68.58
12 3
117.86
881.65
26 3
541.19
4048.4
3 6
9.621
71-97
12 6
122.72
918.00
26 6
55L55
4125.9
3 7
10.085
75-44
12 9
127.68
955-09
26 9
562.00
4204.1
3 8
10.559
78.99
13 o
132.73
992.91
27 o
572.56
4283.0
3 9
11.045
82.62
13 3
137.89
1031.5
27 3
583.21
4362.7
3 10
11-541
86.33
13 6
143.14
1070.8
27 6
593.96
4443-1
3 II
12.048
90.13
13 9
148.49
ino.8
27 9 •
604.81
4524.3
4 o
12.566
94.00
14 o
153-94
H5I.5
28 o
615.75
4606.2
4 I
13.095
97.96
14 3
159.48
1193-0
28 3
626.80
4688.8
4 2
13.635
102.00
14 6
165.13
1235-3
28 6
637.94
4772.1
4 3
14.186
106.12
14 9
170.87
1278.2
28 9
649 . 18
4856.2
4 4
14.748
110.32
IS o
176.71
1321.9
29 o
660.52
4941.0
4 5
15-321
II4.6I
15 3
182.65
1366.4
29 3
671.96
5026 . 6
4 6
15.90
118-97
15 6
188.69
1411.5
29 6
683.49
5112.9
4 7
16.50
123.42
15 9
194.83
1457-4
29 9
695.13
5199.9
4 8
17.10
127-95
16 o
201.06
1504.1
3O 0
706.86
5287.7
4 9
17.72
132.56
16 3
207.39
I55L4
30 3
718.69
5376.2
4 10
18.35
137.25
16 6
213-82
1599-5
30 6
730.62
5465.4
4 II
18.99
142.02
16 9
220.35
1648.4
30 9
742.64! 5555-4
5 o
19.63
146.88
17 o
226.98
1697.9
31 o
754-77
5646.1
5 I
20.29
151.82
17 3
233.71
1748 . 2
31 3
766.99
5737-5
5 2
20.97
156.83
17 6
240.53
1799-3
31 6
779-31
5829.7
5 3
21.65
I6I.93
17 9
247.45
I85I.I
31 9
791-73
5922.6
5 4
22.34
167.12
18 o
254.47
1903.6
32 o
804.25
6016.2
5 5
23-04
172.38
18 3
261.59
1956.8
32 3
816.86
6110.6
5 6
23.76
177.72
18 6
268.80
2010.8
32 6
829.58
6205.7
5 7
24.48
183.15
18 9
276.12
2065 . 5
32 9
842.39
6301.5
Weight of Water in Foot Lengths 303
Weight of Water in Foot Lengths of Pipe of Different Inside Diameters
(62.425 pounds per cubic foot.)
Diam-
eter,
inches
Water,
pounds
Diam-
eter,,
inches
Water,
pounds
Diam-
eter,
inches
Water,
pounds
Diam-
eter,
inches
Water,
pounds
%
0.0053
3
3.0643
7%
20.450
17
98.397
$
0.0213
3%
3.3250
8
21.790
i7y2
104.27
%
0.0479
3%
3.5963
sy4
23.174
18
110.31
y2
0.0851
3%
3.8782
sy2
24-599
isy2
116.53
%
0.1330
3V2
4.1708
8%
26.068
19
122.91
%
0.1915
3%
4-4741
9
27.579
i9y2
129.47
%
0.2607
3%
4.7879
914
29.132
20
136.19
i
0.3405
3%
5.H25
9^2
30.728
21
150.15
iji
0.4309
4
5.4476
9%
32.366
22
164.79
m
0.5320
4#
6.1498
10
34-048
23
180.11
i%
0.6437
4V2
6.8946
IOl/2
37-537
24
196.11
iy2
0.7661
4%
7.6820
II
41 . 198
25
212.80
i%
0.8991
5
8.5119
IlV2
45.028
26
230.16
i%
1.0427
5*4
9.3844
12
49.028
27
248.21
i%
i . 1970
5V2
10.299
12%
53-199
28
266.93
2
1.3619
58/4
11.257
13
57-540
29
286.34
2%
1.5375
6
12.257
i3y2
62.052
30
306.43
aJS
i • 7237
6U
13.300
14
66.733
31
327.20
2%
1.9205
6y2
14.385
14%
7L585
32
348.6s
2y2
2.1280
6%
15.513
15
76.607
33
370.78
2%
2.3461
7
16.683
isy2
81.799
34
393-59
2%
2.5748
•PA
17.896
16
87.162
35
417.08
2%
2.8142
7V2
19.152
i6y2
92.694
36
441 . 26
Weights of water in cylinders of the same length are proportional to
the squares of the diameters. Therefore, to get weight of cylinder of
water one foot long and 60 inches diameter, take from above table
weight of water of so-inch pipe and multiply it by the square of 60 -f- 30,
or the square of two; thus, 306.43 X4 = 1225.72 = the weight of water
in one foot length of a 6o-inch pipe.
304 Water Contents
, in Barrels
Number of Barrels (311/2 Gallons) in Cylindrical Cisterns and Tanks
(i barrel = 311^ gallons =31.5X231/1728 =
4.21094 cu. ft.; reciprocal =0.237477.)
u
Diameter in feet
0) ***
Q.S
5
6
7
8
9
10
II
12
13
i
4-663
6.714
9-139
11.937
I5.io8
18.652
22.569
26.859
31.522
5
23-3
33-6
45-7
55
.7
75
• 5
93-3
112. 8
134-3
157-6
6
28.0
40.3
54-8
71.6
90
.6
in. 9
135.4
161.2
189.1
7
32.6
47-0
64.0
8:
i-6
105
.8
130.6
158.0
188.0
220.7
8
37-3
53-7
73-1
95.5
120
.9
149.2
180.6
214.9
252.2
9
42.0
60.4
82.3
107
• 4
136
.0
167.9
203.1
241.7
283.7
10
46.6
67.1
91.4
119.4
151
.1
186.5
225.7
268.6
315-2
ii
51.3
73-9
100.5
I3I-3
1 66
.2
205.2
248.3
295.4
346.7
12
56.0
80.6
109.7
143
.2
181
.3
223.8
270.8
322.3
378.3
13
60.6
87-3
118.8
155-2
196
• 4
242.5
293.4
349-2
409.8
14
65.3
94-0
127-9
167
.1
211
• 5
261.1
316.0
376.0
441-3
15
69.9
100.7
137- 1
179.1
226
.6
279.8
338.5
402.9
472.8
16
74-6
107.4
146.2
191
.0
241
7
298.4
361.1
429.7
504.4
17
79-3
114.1
155-4
202.9
256
8
3I7-I
383.7
456.6
535-9
18
83-9
120.9
164.5
214
-9
271
9
335-7
406.2
483.5
567.4
19
88.6
127.6
173-6
226.8
287
I
354-4
428.8
510.3
598-9
20
93-3
134-3
182.8
238.7
302
2
373-0
451.4
537-2
630.4
14
15
16
17
18
19
20
21
22
I
36.557
41.966
47.748
53.903
60
431
67.332
74.606
82.253
90.273
5
182.8
209.8
238.7
2t
9-5
30
2.2
336.7
373-0
4II.3
451-4
6
219-3
251.8
286.5
323.4
362.6
404.0
447.6
493-5
541-6
7
255-9
293-8
334-2
37
7-3
42
3-0
471-3
522.2
575-8
631-9
8
292.5
335-7
382.0
431-2
483.4
538.7
596.8
658.0
722.2
9
329.0
377-7
429-7
&
5-1
54
3-9
606.0
67L5
740.3
812.5
10
365.6
419-7
477-5
539-0
604.3
673-3
746.1
822.5
902.7
ii
402.1
461.6
525.2
55
2.0
66
4-7
740.7
820.7
904.8
993-0
12
438.7
503.6
573-0
646.8
725.2
808.0
895-3
987.0
1083.3
13
475-2
545-6
620.7
70
•0.7
78
5-6
875-3
969.9
1069.3
1173- 5
14
511- 8
587.5
668.5
754-6
846.0
942.6
1044.5
II5I-5
1263.8
IS
548.4
629.5
716.2
8c
8.5
90
6-5
IOIO.O
1119.1
1233.8
I354.I
16
584.9
67L5
764.0
8t
2.4
966.9
1077.3
II93-7
1316.0
1444-4
17
621.5
713.4
811.7
91
6.4
102
7-3
1144.6
1268.3
1398.3
1534-5
18
658.0
755-4
859-5
970.3
1087.8
I2I2.0
1342.9
1480.6
1624.9
19
694-6
797-4
907.2
IO2
4-2
114
B.2
1279 3
I4I7.5
1562.8
I7I5-2
20
731- 1
839-3
955 o
1078 . I
1208 . 6
1346.6
1492.1
1645-1
1805.5
23
24 25
26
27
28 29
30
I
98.66(
) 107.432 116.571
126.083
135.968
146.226 156.858
167-863
5
493-3
537-2 582.9
630.4
679.8
731. 1 784.3
839.3
6
592.0
644-6 699.4
756.5
815.8
877.4 941- I
[007.2
7
690.7
752.0 816.0
882.6
951.8
1023.6 1098.0
[175-0
8
789.3
859.5 932.6
1008.7
1087.7
1169.8 1254.9
[342.9
9
888.0
966.9 1049.1
II34-7
1223.7
1316.0 1411.7
[510.8
10
986.7
1074.3 1165.7
1260.8
1359-7
1462.2 1568.6
[678.6
ii
1085.3
1181.8 1282.3
1386.9
1495-6
1608.5 1725.4
[846.5
12
1184.0
1289 2 1398.8
I5I3.0
1631 . 6
1754.7 1882.3
2014.4
13
1282.7
1396.6 I5I5.4
1639-1
1767.6
1900.9 2039.2
2182.2
14
1381.3
1504.0 1632.0
1765-2
1903.6
2047.2 2196.0
2350.1
15
1480.0
1611.5 1748.6
1891.2
2039.5
2193.4 2352.9
2517.9
16
1578.7
1718.9 1865.1
2017.3
2175-5
2339-6 2509.7
2685.8
17
1677.3
1826.3 1981.7
2143-4
2311.5
2485.8 2666.6
2853-7
18
1776.0
1933-8 2098.3
2269.5
2447-4
2632.0 2823.4
3021.5
19
1874.7
2041.2 2214.8
2395-6
2583.4
2778.3 2980.3
3189.4
20
1973.3
2148.6 2321.4
2521.7
2719.4
2924.5 3137.2 .
3357 3
Capacities of Rectangular Tanks 305
Capacities of Rectangular Tanks
U. S. Gallons for Each Fool in Depth (i cubic foot = 7.4805 U. S. gallons.)
1"
Length of tank
|
«l
4-t
11
3
i|
%
1|
«
«!
1
9.92
37-40
46.75
44-88
56.10
67-32
65 = 4!
78.5^
91.6;
104-73
) 130.91
i 157-09
5 183.27
> 209. 45
> 235- 63
[ 261 . 82
5 288.00
\ 314-18
> 340.36
366.54
ft.in.
2 O <
2 6
3 o
36
4 o
4 6
5 o
5 6
6 o
6 6
7 o
> 59.8^
74. 8c
i 89.77
I 104.7;
119.65
67.32
84. ie
100.95
117.82
134.6=
151.4*
74.81
93-51
112. 21
130.91
149.6]
168.3]
187.0]
82. 2f
102. 8(
123.4;
144. oc
164.5^
185.1^
205.7]
226. 2*
89.7,
112. 2]
134-6=
> 157.05
179.5;
201.9-
224.4]
; 246. 8(
269. 3C
97.2=
121. 5(
145.8'
170 . I*
\ 194- 4<
r 2i8.8c
243-1
> 267. 4V
> 291.7,
Capacities of Rectangular Tanks (Concluded)
U. S. Gallons for Each Foot in Depth (i cubic foot= 7.4805 U. S. gallons.)
Width of
tank
Length of tank
ij
1
oo
-MJj
1
o\
-1
2
10 feet
6 inches
1
ii feet
6 inches
£
ft.in.
2 0
2 6
11
4 o
4 6
5 o
5 6
6 o
6 6
7 o
7 6
8 o
8 6
9 2
9 6
10 0
10 6
II 0
ii 6
12 0
112. 21
140.26
I68.3I
196.36
224.41
252.47
280.52
308.57
336.62
364.67
392.72
420.78
119.69
149.61
179.53
209.45
239.37
269.30
299.22
329.14
359.06
388.98
418.91
448.83
478.75
127.17
158.96
190.75
222.54
254-34
286.13
317.92
349-71
381.50
413.30
445.09
476.88
508.67
540.46
134.65
168.31
202.97
235.63
269.30
302.96
336.62
370.28
403.94
437.6o
471 . 27
504.93
538.59
572.25
605.92
142.13
177-66
213.19
248.73
284.26
319.79
355.32
J90.85
126.39
461.92
197-45
532.98
568-51
x>4-05
539.58
575.ii
149.61
187.01
224.41
261.82
299.22
336.62
374.03
411.43
448.83
486.23
523.64
561.04
598.44
>35.84
>73.25
710.65
748.05
157.09
196.36
235.63
274.90
3I4.I8
353-45
392.72
432.00
17L27
510.54
549.8i
589.08
)28.36
)67.63
706.90
746.17
785.45
524.73
164.57
205 . 71
246.86
288.00
329.14
370.28
4H.43
452.57
493.71
534.85
575.99
517.14
558.28
>99-42
740.56
78I.7I
522.86
^64.00
X>5.I4
172.05
215.06
258.07
301.09
344-10
387.11
430.13
473-14
5I6.I5
559.16
602.18
645.19
588.20
731-21
774-23
317.24
$60.26
X53-26
M6.27
179.53
224.41
269.30
314.18
359.06
403.94
448.83
493.71
538.59
583.47
628.36
673.24
718.12
763.00
807.89
852.77
897.66
942.56
987.43
032.3
077.2
306 Discharging Capacities of Pipe
Relative Discharging Capacities of Pipe
Actual
internal
.269
.364
• 493
.622
.824
1.049
1.380
1.610
diameter
Nominal
internal
%
V4
8/8
y2
%
I
1%
i%
diameter
%
Vl
i
2.1
I
%
4-5
2.1
I
y2
8
3-8
1.8
i
8/4
16
8
3-6
2
I
i
30
14
6.6
37
1.8
I
jM,
60
28
13
7
36
2
I
i%
88
41
19
ii
5-3
2-9
1-5
i
2
164
77
36
20
10
5-5
2-7
1.9
2Y2
255
I2O
56
31
16
8
4-3
2.9
3
439
206
97
54
27
15
7
5
3*4
632
297
139
78
38
21
ii
7
4
867
407
191
107
53
29
15
10
4%
i 148
539
253
141
70
38
19
13
5
1525
716
335
188
93
51
26
17
6
2414
I 133
531
297
147
80
40
28
7
3483
I 635
766
428
212
116
58
40
8
4795
2 251
1054
590
292
160
80
55
9
6369
2990
i 401
783
388
212
107
73
10
8468
3976
1862
i 042
516
282
142
97
II
10693
5020
2352
1315
651
356
179
122
12
13292
6 240
2923
1635
809
443
223
152
13
17028
7994
3745
2094
1037
567
286
194
14
20425
9589
4492
2 512
1244
680
343
233
15
24 199
II 361
5322
2976
1474
806
406
276
18 O. D.
31 750
14906
6982
3905
1933
1057
533
362
20 O. D.
41 928
19685
9 221
5157
2553
1396
703
478
22 O. D.
53848
25281
II 842
6623
3279
1793
903
614
24 O. D.
67599
31 737
14866
8315
4116
2251
1 134
771
26 O. D.
28 O. D.
30 O. D.
83267
100932
120 675
39093
47387
"56655
I83I2
22197
26539
10 242
I24I5
14843
5070
6146
7348
2773
336i
4018
1397
1693
2024
950
1152
1377
Nominal
internal
%
¥*
%
V2
8/4
I
1%
itt
diameter
Actual
internal
.269
.364
.493
.622
.824
1.049
1.380
1.610
diameter
Discharging Capacities of Pipe 307
Relative Discharging Capacities of Pipe (Continued)
Actual
internal
2.067
2.469
3.068
3-548
4.026
4.506
5-047
6.065
diameter
Nominal
internal
2
2%
3
3V2
4
4V2
5
6
diameter
Vs
If
Calculations based on the inside diameters of
standard pipe, page 22.
i
Formula
i%
Relative discharge capacity = V inside diameter6.
2
I
2^2
1.6
i
3
2-7
1-7
I
3V2
3.9
2.5
1-4
I
4
5.3
3-4
2
1.4
I
4H
7
4-5
2.6
1.8
1.3
i
5
9
6
3-5
2.4
1.8
1-3
I
6
15
9
5-5
3-8
2.8
2.1
1.6
I
7
21
14
8
5-5
4
3
2.3
1.4
8
29
19
10.9
7-6
5-5
4-2
3.1
2
9
39
25
14
10
7-3
5.5
4-2
2.6
10
52
33
19
13
10
7-4
5-6
3-5
ii
65
42
24
17
12
9-3
7
4-4
12
81
52
30
21
15
12
8.7
5-5
13
104
67
39
27
20
15
ii
7
14
125
80
46
32
24
18
13
8.5
15
148
95
55
38
28
21
16
10
18 O. D.
194
124
72
So
37
28
21
13
20 O. D,
256
164
95
66
48
37
27
17
22 O. D.
329
211
123
85
62
47
35
22
24 O. D.
413
265
154
107
78
59
44
28
26 O. D.
509
326
190
132
96
73
55
34
28 O. D.
617
395
230
160
116
88
66
42
30 0. D.
737
473
275
191
139
105
79
50
[ Nominal
internal
2
2^2
3
sfi
4
4V2
5
6
diameter
Actual
internal
2.067
2.469
3-068
3.548
4.026
4.506
5-047
6.065
diameter
308 Discharging Capacities of Pipe
Relative Discharging Capacities of Pipe (Continued)
Actual
internal
7.023
7.981
8.941
10. O20
II.OOO
12.000
13.250
14.250
diameter
Nominal
internal
diameter
7
8
9
10
II
12
14
O.D.
O. D.
Vs
i
i
if*
2
3
3V2
4
4V2
5
6
7
I
8
1-3
I
9
1.8
1.3
I
10
2.4
1.8
1.3
i
ii
3
2.2
1.7
1-3
I
12
3-8
2.8
2.1
1.6
1.2
I
13
4-9
3-6
2.7
2
1.6
1.3
I
14
5-9
4-3
32
2.4
1.9
1.5
1.2
i
18 O. D.
6.9
9-1
Ll
3-8
5
2.9
3.7
2.3
3
1.8
2.4
1.4
1-9
1.2
1.6
20 0. D.
22 O. D.
12
15
8.7
ii
6.6
8.5
u
3-9
5
3-2
4-1
2.5
3-2
2.1
2.6
24 O. D.
19
14
ii
8
6.3
5-1
4
3-3
26 O. D.
24
17
13
9-8
7-8
6.3
4-9
4-1
28 O. D.
29
21
16
12
9-4
7-6
5-9
4-9
30 O. D.
35
25
19
14
II
9-1
7-1
5-9
Nominal
internal
7
8
9
10
II
12
13
14
diameter
Actual
internal
diameter
7.023
7.981
8.941
10.020
II.OOO
12.000
13.250
14.250
Discharging Capacities of Pipe 309
Relative Discharging Capacities of Pipe (Concluded)
Actual
internal
15.250
17.000
19.000
21.000
23.000
25.000
27.000
29.000
diameter
Nominal
internal
diameter
16
0. D.
18
0. D.
20
0. D.
22
0. D.
24
0. D.
26
0. D.
28
0. D.
30
0. D.
Vj
4
Calculations based on the inside diameters of
SA
standard pipe, page 22.
I
Formula
1 74
Relative discharge capacity = V inside diameter5.
2
3
4 f-
5
6
7
8
9
10
ii
12
13
14
IS
i
18 O. D.
1.3
i
20 O. D.
1.7
1.3
i
22 0. D.
2.2
1-7
1.3
I
24 O. D.
2.8
2.1
1.6
1-3
i
26 O. D.
3-4
2.6
2
1-5
1.2
i
28 O. D.
4-2
3-2
2.4
1-9
i.S
1.2
i
30 0. D.
5
3.8
2.9
2.2
1.8
1-4
1.2
i
Nominal
internal
diameter
IS
18
0. D.
20
0. D.
22
0. D.
24
O. D.
26
0. D.
28
0 D.
ti&
Actual
internal
15.250
17.000
19.000
2I.OOO
23.000
25.000
27.000
29.000
diameter
310 Equivalents
Equivalents of Ounces per Square Inch in Inches of Water and Mercury
(Water at 62° F. weighs 62.355 pounds per cubic foot.)
(Specific gravity of mercury at 62° F. = 13.58.)
Ounces per Pound per
square inch square inch
Inches of water ^g
0.25 .015625
0.433 -03I9
0.50 .03125
0.866 .0638
i .06250
1.732 .1275
2 . I250O
3-464 -2551
3 • 18750
5.196 .3826
4 .25000
6.928 .5102
5 .31250
8.660 .6377
6 .37500
10.392 .7653
7 -43750
12.124 .8928
8 .50000
13.856 .020
9 .56250
15.588 .148
10 . 62500
17.320 .275
ii .68750
19-052 .403
12 .75OOO
20.784 .531
13 .81250
22.516 .658
14 .87500
24.248 .786
15 -93750
25.980 .913
16 i.ooooo
27.712 .041
Equivalents of Pounds per Square Inch in Inches and Feet of Water
and Mercury
(Water at 62° F. weighs 62.355 pounds per cubic foot.)
(Specific gravity of mercury at 62° F. = 13.58.)
Pounds per
Inches of
Feet of
Inches of
Feet of
square inch
water
water
mercury
mercury
i
27.71
2.31
2.041
.1701
2
55-42
4.62
4.081
.3401
3
83-14
6.93
6.122
.5102
4
5
110.85
138.56
9-24
11.55
8.163
IO.2O
.6802
.8503
6
166.27
13-86
12.24
i. 020
7
193-99
16.17
14.28
1.190
8
221.70
18.47
16.33
1.360
9
249.41
20.78
18.37
I.53I
10
277.12
23.09
20.41
1.701
ii
304.84
25.40
22.45 .
1.871
12
332.55
27.71
24.49
2.041
13
360.26
30.02
26.53
2. 211
14
387.97
32.33
28.57
2.381
14-7
407.37
33-95
30.00
2.5OO
IS
415-68
34.64
30.61
2.551
16
443-40
36.95
32.65
2.721
17
471.11
39.26
34.69
2.891
18
498.82
41-57
36.73
3.061
19
526.53
43-88
38.77
3.231
20
554-25
46.19
40.81
3-401
21
581.96
48.50
42.85
3.571
22
609.67
50.81
44.89
3.741
23
637.38
53-12
46.94
3-9II
24
665.10
55-42
48.98
4.081
25
692.81
57-73
51.02
4-251
Conversion Table
311
Conversion Table
BASIS: i cubic foot of water at 3g.i°F. = 62.425 pounds,
i U. S. gallon = 231 cubic inches,
i imperial gallon = 277.274 cubic inches.*
U. S. gallon = 231 .000000 cubic inches.
U. S. gallon = o. 133681 cubic foot.
U. S. gallon = 0.833111 imperial gallon.
U. S. gallon = 3 • 7§5434 liters.
U. S. gallon of water at 39.1° F = 8.345009 pounds.
Imperial gallon = 277 . 274000 cubic inches.*
Imperial gallon = o. 160459 cubic foot.
Imperial gallon = i . 200320 U. S. gallons.
Imperial gallon. = 4.543734 liters.
Imperial gallon of water at 39.1° F = 10.016684 pounds.*
Cubic foot = 7 .480519 U. S. gallons.
Cubic foot = 6. 232103 imperial gallons.
Cubic foot = 28.317016 liters.
Cubic foot of water at 39.1° F = 62 .425000 pounds.
Cubic foot of water at 39.1° F = 0.031212 ton.
Cubic inch = 0.004329 U. S. gallon.
Cubic inch = 0.003607 imperial gallon.
Cubic inch = 0.016387 liter.
Cubic inch of water at 39.1° F = 0.036126 pound.
Cubic inch of water at 39.1° F = 0.578009 ounce.
Pound of water at 39.1° F: = 27.681217 cubic inches.
Pound of water at 39.1° F = 0.016019 cubic foot.
Pound of water at 39.1° F = o. 119832 U. S. gallon.
Pound of water at 39.1° F = 0.099833 imperial gallon.
Pound of water at 39.1° F = 0.453617 liter.
Liter = o. 264170 U. S. gallon.
Liter = o . 220083 imperial gallon.
Liter = 61 .023378 cubic inches.
Liter «= 0.035314 cubic foot.
Liter of water at 39.1° F = 2 . 204505 pounds.
* The British imperial gallon is usually defined as being equal to 277.274
cubic inches, or 10 pounds of pure water at the temperature of 62° F. when
the barometer is at 30 inches.
312 Equivalents
CONVENIENT EQUIVALENTS
i second-foot equals 40 California miner's inches. (Law of March 23,
IQOI.)
i second-foot equals 38.4 Colorado miner's inches.
i second-foot equals 7.48 United States gallons per second; equals
448.8 gallons per minute; equals 646 317 gallons per day.
i second-foot equals 6.23 British imperial gallons per second.
i second-foot for one year covers one square mile 1.131 feet deep;
13.57 inches deep.
i second-foot for one year equals 31 536 ooo cubic feet.
i second-foot equals about one acre-inch per hour.
i second-foot falling 10 feet equals 1.136 horse-power.
100 California miner's inches equal 18.7 United States gallons per
second.
100 California miner's inches equal 96.0 Colorado miner's inches.
100 California miner's inches for one day equal 4.96 acre-feet.
100 Colorado miner's inches equal 2.60 second-feet.
100 Colorado miner's inches equal 19.5 United States gallons per
second.
100 Colorado miner's inches equal 104 California miner's inches.
100 Colorado miner's inches for one day equal 5.17 acre-feet.
loo United States gallons per minute equal 0.223 second-foot.
100 United States gallons per minute for one day equal 0.442 acre-
foot.
i ooo ooo United States gallons per day equal i .55 second-feet.
i ooo ooo United States gallons equal 3.07 acre-feet.
i ooo ooo cubic feet equal 22.96 acre-feet.
i acre-foot equals 325 851 gallons.
i inch deep on i square mile equals 2 323 200 cubic feet.
i inch deep on i square mile equals .0737 second-foot per year.
Gas 313
GAS
Physical Properties of Gases
PAGE
Expansion of Gases; Marietta's Law 314
Law of Charles 314
Avogadro's Law 314
Saturation Point of Vapors 315
Dalton's Law of Gaseous Pressures 315
Mixtures of Vapors and Gases 315
Flow of Gases. 316
Absorption of Gases by Liquids 316
Flow of Gas in Pipes — Low Pressure
Formulas for Discharge 317
Supply of Gas through Pipes. 317
Table of Sizes of House Pipes 319
Flow of Gas in Pipes — High Pressure
Fundamental Considerations 320
Formulae for Discharge 321
Effect of Bends and Fittings 324
Adiabatic Compression of Natural Gas 324
314 Gas
PHYSICAL PROPERTIES OF GASES
(From Kent's Mechanical Engineers' Pocket Book.)
When a mass of gas is inclosed in a vessel it exerts a pressure against
the walls. This pressure is uniform on every square inch of the surface
of the vessel; also, at any point in the fluid mass the pressure is the
same in every direction.
In small vessels containing gases the increase of pressure due to weight
may be neglected, since all gases are very light; but where liquids are
concerned, the increase in pressure due to their weight must always be
taken into account.
Expansion of Gases; Mariotte's Law. The volume of a gas
diminishes in the same ratio as the pressure upon it is increased, if the
temperature is unchanged.
This law, by experiment, is found to be very nearly true for all gases,
and is known as Boyle's or Mariotte's law.
If p = pressure at a volume v, and pi = pressure at a volume vi, pivi =
v
pv; pi = - p; pv = a constant, C.
Vl
The constant, C, varies with the temperature, everything else remain-
ing the same.
Air compressed by a pressure of seventy-five atmospheres has a volume
about 2 per cent less than that computed from Boyle's law, but this
is the greatest divergence that is found below 160 atmospheres pressure.
Law of Charles. The volume of a perfect gas at a constant pres-
sure is proportional to its absolute temperature. If 20 be the volume of
a gas at 32° F., and vi the volume at any other temperature, /i, then
//i+459.2\ / , h -32°\
Vl = VQ [ - ; vi = I + — - }VQ,
\ 491.2 J \ 491.2 I
or, vi =[i + 0.002036 (/i - 32°)] »o.
If the pressure also changes from po to pi,
po (ti + 459.2^
Vi = VQ
pi \ 491.2 I
The Densities of the elementary gases are simply proportional to
their atomic weights. The density of a compound gas, referred to hydro-
gen as i, is one-half its molecular weight; thus the relative density of
CO2is y2 (12+32) = 22.
Avogadro's Law. Equal volumes of all gases, under the same con-
ditions of temperature and pressure, contain the same number of
molecules.
Physical Properties of Gases 315
To find the weight of a gas in pounds per cubic foot at 32° F., multi-
ply half the molecular weight of the gas by 0.00559. Thus i cubic
foot of marsh-gas,
= Vz (12 + 4) X 0.00559 = 0.0447 pound.
When a certain volume of hydrogen combines with one-half its volume
of oxygen, there is produced an amount of water vapor which will occupy
the same volume as that which was occupied by the hydrogen gas when
at the same temperature and pressure.
Saturation Point of Vapors. A vapor that is not near the satu-
ration point behaves like a gas under changes of temperature and pres-
sure; but if it is sufficiently compressed or cooled, it reaches a point where
it begins to condense; it then no longer obeys the same laws as a gas,
but its pressure cannot be increased by diminishing the size of the
vessel containing it, but remains constant, except when the temper-
ature is changed. The only gas that can prevent a liquid evaporating
seems to be its own vapor.
Dalton*s Law of Gaseous Pressures. Every portion of a mass of
gas inclosed in a vessel contributes to the pressure against the sides
of the vessel the same amount that it would have exerted by itself had
no other gas been present.
Mixtures of Vapors and Gases. The pressure exerted against the
interior of a vessel by a given quantity of a perfect gas inclosed in it
is the sum of the pressures which any number of parts into which such
quantity might be divided would exert separately, if each were inclosed
in a vessel of the same bulk alone, at the same temperature. Although
this law is not exactly true for any actual gas, it is very nearly true for
many. Thus if 0.080728 pound of air at 32° F., being inclosed in a
vessel of i cubic foot capacity, exerts a pressure of one atmosphere,
or 14.7 pounds, on each square inch of the interior of the vessel, then
will each additional 0.080728 pound of air which is inclosed, at 32° F.,
in the same vessel, produce very nearly an additional atmosphere of
pressure. The same law is applicable to mixtures of gases of different
kinds. For example, 0.12344 pound of carbonic-acid gas, at 32° F.,
being inclosed in a vessel of one cubic foot capacity, exerts a pressure of
one atmosphere; consequently, if 0.080728 pound of air and 0.12344
pound of carbonic-acid, mixed, be inclosed at the temperature of 32° F.,
in a vessel of one cubic foot capacity, the mixture will exert a pressure of
two atmospheres. As a second example: let 0.080728 pound of air, at
212° F., be inclosed in a vessel of one cubic foot; it will exert a pressure of
212 +459-2
- = 1.366 atmospheres.
32 +459-2
Let 0.03797 pound of steam, at 212° F., be inclosed in a vessel of one
cubic foot; it will exert a pressure of one atmosphere. Consequently,
316 Flow of Gas
if 0.080728 pound of air and 0.03707 pound of steam be mixed and
inclosed together, at 212° F., in a vessel of one cubic foot, the mixture
will exert a pressure of 2.366 atmospheres. It is a common but erro-
neous practice, in elementary books on physics, to describe this law as
constituting a difference between mixed and homogeneous gases; whereas
it is obvious that for mixed and homogeneous gases the law of pressure
is exactly the same, viz., that the pressure of the whole of a gaseous
mass is the sum of the pressures of all its parts. This is one of the laws
of mixture of gases and vapors.
A second law is that the presence of a foreign gaseous substance in
contact with the surface of a solid or liquid does not affect the density
of the vapor of that solid or liquid unless there is a tendency to chemical
combination between the two substances, in which case the density of
the vapor is slightly increased.
If 0.591 pound of air = i cubic foot at 212° F. and atmospheric pres-
sure is contained in a vessel of i cubic foot capacity, and water at 212° F.
is introduced, heat at 2i2°F. being furnished by a steam jacket, the
pressure will rise to two atmospheres.
If air is present in a condenser along with water vapor, the pressure
is that due to the temperature of the vapor plus that due to the quan-
tity of air present
Flow of Gases. By the principle of the conservation of energy,
it may be shown that the velocity with which a gas under pressure will
escape into a vacuum is inversely proportional to the square root of its
density; that is, oxygen, which is sixteen times as heavy as hydrogen,
would, under exactly the same circumstances, escape through an open-
ing only one-fourth as fast as the latter gas.
Absorption of Gases by Liquids. Many gases are readily absorbed
by water. Other liquids also possess this power in a greater or less
degree. Water will, for example, absorb its own volume of carbonic-
acid gas, 430 times its volume of ammonia, 2^ times its volume of
chlorine, and only about MJO of its volume of oxygen.
The weight of gas that is absorbed by a given volume of liquid is
proportional to the pressure. But as the volume of a mass of gas is less
as the pressure is greater, the volume which a given amount of liquid
can absorb at a certain temperature will be constant, whatever the
pressure. Water, for example, can absorb its own volume of carbonic-
acid gas at atmospheric pressure; it will also dissolve its own volume if
the pressure is twice as great, but in that case the gas will be twice as
dense, and consequently twice the weight of gas is dissolved.
Flow of Gas in Pipes — Low Pressure
317
FLOW OF GAS IN PIPES — LOW PRESSURE
The following formulae are intended for low-pressure distribution of
gas, with comparatively small differences between the initial and final
pressures.
Pole's Formula,
Molesworth's Formula,
Gill's Formula,
Q = 1350
Q = 1291
Where Q = quantity of gas discharged in cubic feet per hour.
d = inside diameter of pipe in inches.
h = pressure in inches of water.
5 = specific gravity of gas, air being i.
I = length of main in yards.
The formula of Gill is said to be based on experimental data, and to
make allowance for obstructions by tar, water, and other bodies tending
to check the flow of gas through the pipe.
An experiment made by Mr. Clegg, in London, with a 4-inch pipe,
6 miles long, pressure 3 inches of water, specific gravity of gas 0.398,
gave a discharge into the atmosphere of 852 cubic feet per hour, after a
correction of 33 cubic feet was made for leakage. Substituting this
value for Q in the formula Q = C i/— , we find the coefficient C to be
T Si
997, which corresponds very closely with the formula given by Moles-
worth.
Maximum Supply of Gas Through Pipes in Cubic Feet per Hour, Specific
Gravity being Taken at 0.45, Calculated from the Formula
Q = 1000 Vd52i T- si. (Molesworth)
Length of Pipe = 10 Yards
Inside
diam-
Pressure by the water-gage in inches
pipe in
inches
O.I
0.2
0.3
0.4
o.5
0.6
0.7
0.8
0.9
I.O
%
13
18
22
26
29
31
34
36
38
41
y2
26
37
46
53
59
64
70
74
79
83
%
73
103
126
145
162
187
192
205
218
230
i
149
211
258
298
333
365
394
422
447
471
1%
260
368
451
521
582
638
689
737
781
823
iVz
411
581
711
821
918
1006
1082
1162
1232
1299
2
843
1192
1460
1686
1886
2066
2231
2385
2530
2667
318
Flow of Gas
Length of Pipe = 100 Yards
Inside
Pressure by the water-gage in inches
diam-
pipe in
inches
O.I
0.2
0.3
0.4
o.S
0.75
I.O
1.25
1.5
2.O
2.5
y2
8
12
14
17
19
23
26
29
32
36
42
%
23
32
42
46
51
63
73
81
89
103
115
I
47
67
82
94
105
129
149
167
183
211
236
t%
82
116
143
165
184
225
260
291
319
368
412
iVa
130
184
225
260
290
356
4"
459
503
581
649
2
267
377
462
533
596
730
843
943
1033
1333
2%
466
659
807
932
1042
1276
1473
1647
1804
2083
2329
3
735
1039
1270
1470
1643
2012
2323
2598
2846
3286
3674
3%
1080
1528
1871
2161
2416
2958
3820
4184
4831
5402
4
1508
2133
2613
3017
3373
4131
4770
5333
5842
6746
7542
Length of Pipe = 1000 Yards
Inside diarn-
Pressure by the water-gage in inches
in inches
o.S
o.7S
I.O
1.5
2.0
2.5
3-0
i
33
41
47
58
67
75
82
i^4
92
130
159
205
226
2
189
231
267
327
377
422
462
2V2
329
403
466
571
659
737
807
3
520
636
735
900
1039
1162
1273
4
1067
1306
1508
1847
2133
2385
2613
5
1863
2282
2635
3227
3727
4167
4564
6
2939
3600
4157
5091
5879
6573
7200
Length of Pipe = 5000 Yards
Inside diam-
Pressure by the water-gage in inches
in inches
I.O
1-5
2.0
2.5
3-0
2
"9
146
I69
189
207
3
329
402
465
520
569
4
675
826
955
I 067
i 168
5-
I 179
1443
I 667
1863
2 O4I
6
1859
2277
2629
2939
3 220
7
2733
3347
3865
4 321
4734
8
3816
4 674
5397
6034
6610
9
5 123
6274
7245
8 zoo
8873
10
6667
8165
9428
10 541
II 547
12
10 516
12880
14872
16628
18 215
Flow of Gas in Pipes — Low Pressure 319
Dr. A. C. Humphreys says his experience goes to show that these
tables give too small a flow, but it is difficult to accurately check the
tables, on account of the extra friction introduced by rough pipes,
bends, etc. For bends, one rule is to allow ^2 of an inch pressure for
each right-angle bend.
Where there is apt to be trouble from frost it is well to use no service
of less diameter than % inch, no matter how short it may be. In
extremely cold climates this is now often increased to i inch, even for
a single lamp. The best practice in the United States now condemns
any service less than % inch.
Table Showing the Correct Sizes of House Pipes for Different Lengths of
Pipes and Number of Outlets
(Denver Gas and Electric Company)
Num-
ber of
outlets
Length of pipe in feet
1|
JD'&
i*
a a
5'a
1^
I*
i&
"i1 P.
$1
§
A
Si
£a
ft
Is
|*
-So
fS
i
2
3
4
6
8
10
13
15
20
25
30
35
40
45
75
IOO
125
ISO
175
200
225
250
20
30
27
12
50
50
50
50
33
24
13
70
70
70
70
70
70
So
35
21
16
IOO
IOO
IOO
IOO
IOO
IOO
IOO
IOO
60
45
27
17
12
150
150
ISO
150
.150
150
150
150
150
120
65
42
30
22
17
13
200
200
200
200
200
2OO
20O
200
200
200
200
175
120
90
70
55
45
27
20
300
300
300
300
300
300
300
300
300
300
300
300
300
270
210
165
135
80
60
33
22
15
400
400
400
400
400
400
400
400
400
400
400
400
400
400
400
400
330
200
150
80
50
35
28
21
17
14
In this table the quantity of gas the piping may be called on to con-
vey is stated in terms of % inch outlets on the assumption that each
320 Flow of Gas in Pipes — High Pressure
outlet requires a supply of 10 cubic feet per hour. The aim of the table
is to have the loss in pressure not exceed Vio inch water pressure in 30
feet.
In using the table the following rules should be observed:
In figuring out the size of pipe, always start at the extremities of the
system and work toward the meter.
Gas should not be supplied from a smaller to a larger size pipe.
If the exact number of outlets given cannot be found in the table,
take the next larger number. For example, if 17 outlets are required,
work with the next larger number in the table, which is 20. Or, if,
for the number of outlets given, the exact length which feeds these out-
lets cannot be found in the table, the next larger length corresponding
to the outlets given must be taken to determine the size of pipe required.
Thus if there are 8 outlets to be fed through 55 feet of pipe, the next
larger than 55 in the 8 outlet line in the table, which is 100, should be
used. As this is in the iVi inch column, that size pipe would be required.
For any given number of outlets, a smaller size should not be used than
the smallest size that contains a figure in the table for that number of
outlets. Thus, to feed 15 outlets, no smaller size pipe than i inch may
be used, no matter how short the section of pipe may be.
In any continuous run from an extremity to the meter, there may not
be used a longer length of any size pipe than found in the table for
that size, as 50 feet of % inch, 70 feet of i inch, etc. If any one section
would exceed the limit length, it must be made of larger pipe.
If any outlet is larger than % inch it must be counted as more than
one, in accordance with the following table:
Size of outlet (inches) ¥2 % i iV* iVz 2 2% 3
Value in table 2 4 7 n 16 28 44 64
FLOW OF GAS IN PIPES — HIGH PRESSURE
The formulae given on page 317 do not take account of the varying
density and volume of the gas when subjected to different pressures; they
are applicable, therefore, only to low-pressure distribution where the
difference in pressure is measured in inches of water head. Under the
vastly different conditions connected with high pressure distribution,
where the differences between initial and final pressures are so great as
to cause a material alteration in the volume of the gas, the error involved
in their use is great.
Mariotte's law states that the volume of a gas varies inversely with
the pressure to which it is subjected. If the pressure be doubled the
gas will be compressed to half its former volume. When we consider
the high pressure at which gas is now being distributed in many places,
we may appreciate the disturbances which this degree of compression
introduces into a formula designed for use under far different conditions.
Then there is also the process of expansion continually going on, the
volume increasing as the gas travels farther away from the point at which
Flow of Gas in Pipes — High Pressure 321
the initial pressure is applied. Suppose a quantity of gas is passed
through a pipe at an initial pressure of 20 pounds per square inch and
discharged at i pound per square inch, the consequential expansion
represents a certain amount of work, and this factor must, in all cases,
be taken into account, to whatever degree it has been operating.
The common form of the formula for flow of gas in long pipes under
high pressure is
-V
(Pi2 - P22) ®
Is
where Q = discharge in cubic feet per hour at atmospheric pressure.
Pi = absolute initial pressure in pounds per square inch.
P2 = absolute final pressure in pounds per square inch.
d = inside diameter of pipe in inches.
/ = length of pipe line in feet.
5 = specific gravity of gas, air being i.
c = coefficient, which is variously given in the different formulae.
The expression (Pi1 - P22) may be replaced by (Pi + P2) (Pi - P2).
William Cox (Am. Mach., Mar. 20, 1002) gives the formula in the
form
1 1 p,2
Mr3
—
Q = 3000 1 / - - - when s = 0.65.
E. A. Rix, in a paper on the "Compression and Transmission of
Illuminating Gas," read before the Pacific Coast Gas Association, 1905,
gives for the discharge per minute,
44.66 / (Pi2 - P22) eft
- —
I
from which the discharge per hour would be
2680 /(Pi2 - P22) d6
Q = ~s\~ ~T~
Forrest M. Towl gives
L being given in miles instead of feet. The value of C for air is 38.28
and for gas having a specific gravity of 0.59 is 50.
The Pittsburgh formula for discharge is,
Q = 3450 \/ "l" when * "
322
Oliphant's
Formula
Since the velocity, and therefore the discharge varies inversely as the
square root of the density, all of these formulae may be transformed into
the general form given above,
the value of
Cox
c
c derived fr
> ,i/(Pl2
- /V) $>
lows:
2419
2672
2680
2782
Hiphant for
C V 1S
am the different formulae being as fo
Pittsbu
Rix
rgh
Towl
Oliphant's Formula.
the discharge of gas whe
A formula
n the specifi<
Q = 42 a y/
cubic feet pe
ire in pounds
e in pounds ]
tin in miles,
ee table belo
specific gra1
ire of flowin
ch 5°, and a
t, the discha
t of unity for
follies of Coe
determined by F. H. C
: gravity is 0.60, is
Pi2 - P22
where Q = discharge in
Pi = initial pressi
Pz = final pressur
L = length of ma
a = coefficient (s
For gas of any other
/o.6o
V — - • For temperati
V s
deduct i per cent for ea
less than 60° F.
According to Oliphan
Vd*. Using a coefficien
1
L
r hour at atmospheric pressure,
per square inch (absolute).
3er square inch (absolute),
*).
irity, s, multiply the discharge by
g gas when observed above 60° F.
dd a like amount for temperatures
rge is not strictly proportional to
i inch pipe he gives a — V^5 _j
30
fficient "a"
Inside
diameter,
inches
a
Inside
diameter,
inches
a
Inside
diameter,
inches
a
%
%
8/4
I
x%
2
2Y2
.0317
.1810
.5012
1. 00
2.93
5-92
10.37
3
4
5%
6
8
10
16.5
34-1
60
81
95
198
350
12
16
18
20
24
30
36
556
1160
1570
2055
3285
5830
9330
For 15 inch Outside Diameter Pipe, 14*4 inches Inside Diameter, a = 863.
For 16 inch Outside Diameter Pipe, T5V4 inches Inside Diameter, a = 1025.
For 18 inch Outside Diameter Pipe, 17^4 inches Inside Diameter, a = 1410.
For 20 inch Outside Diameter Pipe, 19*4 inches Inside Diameter, a = 1860.
Comparison of Formulae 323
Unwin' s Formula. Professor Unwin in a paper read before the
British Institution of Gas Engineers in 1904, suggested the following
formula, which takes into account the changes of volume and density,
where Q = discharge in cubic feet per second measured at pressure
D = diameter of pipe in feet.
ui = velocity in feet per second at the inlet of the pipe.
#2 = velocity in feet per second at the outlet of the pipe.
Pi = pressure at the inlet of the pipe (absolute).
Pi = pressure at the outlet of the pipe (absolute).
The value of the velocity is obtained from the following formula,
Ml :
CSlPi2
where, in addition to the notation given above,
5 = specific gravity of gas.
I = length of pipe in feet.
c = coefficient of friction which may be obtained from the formula
c = 0.0044
Comparison of Formulas. That these formulae give diverse results
is shown by the following example. Suppose it is required to find the
discharge per hour of an 8 inch pipe line having an intake pressure of
200 pounds gage and a discharge pressure of 25 pounds gage, the length
being 20 miles, and the specific gravity of the gas being 0.60. The follow-
ing results are obtained, the discharge being given in cubic feet at
atmospheric pressure.
Cox Formula 367 ooo cubic feet per hour.
Unwin Formula 374 700 cubic feet per hour.
Oliphant Formula 392 400 cubic feet per hour.
Pittsburgh Formula 405 500 cubic feet per hour.
Rix Formula 406 700 cubic feet per hour.
Towl Formula 422 100 cubic feet per hour.
The results given above by the various formulae agree within 7 per
cent of the average of results. The rules most generally accepted are
the Oliphant and Pittsburgh formulae. It is understood that all the
formulae quoted apply to straight pipes laid perfectly level. Any
deviation from these conditions will of course affect the amount of
discharge.
Since the quantity of gas discharged varies as the square root of the
difference of the squares of the initial and final pressures, it is evident
that as the initial pressure is increased, the final pressure being fixed,
324
Effect of Bends and Fittings
the discharge becomes more and more in direct ratio to the" increase in
pressure. Thus by increasing the pressure from 100 to 200 pounds
gage, pressure of discharge being 5 pounds, the quantity of gas trans-
mitted is increased 89 per cent.
Effect of Bends and Fittings. The effect of a bend or sharp angle
in a pipe is to reduce the kinetic energy of the gas and, because of the
increased friction, to retard the velocity of the gas. It is found that
these disturbing influences vary to a great extent with the character of
the bend. The resistance offered is least when the radius of the bend is
equal to five times the radius of the pipe. The most convenient way
of stating the resistance offered by bends is in terms of equivalent length
of straight pipe which offers the same resistance to flow as the extra
resistance due to the bend. A formula given for this equivalent length is
/ r \0.83
L = 12.85 -1 I,
\K/
where L = equivalent length in feet.
/ = radius of pipe.
R = radius of curve.
/ = length of curve in feet measured along the center line.
The resistance of a bend whose radius is five times the radius of the
pipe, that is — = .2, is equal to the resistance of 3.38 /.
R
The reduction of pressure produced by elbows, tees and globe valves
is also taken account of by the addition of an equivalent length to the
length of straight pipe. The following table shows the additional length
required to equal the friction due to globe valves. For elbows and tees
take % of the value given in the table.
Diameter of
Additional
Diameter of
Additional
. pipe in inches
length in feet
pipe in inches
length in feet
i
2
7
44
1%
4
8
53
2
7
10
70
2l/2
10
12
88
3
13
IS
US
$i
. 16
18
143
4
20
20
162
5
28
22
181
6
36
24
200
Adiabatic Compression of Natural Gas
The following table and the curve, Fig. 130, on page 325, give the
rise in temperature due to the adiabatic compression of natural gas.
Pi is the absolute initial and Pz the absolute final pressure, — being
therefore the ratio of compression.
is assumed to be 60° F.
The initial temperature of the gas
Adiabatic Compression of Natural Gas 325
..
P Ris<
- tempoe
; if Po
rature ^
\ * i
Rise in
temperature
°F.
P2
PI
Rise in
temperature
op
i.
I:5 l
2.5 i]
3. i;
3.5 ^
4. I'
4-5 15
5- 2]
5-5 2;
o° 6.
J7 6.5
52 7.
o 7-5
55 8.
7 8.5
7 9-
>4 10.
0 II.
>4 12.
238°
251
263
274
285
296
305
324
34i
357
14-
16.
18.
20.
25.
30.
35-
40.
45-
50.
386°
412
435
456
503
543
578
609
638
664
600°
o
550
600
450°
400°
U.
O
Ul
C 0
•2 350
Q.
£ 300°
Z
8 250°
200°
150°
100°
60°
S
s>
^
^
^
^
/
. '
f
2
jr
~£_
/
^
,?
~j_
It
1
7
f
/ .
. i
-jf.-
j
7
_I
5
10 15 20 25 30 35 40
RATIO OF COMPRESSION^-
Fig. 130
326 Steam
STEAM
Properties PAGE
Temperature and Pressure 327
The Heat-unit 327
Total Heat of Water 327
Latent Heat of Steam 327
Total Heat of Saturated Steam 327
Specific Heat of Saturated Steam 328
Volume of Saturated Steam 328
Absolute Zero 328
Mechanical Equivalent of Heat 328
Table of Properties of Saturated Steam 329
Factors of Evaporation 333
Superheated Steam
Volume 337
Specific Heat 337
Advantages of Superheating 338
Table of Properties 339
Flow of Steam
Flow of Steam from Orifices 341
Flow of Steam into the Atmosphere 341 .
Flow of Steam in Pipes 342
Flow in Low-pressure Heating Lines 345
Resistance due to Entrance, Bends and Valves 346
Expansion of Steam Pipes 346
Sizes of Steam Pipes for Engines 347
Loss of Heat from Steam Pipes
Loss of Heat from Bare Steam Pipes 348
Condensation in Bare Steam Pipes 348
Steam Pipe Coverings 348
Steam 327
STEAM
The Temperature of Steam in contact with water depends upon the
pressure under which it is generated. At the ordinary atmospheric
pressure (14.7 pounds per square inch) its temperature is 212° F, As
the pressure is increased, as when steam is generated in a closed vessel,
its temperature, and that of the water in its presence, increases.
Saturated Steam is steam in its normal state, that is, steam whose
temperature is that due to its pressure; by which is meant steam at the
same temperature as that of the water from which it was generated
and upon which it rests.
Superheated Steam is steam at a temperature above that due to its
pressure.
Dry Steam is steam which contains no moisture. It may be either
saturated or superheated.
Wet Steam is steam containing free moisture in the form of spray
or mist. It has the same temperature as dry saturated steam of the
same pressure.
Water introduced into superheated steam will be vaporized until
the steam becomes saturated, and its temperature becomes that due to
its pressure. Cold water, or water at a lower temperature than that
of the steam, introduced into saturated steam, will condense some of it,
thus lowering both the temperature and pressure of the rest until the
temperature again equals that due to its pressure.
The Heat-unit, or British Thermal Unit. The old definition of
the heat-unit (Rankine), viz., the quantity of heat required to raise
the temperature of i pound of water i° F., at or near its temperature
of maximum density (39.1° F.), is now no longer used. Peabody de-
fines it as the heat required to raise a pound of water from 62° to 63° F.,
and Marks and Davis as of the heat required to raise i pound of
180
water from 32° to 212° F. By Peabody's definition the heat required
to raise i pound of water from 32° to 212° is 180.3 instead of 180 units,
and the heat of vaporization at 212° is 969.7 instead of 970.4 units.
The Total Heat of the Water is the number of British thermal
units needed to raise one pound of water from 32° F. to the boiling point,
under the given pressure.
The Latent Heat of Steam or Heat of Vaporization is the num-
ber of British thermal units required to convert one pound of water,
at the boiling point, into steam of the same temperature.
The Total Heat of Saturated Steam is the number of heat-units
required to raise a pound of water from 32° F. to the boiling point, at
the given pressure, plus the number required to convert the water at
that temperature into steam of the same temperature.
328 Steam
The total heat in steam (above 32°) includes three elements:
First. The heat required to raise the temperature of the water to
the temperature of the steam.
Second. The heat required to evaporate the water at that temper-
ature, called internal latent heat.
Third. The latent heat of volume, or the external work done by the
steam in making room for itself against the pressure of the superincum-
bent atmosphere (or surrounding steam if enclosed in a vessel).
The sum of the last two elements is the latent heat of steam.
The following shows the heat required to generate one pound of steam
from water at 32° F.:
Heat-units
Sensible heat, to raise the water from 32° to 212° = 180.0
Latent heat, i, of the formation of steam at 212° = 897.6
2, of expansion against the atmos-
pheric pressure, 2116 pounds per
square foot X 26.79 cubic feet =
56 688 foot-pounds -T- 778 = 72.8 970.4
Total heat above 32° F 1150.4
Specific Heat of Saturated Steam. When a unit weight of satu-
rated steam is increased in temperature and in pressure, the volume
decreasing so as to keep it saturated, the specific heat is negative, and
decreases as the temperature increases.
Volume of Saturated Steam. The values of specific volume o!
saturated steam as given in the Properties of Saturated Steam are com-
puted by Clapyron's equation.
Absolute Zero. The value of the absolute zero has been variously
given as from 459.2 to 460.66 degrees below the Fahrenheit zero. Marks
and Davis,, comparing the results of Berthelot (1903), Buckingham
(1907), and Rose-Innes (1908), give as the most probable value
—459.64° F. The value —460° is close enough for all engineering
calculations.
The Mechanical Equivalent of Heat. The value generally accepted,
based on Rowland's experiments, is 778 foot-pounds. Marks and Davis
give the value 777.52 standard foot-pounds, based on later experiments,
and on the value of g = 980.665 centimeters per second2 = 32.174 feet
per second2, fixed by international agreement (1901). These values of
the absolute zero and of the mechanical equivalent of heat have been
used by Marks and Davis in the computation of their steam tables.
In refined investigations involving the value of the mechanical equiva-
lent of heat, the value of g for the latitude in which the experiments are
made must be considered.
Properties of Saturated Steam 329
Properties of Saturated Steam
(Condensed by Kent from Marks and Davis's Steam Tables.
"o
$
Total heat
«
o
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1^
£.15
above 32° F.
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29.74
0.0886
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1073.4
1073.4
3294.
0.000304
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2.1832
29.67
0.1217
40
8.05
1076 . 9
1068.9
2438.
0.000410
0.0162
2.1394
29.56
0.1780
5o
18.08
1081.4
1063.3
1702.
0.000587
0.0361
2.0865
29.40
0.2562
60
28.08
1085.9
1057.8
1208.
0.000828
0.0555
2.0358
29.18
0.3626
70
38.06
1090.3
1052.3
871.
0.001148
0.0745
.9868
28.89
0.505
80
48.03
1094.8
1046.7
636.8
0.001570
0.0932
.9398
28.50
0.696
90
58.00
1099.2
1041.2
469.3
0.002131
0.1114
.8944
28.00
0.946
100
67.97
1103.6
1035.6
350.8
0.002851
0.1295
.8505
27.88
I
101.83
69.8
1104.4
1034.6
333.0
0.00300
0.1327
.8427
25.85
2
126.15
94-0
1115.0
I02I.O
173-5
0.00576
0.1749
.7431
23.81
3
141.52
109.4
II2I.6
1012.3
118.5
0.00845
0.2008
.6840
21.78
4
I53.oi
120.9
1126.5
1005-7
90.5
0.01107
0.2198
.6416
19.74
5
162.28
130.1
H39-5
1000.3
73-33
0.01364
0.2348
.6084
17.70
6
170.06
137-9
II33-7
995-8
61.89
o. 01616
0.2471
.5814
15.67
7
176.85
144-7
1136.5
991-8
53.56
0.01867
0.2579
.5582
13.63
8
182.86
150.8
1139-0
988.2
47-27
0.02115
0.2673
.5380
II. 60
9
188.27
156.2
1141.1
985.0
42.36
0.02361
0.2756
.5202
9.56
10
193.22
161.1
II43- I
982.0
38.38
0.02606
0.2832
.5042
7-52
ii
197-75
165.7
II44-9
979-2
35-10
0.02849
0.2902
.4895
5-49
12
201.96
169.9
1146.5
976.6
32.36
0.03090
0.2967
.4760
3-45
13
205.87
173-8
1148.0
974-2
30.03
0.03330
0.3025
.4639
1.42
14
209.55
177-5
II49-4
971-9
28.02
0.03569
0.3081
.4523
Lbs.
gage
14.70
212.0
180.0
1150.4
970.4
26.79
0.03732
0.3118
• 4447
0.3
15
213.0
181.0
1150.7
969.7
26.27
0.03806
0.3133
.4416
1.3
16
216.3
184.4
1152.0
967.6
24-79
0.04042
0.3183
• 4311
2.3
17
219.4
187.5
H53.I
965.6
23.38
0.04277
0.3229
• 4215
3-3
18
222.4
190.5
1154.2
963.7
22.16
0.04512
0.3273
• 4127
4-3
19
225.2
193-4
II55-2
961.8
21.07
0.04746
0.3315
• 4045
5-3
20
228.0
196.1
1156.2
960.0
20.08
0.04980
0.3355
.3965
6.3
21
230.6
198.8
II57-I
958.3
19.18
0.05213
0.3393
.3887
7-3
22
233.1
201.3
1158.0
956.7
18.37
0.05445
0.3430
.3811
8.3
23
235-5
203.8
1158.8
955-1
17.62
0.05676
0.3465
• 3739
9-3
24
237-8
206.1
H59.6
953-5
16.93
0.05907
0.3499
.3670
10.3
25
240.1
208.4
1160.4
952.0
16.30
0.0614
0.3532
.3604
ii. 3
26
242.2
210.6
1161.2
950.6
15.72
0.0636
0.3564
• 3542
12.3
27
244.4
212.7
1161.9
949-2
15.18
0.0659
0.3594
.3483
13-3
28
246.4
214-8
1162.6
947-8
14.67
0.0682
0.3623
• 3425
14-3
29
248.4
216.8
1163.2
946.4
14.19
0.0705
0.3652
.3367
15-3
30
250.3
218.8
1163.9
945.1
13-74
0.0728
0.3680
• 33II
16.3
31
252.2
22O.7
1164.5
943-8
13.32
0.0751
0.3707
•3357
330 Properties of Saturated Steam
Properties of Saturated Steam (Continued;
(Condensed by Kent from Marks and Davis's Steam Tables.)
o>
Total heat
o5
o
0?
tj
<u
above 32 °F.
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17-3
32
254.1
222.6
II65.I
942.5
12.93
0.0773
0.3733
.3205
18.3
33
255.8
224.4
II65.7
941-3
12.57
0.0795
0.3759
.3155
19-3
34
257.6
226.2
II66.3
940.1
12.22
0.0818
0.3784
.3107
20.3
35
259.3
227.9
II66.8
938.9
11.89
0.0841
0.3808
.3060
21.3
36
261.0
229.6
II67.3
937-7
11.58
0.0863
0.3832
.3014
22.3
37
262.6
231.3
II67.8
936.6
11.29
0.0886
0.3855
.2969
23.3
38
264.2
232.9
II68.4
935-5
II. OI
0.0908
0.3877
.2925
24.3
39
265.8
234.5
II68.9
934-4
10.74
0.0931
0.3899
.2882
25.3
40
267.3
236.1
II69.4
933-3
10.49
0.0953
0.3920
.2841
26.3
41
268.7
237.6
II69.8
932.2
10.25
0.0976
0.3941
.2800
27.3
42
270.2
239-1
H70.3
931.2
10.02
0.0998
0.3962
.2759
28.3
43
271.7
240.5
II70.7
930.2
9.80
O.IO2O
0.3982
.2720
29.3
44
273.1
242.0
II7I.2
929.2
9.59
0.1043
0.4002
.2681
30.3
45
274.5
243-4
II7I.6
928.2
9-39
0.1065
0.4021
.2644
31-3
46
275.8
244-8
II72.O
927.2
9.20
0.1087
0.4040
.2607
32.3
47
277.2
246.1
II72.4
926.3
9.02
0.1109
0.4059
.2571
33-3
48
278.5
247-5
II72.8
925.3
8.84
0.1131
0.4077
- .2536
34-3
49
279.8
248.8
II73-2
924.4
8.67
O.H53
0.4095
.2502
35-3
50
281.0
25O.I
H73.6
923.5
8.51
0.1175
0.4113
.2468
36.3
51
282.3
251.4
II74.0
922.6
8.35
O.U97
0.4130
.2435
37-3
52
283.5
252.6
H74.3
921.7
8.20
0.1219
0.4147
.2402
38.3
53
284.7
253-9
II74-7
920.8
8.05
0.1241
0.4164
.2370
39-3
54
285.9
255-1
II75.0
919.9
7-91
0.1263
0.4180
.2339
40.3
55
287.1
256.3
II75-4
919.0
7-78
0.1285
0.4196
.2309
41-3
56
288.2
257-5
II75-7
918.2
7-65
0.1307
0.4212
.2278
42.3
57
289.4
258.7
II76.0
917.4
7-52
0.1329
0.4227
.2248
43-3
58
290.5
259-8
II76.4
916.5
7-40
0.1350
0.4242
.2218
44-3
59
291.6
26l.O
II76.7
915.7
7.28
0.1372
0.4257
.2189
45-3
60
292.7
262.1
II77-0
914.9
7.17
0.1394
0.4272
.2160
46.3
61
293.8
263.2
II77-3
914.1
7.06
0.1416
0.4287
.2132
47-3
62
294.9
264.3
II77-6
913.3
6.95
0.1438
0.4302
.2104
48.3
63
295.9
265.4
II77-9
912.5
6.85
0.1460
0.4316
.2077
49.3
64
297.0
266.4
II78.2
911.8
675
0.1482
0-4330
.2050
50.3
65
298.0
267.5
II78.5
911.0
6.65
0.1503
0.4344
.2024
51-3
66
299.0
268.5
II78.8
910.2
6.56
0.1525
0.4358
.1998
52.3
67
300.0
269.6
II79-0
909.5
6.47
0.1547
0.4371
.1972
53-3
68
301.0
27O.6
II79-3
908.7
6.38
0.1569
0.4385
.1946
54-3
69
302.0
271.6
II79-6
908.0
6.29
0.1590
0.4398
.1921
55-3
TO
302.9
272.6
II79-8
907.2
6.20
0.1612
0.4411
.1896
56.3
71
303.9
273-6
1180.1
906.5
6.12
0.1634
0.4424
.1872
Properties of Saturated Steam 331
Properties of Saturated Steam (Continued)
(Condensed by Kent from Marks and Davis's Steam Tables.)
CD~
Total heat
^
o
oT
P
<u"
above 32° F.
•
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57.3
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304.8
274-5
1180.4
905.8
6.04
0.1656
0.4437
.1848
58.3
73
305.8
275-5
1180.6
905.1
5.96
0.1678
o. 4449
.1825
59.3
74
306.7
276.5
1180.9
904.4
5.89
0.1699
0.4462
.1801
60.3
75
307.6
277.4
1181.1
903-7
5.8i
0.1721
0.4474
.1778
61.3
76
308.5
278.3
1181.4
903.0
5-74
0.1743
0.4487
.1755
62.3
77
309.4
279.3
1181.6
902.3
5.67
0.1764
0.4499
.1732
63.3
78
310.3
280.2
1181.8
901.7
5.6o
0.1786
0.45H
.1710
64.3
79
3H. 2
281.1
1182.1
901.0
5-54
0.1808
0.4523
.1687
65.3
80
312.0
282.0
1182.3
900.3
5-47
0.1829
0.4535
.1665
66.3
81
312.9
282.9
1182.5
899.7
5-41
0.1851
0.4546
.1644
67-3
82
313.8
283.8
1182.8
899.0
5-34
0.1873
0.4557
1623
68.3
83
314.6
284.6
1183.0
898.4
5.28
0.1894
0.4568
.1602
69.3
84
315.4
285.5
1183.2
897.7
5.22
0.1915
0.4579
1581
70.3
85
316.3
286.3
1183.4
897.1
5.16
0.1937
0.4590
.1561
71-3
86
317.1
287.2
1183.6
896.4
5-10
0.1959
0.4601
.1540
72.3
87
317.9
288.0
1183.8
895.8
5-05
0.1980
0.4612
1520
73.3
88
318.7
288.9
1184.0
895.2
S.oo
O.20OI
0.4623
1500
74-3
89
319.5
289.7
1184.2
894.6
4-94
0.2023
0.4633
.1481
75-3
90
320.3
290.5
1184.4
893.9
4.89
0.2044
0.4644
.1461
76.3
91
321.1
291.3
1184.6
893.3
4.84
0.2065
0.4654
.1442
77-3
92
321.8
292.1
1184.8
892.7
4-79
0.2087
0.4664
.1423
78.3
93
322.6
292.9
1185.0
892.1
4-74
0.2109
0.4674
.1404
79-3
94
323.4
293-7
1185.2
891.5
4.69
0.2130
0.4684
.1385
80.3
95
324.1
294-5
1185.4
890.9
4.65
0.2151
0.4694
.1367
81.3
96
324.9
295-3
1185.6
890.3
4.60
0.2172
o . 4704
.1348
82.3
97
325.6
296.1
1185.8
889.7
4.56
0.2193
0.4714
.1330
83-3
98
326.4
296.8
1186.0
889.2
4-51
0.2215
0.4724
.1312
84.3
99
327.1
297.6
1186.2
888.6
4-47
0.2237
0.4733
.1295
85-3
100
327.8
298.3
1186.3
888.0
4-429
o 2258
0.4743
.1277
87-3
102
329.3
299-8
1186.7
886.9
4.347
0.2300
0.4762
.1242
89-3
104
330.7
301.3
1187.0
885.8
4.268
0.2343
0.4780
.1208
9L3
106
332.0
302.7
1187.4
884.7
4-192
0.2336
0.4798
.1174
93 3
108
333 4
304.1
1187.7
883.6
4.118
o . 2429
0.4816
.1141
95-3
IO
334.8
305.5
1188.0
882.5
4.047
0.2472
o . 4834
.1108
97-3
12
336.1
306.9
1188.4
881.4
3.978
0.2514
0.4852
.1076
99-3
14
337-4
308.3
1188.7
880.4
3-912
0.2556
0.4869
.1045
101.3
16
338.7
309.6
1189.0
879-3
3.848
0.2599
0.4886
.1014
103.3
18
340.0
311.0
1189.3
878.3
3-786
0.2641
0.4903
.0984
105-3
20
341-3
312.3
1189.6
877.2
3.726
0.2683
0.4919
.0954
107-3
22
342.5
313.6
1189.8
876.2
3.668
0.2726
0.4935
.0924
332 Properties of Saturated Steam
Properties of Saturated Steam (Continued)
(Condensed by Kent from Marks and Davis's Steam Tables.)
0?
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Total heat
above 32° F.
tu
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314.9
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3.611
0.2769
0.4951
1.0895
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126
345-0
316.2
II90.4
874.2
3-556
0.2812
0.4967
1.0865
113 3
128
346.2
317.4
II90.7
873.3
3.504
0.2854
0.4982
1.0837
US 3
130
347-4
318.6
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872.3
3-452
0.2897
0.4998
1.0809
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348.5
319.9
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871.3
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0.2939
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0.3023
0.5043
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138
352.0
323.4
II92.O
868.5
3.263
0.3065
0.5057
1.0702
125-
140
353-1
324.6
II92.2
867.6
3.219
0.3107
0.5072
1.0675
127.
142
354-2
325.8
H92.5
866.7
3-175
0.3150
0.5086
1.0649
129.
144
355-3
326.9
II92.7
865.8
3-133
0.3192
0.5100
1.0624
131.
146
356.3
328.0
II92.9
864.9
3.092
0.3234
0.5114
1.0599
133-
148
357-4
329.1
II93-2
864.0
3-052
0.3276
0.5128
1.0574
135-
150
358.5
330.2
II93-4
863.2
3.012
0.3320
0.5142
1.0550
137-
152
359-5
331-4
II93-6
862.3
2-974
0.3362
0.5155
1.0525
139-
154
360.5
332.4
II93-8
861.4
2.938
0.3404
0.5169
1.0501
141.
156
361.6
333-5
II94.I
860.6
2.902
0.3446
0.5182
1.0477
143-
158
362.6
334-6
II94-3
859-7
2.868
0.3488
0.5195
1.0454
145-
160
363.6
335-6
II94-5
858.8
2.834
0.3529
0.5208
1.0431
147-
162
364.6
336.7
II94-7
858.0
2.801
0.3570
0.5220
1.0409
149-
164
365.6
337-7
II94-9
857.2
2.769
0.3612
0.5233
1.0387
151.
166
366.5
338.7
II95-I
856.4
2.737
0.3654
0.5245
1.0365
153-
168
367.5
339-7
II95-3
855.5
2.706
0.3696
0.5257
1.0343
155-
170
368.5
340.7
II95-4
854.7
2.675
0.3738
0.5269
1.0321
157-
172
369.4
341-7
II95-6
853-9
2.645
0.3780
0.5281
1.0300
159-
174
370.4
342.7
II95-8
853-1
2.616
0.3822
0.5293
1.0278
161.
176
371-3
343-7
II96.0
852.3
2.588
0.3864
0.5305
1.0257
163.
178
372.2
344-7
II96.2
851.5
2.560
0.3906
0.5317
1.0235
165.
180
373-1
345-6
II96.4
850.8
2.533
0.3948
0.5328
1.0215
167.
182
374-0
346.6
II96.6
850.0
2.507
0.3989
0.5339
1.0195
169-
184
374-9
347-6
II96.8
849.2
2.481
0.4031
0.5351
1.0174
171.
186
375-8
348.5
II96.9
848.4
2.455
0.4073
0.5362
1.0154
173-3
188
376.7
349-4
II97-I
847.7
2.430
0.4115
0.5373
I. 0134
175.3
190
377-6
350.4
II97-3
846.9
2.406
0.4157
0.5384
1.0114
177-3
192
378.5
351-3
II97-4
846.1
2.381
0.4199
0.5395
1.0095
179-3
194
379-3
352.2
II97-6
845.4
2.358
0.4241
0.5405
1.0076
181.3
196
380.2
353-1
II97-8
844.7
2.335
0.4283
0.5416
1.0056
183.3
198
381.0
354-0
II97-9
843.9
2.312
0.4325
0.5426
1.0038
185.3
200
381.9
354-9
II98.I
843.2
2.290
0.437
0.5437
1.0019
190.3
205
384.0
357-1
II98.5
841.4
2.237
0.447
0.5463
0.9973
Properties of Saturated Steam 333
Properties of Saturated Steam (Concluded)
(Condensed by Kent from Marks and Davis 's Steam Tables.)
£*-;iq
ID*
®4*
Total heat
above 32° F.
^
f-
Is
V
*o o
S & c
£ ^J
ss
^
g
JaT'S
3^ g
M "I'd
*o **
•ll
4) 3 a
llg
til
!i
rt ^
Sgl
far!
Ij|
rt^.a
is*
II1
felS
f3
O o
"a «J
0
$
H
+> ol
-t-> 0)
M
^H *«H
o
fc»-
m
*
a ^H
rt -3
»— 1
195.3
2IO
386.0
359-2
II98.8
839.6
2.187
0.457
0.5488
0.9928
200.3
215
388.0
361.4
II99.2
837.9
2.138
0.468
0.5513
0.9885
205.3
22O
389.9
363.4
II99.6
836.2
2.091
0.478
0.5538
0.9841
210.3
225
391-9
365.5
II99.9
834.4
2.046
0.489
0.5562
0.9799
215.3
230
393-8
367.5
1200.2
832.8
2.004
0.499
0.5586
0.9758
220.3
235
395.6
369-4
1200.6
83I.I
1.964
0.509
0.5610
0.9717
225.3
240
397-4
371-4
I20O.9
829.5
1.924
0.520
0.5633
0.9676
230.3
245
399-3
373.3
I20I.2
827.9
1.887
0.530
0.5655
0.9638
235.3
250
401.1
375-2
1201 . 5
826.3
.850
0.541
0.5676
0.9600
245.3
260
404-5
378.9
I2O2.I
823.1
.782
0.561
0.5719
0.9525
265.3
270
280
407.9
411.2
382.5
386.0
1202.6
I2O3.I
820.1
8I7.I
.718
.658
0.582
0.603
0.5760
0.5800
0.9454
0.9385
275.3
290
414.4
389.4
1203.6
814.2
.602
0.624
0.5840
0.9316
285.3
300
417.5
392.7
I204.I
8II.3
.551
0.645
0.5878
0.9251
295.3
420.5
395-9
1204.5
808.5
.502
0.666
0.5915
0.9187
305.3
320
423-4
399-1
1204.9
805.8
.456
0.687
0.5951
0.9125
315.3
330
426.3
402.2
1205.3
803.1
.413
0.708
0.5986
0.9065
325.3
340
429.1
405-3
1205.7
800.4
.372
0.729
0.6020
0.9006
335-3
350
431-9
408.2
I2O6. I
797-8
.334
o.75o
0.6053
0.8949
345-3
36o
434-6
4H. 2
1206.4
795-3
.298
0.770
0.6085
0.8894
355-3
370
437-2
414-0
1206. 8
792.8
.264
0.791
0.6116
0.8840
365.3
38o
439.8
416.8
1207.1
790.3
.231
0.812
0.6147
0.8788
375-3
390
442.3
419.5
1207.4
787.9
.200
0.833
0.6178
0.8737
385.3
400
444-8
422.
1208.
786.
.17
0.86
0.621
0.868
435-3
450
456.5
435.
1209.
774-
.04
0.96
0.635
0.844
485.3
500
467.3
448.
1210.
762.
.93
i. 08
0.648
0.822
535-3
550
477-3
459-
I2IO.
751-
-83
1.20
0.659
0.801
585.3
600
486.6
469.
1210.
741-
• 76
1.32
0.670
0.783
Factors of Evaporation
The factors in the following table, which has been condensed from
Kent's Mechanical Engineers' Pocket Book, were obtained, for the
various feed-water temperatures and steam pressures given, by sub-
tracting the heat above 32° in one pound of feed-water from the total
heat above 32° in one pound of steam, and dividing the remainder by
970.4, the latent heat of steam at 212°. The values of the total heat
of steam, heat of feed-water and latent heat of steam are those given
in Marks and Davis's steam tables. Intermediate values may be found
by interpolation.
334 Factors of Evaporation
Example: Given the boiler pressure =115 pounds per square inch
absolute, and the temperature of feed-water = 62° F., to find the factor
of evaporation. Look in the column headed 115 and opposite 62°;
the factor required is 1.1941. It will therefore require 1.1941 times as
many heat-units to evaporate a certain weight of water from a feed-
water temperature of 62° F. into steam under 115 pounds pressure, as
would be required to evaporate the same weight of water from a temper-
ature of 212° F. into steam at 212° F., that is, from and at 212° F.
Factors of Evaporation
Gage pres-
sure, pounds
o.3
10.3
20.3
30.3
40.3
50.3
60.3
70.3
80.3
Absolute
pressure,
15.
25-
35.
45-
55-
65-
75-
85.
95-
pounds
Temperature
of feed-water,
Factors of evaporation
32
i . 1858
I . 1958
I . 2024
1.2073
1.2113
1.2144
1.2171
1.2195 i. 2216
38
.1796
I . 1896
i . 1962
I.20II
i . 2050
i . 2082
1 . 2109
1.21331.2153
44
.1734
I . 1834
1.1900
I . 1949
1.1988
I . 2020
i . 2047
1.2071
1.2091
50
.1672
I.I772
i . 1838
1.1887
i . 1926
I • 1958
1.1985
1.2009
1.2029
56
.1610
1.1710
i . 1776
I . 1825
I . 1864
I.I896
I . 1923
I . 1947
I . 1967
62
.1548
I . 1648
1.1714 1.1763
1.1803
I - 1835
i . 1861
1.1885
1.1906
68
.1486
1.1586
i . 1652
I . 1702
1.1741
I- 1773
1.1800
I . 1823
I . 1844
74
.1425
I.I525
1.1591
I . 1640
i . 1679
1.1711
I.I738
I . 1762
I . 1782
80
.1363
1.1463
I . 1529
I . 1578
1.1618
I . 1650
I . 1676
1.1700
1.1721
86
.1301
I . 1401
I . 1467
I.I5I8
i • 1556
1.1588
1.1615
1.1638
I . 1659
92
.1240
I . 1340
i . 1406
I • 1455
i . 1494
I . 1526
i - 1553
i. 1577
I - 1597
98
.1178
I . 1278
I. 1344
I . 1393
i • 1433
I.I465
1.1491
I.I5I5
I.I536
104
.1116
1.1216
I . 1282
I . 1332
I.I37I
I.I403
i . 1430
I. 1453
I . 1474
no
.1055
I.H55
I.I22I
I . 1270
1.1309
I . 1341
1.1368
I . 1392
1.1412
116
.0993
i . 1093
I.H59
I . 1209
i . 1248
I . 1280
i . 1306
i • 1330
I . 1351
122
.0931
i . 1031
I. 1097
I. 1147
1.1186
1.1218
i . 1245
I . 1269
I . 1289
128
.0870
1.0970
I . 1036
I . 1085
I. 1124
1.1156
1.1183
I . 1207
I . 1227
134
.0808
1.0908
1.0974
I . 1023
i . 1063
I • IQ95
I.II2I
i. 1145
1.1166
140
.0746
1.0846
1.0912
1.0962
I.IOOI
I . 1033
I. I060
1.1083
1.1104
146
.0685
1.0785
1.0851
1.0900
1.0939
1.0971
1.0998
I . IO22
I . 1042
152
.0623
.0723
1.0789
.0838
.0877
1.0909
1.0936
.0960
1.0980
158
.0561
.0661
1.0727
.0776
.0816
1.0847
1.0874
.0898
1.0919
164
.0499
• 0599
1.0665
.0715
.0754
1.0786
I. 0812
.0836
1.0857
170
• 0437
.0537
1.0603
.0653
.0692
1.0724
I.075I
.0774
1.0795
I76
.0375
• 0475
1.0541
• 0591
.0630
I . 0662
1.0689
.0712
1.0733
182
•0313
.0413
1.0479
.0529
.0568
I. 0600
1.0627
-0650
1.0671
188
• 0251
•0351
1.0417
1.0467
,0506
1-0538
1.0565
.0588
1.0609
194
.0189
.0289
1-0355
1.0405
.0444
I . 0476
1.0503
.0526
1.0547
200
1.0127
1.0227
1.0293
1.0343
1.0382
1.0414
I.044I
1.0464
1.0485
206
1.0065
1.0165
1.0231
1.0281
1.0320
1.0352
1.0379
1.0402
1.0423
212
1.0003
1.0103
1.0169
I.02I8
I
1.0258
1.0290
1.0316
i . 0340
1.0361
Factors of Evaporation 335
Factors of Evaporation (Continued)
Gage pres-
sure, pounds
90.3
100.3
110.3
120.3
130.3
140.3
150.3
160.3
170.3
Absolute
pressure,
105.
115-
125-
135-
145-
155-
165.
175.
185.
pounds
Temperature
of feed- water,
Factors of evaporation
32
1.2234
.2251
I . 2266
1.2279
I . 2292
1.2304
I.23I5
i . 2324
I 2333
38
1.2172
.2188
I . 2204
1.2217
I . 2230
I . 2242
I . 2252
i . 2262
I . 2271
44
I.2IIO
.2126
1.2142
I. 2155
.2168
I . 2180
1.2190
1.2200
1.2209
So
I . 2048
.2064
I . 2080
I . 2093
.2106
I.2II8
I . 2128
I. 2137
1.2147
56
I . 1986
.2002
I . 2018
I . 2031
.2044
I . 2056
1.2066
I . 2076
1.2085
62
I . 1924
.1941
I . 1956
I . 1970
.1982
I . 1994
1.2005
I . 2014
I . 2023
68
I.I862
.1879
I . 1894
1.1908
.1920
I • 1933
I • 1943
I . 1952
I . 1961
74
I . 1801
1.1817
1.1833
i . 1846
.1859
1.1871
I . 1881
1.1890
1.1900
80
I . 1739
I . 1756
1.1771
1.1785
I. 1797
1.1809
I . 1820
I . 1829
1.1838
86
i . 1678
I . 1694
1.1710
1.1723
i • 1735
I . 1748
I.I758
1.1767
I.I776
92
1.1616
I . 1632
I . 1648
1.1661
I . 1674
I . 1686
I . 1696
I . 1705
I.I7I5
98
I - 1554
I.I57I
I . 1586
i. 1600
i. 1612
I . 1624
I.I635
I . 1644
I.I653
104
I . 1492
I . 1509
I.I525
I.I538
I.I550
1.1563
I. 1573
I . 1582
I.I592
no
1.1431
I . 1447
I . 1463
i . 1476
I . 1489
I . 1501
1.1511
1.1521
I.I530
116
1.1369
1.1386
i . 1401
1.1415
r . 1427
I • 1439
i . 1450
I . 1459
I . 1468
122
i . 1308
1.1324
I . 1340
i. 1353
I . 1365
I.I378
1.1388
I . 1397
1.1407
128
1.1246
I . 1262
I . 1278
1.1291
1.1304
1.1316
I . 1326
I • 1336
I. 1345
134
1.1184
I . 1201
1.1216
1.1230
1.1242
I. 1254
i . 1265
1.1274
I . 1283
140
1.1123
I.II39
I.II54
1.1168
1.1180
I . 1193
i . 1203
1.1212
I.I22I
146
i . 1061
1.1077
1.1093
1.1106
I.III9
1.1131
1.1141
I.II50
1.1160
152
1.0999
.1015
I . 1031
.1044
.1057
I . 1069
.1079
I.I089
1.1098
158
1.0937
.0954
1.0969
.0982
.0995
1.1007
.1018
I . 1027
i . 1036
164
1.0875
.0892
1.0907
.0921
.0933
1.0945
.0956
1.0965
1.0974
170
1.0813
.0830
1.0845
.0859
.0871
1.0883
.0894
1.0903
1.0912
176
1.0752
.0768
1.0783
.0797
.0809
1.0822
.0832
I.084I
1.0850
182
1.0690
.0706
1.0721
• 0735
• 0747
1.0760
.0770
1.0779
1.0788
188
1.0628
.0644
I. 0660
.0673
.0685
1.0698
.0708
1.0717
1.0727
194
1.0566
.0582
1.0597
.0611
.0623
1.0636
.0646
1.0655
1.0664
200
1.0504
.0520
1.0535
• 0549
.0561
1.0574
.0584
1.0593
1. 0602
206
1.0441
.0458
1.0473
.0487
.0499
1.0511
.0522
I.053I
1.0540
212
1.0379
.0396
1.0411
.0425
.0437
1.0449
.0460
1.0469
1.0478
336 Factors of Evaporation
Factors of Evaporation (Concluded)
Gage pres-
sure, pounds
180.3
190.3
200.3
210.3
220.3
230.3
240.3
250.3
Absolute
pressure,
195-
205.
215.
225.
235-
245.
255-
265.
pounds
Temperature
of feed-water,
Factors of evaporation
32
1.2342
.2351
1.2358
1.2365
1.2372
1.2378
1.2384
1.2390
38
1.2280
.2288
i . 2296
i . 2303
I . 2310
I . 2316
I . 2322
I . 2328
44
1.2218
.2226
1.2234
I . 2241
I . 2248
1.2254
1.2260
1.2266
50
c6
i . 2156
.2164
1.2171
1.2179
I. 2186
I . 2192
1.2198
I . 2204
§
62
i . 2094
1.2032
,2041
i . 2048
1.2055
1.2062
I . 2130
1.2068
I . 2136
1.2074
I .2142
I. 2080
68
i . 1971
.1979
i . 1986
I. 1993
I.2OOI
1.2007
I . 2012
I . 2019
74
1.1909
.1917
1.1924
I.I932
I- 1939
I. 1945
I • 1951
I.I957
80
1.1847
.1856
1.1863
I . 1870
I . 1877
I . 1883
I.I889
I.I895
86
1.1786
.1794
I . 1801
i. 1808
1.1816
I . 1822
I . 1827
1.1834
92
1.1724
.1732
I • 1739
I . 1747
I • 1754
1.1760
I . 1766
I . 1772
98
1.1662
.1671
I . 1678
1.1685
1.1692
1.1698
I.I704
I.I7IO
104
1.1601
.1609
1.1616
I . 1624
I . 1631
I.I637
I . 1643
1.1649
no
I . 1539
.1547
I. 1555
I . 1562
1.1569
I. 1575
I.I58I
I.I587
116
I . 1478
.1486
I. 1493
1.1500
1.1507
I.I5I4
I . 1519
I . 1525
122
1.1416
• 1424
I.I43I
I. 1439
I . 1446
I.I452
I . 1458
I . 1464
128
I. 1354
.1362
I.I370
I. 1377
1.1384
I.I390
I • 1396
I . 1402
134
1 . 1292
.1301
I . 1308
I.I3I5
I . 1322
I . 1329
I • 1334
.1340
140
1.1231
.1239
I . 1246
I . 1253
I . 1261
I . 1267
I . 1272
.1279
146
1.1169
.1177
1.1184
1.1192
I. 1199
1 . 1205
I.I2II
.1217
152
1.1107
.1115
I. 1123
1.1130
I.H37
I.II43
I.II49
.1155
158
I. 1045
.1054
I . 1061
1.1068
1.1075
I . 1081
1.1087
.1093
164
1.0984
.0992
1.0999
i. 1006
I . 1013
I . 1019
I . 1025
.1031
170
1.0922
.0930
1.0937
1.0944
1.0951
1.0958
1.0963
.0969
I76
I. 0860
.0868
1.0875
1.0882
1.0890
1.0896
1.0901
.0908
182
1.0798
.0806
1.0813
1.0820
1.0828
1.0834
1.0839
.0846
188
1.0736
.0744
1.0751
1.0758
1.0766
1.0772
1.0778
.0784
194
1.0674
.0682
1.0689
1.0696
1.0704
1.0710
1.0715
.0722
200
I. 0612
.0620
1.0627
1.0634
1.0642
1.0648
1.0653
.0660
206
1.0550
.0558
1.0565
1.0572
1.0579
1.0586
1.0591
.0597
212
1.0487
.0496
1.0503
1.0510
1.0517
1.0523
1.0529
.0535
Superheated Steam
337
SUPERHEATED STEAM
Steam in the presence of the water from which it is generated is called
"saturated steam"; it has the same temperature as the water, and can
have only one pressure and one density at any given temperature —
the three are in fixed relationship to each other. Superheated steam
has a higher temperature than saturated steam at the same pressure,
and is produced by adding heat to saturated steam in a separate vessel
called a superheater. It is independent of pressure, since at any pressure
the steam may have any desired temperature. In practice the super-
heater is an extension of the steam space of the boiler, with which it is
in open communication, and the pressure of the steam in the superheater
is practically the boiler pressure.
Volume of Superheated Steam. Superheated steam is greater in
volume than saturated steam of the same pressure. Linde's equation
(1905) is
/ 1 50 300 ooo
pv = 0.5962 T-p(i + 0.0014 p) ( -—fi 0-0833
where p = pressure in pounds per square inch;
v = volume in cubic feet;
T = absolute temperature.
Specific Heat of Superheated Steam. The following table of
Knoblauch and Jakob (from Peabody's Steam Tables) gives the mean
specific heat of superheated steam from the temperature of saturation
to various temperatures at several pressures:
Kilograms
per square
I
2
4
6
8
10
12
14
16
18
20
centimeter
Pounds per
square inch
14.2
28.4
56.9
85-3
113-8
142.2
170.6
I99-I
227.5
256.0
284.4
Temperature
saturation
99
120
143
158
169
179
187
194
200
206
211
Temperature
saturation
210
248
289
316
336
354
369
381
392
403
412
212
100
0.463
302
150
.462
• 478
.515
392
200
.462
• 475
.502
.530
.560
.597
.635
.677
482
250
.463
• 474
.495
.514
.532
• 552
.570
.588
.609
.635
.664
572
300
.464
.475
.492
.505
.517
.530
• 541
.550
.561
.572
.585
662
350
.468
• 477
.492
.503
.512
.522
.529
.536
.543
.550
• 557
752
400
.473
.481
• 494
.504
.512
.520
.526
.531
.537
.542
.547
338 Superheated Steam
Thus the mean specific heat of steam at 142.2 pounds pressure when
superheated to 572° F. is 0.53. The heat required to raise i pound of
steam from a saturation temperature of 354° to 572° is (572 — 354)
0.53 = H5-5 B.T.U. The total heat of the superheated steam is the
sum of this quantity and the heat in the saturated steam. It is given
directly in the properties of superheated steam for various degrees of
superheat, pages 339 and 340.
Advantages of Superheating. The advantage to be gained by
superheating is not due to increased thermodynamic efficiency. The
economy which results from the application of superheat is due to the
reduction of the internal thermal waste of the engine, incident to cylin-
der condensation. The steam entering the cylinder strikes the walls,
which have been cooled by the previous exhaust. The heat necessary
to warm the walls to the temperature of the entering steam can be
supplied only by the steam, and if it is saturated some of it must be
condensed. If the steam is superheated it must be reduced to the
temperature of saturated steam at the given pressure, before conden-
sation takes place.
Superheating is superior to any other known means of reduction of
this internal waste. The saving due to its use is found to be greater
with engines that are most inefficient with saturated steam; small
engines profit more by it than large, slow engines more than fast, and
single engines more than multiple expansion engines.
Properties of Superheated Steam 339
Properties of Superheated Steam
(Condensed by Kent from Marks and Davis's Steam Tables.)
V= specific volume in cubic feet per pound; H= total heat, from water at
32° F. in B.T.U. per pound; N = entropy, from water at 32°.
Pres-
sure abso-
Temper-
Degrees of superheat
lute, Ibs.
ature
per
sq. inch
saturated
steam
0
20
50
IOO
150
20
228.0
V 20.08
20.73
21.69
23.25
24.80
H 1156.2
1165.7
II79-9
1203.5
1227.1
N 1.7320
I • 7456
I . 7652
I . 7961
1.8251
40
267.3
V 10.49
10.83
H.33
12.13
12.93
H 1169.4
"79 -3
1194.0
1218.4
1242.4
N 1.6761
1.6895
1.7089
1.7392
I . 7674
60
292.7
v 7.17
7-40
7-75
8.30
8.84
H 1177.0
1187.3
1202.6
1227.6
1252.1
N 1.6432
1.6568
I . 6761
I . 7062
I • 7342
80
312.0
V 5-47
5-65
5-92
6.34
6-75
H 1182.3
H93.0
1208.8
1234-3
1259-0
N 1.6200
1.6338
1.6532
1.6833
1.7110
IOO
327.8
V 4-43
4-58
4-79
5-14
5-47
H 1186.3
II97-5
I2I3.8
1239-7
1264.7
N 1.6020
i. 6160
1.6358
1.6658
1.6933
120
341-3
V 3.73
3-85
4-04
4-33
4.62
H 1189.6
1201 . I
I2I7.9
1244.1
1269.3
N 1.5873
I. 6oi6
I.62I6
1.6517
1.6789
140
353-1
V 3-22
3-32'
3-49
3-75
4.00
H 1192.2
1204.3
1221.4
1248.0
1273-3
N 1.5747
1.5894
1.6096
1.6395
1.6666
160
363.6
V 2.83
2.93
3-07
3-30
3-53
H II94-5
1207.0
1224.5
I25L3
1276.8
N 1.5639
1.5789
1-5993
1.6292
i . 6561
180
373.1
V 2.53
2.62
2.75
2.96
3-i6
H 1196.4
1209.4
1227.2
1254.3
1279.9
N 1.5543
1.5697
1-5904
I . 6201
1.6468
200
381.9
V 2.29
2.37
2.49
2.68
2.86
H 1198.1
I2II.6
1229.8
1257.1
1282.6
N 1.5456
1.5614
1.5823
1.6120
1.6385
220
389.9
V 2.09
2.16
2.28
2.45
2.62
H 1199.6
1213.6
1232 . 2
1259-6
1285.2
N 1.5379
1.5541
1.5753
1.6049
I . 6312
240
397-4
V 1.92
1.99
2.09
2.26
2.42
H 1200.9
1215.4
1234-3
1261.9
1287.6
N 1.5309
1.5476
1.5690
1.5985
I . 6246
260
404.5
F 1.78
1.84
1.94
2.10
2.24
# 1202. I
1217.1
1236.4
1264 . I
1289 . 9
N 1.5244
1.5416
1.5631
1.5926
I. 6186
280
4II.2
V 1.66
1.72
1.81
1.95
2.09
H 1203.1
1218.7
1238 . 4
1266.2
1291.9
AT 1.5185
1.5362
i.558o
1.5873
I.6I33
300
417.5
F 1.55
1. 00
1.69
1.83
1.96
H 1204.1
1220.2
1240.3
1268.2
1294.0
.ZV 1.5129
I-53IO
1.5530
1.5824
1.6082
400
444-8
V 1. 17
1. 21
1.28
1.40
1.50
# 1207.7
1227 . 2
1248.6
1276.9
1303.0
A/" 1.4894
I.5I07
1.5336
1.5625
1.5880
500
467.3
V 0.93
0.97
1.03
1. 13
1.22
77 1210
1233
1256
1285
I3II
A/" 1.470
1.496
I.5I9
1.548
1.573
340 Superheated Steam
Properties of Superheated Steam (Concluded)
(Condensed by Kent from Marks and Davis's Steam Tables.)
V= specific volume in cubic feet per pound; H= total heat, from water at
32° F. in B.T.U. per pound; N= entropy, from water at 32°.
Pres-
sure abso-
Temper-
Degrees of superheat
lute, Ibs.
ature
per
sq. inch
saturated
steam
200
250
300
400
500
20
228.0
V 26.33
27-85
29.37
32.39
35-40
H 1250.6
1274.1
1297.6
1344-8
1392.2
N 1.8524
1.8781
1.9026
1-9479
1.9893
40
267.3
V 13.70
14.48
15.25
16.78
18.30
H 1266.4
1290.3
1314-1
1361.6
1409.3
N 1.7940
1.8189
1.8427
1.8867
1.9271
60
292.7
V 9.36
9.89
10.41
11.43
12.45
H 1276.4
1300.4
1324.3
1372.2
1420.0
N 1.7603
1.7849
I. 8081
1.8511
1.8908
80
312.0
V 7-17
7.56
7-95
8.72
9 49
H 1283.6
1307.8
I33I-9
1379 8
1427.9
N 1.7368
i . 7612
I . 7840
1.8265
1.8658
ICO
327.8
V 5.80
6.12
6.44
7-07
7-69
H 1289.4
1313-6
1337.8
1385.9
I434-I
N 1.7188
1.7428
1.7656
1.8079
1.8468
1 20
34L3
V 4.89
5-17
5-44
5-96
6.48
H 1294.1
1318.4
1342.7
I39I.O
1439-4
N 1.7041
1.7280
1.7505
1.7924
1.8311
140
353-1
V 4-24
4.48
4-71
5.16
5.6i
H 1298.2
1322.6
1346.9
1395-4
1443-8
N 1.6916
1.7152
1.7376
1.7792
1.8177
-160
363.6
V 3-74
3-95
4-15
4.56
4-95
H 1301.7
1326.2
1350.6
1399-3
1447-9
N 1.6810
1.7043
1.7266
1.7680
1.8063
180
373-1
V 3.35
3-54
3-72
4-09
4-44
H 1304.8
1329.5
1353-9
1402.7
I45I-4
N 1.6716
1.6948
1.7169
I.758I
1.7962
200
381.9
V 3.04
3.21
3-38
3-71
4-03
H 1307.7
1332.4
1357-0
1405.9
1454-7
N 1.6632
1.6862
1.7082
1.7493
1.7872
220
389.9
V 2.78
2.94
3.10
3-40
3-69
H 1310.3
I335-I
1359-8
1408.8
1457-7
N 1.6558
1.6787
1.7005
I.74I5
1.7792
240
397-4
F 2.57
2.71
2.85
3-13
3-40
H 1312.8
1337-6
1362.3
I4II.5
1460.5
AT" 1.6492
I . 6720
1.6937
1.7344
I.772I
260
404.5
V 2.39
2.52
2.65
2.91
3-i6
# 1315.1
1340.0
1364.7
1414.0
1463.2
AT 1.6430
1.6658
1.6874
1.7280
1.7655
280
411.2
F 2.22
2.35
2.48
2.72
2.95
H 1317-2
1342.2
1367.0
1416.4
1465.7
A7 1.6375
1.6603
i. 6818
1.7223
1-7597
300
417.5
V 2.09
2.21
2-33
2.55
2.77
# 1319.3
1344-3
1369.2
1418.6
1468.0
N 1.6323
1.6550
1.6765
1.7168
I.754I
400
444-8
F i. 60
1.70
1.79
i 97
2.14
H 1328.6
1353-9
I379-I
1429.0
1478.9
AT 1.6117
1.6342
1.6554
1.6955
1.7323
500
467.3
F i. 31
1.39
1.47
1.62
1.76
H 1337
1362
1388
1438
1489
N 1.597
1.619
1.640
1.679
I.7I5
Flow of Steam 341
FLOW OF STEAM
Flow of Steam from Orifices. The flow of steam of a higher
pressure toward a lower pressure increases as the difference of pressure
is increased, until the external pressure becomes only 58 per cent of the
absolute initial pressure. Any further reduction of the external pres-
sure, even to the extent of a perfect vacuum, neither increases nor dimin-
ishes the flow of steam. In flowing through a nozzle of the best form,
the steam expands to the external pressure and to the volume corre-
sponding to this pressure, so long as it is not less than 58 per cent of the
internal pressure. For an external pressure of 58 per cent or less, the
ratio of expansion is 1.624.
The following formula is frequently used to determine the flow of
steam through an orifice against a pressure greater than 58 per cent
of the discharge:
W=i.gAK\/(P-d)d,
where
W = weight discharged in pounds per minute;
A = area of orifice in square inches;
P = absolute initial pressure in pounds per square inch;
d = difference in pressure between the two sides, in pounds per
square inch;
K = coefficient = .93 for a short pipe = .63 for a hole in a thin plate.
Flow of Steam into the Atmosphere. When steam of varying
initial pressure is discharged into the atmosphere — the atmospheric
pressure being not more than 58 per cent of the initial pressure — the
velocity of outflow at constant density, that is, supposing the initial
density to be maintained, is given by the formula,
V = 3-5953 V^A,
where V = the velocity of outflow in feet per second, as for steam of the
initial density, and h = the height in feet, of a column of steam of the
given initial pressure, the weight of which is equal to the pressure on
the unit of base.
The lowest initial pressure to which this formula applies, when steam
is discharged into the atmosphere, is 25.37 pounds per square inch.
The following table gives the outflow of steam into the atmosphere
for various internal pressures. The velocity of steam above 25.37 pounds
per square inch absolute pressure, increases very slowly with the pres-
sure, because the density, and the weight to be moved, increase with the
pressure. An average of 900 feet per second may, for approximate cal-
culations, be taken for the velocity of outflow as for constant density,
that is, taking the volume of the steam at the initial volume.
342
Flow of Steam
Outflow of Steam into the Atmosphere
(D. K. Clark.)
Initial
pressure,
pounds per
square inch
absolute
External
pressure,
pounds per
square inch
absolute
Expansion
in nozzle,
ratio
Velocity of
outflow at
constant
density,
feet per
second
Actual
velocity of
outflow
expanded,
feet per
second
Discharge,
pounds
per square
inch per
minute
25-37
14.7
.624
863
1401
22.81
30
14.7
.624
867
1408 .
26.84
40
14-7
.624
874
1419
35-18
45
14.7
.624
877
1424
39.78
50
14-7
.624
880
1429
44-06
60
14.7
.624
885
1437
52.59
70
14-7
.624
889
1444
61.07
75
14-7
.624
891
1447
65.30
90
14-7
.624
895
1454
77-94
100
14-7
.624
898
1459
86.34
US
14-7
.624
902
1466
98.76
135
14-7
.624
906
1472
115.61
155
14.7
.624
910
1478
132.21
165
14-7
.624
912
1481
140.46
215
14 7
.624
919
1493
181.58
Napier's approximate formula for the outflow of steam into the atmos-
phere, when the pressure of the atmosphere receiving the steam is less
than 58 per cent of the initial pressure, is W = ap -r 70, where W is
weight discharged, in pounds per second, a = area of orifice in square
inches, and p = absolute initial pressure in pounds per square inch.
Flow of Steam in Pipes. The most generally accepted formula
for the flow of steam in pipes is
w(pi —
Pi-l
-- 0.000132
/ 3.6\TF2L
I+-T — F
\ d j wdb
where W
Pi
weight of steam in pounds per minute;
initial pressure in pounds per square inch;
pz = final pressure in pounds per square inch;
L = length of pipe in feet;
d = inside diameter of pipe in inches;
w = density of steam in pounds per cubic foot.
The quantity of steam flowing with a given drop in pressure may be
calculated by formula (i), while the drop for a given flow may be
obtained from formula (2). The following table computed by E. C.
Sickles (Trans. A. S. M. E., XX, 354) is calculated by a .formula which,
Flow of Steam in Pipes 343
when reduced to a form similar to that of formula (i), gives a coefficient
87.45 instead of 87.
Table I gives the discharge in pounds per minute for pipes of various
diameters corresponding to drops of pressure as given in Table II.
The drops of pressure are computed for a length of i ooo feet; for any
other length the drop is proportional to the length divided by 1000.
In using the table the absolute pressure should be taken as the mean
of the initial and final pressures in computing the carrying capacity.
Table I. — Steam in Pounds per Minute, Corresponding to Drop in
Pressure in Table II.
Diam-
eter
24
22
20
18
16
15
14
13
12
II
10
Line
i
14 ooo
ii 188
8772
6678
4923
4163
348i
2871
2328
1853
1443
2
13 ooo
10392
8144
6203
4573
3867
3233
2667
2165
1721
1341
3
12 000
9593
7517
5724
4220
3569
2983
2461
1996
1589
1237
4
II 000
8804
6891
5247
3868
3271
2736
2256
1830
1456
"34
5
IOOOO
7992
6265
4770
3517
2974
2486
2051
1663
1324
1031
6
9500
7705
5947
4532
3341
2825
2362
1940
1580
1258
979
7
9 ooo
7205
5638
4293
3165
2676
2237
1846
1497
1192
928
8
8500
6905
5321
4054
2989
2527
2113
1743
1414
1125
876
9
8000
6506
5012
3816
2814
2379
1989
1640
1331
1059
825
10
7500
6106
4695
3577
2638
2230
1865
1538
1248
993
773
ii
7 ooo
5707
4385
3339
2462
2082
1740
1435
Il64
927
722
12
6 500
5307
4069
3100
2286
1933
1616
1333
1081
860
670
13
6000
4908
3758
2862
21 10
1784
1492
I23C
998
794
619
14
55oo
4508
3443
2623
1934
1635
1368
1128
915
728
567
IS
5 ooo
4 108
3132
2385
1758
1487
1243
1025
832
662
5i6
TV
Uiam-
eter
9
8
7
6
5
4
3*
3
2*
2
I*
I
Line
i
1093
799
560
371
227
123
71.6
55-9
28.8
8.1
6.81
2.52
2
1015
742
521
344
210
114.6
68.6
51-9
27.6
6.8
6.52
2.34
3
937
685
481
318
194
106.0
65.6
47-9
26.4
5-5
6.24
.16
4
859
628
441
292
178
97-0
62.7
43-9
25.2
4.2
5-95
• 98
5
781
571
401
265
162
88.2
59-7
39-9
24.0
2.9
5.67
.80
6
742
542
381
252
154
83.8
56.5
37-9
22.8
2.3
5-29
• 71
7
703
514
36i
239
146
79-4
53-5
35-9
21.6
1.6
5-00
.62
8
664
485
34i
226
138
75-0
50.5
33-9
20.4
0.9
4-72
• 53
9
625
457
321
212
130
70.6
47-6
31-9
19.2
10.3
4-43
• 44
10
586
428
301
199
122
66.2
44-5
29-9
18.0
9.68
4-15
.35
ii
547
400
281
186
H3
61.7
41.6
27.9
16.8
9-03
3-86
.26
12
508
371
261
172
105
57-3
38.6
25-9
15.6
8.38
3.68
.17
13
469
343
241
159
97-2
52.9
35-6
23-9
14.4
7-74
3.40
.08
14
430
314
221
146
89.1
48.5
32.6
21.9
13.2
7.10
3- II
• 99
15
390
286
200
132
81.0
44-1
29.6
20. 0
12. 0
6.45
2.83
.90
344 Flow of Steam
Table II. — Drop in Pressure in Pounds per Square Inch, per 1000 Feet
Length, Corresponding to Discharge in Table :
[
Density
0.208
0.230
0.273
0.295
0.316
0.338
0.401
0.443
0.485
0.548
Pres- )
sure \
90
100
1 20
130
140
150
180
200
220
250
Line
i
18.1
16.4
13-8
12.8
II. 9
ii. i
9-39
8.50
7-76
6.87
2
15.6
14.1
II. 9
II. 0
10.3
9.60
8.09
7-33
6.69
5-92
3
13-3
12.0
IO.I
9.38
8.75
8.18
6.90
6.24
5-70
5.05
4
ii. i
IO.O
8.46
7.83
7-31
6.83
5.76
5-21
4.76
4.21
5
9-25
8.36
7-5
6.52
6.09
5.69
4.80
4-34
3-97
3-51
6
8.33
7.53
6.35
5.87
5.48
5.13
4-32
3-91
3-57
3.16
7
7.48
6.76
5-70
5-27
4-92
4.60
3-88
3-51
3-21
2.84
8
6.67
6.03
5-08
4-70
4-39
4.10
3.46
3-13
2.86
2.53
9
5-91
5.35
4-50
4-17
3.89
3.64
3-07
2.78
2.53
2.24
10
5-19
4.69
3-95
3-66
3-42
3.i9
2.69
2.44
2.23
-97
ii
4-52
4.09
3-44
3-19
2.98
2.78
2.34
2.12
1-94
.72
12
3-90
3.53
2.97
2.75
2.57
2.40
2. 02
1.83
1.67
• 48
13
3-32
3.00
2.53
2.34
2.19
2.04
1.72
1.56
1.42
.26
14
2.79
2.52
2.13
1.97
1.84
1.72
1.45
1.31
1.20
.06
15
2.31
2.09
1.76
1.63
1.52
1.42
1.20
1.08
0.991
0.877
Density in pounds per cubic foot. Pressure in pounds per square inch absolute.
Examples in the Use of the Table. Suppose it is required to find the
discharge from a 5-inch pipe line, steam pressure being 120 pounds per
square inch absolute, and the loss in pressure being 4.5 pounds per 1000
feet length. In Table II we find the drop 4.5 under 120 pounds pres-
sure to be in line 9. In Table I in line 9 under s-inch diameter we find
the discharge to be 130 pounds per minute.
Or, suppose it is required to find the size of pipe to carry
1000 paunds
of steam per minute, mean absolute pressure being 130 pounds and the
drop in pressure being assumed as ii pounds. In Table
II the drop
ii under 130 pounds pressure is in line 2. In Table I in line 2 the tabu-
lar quantity which corresponds nearest to 1000 is in the 9-inch column.
A 9-inch line will, therefore, be required.
Kent modifies Darcy's Formula for flow of water to make it apply
to steam, and gives for the flow,
/(Pi - pt)d*
Q-C\ wL
W=c\/
'w(pi-p^
L
where Q = volume of steam in cubic feet per minute;
W = weight of steam in pounds per minute;
pij= initial pressure in pounds per square inch;
p2 = final pressure in pounds per square inch;
L = length of pipe in feet;
d= inside diameter of pipe in inches;
w = density of steam in pounds per cubic foot;
c = coefficient, depending on the diameter of the pipe.
Flow of Steam in Low-Pressure Heating Lines 345
The
Nomin
Value
Nomin
Value
Nomin
Value
Flo
table
Darcy
Thed
which
Flow <
values of c are as fo
al diameter, inches Vsi
oic 36. £
lows:
%
42
4
57-8
12
62.1
-pressi
. V. E.,
water i
ed is i
may b
sure in
1 per 10
3
3 56.2
9
3 61.3
24
2 63.2
Allowing
ation of
i above,
sis from
m Drop
36
45-3 48 50 52.7 54-
4^2 5 6 7 8
58.3 58-7 59-5 60.2 60.
14 16 18 20 22
62.3 62.6 62.7 62.9 63.
ire Heating Lines. The f
1907) is based on his adapt
to the flow of steam as giver
pound per 1000 feet, as a ba
e calculated.
Pounds per Hour f8r a Unifoi
oo Feet Length of Straight Pi]
al diameter, inches 3%
of c . . . 57 i
al diameter, inches 10
of c 61 .;
w of Steam in Low
by W. Kent (A. S. H
's formula for flow of
rop in pressure assum
the flow at any drop
rf Steam at Low Pres
at the Rate of i Pounc
Nominal diam-
eter of pipe
Initial steam pressure, pounds (gage)
0.3
1.3
2.3
3-3
4-3
5-3
6.3
8.3
10.3
Flow of steam, pounds per hour
Ins.
%
%
i
i%
i%
2
2%
3
3V2
4
4%
5
6
8
9
10
12
4-9
II. 3
22.3
46.9
71.9
141.5
229.2
404.7
591.8
822.0
IIOO.
1467.
2356.
3440.
4783.
6396.
8562.
13542.
5.1
n. 8
23.2
49-0
75-0
147-7
239-2
422.4
618.0
857.4
1148.
I53L
2459.
3590.
4991.
6678.
8940.
I4I36.
5-3
12.3
24.2
50.9
78.0
153-6
248.8
439-3
642.6
891.6
1193.
1592.
2557.
3733.
5I9L
6942.
9294.
14700.
9-7
19.0
40.1
61.4
120.8
195.7
345-5
505.3
701.4
938.7
1252.
2OII.
2936.
4082.
54,62.
7314.
H550.
10. 0
19.6
41-3
63.2
124-5
201.8
356.1
520.8
723.0
967.6
1291.
2074.
3027.
4208.
5630.
7536.
11916.
10.3
20. 2
42.5
65.1
128.2
207-5
366.5
535-9
744-0
995-8
1328.
2134-
3H5.
4331.
5794-
7758.
12264.
10.5
20.7
43-7
66.8
131.6
213.2
376.4
550.5
764.4
1023.
1364.
2192.
3I99-
4448.
5951.
7968.
12594-
10.8
21.2
44-8
68.6
135.0
218.7
386.1
564.7
784.2
1049.
1399-
2248.
3281.
4564.
6102
8172.
12918.
II. O
21.7
45-9
70.3
138.3
224.0
395-5
578.5
803.4
1075-
1433.
2303.
3362
4674.
6252.
8370.
13236.
For any other drop of pressure per 1000 feet length, multiply the
figures in the table by the square root of that drop.
Kent says, "In all cases the judgment of the engineer must be used
in the assumption of the drop to be allowed. For small distributing
pipes it will generally be desirable to assume a drop of not more than
346 Resistance to Flow of Steam
one pound per 1000 feet to insure that each single radiator shall always
have an ample supply for the worst conditions, and in that case the size
of piping given in the table up to two inches may be used; but for
main pipes supplying totals of more than 500 square feet, greater drops
may be allowed. "
Resistance Due to Entrance, Bends and Valves. Mr. Briggs
states, in "Warming Buildings by Steam," that the resistance at the
entrance to a pipe consists of two parts, namely, the head — which
2 g
is necessary to create the velocity of flow, and the head 0.505 — , which
overcomes the resistance to entrance offered by the mouth of the pipe.
The total loss of head at entrance then equals the sum of these, or
1-505 — , in which v = velocity of flow of steam in the pipe, in feet per
2 g •
second, and g = acceleration due to gravity, or 32.2.
The Babcock & Wilcox Co. state in "Steam" that the resistance at
the opening, and that at a globe valve, are each about the same as that
caused by an additional length of straight pipe, as computed by the
formula,
n4D
LI = —
where L is the additional length of pipe in inches and D is the diameter
of pipe in inches. From this formula has been computed the following
table:
D in inches i iVz 2 iVz 3 3^ 456
L in feet 2 4 7 10 13 16 20 28 36
D in inches 7 8 10 12 15 18 20 22 24
Lin feet 44 53 70 88 115 143 162 181 200
The resistance to flow at a right-angled elbow is about equal to
% that of a globe valve.
The above values are to be considered as being only approximations
to the truth.
Expansion of Steam Pipes. The linear expansion and contraction
of a pipe carrying steam, with the rise and fall of the temperature,
must be taken care of by the use of some form of expansion joint or
bend. To find the total expansion due to an increase in temperature,
multiply the length of pipe in inches by the coefficient of expansion
and by the temperature range.
The-expansion for each 100 feet of length for different degrees Fahren-
heit is given in the following table, which is taken from the Practical
Engineer, January, 1911. The expansion for any length between two
temperatures is found by taking the difference in length at these tem-
peratures, dividing by 100 and multiplying by the length of the pipe
in feet.
Expansion of Steam Pipes
347
Expansion of Pipes
(Increase in inches per 100 feet.)
Temperature,
degrees
Fahrenheit
Cast iron
Wrought iron
Steel
Brass and
copper
0
0.00
o.oo
.00
0.00
5o
0.36
0.40
-38
0.57
TOO
0.72
0.79
.76
1.14
125
0.88
0-97
92
1.40
ISO
I. 10
1. 21
• 15
1-75
175
1.28
1.41
• 34
2.04
2OO
1.50
1.65
• 57
2.38
225
1.70
1.87
• 78
2.70
250
1.90
2.09
• 99
3.02
275
2.15
2.36
.26
3-42
300
2.35
2.58
• 47
3-74
325
2.60
2.86
2.73
4-13
350
2.80
3-08
2.94
4-45
375
3.15
3.46
3-31
5.01
400
3-30
3-63
3.46
5-24
425
3-68
4-05
3-86
5-85
450
3.89
4.28
4.08
6.18
475
4.20
4.62
4-41
6.68
500
4-45
4.90
4.67
7.06
525
4-75
5.22
4-99
7-55
550
5-05
5-55
5-30
8.03
575
5.36
5-90
5.63
8.52
600
5-70
6.26
5.98
9.06
625
6.05
6.65
6.35
9.62
650
6.40
7-05
6.71
10.18
675
6.78
7.46
7.12
10.78
700
7-15
7.86
7-50
H.37
725
7.58
8.33
7.96
12.06
75o
7.96
8.75
8.36
12.66
775
8.42
9.26
8.84
13.38
800
8.87
9.76
9-31
14.10
Sizes of Steam Pipes for Engines. A common rule is that steam
pipes supplying stationary engines should be of such size that the mean
velocity of steam in them does not exceed 6000 feet per minute, in order
that the loss due to friction may not be excessive. There are many-
cases where this rule gives unnecessarily large pipes, and the velocity
could be increased with advantage. The larger the pipe, the greater
the surface, and the greater the amount of condensation. For large
engines and high pressures it is best to assume the drop in pressure and
calculate the diameter from- the formulae given above, or obtain it from
the tables. In marine work the steam pipes are generally not as large
as in stationary practice for the same sizes of cylinders, a velocity of
9000 feet per minute being often used. In proportioning exhaust pipes
348 Loss of Heat from Steam Pipes
the velocity should not exceed 4000 feet per minute for stationary engines,
nor 6000 feet for marine engines.
Having assumed a velocity of flow in the pipe supplying steam to the
engine, the size of pipe required is such that its area is given by the
formula,
Cylinder Area x Piston Speed
Mean Velocity of Steam in Pipe
Or since the areas are proportional to the squares of their diameters,
/(Cylinder Diame
y Mean Velocit;
/(Cylinder Diameter)2 x Piston Speed
Pipe Diameter =4 /
**— i Velocity of Steam in Pipe
This assumes that steam is admitted during full stroke.
LOSS OF HEAT FROM STEAM PIPES
Loss of Heat from Bare Steam Pipes. A bare pipe carrying
steam and made of steel, iron or other conducting material, loses heat by
convection to the surrounding air and by radiation to the surrounding
objects, both of which cause a loss of steam by condensation.
For bare steam pipes this loss may be taken as 2.7 B.T.U. per hour
per square foot of surface per degree Fahrenheit difference between
the temperatures of the steam and the outside air. Thus, if the pres-
sure of the steam is 120 pounds absolute, the corresponding tempera-
ture being 341°, and the temperature of the air 60°, then the loss per
hour per foot length from a 4-inch steam pipe, the external surface of
which is 1.178 square feet per foot of length, will be 1.178 x (341 — 60) x
2.7 = 894 B.T.U.
Condensation in Bare Steam Pipes. The corresponding conden-
sation can be found by dividing this heat quantity by the latent heat of
steam at the given pressure. In the example given above, the latent
heat of steam at 120 pounds pressure, absolute, is 877.2 B.T.U. There-
fore the condensation per hour per foot length of pipe is 8944- 877.2 =
i. 02 pounds.
Steam Pipe Coverings. This loss is lessened in practice by cover-
ing the steam pipe with a material that will offer a greater resistance
to the flow of heat than that offered by the material of the pipe. A good
material for this purpose should not suffer serious deterioration from
the heat or vibration to which it would be subjected in practice; and
in all cases where damage from fire might result, it should never consist
of combustible matter. Any covering should be kept perfectly dry,
as still water is an excellent carrier of heat.
The best insulating substance known is .air confined in minute cells,
and the best nonconducting coverings owe their efficiency to the numer-
ous air cells in their structure. In general the value of a covering is
inversely proportional to its weight, and other things being equal, the
Steam Pipe Coverings
349
incombustible mineral substances are to be preferred to combustible
material. No covering should be less than one inch in thickness.
Hair or wool felt and most of the better nonconducting materials
have the disadvantage of becoming charred at high temperature and
partly losing their insulating power. There is also the danger of taking
fire. Mineral wool, a fibrous material made from blast furnace slag,
is the best noncombustible covering, but being brittle it is liable to fall
to a powder when subjected to jarring.
Pipe covering may be sectional, or plastic. The former is built up
in sections and attached to the pipe by bands, which allow easy removal
of the covering. The latter is put on in a soft, plastic condition, and is
hardened in place; it obviates joints and adheres closely to the pipe.
The following table, taken from the various sources noted, gives the
results of experiments on steam pipe coverings. In almost all cases
the figures given are the averages of a number of tests.
Steam Pipe Coverings
Number |
Kind of covering
Size
of
pipe,
ins.
Thick-
ness of
cover-
• n£ •
i ches
B.T.U. per
square foot
per hour per
degree differ-
ence of
temperature
Per
cent
heat
lost
Authority
i
Bare pipe
2.7
IOO
?
Mineral wool . . .
8
.30
0.285
10.6
Brill
3
Rock wool
8
.60
0.256
9-5
Brill
4
Hair felt...
2
.96
0.387
14.3
Jacobus
5
Hair felt
8
82
0.422
15.6
Brill
6
Remanit
2
• 51
0.302
II. 2
Stott
7
Remanit
2
.30
0.363
13.4
Jacobus
8
Remanit
2
.88
0.434
16.1
Jacobus
9
Solid cork . .
2
.68
0.348
12.9
Stott
0
Solid cork
2
.20
0.427
15.8
Stott
T
Magnesia
2
.41
0.302
II. 2
Stott
2
Magnesia
IO
37
0.354
I3.I
Barrus
^
Magnesia
8
.25
0.384
14.2
Brill
4
Magnesia
2
.16
0.439
16.3
Stott
$
Magnesia
4
.12
0.465
17.2
Norton
T6
Magnesia
2
.08
0.304
II. 3
Jacobus
17
Magnesia
2
08
o 531
19.7
Barrus
18
19
20
21
22
23
24
25
26
27
28
29
30
31
V
Asbestos sponge felted.
Asbestos sponge felted.
Asbestos sponge felted.
Asbestos sponge felted.
Manville sectional ....
Manville sectional
Manville sectional ....
Asbestos air cell
Asbestos air cell
Asbestos air cell
Asbestos air cell
Asbestos fire felt
Asbestos fire felt
Asbestos fire felt
Fossil meal
2
10
2
2
8
4
2
2
4
2
2
8
2
2
8
'I4
-63
.21
.24
.70
.25
• 31
.26
.12
-96
.02
• 30
.OO
• 99
• 75
0.260
0.280
0.490
0.532
0.350
0.453
0.572
0.486
0.525
0.716
0.793
0.502
0.721
0.766
0.879
9-6
10.4
18.1
19.7
13.0
16.8
21.2
18.0
19.4
26.5
29.4
18.6
26.7
28.4
32.6
Jacobus
Barrus
Barrus
Stott
Brill
Norton
Paulding
Stott
Norton
Jacobus
Barrus
Brill
Paulding
Jacobus
Brill
13
Riley cement
8
75
O.953
35-3
Brill
350 Steam Pipe Coverings
A brief description of some of these coverings is given below:
No. 4. A layer of asbestos paper Vs2 inch thick next to the pipe,
then the hair felt, then a layer of paper, and outside of all a canvas
covering.
No. 5. The hair felt was bound tightly around the pipe, with no can-
vas covering; it had a layer of asbestos paper under it.
No. 6. A covering composed of two layers wound in reverse direction
with ropes of carbonized silk; the inner layer 2^ inches wide and Vz inch
thick; the outer layer 2 inches wide and % inch thick, over which was
wound a network of wire; Vs inch asbestos next to pipe.
No. 7. A grade known as high- pressure remanit; encased in canvas.
No. 8. A grade known as intermediate-pressure remanit; encased in
canvas.
Nos. 9 and 10. Solid sectional covering of granulated cork with
%-inch asbestos paper next to pipe.
No. ii. 85 per cent carbonate of magnesia. Average of a number of
tests of moulded sectionals, thickness of covering ranging from 2.20 to
2.71 inches.
No. 12. Carbonate of magnesia with some asbestos fiber; outside
finished with canvas.
No. 14. Average of tests, thickness of covering ranging from 1.12 to
1.19 inches.
No. 15. Moulded sectional covering composed of about 90 per cent
carbonate of magnesia.
No. 17. Similar, except in thickness, to No. 12.
Nos. 1 8, 19, 20 and 21. Laminated sectional, composed of a number
of layers of asbestos paper in which were imbedded small pieces of
sponge.
No. 23. A sectional covering composed of an inner layer of earthy
material covered by a layer of wool felt.
No. 25. Laminated sectional with ^-inch asbestos paper next to
pipe.
No. 26. Made of thin sheets of corrugated asbestos paper, stuck
together with silicate of soda.
Nos. 27 and 28. Similar to No. 26.
Nos. 32 and 33. Mixed with water and plastered on the pipe.
Air 351
AIR
Properties
PAGE
Composition 352
Weight 352
Pressure, Volume and Temperature 352
Pressure of the Atmosphere 352
Specific Heat of Air 355
Adiabatic Expansion and Compression 355
Work of Adiabatic Compression of Air .- 356
Isothermal Expansion and Compression 356
Work of Isothermal Compression of Air 356
Flow of Air
Flow of Air under Pressure from Orifices into the Atmosphere. . . 357
Velocity of Efflux of Compressed Air 357
Discharge of Air through an Orifice 35&
Flow of Air in Pipes 359
Loss of Pressure in Pipes 359
Flow of Compressed Air in Pipes 360
Loss of Pressure in Compressed Air Transmission , 360
Effect of Bends and Fittings 364
352
Properties of Air
PEOPERTIES OF AIE
Air is a mechanical mixture of the gases oxygen and nitrogen with a
small amount of argon. By volume its composition is 78 per cent
nitrogen, 21 per cent oxygen and i per cent argon. Atmospheric air
of ordinary purity contains about 0.04 per cent of carbon dioxide.
Weight of Air. The weight of pure air at 32° F. and a barometric
pressure of 29.92 inches of mercury, or 14.6963 pounds per square inch
is 0.080728 pound per cubic foot. The volume of a pound of air is
therefore 12.387 cubic feet. At any other temperature and pressure its
weight in pounds per cubic foot is W = — — — , where B = height
of barometer in inches and T = absolute temperature Fahrenheit.
The weight per cubic foot at various temperatures and pressures is
given in the table on pages 353 and 354.
Pressure, Volume and Temperature. The relation between
pressure, volume and temperature of air is such that
p\v\
~
-- 53-3,
in which pi and pz are absolute pressures in pounds per square foot,
vi and v 2 the volumes in cubic feet of i pound of air, and T\ and T*
the absolute temperatures. When the pressure remains constant the
volume is directly proportional to the absolute temperature. If the
temperature remains constant the volume is inversely proportional to
the absolute pressure.
Pressure of the Atmosphere. .The following table gives the pres-
sure of the atmosphere in pounds per square inch and pounds per square
foot for various readings of the barometer. It is based on i inch of
mercury at 32° F. being equal to a pressure of 0.491 pound per square
inch.
Pressure of the Atmosphere for Various Readings of the Barometer
Barometer,
inches
Pounds per
square inch
Pounds per
square foot
Barometer,
inches
Pounds per
square inch
Pounds per
square foot
28.00
28.25
28.50
28.75
13-75
13.87
13-99
14.12
1980
1997
2015
2033
29-75
30.00
30.25
30.50
14.61
14-73
14.85
14.98
2103
2121
2139
2156
29.00
29.25
29.50
14.24
14-36
14.48
2050
2068
2086
30.75
31.00
31.25
15.10
15.22
15.34
2174
2192
22IO
Weight of Air 353
Weight of Air at Various Pressures and Temperatures
(Based on an Atmospheric Pressure of 14.7 Pounds)
Gage pressure, pounds
Temper-
ature of
air, degrees
o
5
10
20
30
40
50
60
70
80
90
Weight in pounds per cubic foot
— 20
.0900
.1205
.1515
.2125
.2744
.3360
• 3970
.458o
.5190 .5800
.6410
— 10
.0882
.1184
.1485
.2090
.2685
.3283
.3880
• 4478
.5076 .5674
.6272
O
.0864
.1160
.1455
.2040
.2630
• 3215
.3800
.4385
•4970
• 5555
.6140
IO
.0846
.1136
.1425
.1995
.2568
.3145
• 3720
.4292
.4863
• 5433
.6006
20
.0828
.1112
.1395
.1955
.2516
.3071
.3645
.4205
•4770
• 5330
.5890
30
.0811
.1088
.1366
.1916
2465
• 3015
• 3570
.4121
.4672
.5221
• 5771
40
•0795
.1067
.1338
.1876
.2415
• 2954
• 3503
.4038
•4576
-5II4
.5652
So
.0780
• 1045
.1310
.1839
.2367
.2905
3432
.3960
.4487
• 5014
• 5541
60
.0764
.1025
.1283
.1803
.2323
.2840
.3562
.3882
.4402
.4927
• 5447
70
• 0750
.1005
.1260
.1770
.2280
.2791
• 3302
.3808
.4316
.4824
• 5332
80
.0736
.0988
.1239
.1738
.2237
.2739
.3242
• 3738
•4234
• 4729
.5224
90
.0723
.0970
.1218
.1707
• 2195
.2688
.3182
.3670
•4154
.4639
.5122
100
.0710
• 0954
.1197
.1676
.2155
.2638
.3122
.3602
.4079
.4555
• 5033
no
.0698
.0937
.1176
.1645
.2115
• 2593
.3070
• 3542
.4011
.4481
• 4950
120
.0686
.0921
.H55
.1618
.2080
.2549
.3018
.3481
• 3944
.4403
.4866
130
.0674
• 0905
.1135
.1590
.2045
.2505
.2966
.3446
.3924
.4296
• 4770
140
.0663
.0889
.HIS
.1565
.2015
.2465
.2915
.3364
.3813
.4262
• 4711
150
.0652
.0874
.1096
.1541
.1985
.2425
.2865
.3308
.3751
.4193
-4636
175
.0626
.0840
.1054
.1482
.1910
.2335
.2755
.3181
.3607
.4033
• 4450
200
.0603
.0809
.1014
.1427
.1840
.2248
.2655
.3054
.3473
.3882
.4291
225
.0581
.0779
.0976
• 1373
.1770
.2163
.2555
.2949
• 3344
.3738
.4129
250
.0560
.0751
.0941
.1323
.1705
.2085
.2466
.2845
.3223
.3602
.3981
275
.0541
.0726
.0910
.1278
.1645
.2011
.2378
.2745
.3111
.3478
.3844
300
.0523
.0707
.0881
• 1237
.1592
•1945
.2300
.2654
.3008
.3362
.3716
350
.0491
.0658
.0825
.1160
• 1495
.1828
.2160
.2492
.2824
.3156
.3488
400
.0463
.0621
.0779
.1090
.1405
.1720
.2035
.2348
.2661
.2974
.3287
450
.0437
.0586
.0735
.1033
.1330
.1628
.1925
.2220
.2515
.2810
.3105
500
.0414
.0555
.0696
.0978
.1260
•1540
.1820
.2100
.2380
.2660
.2940
550
.0394
.0528
.0661
.0930
.1198
.1464
.1730
.1996
.2262
.2528
• 2794
600
.0376
.0504
.0631
.0885
.1140
.1395
.1650
.1904
.2158
.2412
.2668
354 Weight of Air
Weight of Air at Various Pressures and Temperatures (Concluded)
(Based on an Atmospheric Pressure of 14.7 Pounds)
Gage pressure, pounds
Temper-
ature of
air, degrees
IOO
no
1 20
130
140
ISO
175
200
225
250
300
x1 anrenneit
Weight in pounds per cubic foot
— 20
.702
.764
.825
.886
.948
1. 010
.165
1.318
1.465
1.625
• 930
— 10
.687
• 747
.807
868
.928
989
.139
1.288
1.438
1-588
.890
o
.672
• 731
.790
.849
.908
.968
.114
1.260
1.406
1-553
.850
10
.658
.716
.774
.832
.889
• 947
.090
1.233
1.376
1.520
.810
20
.645
.701
.757
.813
.869
.927
.067
1.208
• 348
1.489
.770
30
.632
.687
.742
• 797
.852
.908
.046
1.184
322
1.460
• 735
40
.619
.673
.727
.781
.835
.890
.025
1.161
.296
I.43I
.701
50
.607
.660
.713
.766
.819
.873
i. 006
1. 139
.271
1.403
.668
60
.596
.649
.700
• 752
.804
.856
.988
1.116
.245
1.376
.636
?o
.584
.635
.686
• 737
.788
.839
.967
1-095
.223
1.350
.604
80
• 572
.622
•673
.723
• 774
.824
• 949
1.074
.199
1.325
• 573
90
.561
.611
.660
.709
.759
.809
• 932
1.054
.177
1.300
• 544
100
• 551
• 599
.648
.696
.745
.794
.914
1.035
-155
1.276
• 517
no
.542
.589
.637
.685
• 732
.780
.899
1.017
.135
1.254
.491
120
.533
.579
.626
.673
.720
.767
.884
1. 001
.118
1.234
• 465
130
.524
.570
.616
.662
.708
.754
.869
.984
.099
1.214
• 440
140
.516
.561
.606
.651
.696
.742
.855
.968
1.081
1. 194
.416
ISO
.508
• 552
.596
.640
.685
.730
.841
.953
1.064
1. 175
• 392
175
.488
.531
.573
.6 6
.658
.701
.808
.914
1. 021
1.128
.337
200
• 470
.511
• 552
• 592
.633
.674
.776
.879
.982
1.084
.287
225
• 452
.491
.531
-570
.609
.649
• 747
.846
• 944
1.043
.240
250
.436
• 474
.513
• 551
.589
.627
.722
.817
.912
1.007
.197
275
.421
.458
• 494
.531
.568
.605
.697
.789
.881
• 972
• 155
300
.407
• 442
.478
.513
• 549
.585
.673
.762
.852
.940
.118
350
.382
.415
• 449
.482
.516
• 549
.632
• 715
• 799
.883
1.048
400
.360
.391
.423
• 454
.486
.517
• 596
.674
• 753
.831
.987
450
• 340
.369
• 399
.429
.458
.488
.562
.637
.711
.786
• 934
500
.322
• 351
• 379
.407
.435
.463
• 534
.604
.675
.746
.885
550
.306
.333
• 359
.386
.413
.440
.507
.573
.641
• 749
.841
600
.292
.317
.343
.368
• 393
• 419
.483
• 547
.611
.675
.801
Expansion and Compression of Air 355
Specific Heat of Air. The specific heat of a gas is the heat, in heat
units, required to raise the temperature of one pound of the gas one
degree Fahrenheit. The mean specific heat of air at constant pres-
sure is Cp = 0.2375 and at constant volume is cv = 0.1689.
Adiabatic Expansion and Compression. Adiabatic expansion or
compression of a gas means that the gas is expanded or compressed
without transmission of heat to or from the gas. This would be the case
were the expansion or compression to take place in an absolutely non-
conducting cylinder, in which case the temperature, pressure and volume
of air would vary as indicated by the following formulae:
i>i \Pz / PI \vz 1 Ti \i)z 1
in which pi, vi and Ti = initial absolute pressure, volume and absolute
temperature, and pz, vz and Tz = final absolute pressure, volume and
absolute temperature of the air after compression. The manner in which
the temperature and volume vary with the change in pressure is shown
in the following table:
Table for Adiabatic Compression or Expansion of Air
(Proc. Inst. M. E., Jan., 1881, p. 123.)
Absolute pressure
Absolute temperature
Volume
Ti
h
P2
1
'A
1
v*
1.2
1.4
1.6
1.8
.833
.714
.625
.556
1.054
1. 102
.146
.186
.948
.907
.873
.843
.138
.270
.396
.518
.879
.788
.716
.659
2.0
2.2
2-4
2.6
.500
.454
.417
.385
.222
.257
.289
.319
.818
.796
.776
.758
.636
• 750
.862
.971
.611
• 571
• 537
• 507
2.8
3-0
3-2
3-4
.357
• 333
.312
.294
.348
• 375
.401
.426
.742
.727
.714
.701
2.077
2.182
2.284
2.384
.481
.458
.438
.419
3-6
3-8
4-0
4-2
.278
.263
.250
.238
• 450
• 473
• 495
.516
.690
•679
.669
.660
2.483
2.580
2.676
2.770
.403
.388
.374
.361
4.4
4-6
4-8
5-0
.227
.217
.208
.200
.537
• 557
.576
• 595
.651
.642
.635
.627
2.863
2.955
3.046
3-135
.349
.338
.328
.319
6.0
7.0
8.0
9-0
IO.O
.167
.143
.III
.100
.681
.758
.828
.891
• 950
.595
.569
.547
.529
.513
3.569
3.981
4-377
4-759
5-129
.280
.251
.228
.210
.195
356 Expansion and Compression of Air
Work of Adiabatic Compression of Air. If air is compressed from
a volume v\ and pressure pi, to a volume vz and pressure pz, in a non-
conducting cylinder without clearance, the work involved in delivering
one pound is as follows:
\~f fli\°-41
Work of compression = 2.46 pivi I — j — i I
Work of expulsion = pzvz = pivi
f pz \0-29
I — .
\£i/
Total work is the sum of the work of compression and expulsion less
the work, pivi, of the atmosphere done on the piston during admission, or
K£2\0.29 "1
) ~ * *
The mean effective pressure equals the total work -5- the initial volume,
vi, or r/M°-29 ~l
3,^g| -,].
Isothermal Expansion and Compression. Isothermal expansion
or compression of a gas means that the gas is expanded or compressed
with the addition or rejection of sufficient heat to maintain a constant
temperature. The temperature being constant the pressure and volume
will vary according to the law
in which pi and pz are the initial and final absolute pressures in pounds
per square foot, v\ and vz are the initial and final volumes in cubic feet,
and C is a constant depending on the temperature. For a temperature
of 32° F. this constant is 26 214 foot-pounds, and for isothermals corre-
sponding to other temperatures it may be found from the formula C =
53-3 T, in which T is the absolute temperature of the isothermal.
Work of Isothermal Compression of Air. If air is compressed
from a volume vi and pressure pi to a volume vz and pressure pz, in a
cylinder without clearance, in such manner as to keep the temperature
constant, the work involved in delivering one pound is as follows:
Work of compression = pivi \oge — •
Vz
Work of expulsion = pzvz = pivi.
The total work then is the sum of the work of compression and expul-
sion less the work, pivi, of the atmosphere done on the piston during admis-
sion, or Vl Vl
Total work = pivi \oge h PIVI - PIVI = pivi \oge — •
Vz Vz
In this formula, Naperian, or hyperbolic, logarithms must be used.
These may be obtained from the common logarithms by multiplying
by the constant 2.303.
The mean effective pressure equals the total work divided by the
initial volume vi, or pi loge vi/vz.
Flow of Air
357
FLOW OF AIR
Flow of Air under Pressure from Orifices into the Atmosphere.
The following table gives the theoretical velocity for the discharge of
air into the atmosphere under very low pressures, less than one-quarter
of a pound per square inch. In this case the variation due to difference
in air density is so small that it has not been considered. These theo-
retical velocities are to be reduced by multiplying by a coefficient c,
varying with the form of the orifice. For an orifice with a sharp edge in
a thin plate c is 0.65, for a plate with rounded orifice on the inside c is
from 0.70 to 0.75, and for a nozzle of good form c may be taken as 0.93.
Velocity of Air Under Low Pressures
(Temperature 62° F. Barometer 30 inches.)
Pressure
Theoretical
Pressure
Theoretical
Inches
of
water
Pounds
per square
foot
velocity,
feet per
second
Inches
of
water
Pounds
per square
foot
velocity,
feet per
second
.01
.052
6.61
.8
4-15
59-1
.02
.104
9-35
• 9
4-67
62.7
.04
.208
13.2
I.O
5-19
66.1
.07
.363
17-4
1.5
7-79
80.9
.10
• 519
20.9
2.O
10.38
93-5
.20
1.038
29-5
2-5
12.08
104.0
.30
1-558
36.2
3-0
15.58
114.0
• 40
2.077
41.8
3.5
18.18
124.0
.45
2.337
44-3
4.0
20.77
132.0
• So
2.597
46.7
4-5
23-37
140.0
.60
3.n6
51.2
5-0
25-97
148.0
.70
3.635
55-3
6.0
31.16
162.0
For the velocity of air under higher pressures discharging into the
atmosphere, Hiscox in "Compressed Air" gives the following table:
Velocity of Efflux of Compressed Air
Pressure
Theoret-
Pressure
Theoret-
Atmos-'
pheres '
Inches
of
mercury
Pounds
per
square
inch
ical veloc-
ity, feet
per
second
Atmos-
pheres
Inches
of
mercury
Pounds
per
square
inch
ical veloc-
ity, feet
per
second
OIO
0.30
0.147
94-4
.680
20.4
10.
780
.066
2.10
I.OO
246.
.809
24.28
12.
855
.100
3.00
1.47
299-
3o.
14.7
946
.136
4.08
2.00
348.
2.
60.
29-4
1094
.204
6.12
3.00
472.
5-
150.
73.5
1219
.272
8.16
4.00
493.
10.
300.
147.
1275
.340
10.20
S.oo
552.
20.
600.
294.
1304
.408
12.24
6.00
604.
40.
1200.
588.
1323
.500
15-00
7.35
673.
IOO.
3000.
I47o.
I33i
.544
16.32
8.00
697.
20O.
6000.
2940.
1334
.611
18.34
9.00
741.
358
Discharge of Air
To obtain the actual velocity, this theoretical velocity should be
multiplied by a coefficient varying with the nature of the orifice and the
air pressure. The coefficients for an orifice in a thin plate and for a
short tube whose length is three times its diameter are given below.
The pressures are in atmospheres above atmospheric pressure.
Coefficients of Air Discharge
Orifice in thin plate
Short tube
Pressure in atmospheres
.65
-834
• 57
• 71
• 54
.67
.45
.53
.436
The quantity of air discharged into the atmosphere from a round
hole in a receiver in cubic feet of free air per minute is given in the
following table:
Discharge of Air Through an Orifice
(Ingersoll-Rand Company. )
14
fj8
I
1%
1%
Receiver gage pressure, pounds per square inch
.038
.153
.647
2.435
9-74
21.95
39-0
61.0
87.6
II9-5
156.
242.
350.
625.
•0597
.242
.965
3-86
15.4
34-6
61.6
96.5
133-
189.
247-
384.
550.
985.
.0842
• 342
1.36
5-45
21.8
49-
87.
136.
196.
267.
350.
543-
780.
.103
.418
1.67
6.65
26.7
60.
107.
167.
240.
326.
427.
665.
960.
.119
.485
1-93
7-7
30.8
69.
123.
193.
277.
378.
494-
770.
.133
• 54
2.16
8.6
34-5
77-
138.
216.
3io.
422.
550.
860.
.156
.632
2.52
10.
40.
90.
161.
252.
362.
493-
645.
IOOO.
.173
• 71
2.80
II. 2
44-7
IOO.
179.
280.
400.
550.
715-
.19
.77
3-07
12.27
49-09
H0.45
196.35
306.80
441-79
601.32
785.40
Diameter
of orifice,
inches
Receiver gage pressure, pounds per square inch
45
60
70
80
90
IOO
125
V64
H
8/4
.208
.843
3.36
13.4
53-8
121.
215.
336.
482.
658.
860.
.225
.914
3.64
14-5
58.2
130.
232.
364.
522.
710.
930.
.26
1.05
4.2
16.8
67.
5i.
268.
420.
604.
822.
.295
1. 19
4.76
19-
76.
171.
304.
476.
685.
930.
-33
1-33
5-32
21.2
85-
191.
340.
532.
765.
1004.
.364
1.47
5-87
23-5
94.
211.
376.
587.
843.
.40
1.61
6.45
25.8
103.
231.
412.
645.
925.
.486
1-97
7-85
31-4
125.
282.
502.
785.
Flow of Air
359
Flow of Air in Pipes. For the flow of air in pipes at or near atmos-
pheric pressure, the following formulae, which are deduced from Hawks-
ley's formula, may be used. f
hd
13 nod
where v — velocity of air in feet per second;
h = head, in inches of water column, causing flow, or the loss of
head for a given flow;
d = inside diameter of pipe, in inches;
L = length of pipe, in feet.
The formulae used by the B. F. Sturtevant Company, derived from
Weisbach, are given below. They correspond to Hawksley's formula
with a coefficient 120.1 instead of 114.5.
25 ooo dp
25 ooo d
where v = velocity in feet per second;
p = loss of pressure, in ounces per square inch;
d = inside diameter of pipe, in inches;
L = length of pipe, in feet.
The quantity of air discharged in cubic feet per second is the product
of the velocity, as obtained above, and the area of the pipe in square
feet. The horse-power required to drive air through a pipe is the volume
in cubic feet per second multiplied by the pressure in pounds per square
foot and divided by 550.
The following table condensed from one given in the catalogue of the
B. F. Sturtevant Company gives the loss in pressure by friction of air in
pipes 100 feet long; for any other length the loss is directly proportional.
Loss of Pressure in Pipes
Velocity, feet
per minute
Diameter of pipe in inches
i
2
3
4
5
6
7
8
9
10
II
12
Loss in ounces per square inch per 100 feet
600
1200
I800
24OO
3000
3600
4200
4800
6000
0.400
1.600
3.600
6.400
10.000
14.400
O.200
0.800
I.SOO
3.200
S.OOO
7.200
9.800
12.800
20.0OO
0.133
0.533
1. 200
2.133
3-333
4.800
6.533
8.533
13.333
O.IOO
0.400
0.900
1.600
2.500
3.600
4.900
6.400
IO.OOO
0.080
0:320
0.720
1.280
2. OOO
2.880
3-920
5-120
8.000
0.067
0.267
0.600
1.067
1.667
2.400
3.267
4.267
6.667
0.057
0.229
0.514
0.914
1.429
2.057
2.800
3.657
5.714
0.050
0.200
0.450
0.800
1.250
1.800
2.450
3.200
5.000
0.044
0.178
0.400
O.7II
I. Ill
1.600
2.178
2.844
4.444
0.040
0.160
0.360
0.640
I. OOO
1.440
1.960
2.560
4.000
0.036
0.145
0.327
0.582
0.909
1.309
1.782
2.327
3.636
0.033
0.133
0.300
0.533
0.833
1. 200
1.633
2.133
3-333
360
Flow of Compressed Air
Loss of Pressure in Pipes (Concluded)
Velocity, feet per
minute
Diameter of pipe in inches
14
16
18
20
22
24
28
32
36
40
44
48
Loss in ounces per square inch per 100 feet
600
1200
1800
2400
.029
.114
.257
.457
.025
.100
.225
.400
.022
.089
.200
.356
.020
.080
.180
.320
.018
.073
.164
.291
.017
.067
.150
.267
.014
.057
.129
.239
.012
.050
.112
.200
.Oil
.044
.100
.178
.010
.040
.090
.160
.009
.036
.082
.145
.008
.033
.075
.133
3000
3600
4200
4800
• 714
1.029
1.400
1.829
.625
.900
1.225
1. 600
.556
.800
1.089
1.422
.500
.720
.980
1.280
.455
.655
.891
1.164
.417
.600
.817
1.067
.357
.514
.700
.914
• 312
• 450
.612
.800
.278
.400
-544
.711
.250
.360
.490
.640
.227
.327
.445
.582
.208
.300
.408
• 533
6000
2.857
2.500
2.222
2.OOO
1.818
1.667
1.429
1.250
I. Ill
I.OOO
.909
.833
Flow of Compressed Air in Pipes. In considering the flow of com-
pressed air in pipes the density of the air should be taken into account.
A common formula, which can be used only when the difference of
pressure at the two ends of the pipe is small and the density of the air,
therefore, nearly constant, is
where Q = volume, in cubic feet per minute;
p = difference in pressure, in pounds per square inch;
d = inside diameter of pipe, in inches;
w = density of entering air, in pounds per cubic foot;
L = length of pipe, in feet.
In long pipes with large differences of pressure, the density decreases
and the volume and velocity increase during the flow from one end of
the pipe to the other. For the flow of air under such conditions see
under the flow of high pressure gas in pipes, page 320.
Loss of Pressure in Compressed Air Transmission. The follow-
ing tables, which are taken from the catalogue of the Ingersoll-Rand
Company, give the drop in pressure for different deliveries at various
pressures for sizes of pipe from i inch to 16 inches. The loss is given
for 1000 feet length of pipe; for any other length the loss is directly
proportional.
Flow of Compressed Air 361
Flow of Compressed Air at 60 Pounds Gage
(Loss of Pressure in Pounds per 1000 Feet.)
Size of
pipe
Delivery in cubic feet of compressed air per minute at
60 pounds gage
9.84
14-73
19.64
24.60
29-45
34-44
39-35
49.20
58.90
78.6
Equivalent delivery in cubic feet of free air per minute
So
75
IOO
125
150
175
200
250
300
400
I
1%
m
2
*%
3V2
4
4*4
i
7
8
18.24
5.06
1. 95
.42
.13
.05
H.34
4-33
.95
.29
.11
.05
20. l6
7.79
1.69
.52
.19
.08
.04
12.23
2.65
.81
.30
.13
.07
.03
17.53
3.80
1.16
• 44
.19
.09
.05
.03
5-17
1.58
•59
.26
.13
.07
.04
.01
6.77
2.09
£
.17
.09
.06
.02
.01
10.61
3-24
1.22
.55
• 27
.15
.08
.03
.01
15-20
4.65
1.78
.78
.38
.21
.12
.05
.02
.01
8.28
3- II
1.40
.69
.39
.22
.08
.04
.01
Size of
pipe
Delivery in cubic feet of compressed air per minute at
60 pounds gage
98.4
118.1
156.6
196.4
294.5
393.7
492
589
786
984
Equivalent delivery in cubic feet of free air per minute
500
600
800
IOOO
1500
2000
2500
3000
4000
5OOO
3
3V2
4
4V2
6
8
9
10
12
14
16
4.88
2. 2O
1. 08
.60
.34
.14
.06
.03
.01
7-03
3-17
1.56
.87
.49
.19
.09
.04
.02
.01
5-57
2.75
1.52
.87
• 34
.15
.08
.04
.03
.01
8.77
4.33
2.40
1.37
.54
.24
.12
.06
.04
.02
.OI
9.73
5-39
3-08
1.20
.55
.27
.15
.09
.03
.01
9.65
5.51
2.16
.98
.41
;S
.06
.03
.01
8.61
3.36
1.53
• 77
.42
.25
.09
.04
.02
4.82
2.19
I. II
.61
.36
.14
.06
.03
3-91
1.98
1.08
.63
.25
.11
.05
6.19
3.10
1.69
.99
• 39
.18
.09
362 Flow of Compressed Air
Flow of Compressed Air at 80 Pounds Gage
(Loss of Pressure in Pounds per 1000 Feet.)
Size of
pipe
Delivery in cubic feet of compressed air per minute at
80 pounds gage
7-74
ii. 3
15-2
19.4
23.2
27.2
3i.o
38.7
46.5
62.0
Equivalent delivery in cubic feet of free air per minute
So
75
100
125
I5o
175
200
250
300
400
i
1%
1%
2
2V2
3
3V2
4
4V2
S6
8
14.31
3.96
1.53
• 33
.10
• 03
.01
8.46
3.26
• 71
.21
.08
.03
.01
15.31
5.92
1.28
.39
• 14
.06
.03
.02
.01
9.64
2.09
.64
.24
.11
.05
.03
.01
13-79
2.99
• 91
.34
.15
.07
.04
.02
.01
4.09
1.25
• 47
.21
.10
.06
.03
.01
5-34
1.63
.61
.27
.13
.07
:o4
.01
8.32
2.54
-96
• 43
.21
.12
.07
.02
.01
12.01
3.67
1.38
.62
.30
.17
.09
.03
.01
6.53
2.45
I. II
• 54
.30
• 17
.06
.03
.01
Size of
pipe
Delivery in cubic feet of compressed air per minute at
80 pounds gage
77-4
92.9
124.0
152
232
3io
387
465
620
774
Equivalent delivery in cubic feet of free air per minute
500
600
800
IOOO
1500
200O
2500
3000
4000
5000
2V2
3%
4
4V2
I
7
8
9
10
12
14
16
10.81
3-83
1.73
.85
• 47
.27
.10
.05
.02
.01
5-6J
2.46
1.22
.68
.39
.15
.06
.03
.02
.01
9.86
4.42
2.18
1. 19
.69
.27
.12
.06
.03
.02
.01
6.64
3.29
1.82
1.04
.40
.18
.09
.05
.03
I5.4I
7.62
4-24
2.43
• 95
.43
.22
.12
.06
13.62
7-58
4-32
1.69
• 77
• 39
.21
.12
11.79
6.88
2.64
1. 19
.60
.33
.19
9-72
3-79
1.73
.87
.48
.28
6.78
3.07
1.55
.85
• 49
10.55
4-79
2.46
1.33
-77
.30
.14
.07
.01
.02
.01
.03
.01
.05
.02
.09
.04
Flow of Compressed Air 363
Flow of Compressed Air at 100 Pounds Gage
(Loss of Pressure in Pounds per 1000 Feet.)
Size of
pipe
Delivery in cubic feet of compressed air per minute at
loo pounds gage
6.41
19.22
22.39
25.62
31.62
38.44
51.24
Equivalent delivery in cubic feet of free air per minute
So
75
100
125
150
175
200
250
300
400
i
1%
1%
j 2
2%
3
3%
4
4%
6
8
11.89
3.29
1.28
.27
.08
.03
.01
7.42
2.87
.62
• 19
.07
.03
.01
13-20
5. ii
1. 15
.34
.12
.05
.02
.01
7.75
1.68
.52
.19
.08
.04
.02
.01
11.42
2.48
.76
.29
.13
.06
.03
.02
.01
3.36
1.03
• 39
.17
.09
.04
.03
.01
4-43
1.36
• 51
.23
.12
.06
.04
.02
.01
6.72
2.06
• 77
.35
• 17
• 09
.05
.02
.01
9-95
3.04
1. 14
• 51
.25
.14
.08
.03
.01
5-40
2.06
• 92
.45
• 25
.15
.05
.03
.01
Size of
pipe
Delivery in cubic feet of compressed air per minute at
100 pounds gage
63.24
76.88
102.5
126.5
192.2
256.2
316.2
384.4
512.4
632.4
Equivalent delivery in cubic feet of free air per minute
500
600
800
IOOO
1500
2OOO
25OO
3000
4000
5000
2V2
3
31/2
4
4%
6
7
8
9
10
12
14
16
8.21
3.08
1.39
.68
• 38
.22
.08
.04
.02
.01
12.21
4-58
2.14
1.03
• 57
• 33
.12
•05
.03
.02
.01
8.13
3-67
1.81
1. 00
• 57
.22
.IO
.05
.03
.02
.01
12.39
5-6o
2.76
1.23
.88
• 34
.16
.08
.04
.03
.01
12. 8l
6.68
3-51
2.03
.78
.36
.18
.09
.05
.02
.01
II-35
6.61
3-62
1.41
.67
.33
.18
.10
.04
.02
.01
9.56
5-51
2.14
• 97
• 49
• 27
.16
.06
.03
.01
14.04
8. ii
3.16
1.44
• 76
• 39
.23
.09
.04
.02
14.48
5-59
2.55
1.30
• 72
• 41
.16
• 07
.04
8.51
3.88
1.98
1.07
.63
.25
.11
.06
364 Flow of Compressed Air
Flow of Compressed Air at 125 Pounds Gage
(Loss of Pressure in Pounds per 1000 Feet.)
Size of
pipe
Delivery in cubic feet of compressed air per minute at
125 pounds gage
5-26
7.89
10.51
13.15
15-79
18.41
21.05
26.30
31.58
42.10
Equivalent delivery in cubic feet of free air per minute
So
75
100
125
150
175
200
250
300
400
i
i%
i%
2
2V2
Stt
4
4V2
6
8
9.88
2.70
1. 05
.23
.07
.03
.01
22.20
6.07
2.37
• Si
.16
.06
.03
.01
39.50
10.82
4.22
.91
.28
.10
.05
.02
.01
16.88
6.58
1.42
• 43
.16
.07
.04
.02
.OI
24-33
9-47
2.04
.63
.23
.11
.05
.03
.02
.01
33-05
12.90
2.78
.85
.32
.14
.07
.04
.02
.01
16.84
3.63
I. II
.42
.19
.09
• 05
.03
.01
26.30
5.68
1.73
.65
.29
.15
.08
.05
.02
.OI
37-90
8.18
2.51
• 94
.42
.21
.12
.07
.03
.01
14.51
4-44
1.67
.75
• 37
.21
.12
.05
.02
.01
Size of
pipe
Delivery in cubic feet of compressed-air per minute at
125 pounds gage
52.60
63.20
84.20
I05.I
157-9
210.5
263.0
315.8
422.0
526.0
Equivalent delivery in cubic feet of free air per minute
500
600
800
1000
1500
2000
2500
3000
4000
5000
2
2V2
3
3V2
4
4V2
6
8
9
10
12
a
16
22.68
6. 95
2.61
1.18
• 58
.32
.18
.07
.03
.02
.01
IO.OO
3.76
1.69
.84
.46
.27
.10
.05
.02
.01
.01
17.80
6.68
3.01
1-49
.83
• 47
.18
.08
.04
.02
.01
.01
10.42
4.71
2.32
1.29
• 74
.29
.13
.07
.04
.02
.OI
23.48
10.59
5-23
2.90
1.65
.64
.29
.15
.08
.05
.02
.01
18.81
9-30
5.15
2.94
1. 15
.52
.26
.15
.08
.03
.02
.01
29.40
14.52
8.05
4.60
1. 80
.82
.41
.23
.13
.05
.02
.01
20.90
11-59
6.63
2.59
1.18
.60
• 33
.19
.07
.03
.02
20.61
11.80
4.61
2.19
i. 06
.58
.34
.13
.06
.03
32.20
18.45
7.20
3-27
1.65
.90
.53
.21
.10
.05
Effect of Bends and Fittings. The formulae quoted above are for the
flow of air through straight pipes. For the resistance due to curves, valves
and fittings, see the effect of bends and fittings under the flow of gas in
pipes, page 3 24. In this connection it is well to note that all piping and fit-
tings for airlines should be galvanized, as the scale from black pipe finds its
way to air hammers, drills and cylinders, and causes considerable trouble.
Fifth Roots and Fifth Powers 365
Fifth Roots and Fifth Powers
|1
1
JD £
L
li
I
li
I
li
1
Z%
£
£°
P!
t» *
£*
§
1°
&
.10
.000010
2.30
64.363
(>.L
I 10737
ii. 6
210 034
20. i
3533059
.15 .000075
2.35
71 . 670
\ 6.5 11603
n. 8
228 776
2O. (
3 709 677
.20
.000320
2.40
79.626
: 6.6 12523
12.0
248 832
20.8
3 893 289
•25
.000977
2.45
88.273
i 6-'
' I350I
12.2
27027
21.0
4 084 101
• 30
.002430
2.50
97.656
6.*
14539
12.4
29.3 16
21.2
4 282 322
• 35
.005252
2.55
107.820
6.9 15640
12. (
317 58o
21.4
4 488 166
.40
.010240
2.60
118.814
7.0 16807
12.8
34359
21.6
4 701 850
.45
.018453
2.70
143.489
7-1
18042
13-0
371 293
21.8
4 923 597
• 50
.031250
2.80
172.104
7.2
19349
13-2
400746
22.0
5 153 632
• 55
.050328
2.90
205.111
7-3
20731
13-4
432 040
22.2
5 392 186
.60
.077760
3.00
243.000
7-4
22190
13-6
465 259
22.4
5 639 493
.65
.116029
3.10
286.292
7-5
23730
13-8
500490
22.6
5 895 793
.70
. 168070
3-^20
335-544
7.6
25355
14.0
537 824
22.8
6 161 327
• 75
.237305
3-30
391-354
7-7
27068
14.2
577 353
23.0
6 436 343
.80
.327680
3-40
454-354
7-8
28872
14.4
619 174
23.2
6 721 093
• 85
.443705
3-50
525.219
7-9
30771
14.6
663383
23-4
7015834
.90
.590490
3.6o
604.662
8.0
32768
14.8
710 082
23.6
7 320 825
• 95
.773781
3.70
693.440
8.1 34868
15.0
759 375
23-8
7 636 332
1. 00
I.OOOOO
3.8o
792.352
8.2 37074
15-2
811 368
24.0
7 962 624
1.05
1.27628
3-90
902.242
8.3
39390
15-4
866 171
24.2
8 299 976
1. 10
1.61051
4.00
1024.00
8.4
41821
15-6
923896
24-4
8 648 666
i. IS
2. oi 135
4.10
1158.56
8.5 44371
15.8
984658
24.6
9 008 978
1.20
2.48832
4.20
1306.91
8.6! 47043
16.0
048 576
24.8
9381200
1.25
3.05176
4-30
1470.08
8.7
49842
16.2
US 771
25.0
9 765 625
1.30
3.71293
4-40
1649.16
8.8
52773
16.4
186 367
25.2
o 162 550
1-35
4.48403
4-50
1845.28
8.9 55841
16.6
260493
25-4
o 572 278
1.40
5.37824
4.60
2059.63
9-0
59049
16.8
338 278
25.6
0995116
:i-45
6.40973
4-70
2293-45
9-1
62403
17.0
419 857
25.8
I 431 377
1.50
7-59375
4.80
2548.04
9-2
65908
17.2
505 366
26.0
I 881 376
1.55
8.94661
4.90
2824.75
9-3
69569
17-4
594 947
26.2
2 345 437
1. 60
10.4858
5.00
3125.00'
9-4
73390
17.6
688 742
26.4
2823886
1.65
12.2298
5.10
3450.25
9-5
77378
17.8
786899
26.6
3317055
1.70
14.1986
5-20
3802.04
9-6
81537
18.0
889 568
26.8
3825381
1-75
16.4131
5-30
181.95
9.7 85873
18.2
996903
27.0
4 348 907
i. 80
18.8957
5-40
591.65
9.8' 90392
18.4
109 061
27.2
4 888 280
1.85
21 . 6700
5-50
032.84
9-9
95099
18.6
226 203
27.4
5 443 752
1.90
24.7610
5.6o
507.32
10. 0
IOOOOO
18.8
348 493
27.6
6015681
1.95
28.1951
5-70
5016.92
IO.2
110408
19.0
476 099
27.8
6 604 430
2.00
32.0000
5.8o
563.57
10.4
121 665
19.2
609193
28.0
7 210 368
2.05
36.2051
5-90
149.24
10.6
133 823
19.4
747 949
28.2
7833868
2.10
4O.84IO
6.00
776.00
10.8
146 933
19.6
892 547
8.4
18 475 309
2.15
45-9401
6.10
445.96
II. 0
161 051
19.8
043 1 68
8.6
C9 135 075
2-20 51.5363
6.20
161.33
II. 2
176 234
20. 0
200000
8.8
t9 813 557
2.25
57.6650
6.30
#24.37
II. 4
192 541
20.2
363 232
9.0 <
jo 51 1 149
366 Decimals of a Foot
Fifth Roots and Fifth Powers (Concluded)
S
1
fc^
fc
Jo
fc
Jo
L
5
I?
1
Is
1
la
0
AH
|a
|
29.2
21 228 253
38.5
84 587 005
58
656 356 768
79
3 077 056 399
29.4
21 965 275
39-0
90 224 199
59
714 924 299
80
3 276 800 ooo
29.6
22 722 628
39-5
96 158 012
60
777 600 ooo
81
3 486 784 401
29.8
23 500 728
40
102 40O OOO
61
844 596 301
82
3 707 398 432
30.0
24 300 ooo
41
115 856 201
62
916 132 832
83
3 939 040 643
30.5
26 393 634
42
130 691 232
63
992 436 543
84
4 182 119 424
3i.o
28 629 151
43
147 008 443
64
I 073 741 824
85
4 437 053 125
31-5
31 013 642
44
164 916 224
65
i 160 290 625
86
4 704 270 176
32.o
33 554 432
45
184 528 125
66
I 252 332 576
87
4 984 209 207
32.5
36 259 082
46
205 962 976
67
I 350 125 107
88
5 277 319 168
33-0
39 135 393
47
229 345 007
68
I 453 933 568
89
5 584 059 449
33-5
42 191 410
48
254 803 968
69
I 564 031 349
90
5904900000
34-0
45 435 424
49
282 475 249
70
i 680 700 ooo
91
6 240 321 451
34-5
48 875 98o
50
312 500 ooo
71
I 804 229 351
92
6 590 815 232
35-0
52 521 875
51
345 025 251
72
I 934 917 632
93
6 956 883 693
35-5
56 382 167
52
380 204 032
73
2 073 071 593
94
7 339 040 224
36.0
60 466 176
53
418 195 493
74
2 219 OO6 624
95
7 737 809 375
36.5
64 783 487
54
459 165 024
75
2 373 046 875
96
8 153 726 976
37-0
69 343 957
55
503 284 375
76
2 535 525 376
97
8 587 340 257
37-5
74 157 715
56
550 731 776
77
2 706 784 157
98
9 039 207 968
38.0
79 235 168
57
601 692 057
78
2 887 174 368
99
9 509 900 499
Decimals of a Foot for Each %4th of an Inch
Inch
|
|
o
I
43
.S
1
o
•S
8
1
1
1
1
1"
o
8
1
o
M
M
PO
«*•
in
NO
*"
00
Ov
M
0
0
.0833
1667
.2500
.3333
.4167
.5000
.5833
.666'
r -75oc
•8333
.9167
%*
.0013
.0846
1680
.2513
.3346
.4180
.5013
.5846
.668c
> .75i;
.8346
.9180
.0026
.0859
1693
.2526
.3359
.4193
.5026
.5859
.669,
J .752^
.8359
-9I93
%4
.0039
.0872
1706
.2539
.3372
.4206
.5039
.5872
.67o<
) .7535
-8372
.9206
.0052
.0885
1719
.2552
.3385
.4219
.5052
.5885
.6711
) -7552
-8385
.9219
%4
.0065
.0898
1732
• 2565
.3398
4232
.5065
.5898
.673-
2 .7565
8398
.9232
%2
.0078
.O9II
1745
.2578
.3411
.4245
.5078
• 5911
.6745(457*
.8411
.9245
%4
.0091
.0924
1758
.2591
.3424
.4258
.5091
.5924
.6758 .7591
.8424
.9258
Vs
.0104
.0937
1771
.2604
• 3437
.4271
-5I04
.5937
.677
[ . 760^
.8437
.9271
%4
.0117
.0951
1784
.2617
• 3451
.4284
.5117
• 5951
.678.
I .7617
.8451
.9284
%2
.0130
.0964
1797
.2630
.3464
.4297
.5130
.5964
.679'
r -763C
.8464
.9297
H'64
.0143
.0977
1810
.2643
• 3477
.4310
.5143
• 5977
.68ic
> .7643
.8477
• 9310
.0156
.0990
1823
.2656
• 3490
.4323
.5156
• 5990
.682;
.7656
.8490
• 9323
18/64
.0169
.1003
1836
.2669
3503
.4336
.5169
.6003
.683*:
.7669
.8503
9336
7/32
0182
.1016 .
1849
.2682
35i6
• 4349
.5182
.6016
.6845
.7682
.8516
• 9349
15/64
0195
.1029 .
1862
.2695
.3529
.4362
.5195
.6029
.6862
7695
.8529
.9362
%
0208
.1042 .
1875
.2708
• 3542
•4375
.5208
.6042
.6875
.7708
.8542
• 9375
17/64
O22I
.1055 •
1888
.2721
.3555
• 4388
-5221
.6055
6888
.7721
.8555
-9388
o"
%2
0234
.1068 .
1901
.2734
.3568
.4401
.5234
.6068
6901
• 7734
,8568
• 9401
Decimals of a Foot 367
Decimals of a Foot for Each ^64th of an Inch (Concluded)
Inch
8
8
8
8
§
I
1
1
o
1
1
1
c
CJ
CJ
I
o
(3
o
u
I
o
0
M
«
CO
"*
l/>
0
N
00
Ov
M
1%4
.0247
.1081
.1914
.2747
.3581
.4414
.5247
.6081
.6914
• 7747
.8581
.9414
5/16
.0260
.1094
.1927
.2760
• 3594
.4427
.5260
.6094
.6927
.7760
.8594
.9427
21/64
.0273
.1107
.1940
.2773
.3607
.4440
.5273
.6107
.6940
• 7773
.8607
•9440
^32
.0286
.1120
.1953
.2786
.3620
• 4453
.5286
.6120
.6953
• 7786
.8620
.9453
2%4
.0299
.1133
.1966
.2799
.3633
.4466
.5299
.6133
.6966
• 7799
.8633
.9466
.0312
.1146
.1979
.2812
.3646
• 4479
• 5312
.6146
.6979
.7812
.8646
• 9479
25/64
.0326
.1159
.1992
.2826
.3659
• 4492
.5326
.6159
.6992
.7826
.8659
• 9492
13/32
.0339
.1172
.2005
.2839
.3672
.4505
• 5339
.6172
.7005
.7839
.8672
.9505
27/64
.0352
.1185
.2018
.2852
.3685
.4518
• 5352
.6185
.7018
-7852
.8685
.9518
.0365
.1198
.2031
.2865
.3698
.4531
.5365
.6198
.7031
.7865
.8698
.9531
2%4
.0378
.1211
.2044
.2878
• 3711
.4544
.5378
.6211
.7044
.7878
.8711
• 9544
15/32
.0391
. 1224
.2057
.2891
.3724
• 4557
• 5391
.6224
.7057
.7891
.8724
• 9557
.0404
.1237
.2070
.2904
.3737
• 4570
• 5404
.6237
.7070
.7904
.8737
.9570
%
.0417
.1250
.2083
.2917
• 3750
.4583
• 5417
.6250
.7083
.7917
.8750
.9583
33/64
.0430
.1263
.2096
.2930
.3763
.4596
• 5430
.6263
.7096
• 7930
.8763
.9596
17/32
.0443
.1276
.2109
.2943
.3776
.4609
• 5443
.6276
.7109
• 7943
.8776
.9609
35/64
.0456
.1289
.2122
.2956
.3789
.4622
.5456
.6289
.7122
.7956
.8789
.9622
.0469
.1302
.2135
.2969
.3802
.4635
.5469
.6302
.7135
.7969
.8802
.9635
37/64
.0482
.1315
.2148
.2982
.3815
.4648
.5482
.6315
.7148
.7982
.8815
.9648
19/32
.0495
.1328
.2161
.2995
.3828
.4661
• 5495
.6328
.7161
• 7995
.8828
.9661
39/64
.0508
.1341
.2174
.3008
.3841
.4674
.5508
.6341
.7174
.8008
.8841
.9674
.0521
.1354
.2188
.3021
.3854
.4688
• 5521
.6354
.7188
.8021
.8854
.9688
4V64
.0534
.1367
.2201
.3034
.3867
• 4701
• 5534
.6367
.7201
.8034
.8867
• 9701
2Ml2
.0547
.1380
.2214
.3047
.3880
.4714
• 5547
.6380
.7214
.8047
.8880
.9714
.0560
.1393
.2227
.3060
.3893
.4727
.556o
.6393
.7227
.8060
.8893
.9727
Hie
.0573
.1406
.2240
.3073
.3906
.4740
.5573
.6406
.7240
.8073
.8906
• 9740
45/64
.0586
.1419
.2253
.3086
.3919
• 4753
-5586
.6419
.7253
.8086
-8919
.9753
28/82
.0599
.1432
.2266
.3099
• 3932
.4766
• 5599
.6432
.7266
.8099
.8932
.9766
47/64
.0612
.1445
.2279
.3112
• 3945
• 4779
.5612
.6445
.7279
.8112
.8945
.9779
%
.0625
.1458
.2292
.3125
• 3958
• 4792
.5625
.6458
.7292
.8125
.8958
• 9792
4%4
.0638
.1471
.2305
.3138
• 3971
.4805
.5638
.6471
.7305
.8138
.8971
.9805
2V32
.0651
.1484
.2318
.3151
.3984
.4818
.5651
.6484
.7318
.8151
.8984
.9818
5 ^64
.0664
.1497
.2331
.3164
• 3997
.4831
.5664
.6497
.7331
.8164
.8997
.9831
13/16
.0677
.1510
.2344
• 3177
.4010
.4844
.5677
.6510
• 7344
.8177
.9010
.9844
53/64
.0690
.1523
.2357
.3190
.4023
.4857
.5690
.6523
• 7357
.8190
.9023
.9857
27/82
.0703
.1536
.2370
.3203
.4036
.4870
.5703
.6536
• 7370
.8203
.9036
.9870
55/64
.0716
.1549
.2383
.3216
.4049
.4883
.5716
.6549
.7383
.8216
.9049
.9883
.0729
.1562
.2396
.3229
.4062
.4896
.5729
.6562
.7396
.8229
.9062
.9896
57/64
.0742
.1576
.2409
.3242
.4076
.4909
• 5742
.6576
.7409
.8242
.9076
.9909
2%2
• 0755
.1589
.2422
• 3255
.4089
.4922
• 5755
.6589
• 7422
.8255
.9089
.9922
5%4
.0768
.1602
. 2435
.3268
.4102
• 4935
.5768
.6602
.7435
.8268
.9102
• 9935
15/16
.0781
.1615
.2448
.3281
.4115
.4948
.5781
.6615
.7448
.8281
.9U5
.9948
6%4
.0794
.1628
.2461
.3294
.4128
.4961
• 5794
.6628
.7461
.8294
.9128
.9961
8^,30
.0807
.1641
.2474
.3307
.4141
• 4974
.5807
.6641
• 7474
.8307
.9141
• 9974
6%I
.0820
.1654
.2487
• 3320
.4154
.4987
.5820
.6654
.7487
.8320
-9IS4
.9987
I
I. 0000
368
Decimals of an Inch
Decimals of an Inch for Each Ve4th
V32
%4>
Decimal
Fraction
%2
%4
Decimal
Fraction
I
.015625
33
.515625
I
2
.03125
17
34
.53125
3
.046875
35
.546875
2
4
.0625
Vie
18
36
.5625
9/16
5
.078125
37
578125
3
6
.09375
19
38
•59375
7
. 109375
39
.609375
4
8
.125
%
20
40
.625
%
9
.140625
41
.640625
5
10
. 15625
21
42
.65625
ii
. 171875
43
.671875
6
12
.1875
3/16
22
44
.6875
*H«
13
.203125
45
.703125
7
14
.21875
23
46
.71875
IS
.234375
47
.734375
8
16
.25
&
24
48
.75
8/4
17
.265625
49
.765625
9
18
.28125
25
50
.78125
19
.296875
51
.796875
10
20
.3125
5/16
26
52
.8125
13/16
21
.328125
53
.828125
II
22
•34375
27
54
.84375
23
.359375
55
.859375
12
24
•375
%
28
56
.875
%
25
.390625
57
.890625
13
26
.40625
29
58
.90625
27
.421875
59
.921875
14
28
.4375
7/16
30
60
.9375
m&
29
.453125
61
.953125
15
30
.46875
31
62
.96875
31
.484375
63
.984375
16
32
.5
%
32
64
I
i
Wire and Sheet Metal Gages 369
Wire and Sheet Metal Gages in Approximate Decimals of an Inch
(Adopted by the Association of American Steel Manufacturers, Dec. 10, 1908.)
|
«<*«
08 • .^
|
l«s
1
g
A
||
•a3
•c ^ rt
v Q-z
•^H § (U tH £
1
ffsf
'gee g
- .§
jfl
||
tlfrO
H
ID co
gpq1^
»4jwlfcff
§
!*£
&
*c a
O
<
&*
H
W
®
pq
O
7-0
.500
.500
7-O
6-0
.469
.460
.464
6-0
5~o
438
.430
.450
.432
5~o
4-0
.406
.460
.394
.400
• 454
.400
4-o
ooo
• 375
.410
.363
.360
.425
•372
ooo
oo
• 344
^365
.331
.330
.380
• o/^
.348
oo
0
• 313
.325
• 307
.305
.340
.324
O
I
.281
.289
.283
.285
.300
.227
.300
I
2
.266
.258
.263
.265
.284
.219
.276
2
3
.250
.229
.244
.245
.259
.212
.252
3
4
.234
.204
.225
.225
.238
.207
.232
4
5
.219
.182
.207
.205
.220
.204
.212
5
6
.203
.162
.192
.190
.203
.201
.192
6
7
.188
• 144
.177
.175
.180
.199
.176
7
8
.172
.128
.162
.160
.165
.197
.I60
8
9
.156
.114
.148
.145
.148
.194
.144
9
10
.141
.102
.135
.130
.134
.191
.128
10
ii
.125
.0907
.121
.118
.120
.188
.116
ii
12
.109
.0808
.106
.105
.109
.185
.104
12
13
.0938
.072
.0915
.0925
.095
.182
.092
13
14
.0781
.0641
.080
.0806
.083
.180
.080
14
15
.0703
.0571
.072
.070
.072
.178
.072
15
16
.0625
.0508
.0625
.061
.065
.175
.064
16
17
.0563
• 0453
.054
.0525
.058
.172
.056
17
18
.050
.0403
.0475
.045
.049
.168
.048
18
19
.0438
• 0359
.041
.040
.042
.164
.040
19
20
.0375
.032
.0348
.035
.035
.161
.036
20
21
.0344
.0285
.0318
.031
.032
.157
.032
21
22
.0313
.0253
.0286
.028
.028
.155
.028
22
23
.0281
.0226
.0258
.025
.025
.153
.024
23
24
.025
.0201
.023
.0225
.022
.151
.022
24
25
.0219
• 0179
.0204
.020
.O2O
.148
.020
25
26
.0188
• 0159
.0181
.018
.018
.146
.018
26
27
.0172
.0142
.0173
.017
.Ol6
.143
.0164
27
| 28
.0156
.0126
.0162
.016
.014
.139
.0149
28
29
.0141
.0113
.015
.015
.013
.012
.134
. 127
.0136
.0124
29
30
31
.0109
.0089
.0132
.013
.010
.120
.0116
31
32
.0102
.008
.0128
.012
.009
.115
.0108
32
33
.0094
.0071
.0118
.Oil
.008
.112
.010
33
34
.0086
.0063
.0104
.010
.007
.110
.0092
34
35
.0078
.0056
.0095
.0095
.005
.108
.0084
35
36
.007
.005
.009
.009
.004
.106
.0076
36
37
.0066
.0045
.0085
.0085
.103
.0068
37
38
.0063
.004
.008
.008
.101
.006
38
39
.0035
.0075
.0075
.099
.0052
39
40
.0031
.007
.007
.097
.0048
40
370 Proportions of Screw Threads, Nuts and Bolt Heads
PROPORTIONS OF SCREW THREADS
NUTS AND BOLT HEADS
(Recommended by the Franklin Institute.)
Screw Threads.
D = diameter of bolt, W = width of flat, top or bot-
Di = diameter at root of thread, torn of each thread,
P = pitch, T = depth of V,
N = number of threads per inch, T\ = depth of thread.
P = ~ • T = cos 30° P = .866 P.
D = Di + 2 X 0.866 X 0.75 P = Di + 1.299 P.
Square and Hexagon Heads and Nuts. Short diameter of rough
nut =» il/2 X diameter of bolt + Vs inch.
Short diameter of finished nut = i% X diameter of bolt + Vie inch.
Thickness of rough nut = diameter of bolt.
Thickness of finished nut = diameter of bolt - Vie inch.
Short diameter of rough head = iV2 X diameter of bolt+ Vs inch.
Short diameter of finished head = iM$ X diameter of bolt + Vie inch.
Thickness of rough head = Vz of short diameter of head.
Thickness of finished head = diameter of bolt — V\Q inch.
The long diameter of a hexagon nut may be obtained by multiplying
the short diameter by 1.155 and the long diameter of a square nut by
multiplying the short diameter by 1.414.
In 1864, a committee of the Franklin Institute recommended the above
system of screw threads and bolts, which was devised by Mr. William
Sellers of Philadelphia. This system, as far as it relates to screw threads,
is generally used in the United States, but the proportions of bolt heads
and nuts have not been generally accepted because the sizes of bar re-
quired to make the nuts are special, and extra work is necessary to make
the bolt heads. Under the name of United States Standard, the U. S.
Navy Department in 1868 adopted the Sellers System, except for finished
heads and nuts, which it made the same as for rough heads and nuts.
Dimensions of Screw Threads, Nuts and Bolt Heads 371
Dimensions of Screw Threads, Nuts and Bolt Heads
(Recommended by the Franklin Institute.)
Bolts and threads
J
Tensile strength
LJ
.2
1 w
*$
I*8
1'
Bottom of thread
3
1
?1
»! $
•"
1
u •-<
HI
05^3
*o
a
1
:§?
0) 4->
fa
1*
CTJ
E
O aj
2 o< D
Nt3 rt -o
|lil
^
5
^l"'a
^l"'5
^I-'s
Inches
Inch
Inches
Square
inches
Square
inches
Pounds
Pounds
Pounds
V4
20
.0063
.185
.027
.049
269
336
471
5/16
18
.0069
.240
.045
.077
454
568
795
16
.0078
.294
.068
.110
678
848
I 187
i?6
14
.0089
• 345
.093
.150
933
i 166
I 633
t£
13
.0096
.400
.126
.196
I 257
i 57i
2 2OO
9/ie
12
.0104
.454
.162
• 249
I 621
2026
2837
5/8
II
.0114
.507
.202
.307
2018
2523
3532
%
10
.0125
.620
.302
.442
3020
3775
5285
7/8
9
.0139
.731
.419
.601
4 193
5241
7338
I
8
.0156
.838
• 551
.785
55io
6888
9643
7
.0179
.939
.693
.994
6931
8664
12 129
i%
7
.0179
1.064
.890
1.227
8899
II 124
15573
i3/
6
.0208
I.I58
1.054
1.485
10541
13 176
18447
iVz
6
.0208
1.283
1.294
1.767
12938
I6I73
22642
sV2
.0227
1.389
I.5I4
2.074
IS 149
18936
26 511
5
.0250
1.490
1-744
2.405
17 441
21 801
30522
I7/8
5
.0250
I.6l5
2.048
2.761
20490
25613
35858
2
.0278
I.7II
2.300
3.142
23001
28751
40252
2*4
4%
.0278
1.961
3.021
3.976
30213
37766
52873
aj{
4
.0313
2.175
3.715
4.909
37163
46454
65035
2%
4
.0313
2.425
4.619
5-940
46 196
57745
80843
3
3%
.0357
2.629
5.427
7.069
54277
67 846
94985
3V4
3%
.0357
2.879
6.508
8.296
65092
81 365
113 911
3V4
.0385
3.100
7.548
9.621
75491
94364
132109
33/4
3
.0417
3-317
8.640
11.045
86412
108 015
151 221
4
3
.0417
3.567
9-991
12.566
99929
124 911
174 876
4V4
2%
.0435
3.798
11.328
14.186
113 302
141 628
198 279
4Va
28/4
.0455
4.027
12.738
15.904
127 405
159 256
222 959
48/4
2%
.0476
4-255
14.218
17.721
142 205
177 756
248 859
5
.0500
4.480
15.763
19.635
157 659
197 074
275903
2%
.0500
4-730
17.572
21.648
175 745
219 681
307 554
#!
2%
.0526
4-953
19.265
23.758
192 678
240 848
337 187
5%
2%
.0526
5.203
21 . 259
25.967
212 620
265 775
372085
6
2^4
.0556
5.422
23.091
28.274
230 947
288 684
404 157
372 Dimensions of Screw Threads, Nuts and Bolt Heads
Dimensions of Screw Threads, Nuts and Bolt Heads (Concluded)
(Recommended by the Franklin Institute.)
Bolts and threads
Rough nuts and heads
Shearing strength
Sfwl
In
y
1
1
Full bolt
Bottom of threac
jj TJ
6 <i) o
o5 &} bo
<L>
OJ 0)
as
.5 ^
fi
oj ra
a
"o
1-8
3
§> M £ -^
^
0 o, <u
° M J3^
|lj[
§sg^
^ oj rt
fi-l
g-Q
_o
|l
PI -a «
o-d gc
£-d § c
O T3 j| C
ro ®
jj
3
'tt*
r^
< § £-s
"!«
<5 ^ «""
^ § g1'^
W
a
< a
a
< a
In.
Pounds
Pounds
Pounds
Pounds
In.
In.
In.
In.
In.
14
368
491
202
269
y2
.707
.578
&
1/4
%6
575
767
341
454
1%9
.840
.686
%6
X%4
%
828
i 104
509
678
Hie
• 972
• 794
%
11,^2
m
i 127
1503
700
933
25/32
1.105
.902
7/16
25/64
y2
1472
1963
943
I 257
7/8
1.237
I. Oil
Jjl
7/io
9/ie
i 864
2485
I 216
I 621
31,32
1-370
I. Up
%6
3-Ve4
2301
3068
1514
2018
lVl6
1.502
1.227
%
17/82
%
3314
44i8
2 265
3 020
iH
1.768
1-444
%
%
7/8
45io
6013
3145
4 193
I7/16
2.033
1. 660
7/8
23/S2
I
5891
7854
4 133
55io
I5/^
2.298
1.877
I
18/io
i-Vs
7455
9940
5198
6931
2.563
2.093
1-^8
2%2
i%
9 204
12272
6674
8899
2
2.828
2.310
1%
i
1%
II 137
14849
7006
I054I
23/16
3-093
2.527
1%'
I%2
13253
17 671
9 704
12938
2%
3-358
2.743
1%
I%6
1%
15554
20739
n 362
15 149
29/16
3.623
2.960
1%
I%2
13/4
18 040
24053
13081
I744I
2%
3-889
3.176
I3/4
1%
1%
20709
27 612
15368
20490
2l5/16
4-154
3-393
I7/8
I15/82
2
23562
31 4i6
17251
23001
3-^8
4-419
3-609
2
I9/16
2V4
29 821
39 76l
22660
30213
3V2
4-949
4-043
2^4
1%
36 815
49087
27872
37163
37/8
5-479
4.476
2l/2
i15/ie
2%
44547
59396
34647
46196
4V4
6.010
4-909
2%
2^8
3
53015
70686
40708
54277
4%
6.540
5,342
3
25/16
62 219
82 958
48819
65092
5
7.070
5-775
3V4
2^2
iVa
72 158
96211
56618
75491
5%
7.600
6.208
3V2
21Vl6
38/4
82835
no 447
64809
86 412
5%
8.131
6.641
3%
2%
4
94 248
125 664
74947
99929
61/8
8.661
7.074
4
3Vl6
4V4
106 397
141 863
84977
113 302
9.191
7.5o8
4-Vi
3H
119 282
159 043
95554
127 405
6%
9-721
7-941
4V2
37/16
43/4
132904
177 205
106 654
142 205
7V4
10.252
8-374
4%
3%
5
147 263
196 350
118 244
157 659
75/X8
10.782
8.807
5
318/ie
5V4
162 356
216 475
131 809
175 745
8
11.312
9.240
5^4
4
$*
178 187
237 583
144 509
192 678
8%
11.842
9.673
43/ie
53/4
194 754
259 672
159 465
212 620
83/4
12.373
10.106
53/4
4%
6
212 057
282 743
173 210
230 947
PVs
12.903
10.539
6
49/16
Area Factors for Tubes
373
AREA FACTORS FOR TUBES
Explanation of Table
This table of area factors may be used to calculate the sectional area of tubes
of any diameter and any wall thickness, both being expressed to the nearest
one thousandth of an inch. To apply the table, use the following
Rule. Subtract the thickness of the tube wall from the outside diameter,
both expressed in inches and decimals; then multiply this remainder by the
tabular area factor corresponding to the given thickness. The result will be the
sectional area of the tube in square inches.
Example. Find the sectional area of a tube whose outside diameter is 8%
inches and thickness of wall 0.284 inch.
Solution. Outside diameter less thickness =8.625 — 0.284=8.341.
Tabular area factor corresponding to the given thickness, 0.284 inch, is 0.8922,
which is found in the column headed .004 and opposite .28 in column one.
The required area is
8.341 X .8922= 7.442 square inches.
Note. When the thickness of wall exceeds one inch, add to the tabular area
factor corresponding to the decimal part of the thickness, one, two, or three,
etc., times the factor corresponding to i.ooo inch, as the case may be, thus:
Area factor for thickness of 1.625 inch will be
Area factor for .625=1.9635
Area factor for 1.000=3.1416
Area factor for 1.625 =5.1051
In like manner the area factor corresponding to a thickness of 2.625 inches will
be 1.9635 +(2 X 3.1416) = 8.2467.
Basis of Table. This table was calculated by means of the formula
A = *t(D-t),
where A = sectional area in square inches;
D= outside diameter in inches;
t = thickness of wall in inches.
Thick-
ness in
inches
.000
.001
.002
.003
.004
.005
.006
.007
.008
.009
.00
.0031
.0063
.0094
.0126
.0157
.0188
.0220
.0251
.0283
.01
.0314
.0346
.0377
.0408
.0440
.0471
.0503
.0534
.0565
.0597
.02
.0628
.0660
.0691
.0723
.0754
.0785
.0817
.0848
.0880
.0911
.03
.0942
.0974
.1005
.1037
.1068
.IIOO
.1131
.1162
.1194
.1225
.04
.1257
.1288
.1319
.1351
.1382
.1414
.1445
.1477
.1508
.1539
.05
.1571
.1602
.1634
.1665
.1696
.1728
.1759
.1791
.1822
.1854
.06
.1885
.1916
.1948
.1979
.2011
.2042
.2073
.2105
.2136
.2168
.07
.2199
.2231
.2262
.2293
.2325
.2356
.2388
.2419
.2450
.2482
.08
.2513
.2545
.2576
.2608
.2639
.2670
.2702
.2733
.2765
.2796
.09
.2827
.2859
.2890
.2922
.2953
.2985
.3016
.3047
.3079
.3110
.10
.3142
• 3173
.3204
.3236
.3267
.3299
.3330
.3362
.3393
.3424
.11
.3456
.3487
.3519
• 3550
.3581
.3613
.3644
.3676
.3707
.3738
.12
• 3770
.3801
.3833
.3864
.3896
.3927
.3958
.3990
.4021
.4053
.13
.4084
• 4115
.4147
.4178
.4210
.4241
.4273
.4304
.4335
.4367
.14
.4398
• 4430
.4461
.4492
.4524
-.4555
.4587
.4618
.4650
.4681
.15
• 4712
• 4744
• 4775
.4807
,4838
.4869
.4901
• 4932
.4964
.4995
374 Area Factors for Tubes
Area Factors for Tubes (Continued)
Thick-
ness in
.000
.001
.002
.003
.004
.005
.006
.007
.008
.009
inches
• 15
• 4712
• 4744
• 4775
.4807
.4838
.4869
.4901
• 4932
.4964
• 4995
.16
.5027
.5058
.5089
.5121
.5152
.5184
.5215
.5246
.5278
.5309
.17
.5341
• 5372
.5404
• 5435
-5466
• 5498
.5529
.5561
.5592
.5623
.18
.5655
.5686
.5718
• 5749
.5781
.5812
.5843
.5875
.5906
.5938
.19
.5969
.6000
.6032
.6063
• 6095
.6126
.6158
.6189
.6220
.6252
.20
.6283
• 6315
.6346
.6377
.6409
.6440
.6472
.6503
.6535
.6566
.21
-6597
.6629
.6660
.6692
.6723
.6754
.6786
.6817
.6849
.6880
.22
.6912
.6943
.6974
.7006
.7037
.7069
.7100
.7131
.7163
.7194
.23
.7226
.7257
.7288
• 7320
.7351
.7383
.7414
.7446
.7477
.7508
.24
• 7540
• 7571
.7603
.7634
.7665
.7697
.7728
.7760
• 7791
.7823
.25
.7854
.7885
-79I7
.7948
.7980
.8011
.8042
.8074
.8105
.8137
.26
.8168
.8200
.-8231
.8262
.8294
.8325
.8357
.8388
.8419
.8451
.27
.8482
.8514
.8545
.8577
.8608
.8639
.8671
.8702
.8734
.8765
.28
.8796
.8828
.8859
.8891
.8922
.8954
.8985
.9016
.9048
.9079
.29
.9111
.9142
.9173
.9205
• 9236
.9268
.9299
• 9331
.9362
-9393
.30
• 9425
• 9456
.9488
.9519
• 9550
.9582
.9613
.9645
.9676
.9708
.31
• 9739
• 9770
.9802
.9833
.9865
.9896
.9927
• 9959
.9990
1.0022
.32
1.0053
1.0085
1.0116
1.0147
1.0179
I. 0210
1.0242
1.0273
.0304
1.0336
.33
1.0367
1.0399
1.0430
1.0462
1.0493
1.0524 1.0556
1.0587
.0619
1.0650
.34
i. 0681
1.0713
1.0744
1.0776
1.0807
1.0838
1.0870
1.0901
.0933
1.0964
.35
1.0996
I . 1027
i . 1058
1.1090
I.II2I
I.H53
1.1184
I. 1215
.1247
I . 1278
.36
i . 1310
I . 1341
i • 1373
i . 1404
i • 1435
i . 1467
i . 1498
I . 1530
.1561
I • 1592
.37
i . 1624
I . 1655
1.1687
1.1718
I . 1750
i . 1781
i. 1812
I . 1844
.1875
I.I907
.38
i . 1938
1.1969
I.20OI
I . 2032
1.2064
1.2095
i . 2127
1.2158
.2189
I . 2221
• 39
i . 2252
I . 2284
I.23I5
1.2346
1.2378
1.2409
1.2441
I . 2472
.2504
1.2535
.40
1.2566
1.2598
I . 2629
1.2661
1.2692
1.2723
1.2755
1.2786
.2818
.2849
• 41
1.2881
I . 2912
1-2943
1.2975
1.3006
1.3038
1.3069
1.3100
.3132
,3163
.42
I.3I95
1.3226
1.3258
1.3289
1.3320
1.3352
1.3383
I.34I5
.3446
• 3477
.43
1-3509
1.3540
1.3572
1.3603
1.3635
1.3666
1.3697
1.3729
.376o
.3792
• 44
1.3823
1.3854
1.3886
I.39I7
1.3949
i.398o
1.4012
1.4043
.4074
.4106
• 45
I.4I37
1.4169
I . 4200
1.4231
1.4263
1.4294
1.4326
1.4357
.4388
.4420
.46
I.445I
1.4483
I.45I4
1.4546
1.4577
1.4608
1.4640
1.4671
• 4703
.4734
.47
1.4765
1-4797
1.4828
1.4860
1.4891
1.4923
1.4954
1.4985
.5017
.5048
.48
1.5080
1.5111
I.5I42
L5I74
1.5205
1.5237
1.5268
1.5300
• 5331
.5362
.49
1.5394
1.5425
1-5457
1.5488
I.55I9
I.555I
1.5582
1.5614
.5645
.5677
.50
I.57o8
1.5739
I-577I
1.5802
1.5834
1.5865
1.5896
1.5928
.5959
• 5991
.51
1.6022
1.6054
1.6085
1.6116
1.6148
1.6179
1.6211
1.6242
.6273
.6305
.52
1.6336
1.6368
1.6399
1.6431
I . 6462
1.6493
1.6525
1.6556
.6588
.6619
• 53
1.6650
1.6682
1.6713
1.6745
1.6776
i. 6808
1.6839
1.6870
1.6902
.6933
.54
1.6965
1.6996
1.7027
1.7059
1.7090
1.7122
I.7I53
I.7I85
1.7216
1.7247
• 55
1.7279
I.73IO
1.7342
1.7373
1.7404
1.7436
1.7467
1.7499
1.7530
1.7562
.56
1.7593
1.7624
1.7656
1.7687
I . 7719
1-7750
1.7781
I.78I3
1.7844
1.7876
• 57
1.7907
1-7939
1.7970
1.8001
1.8033
1.8064
1.8096
1.8127
1.8158
1.8190
.58
I.822I
1.8253
1.8284
I.83I5
1.8347
1.8378
1.8410
1.8441
1.8473
1.8504
Area Factors for Tubes 375
Area Factors for Tubes (Concluded)
Thick-
ness in
inches
.000
.001
.002
.003
.004
.005
.006
.007
.008
.009
.58
• 59
.60
.61
.8221
.8535
.8850
.9164
1.8253
1.8567
I. 8881
1.9195
1.8284
1.8598
I.89I2
1.9227
1.8315
1.8630
1.8944
1.9258
1.8347
1.8661
1.8975
1.9289
1.8378
1.8692
I.9OO7
I.932I
1.8410
1.8724
1.9038
1-9352
.8441
•8755
.9069
.9384
1.8473
1.8787
1.9101
I.94I5
1.8504
I. 8818
I.9I32
1.9446
.62
.63
.64
.65
.9478
• 9792
2.0106
2.0420
1.9509
1.9823
2.0138
2.0452
I-954I
1.9855
2.0169
2.0483
1.9572
1.9886
2.O200
2.0515
I .9604
1.9918
2.0232
2 .0546
1.9635
1.9949
2.0263
2.0577
1.9666
1.9981
2.0295
2.0609
.9698
.0012
2.0326
2.0640
1.9729
2.0043
2.0358
2.0672
I.976I
2.0075
2.0389
2.0703
.66
.67
.68
.69
2.0735
2.1049
2.1363
2.1677
2.0766
2.1080
2.1394
2.1708
2.0797
2.III2
2.1426
2.1740
2.0829
2.H43
2.1457
2.1771
2.0860
2.II74
2.1489
2.1803
2.0892
2 . 1206
2 . 1520
2 . 1834
2.0923
2 . 1237
2.I55I
2.1865
2.0954
2.1269
2.1583
2.1897
2.0986
2.1300
2.1614
2.1928
2.IOI7
2.I33I
2.1646
2.1960
.70
• 71
.72
• 73
2.1991
2.2305
2 . 2619
2.2934
2 . 2023
2.2337
2.2651
2.2965
2.2054
2 . 2368
2.2682
2.2996
2.2085
2.2400
2.2714
2 . 3028
2.2II7
2 . 2431
2 . 2745
2 - 3059
2 . 2148
2 . 2462
2.2777
2.3091
2. 2180
2.2494
2.2808
2.3122
2.22II
2.2525
2.2839
2.3154
2.2242
2.2557
2.2871
2.3185
2.2274
2.2588
2.2902
2.3216
• 74
• 75
.76
• 77
2.3248
2.3562
2.3876
2.4190
2.3279
2-3593
2.3908
2.4222
2.33II
2.3625
2-3939
2.4253
2.3342
2.3656
2.3970
2.4285
2-3373
2.3688
2.4002
2 . 4316
2.3405
2.3719
2.4033
2-4347
2.3436
2.3750
2.4065
2.4379
2.3468
2.3782
2.4096
2.4410
2.3499
2.3813
2.4127
2.4442
2.3531
2.3845
2.4159
2.4473
• 78
79
.80
.81
2.4504
2.4819
2.5133
2.5447
2.4536
2.4850
2.5164
2.5478
2.4567
2.4881
2.5196
2.5510
2 . 4599
2 . 4913
2.5227
2 . 5541
2 . 4630
2 . 4944
2.5258
2.5573
2.4662
2.4976
2.5290
2.5604
2.4693
2.5007
2.5321
2.5635
2.4724
2.5038
2.5353
2.5667
2.4756
2.5070
2.5384
2.5698
2.4787
2.5101
2.5415
2.5730
.82
.83
-84
.85
2.5761
2.6075
2.6389
2.6704
2.5792
2 . 6l07
2.6421
2.6735
2.5824
2.6138
2.6452
2.6766
2.5855
2.6l69
2 . 6484
2.6798
2.5887
2 . 62OI
2 . 6515
2 . 6829
2.5918
2.6232
2.6546
2 . 686l
2.5950
2 . 6264
2.6578
2.6892
2.5981
2.6295
2.6609
2.6923
2. 6OI2
2.6327
2.6641
2.6955
2.6044
2.6358
2.6672
2.6986
.86
.87
.88
.89
.90
• 91
.92
.93
2.7018
2-7332
2.7646
2.7960
2.8274
2.8589
2.8903
2.9217
2.7049
2.7363
2.7677
2.7992
2.8306
2.8620
2.8934
2.9248
2.7081
2.7395
2.7709
2.8023
2.8337
2.8651
2.8965
2.9280
2.7II2
2 . 7426
2.7740
2.8054
2.8369
2.8683
2.8997
2.93II
2 . 7143
2.7458
2.7772
2.8086
2.8400
2.8714
2.9028
2.9342
2 . 7175
2.7489
2.7803
2 . 72O6
2.7520
2.7835
2.7238
2.7552
2.7866
2.8180
2.8494
2.8808
2.9123
2.9437
2.7269
2.7583
2.7897
2.8212
2.8526
2.8840
2.9154
2.9468
2.7300
2.7615
2.7929
2.8243
2.8557
2.8871
2.9185
2.9500
2.8431
2.8746
2.9060
2.9374
2.8463
2.8777
2.9091
2-9405
• 94
-95
• 96
• 97
2.9531
2.9845
3-0159
3-0473
2.9562
2.9877
3.0I9I
3.0505
2-9594
2.9908
3.0222
3.0536
2.9625
2.9939
3-0254
3.0568
2.9657
2.9971
3.0285
3-0599
2.9688
3.0002
3.0316
3.0631
2.9719
3-0034
3.0348
3.0662
2.9751
3.0065
3-0379
3.0693
2.9782
3.0096
3.04H
3.0725
2.9814
3.0128
3.0442
3.0756
• 98
-.99
1. 00
1
3-0788
3.1102
3.1416
3.0819
3-II33
3-1447
3.0850
3.H65
3.1479
3.0882
3.H96
3.I5IO
3^0913
3-1227
3.1542
3-0945
3-1259
3-1573
3.0976
3.I29O
3.1604
3.1008
3.1322
3.1636
3-1039
3-1353
3.1667
3.1070
3.1385
3.1699
376 Weight Factors for Steel Tubes
WEIGHT FACTORS FOR STEEL TUBES
This table of weight factors may be used to calculate the weights per
foot length of steel pipe and tubes of any diameter and for any thick-
ness, both being expressed to the nearest one-thousandth inch. To
apply the table use the following:
Rule. Subtract the thickness of tube wall from the outside diameter, .
both being expressed in inches and decimals, then multiply the remainder
by the tabular weight factor corresponding to the given thickness. The
result will be the weight of tube in pounds per foot length.
Example. Find the weight in pounds per foot of a tube whose out-
side diameter is 8% inches and thickness of wall 0.284 inch.
Solution, (i) Outside diameter less thickness = 8.625 — 0.284 =
8.341; (2) tabular weight factor corresponding to the given thickness
of 0.284 inch is 3.033, which is found in column headed .004 and opposite
.28 in column one; (3) the required weight equals 8.341 X 3.033 =
25.30 pounds per foot.
Note. When the thickness of tube wall exceeds one inch, add to the
tabular weight factor corresponding to the decimal part of the given
thickness, once, twice, thrice, etc., that corresponding to i.ooo inch,
as the case may be, thus:
Weight factor for thickness of 1.625 will be
Weight factor for .625= 6.675
Weight factor for i . ooo = 10. 6802
Weight factor for 1.625 = 17.355
In like manner the weight factor corresponding to a thickness of
2.625 inches will be 6.675 + (2 X 10.6802) = 28.035.
Basis of Table. This table was calculated on an eight-slot Burk-
hardt machine by means of the formula
W = 10.680158 (D - i) t,
where W = weight of steel tube in pounds per foot;
D = outside diameter of tube in inches;
/ = thickness of tube wall in inches.
Weight one cubic inch steel = 0.2833 pound.
Weight Factors for Steel Tubes 377
Weight Factors for Steel Tubes, Pounds per Lineal Foot
(Based on weight of one cubic inch of steel equals .2833 pound.)
Thick-
ness in
.000
.001
.002
.003
.004
.005
.006
.007
.008
.009
inches
.00
.Oil
.021
.032
.043
.053
.064
.075
.085
.096
.01
.107
.117
.128
.139
.150
.160
.171
.182
.192
.203
.02
.214
.224
.235
.246
.256
.267
.278
.288
.299
.310
.03
.320
.331
.342
.352
.363
• 374
.384
• 395
.406
.417
.04
.427
.438
.449
.459
.470
.481
.491
.502
• 513
.523
.05
• 534
.545
• 555
.566
.577
.587
.598
.609
.619
.630
.06
.641
.651
.662
.673
.684
.694
.705
.716
.726
• 737
.07
.748
.758
.769
.780
• 790
.801
.812
.822
.833
.844
.08
.854
.865
.876
.886
.897
.908
.918
.929
• 940
• 951
.09
.961
.972
.983
• 993
1.004
1.015
1.025
1.036
1.047
1.057
.10
.068
.079
1.089
I.IOO
.in
1. 121
.132
.143
1. 153
.164
.11
.175
.185
1.196
1.207
.218
1.228
.239
.250
1.260
.271
.12
.282
.292
1-303
I.3M
.324
1-335
.346
.356
1.367
-378
.13
.388
• 399
1.410
1.420
• 431
1.442
.453
.463
I -474
.485
.14
• 495
.506
I.5I7
1.527
.538
1.549
• 559
• 570
1.581
.591
.15
.602
.613
1.623
1.634
.645
1.655
.666
.677
1.687
.698
.16
.709
.720
1-730
i.74i
• 752
1.762
• 773
.784
1-794
.805
.17
.816
.826
1.837
1.848
.858
1.869
.880
.890
1.901
.912
.18
.922
.933
1.944
1-954
.965
1.976
.987
• 997
2.008
2.019
.19
2.029
.040
2.051
2.061
2.072
2.083
2.093
2.104
2. 115
2.125
.20
2.136
2.147
2.157
2.168
2.179
2.189
2.200
2. 211
2.221
2.232
.21
2.243
2.254
2.264
2.275
2.286
2.296
2.307
2.318
2.328
2.339
.22
2-350
2.360
2.371
2.382
2.392
2.403
2.414
2.424
2.435
2.446
.23
2.456
2.467
2.478
2.488
2.499
2.510
2.521
2.531
2.542
2.553
.24
2.563
2.574
2.585
2.595
2.606
2.617
2.627
2.638
2.649
2.659
.25
2.670
2.681
2.691
2.702
2.713
2.723
2-734
2.745
2.755
2.766
.26
2.777
2.788
2.798
2.809
2.820
2.830
2.841
2.852
2.862
2.873
.27
2.884
2.894
2.905
2.916
2.926
2.937
2.948
2.958
2.969
2.980
.28
2.990
3.001
3-012
3.022
3-033
3-044
3-055
3.065
3-076
3-087
.29
3-097
3.108
3.119
3-129
3.140
3-I5I
3.l6l
3.172
3.183
3.193
.30
3.204
3-215
3.225
3.236
3.247
3-257
3.268
3-279
3.289
3-300
.31
3-3II
3-322
3.332
3-343
3-354
3.364
3-375
3.386
3.396
3.407
.32
3.418
3.428
3.439
3-450
3.46o
3-471
3.482
3-492
3-503
3.514
.33
3.524
3-535
3.546
3.556
3.567
3.578
3.589
3.599
3.610
3.621
.34
3.631
3.642
3.653
3.663
3.674
3-685
3.695
3.7o6
3.717
3.727
•35
3.738
3-749
3.759
3-770
3.781
3-791
3.802
3-813
3.823
3.834
.36
3.845
3.856
3.866
3.877
3.888
3.898
3.909
3.920
3-930
3.941
.37
3-952
3.962
3-973
3.984
3-994
4.005
4.OI6
4.026
4-037
4.048
.38
4.058
4.069
4.080
4.091
4.101
4. 112
4.123
4.133
4-144
4.155
.39
4-165
4.176
4-187
4-197
4.208
4.219
4.229
4.240
4-251
4.261
.40
4.272
4.283
4-293
4.304
4-315
4.325
4.336
4-347
4.358
4.368
.41
4.379
4-390
4.400
4.411
4.422
4-432
4-443
4-454
4.464
4-475
.42
4.486
4.496
4.507
4.518
4.528
4-539
4-550
4.500
4-571
4.582
.43
4.592
4-603
4.614
4.625
4.635
4.646
4.657
4-667
4.678
4.689
.44
4.699
4-710
4.721
4-731
4.742
4-753
4.763
4.774
4.785
4-795
.45
4.806
4.817
4.827
4.838
4.849
4.859
4.870
4.881
4.892
4.902
.46
4.913
4.924
4-934
4-945
4.956
4.966
4-977
4.988
4.998
5.009
.47
5.020
5.030
5.041
5.052
5.062
5-073
5.084
5-094
5-105
5.n6
.48
5.126
5.137
5.148
5-159
5.169
5.180
5.I9I
5.201
5-212
5-223
.49
5-233
5-244
5-255
5.265
5.276
5.287
5-297
5.308
5.319
5-329
•50
5.340
5.351
5.36i
5-372
5-383| 5.393
5.404
5-415
5.426
5.436
378 Weight Factors for Steel Tubes
Weight Factors for Steel Tubes, Pounds per Lineal Foot (Concluded)
(Based on weight of one cubic inch of steel equals .2833 pound.)
1 Thick-
ness in
.000
.001
.002
.003
.004
.005
.006
.007
.008
.009
inches
• So
5.340
5-351
5.36i
5-372
5.383
5-393
5.404
5.415
5.426
5.436
.51
5.447
5-458
5.468
5-479
5-490
5-500
5-5II
5-522
5-532
5-543
• 52
5.554
5.564
5-575
5-586
5.596
5-607
5-6l8
5.628
5.639
5-650
• 53
5.660
5.671
5-682
5-693
5.703
5.714
5.725
5-735
5-746
5-757
• 54
5.767
5-778
5.789
5-799
5-Slo
5.821
5.831
5.842
5-853
5-863
• 55
5.874
5-885
5.895
5.906
5.917
5.927
5-938
5-949
5.96o
5-970
.56
5.981
5-992
6.002
6.013
6.024
6.034
6.O45
6.056
6.066
6.077
• 57
6.088
6.098
6.109
6.120
6.130
6.141
6.152
6.162
6.173
6.184
.58
6.194
6.205
6.216
6.227
6.237
6.248
6.259
6.269
6.280
6.291
• 59
6.301
6.312
6.323
6.333
6.344
6.355
6.365
6.376
6.387
6.397
.60
6.408
6.419
6.429
6.440
6.451
6.461
6.472
6.483
6.404
6.504
.61
6-515
6.526
6.536
6.547
6.558
6.568
6.579
6.590
6.600
6.611
.62
6.622
6.632
6.643
6.654
6.664
6.675
6.686
6.696
6.707
6.718
.63
6.728
6.739
6.750
6.761
6.771
6.782
6.793
6.803
6.814
6.825
.64
6.835
6.846
6.857
6.867
6.878
6.889
6.899
6.910
6.921
6-931
.65
6.942
6.953
6.963
6.974
6.985
6.996
7.006
7-017
7.028
7-038
.66
7.049
7.060
7.070
7.081
7.092
7.102
7- H3
7.124
7-134
7-145
.6?
7.156
7.166
7.177
7.188
7.198
7.209
7.220
7.230
7.241
7-252
.68
7.263
7-273
7.284
7-295
7.305
7.3i6
7-327
7-337
7.348
7-359
.69
7.369
7.38o
7-391
7.401
7.412
7-423
7-433
7-444
7.455
7.465
.70
7.476
7.487
7-497
7.508
7.519
7-530
7-540
7-551
7.562
7-572
.71
7.583
7-594
7.604
7-615
7.626
7-636
7.647
7-658
7.668
7.679
.72
7.690
7.700
7-7II
7.722
7-732
7-743
7-754
7.764
7-775
7-786
.73
7-797
7.807
7.818
7-829
7.839
7.850
7.861
7-871
7.882
7-893
.74
7.903
7.914
7.925
7-935
7.946
7-957
7.967
7-978
7.989
7-999
• 75
8.010
8.021
8.031
8.042
8.053
8.064
8.074
8.085
8.096
8.106
.76
8.117
8.128
8.138
8.149
8.160
8.170
8.181
8.192
8.202
8.213
.77
8.224
8.234
8.245
8.256
8.266
8.277
8.288
8.298
8.309
8.320
.78
8.331
8.341
8.352
8.363
8.373
8.384
8.395
8.405
8.416
8.427
• 79
8.437
8.448
8.459
8.469
8.480
8.491
8.501
8.512
8.523
8.533
.80
8.544
8,555
8.565
8.576
8-587
8.598
8.608
8.619
8.630
8.640
.81
8.651
8.662
8.672
8.683
8.694
8.704
8.715
8.726
8.736
8.747
.82
8.758
8.768
8.779
8.790
8.800
8.811
8.822
8.832
8.843
8.854
.83
8.865
8.875
8.886
8.897
8.907
8.918
8.929
8.939
8.950
8.961
.84
8.971
8.982
8.993
9.003
9-014
9.025
9-035
9.046
9.057
9.067
.85
9.078
9.089
9.099
9.110
9.121
9.132
9.142
9.153
9.164
9-174
.86
9.185
9.196
9.206
9.217
9.228
9.238
9-249
9.260
9.270
9.281
.87
9.292
9-302
9.313
9-324
9-334
9-345
9.356
9-366
9-377
9-388
.88
9-399
9.409
9.420
9-431
9-441
9.452
9.463
9-473
9.484
9-495
.89
9.505
9.5i6
9.527
9-537
9.548
9-559
9.569
9.58o
9-591
9.601
.00
9.612
9.623
9.634
9.644
9.655
9.666
9.676
9-687
9.698
9.708
.91
9.719
9-730
9-740
9-751
9.762
9.772
9.783
9-794
9.804
9.815
.92
9.826
9.836
9.847
9-858
9.868
9.879
9.890
9.901
9.911
9.922
• 93
9-933
9-943
9-954
9-965
9-975
9.986
9-997
10.007
10.018
0.029
.94
10.039
10.050
10.061
10.071
10.082
10.093
10.103
10.114
10.125
0.135
.95
0.146
10.157
10.168
10.178
10.189
IO.2OO
10.210
10.221
10.232
0.242
.96
0.253
10.264
10.274
10.285
10.296
I0.3O6
10.317
10.328
10.338
0.349
• 97
0.360
10.370
10.381
10.392
10.402
10.413
10.424
10.435
10.445
0.456
.98
0.467
10.477
10.488
10.499
10.509
10.520
10.531
10.541
10.552
10.563
.99
0.573
10.584
10.595
10.605
10.616
IO.627
10.637
10.648
10.659
10.669
1. 00
0.6802
Weight in Pounds per Lineal Foot for Pipe and Tubing 379
WEIGHT IN POUNDS PER LINEAL FOOT FOR
PIPE AND TUBING
Table II was calculated for steel pipe or tubes on the basis of one
cubic inch of steel = .2853 pound. To convert these weights to weights
for other materials, see weight factors, page 423. This table was calcu-
lated on an eight-slot Burkhardt machine by means of the formula:
W = 10.680158 (D - 0 /,
where W = weight of steel tube in pounds per foot;
D = outside diameter of tube in inches;
/ = thickness in inches.
Table I may be used to interpolate for the weights of tubes varying
by even 32nds or 64ths of an inch where the wall remains the same as in
Table II. Table I was calculated by the formula:
D = 10.680158/5,
where D — difference in weight per foot;
/ = thickness of wall in inches;
a = difference in outside diameters in inches.
Use of Table I. Example. Find weight per foot of tube iHta
inch outside diameter X %2 inch wall. The next size, given in Table
II, smaller than i41/&4 inch is i% inch. Difference between i41?^ inch
and i% inch is VG& inch.
Weight per foot, from Table II, of tube i% inch outside diameter
X %2 inch wall = i . 533 pounds
Difference in weight per foot, from Table I,
for %2 inch wall and for difference, in out-
side diameter, of %4 inch = .016
Weight per foot of tube iHta inch outside
diameter X %2 inch wall = i . 549 pounds
380 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table I. — Difference in Weight per Foot for Difference in Outside Diameter
of "a", the Wall Remaining the Same for Steel Pipe and Tubing
Weight i cubic inch Steel = .2833 pound
Wall thickness
Difference in outside diameter, "a"
B.W.G.
Inches
1/64
1/32
%4
Vl6
%4
%2
m
24
.0037
.0073
.OIIO
23
.0042
.0083
.OI25
22
.0047
.0093
.0140
21
.0053
.0107
.Ol6o
2O
.0058
.0117
.0175
.0234
.O292
.0350
.0409
19
.0070
.0140
.0210
.0280
.0350
.0421
.0491
18
.0082
.0164
.0245
.0327
.0409
.0491
.0572
17
.0097
.0194
.0290
.0387
.0484
.0581
.0678
Vi6
.0104
.0209
.0313
.0417
.0521
.0626
.0730
16
.0108
.0217
.0325
• 0434
.0542
.0651
.0759
IS
.0120
.0240
.0360
.0481
.0601
.0721
.0841
14
.0139
.0277
.0416
.0554
.0693
.0831
.0970
"'8/32'
.0156
.0313
.0469
.0626
.0782
.0939
.1095
13
• 0159
.0317
.0476
.0634
.0793
.0951
.IIIO
12
.0182
.0364
.0546
.0728
.0909
.1091
.1273
II
.O2OO
.0401
.0601
.0801
.IOOI
.1202
.1402
Vs
.0209
.0417
.0626
.0834
.1043
.1252
.1460
IO
.O224
.0447
.0671
.0894
.1118
.1342
.1565
9
.O247
.0494
.0741
.0988
.1235
.1482
.1729
%2
.026l
.0521
.0782
.1043
.1304
.1464
.1825
8
.0275
.0551
.0826
.IIOI
-1377
. 1652
.1927
7
.0300
.0601
.0901
• . 1202
.1502
.1802
.2103
'"8/16*
.0313
.0626
.0939
.1252
.1564
.1877
.2190
6
.O339
.0678
.1016
.1355
.1694
.2033
.2371
T/82
.0365
.0730
.1095
.1460
.1825
.2190
.2555
5
.0367
.0734
.IIOI
.1469
.1836
.2203
.2570
4
.O397
.0794
.1192
.1589
.1986
.2383
.2780
%
.0417
.0834
.1252
.1669
.2086
.2503
.2920
3
.O432
.0864
.1297
.1729
.2161
.2593
.3025
%2
.0469
.0939
.1408
.1877
.2347
.2816
.3285
2
.O474
.0948
.1422
.1896
.2370
.2844
.3318
I
.O5OI
.IOOI
.1502
.2OO3
.2503
.3004
.3504
5/ie
.0521
.1043
.1564
.2086
.2607
.3129
.3650
*%a
.0574
.1147
.1721
.2295
.2868
.3442
.4015
%
.0626
.1252
.1877
.2503
.3129
.3755
.4381
7/l6
.0730
.1460
.2190
.2920
.3650
.4381
.5in
%
.0834
.1669
.2503
.3338
.4172
.5006
.5841
9/ie
.0939
.1877
.2816
.3755
.4693
.5632
.6571
%
.1043
.2086
.3129
.4172
.5215
.6258
.7301
!%6
.1147
.2295
.3442
.4589
.5736
.6884
.8031
%
.1252
.2503
.3755
.5006
.6258
.7509
.8761
18/16
.1356
.2712
.4068
.5424
.6779
.8135
.9491
%
.1460
.2920
.4381
.5841
.7301
.8761
.022
15/16
.1564
.3129
.4693
.6258
.7822
.9387
.095
I
.1669
.3338
.5006
.6675
.8344
1. 001
.168
11/16
.1773
.3546
.5319
.7092
.8865
1.064
.241
iVs
.1877
.3755
.5632
.7509
.9387
1.126
.314
I%6
.1982
.3963
• 5945
.7927
.9908
1.189
.387
l"U
.2086
.4172
.6258
.8344
1.043
1.252
.460
I5/16
.2190
.4381
.6571
.8761
1-095
1.314
.533
1%
.2295
.4589
.6884
.9178
1. 147
1.377
.606
I%6
.2399
.4798
.7197
.9595
1. 199
1.439
.679
m
.2503
.5006
.7509
1. 001
1.252
1.502
1.752
Weight in Pounds per Lineal Foot for Pipe and Tubing 381
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe and Tubing
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
W6
Vs
8/16
%
5/4e
%
7/16
y2
24
23
22
21
20
19
18
17
16
IS
14
13
12
II
10
9
8
.0095
.0242
,0267
.0290
.0318
.0336
.0372
.0389
.0434
.0477
.0531
.0570
.0653
.0725
.0802
.0834
.0536
.0601
.0664
• 0745
.0804
.0933
.1052
.1189
.1252
.1284
.1369
.1480
.0683
.0768
.0851
.0959
.1037
.1213
.1379
.1577
.1669
.1718
.1849
.2034
.2190
.2207
.0829
.0935
.1038
.1172
.1271
.1494
.1706
.1964
.2086
.2152
.2330
.2588
.2816
.2841
.3097
.3268
.3338
.0976
.1101
.1225
.1386
.1505
-1774
.2033
.2351
.2503
.2586
.2811
.3142
• 3442
.3475
.3824
.4069
.4172
.4344
.4576
.1123
.1268
.1411
.1599
.1738
.2054
.2360
.2738
.2920
.3020
.3291
.3697
.4068
.4109
• 4552
.4870
.5006
.5238
.5564
.5736
.5903
We
%2
%
%2
382 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
9/16
%
mQ
3/4
13/16
7/8
15/16
I
24
23
22
21
20
19
18
17
16
15
14
13
12
II
10
9
8
7
6
5
4
3
2
I
.1270
.1435
.1598
.1813
.1972
.2335
.2687
• 3125
.3338
.3454
• 3772
.4251
.4693
• 4743
.5279
.5671
.5841
.6132
.6552
.6779
• 7005
.7353
.7509
.1417
.1602
.1785
.2027
.2205
.2615
• 3014
• 3512
.3755
.3888
.4252
.4805
.5319
• 5377
.6007
.6472
.6675
.7027
• 7540
.7822
.8106
.8555
.8761
• 9149
.1564
.1769
.1972
.2240
.2439
.2895
.3341
.3899
.4172
• 4321
• 4733
• 5359
• 5945
.6012
.6735
.7273
• 7509
• 7921
.8528
.8865
.9208
• 9756
1. 001
1.050
1.095
1.098
.1711
.1936
.2159
.2454
.2673
.3176
.3669
.4287
.4589
• 4755
.5214
.5913
.6571
.6646
.7462
.8074
.8344
.8816
.9516
.9908
1.031
1.096
1.126
1.186
1.241
1. 245
1.301
1.335
.1857
.2103
.2346
.2667
.2906
.3456
.3996
.4674
.5006
.5189
.5694
.6467
.7197
.7280
.8190
.8875
.9178
.9710
1.050
1.095
1.141
1. 216
1.252
1.321
1.387
1.392
1.460
1.502
I.53I
.2O04
.2270
.2533
.2881
.3140
• 3737
.4323
.5061
.5424
.5623
.6175
.7021
.7822
.7914
.8917
.9676
.001
.060
.149
.199
.251
.336
.377
• 457
• 533
.539
.619
.669
.704
.784
• 793
.2151
.2436
.2720
.3095
.3374
.4017
.4650
• 5448
.5841
.6057
.6655
• 7575
.8448
.8548
.9645
1.048
.085
.150
.248
• 304
.361
.456
.502
• 592
.679
.686
.778
.836
-877
.971
.982
.043
2.086
.2298
.2603
.2907
.3308
.3607
.4297
• 4977
.5835
.6258
.6491
.7136
.8129
.9074
.9182
• 037
.128
.168
.239
• 347
.408
• 471
.576
.627
.728
.825
.833
.937
.003
2.050
2.159
2.172
2.243
2.295
Vie
%2
%
%2
8/16
%2
y*
%2
5/16
Weight in Pounds per Lineal Foot for Pipe and Tubing 383
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
itte
iVs
I%6
$A
I5/16
i%
i%e
W
20
19
18
17
16
15
14
13
12
ii
10
9
8
7
6
5
4
3
2
I
.3841
.4578
.5304
.6222
.6675
.6925
.7617
.8683
.9700
.9816
I. IIO
1.208
1.252
1.329
1.446
1.512
1.582
1.697
1.752
1.863
1.971
1.980
2.096
2.169
2.223
2.347
2.361
2.443
2.503
2.639
.4074
.4858
.5631
.6610
.7092
.7359
.8097
.9237
1.033
1.045
1.183
1.288
1.335
1.418
1-544
1.617
1.692
1.817
1.877
1-999
2. 117
2.126
2.255
2.336
2.395
2.534
2.551
2.643
2.712
2.868
3.004
.4308
.5138
• 5958
.6997
.7509
• 7793
.8578
.9791
.095
.108
.256
.368
.418
.508
.643
.721
.802
• 937
2.003
2.134
2.263
2.273
2.414
2.503
2.568
2.722
2.740
2.844
2.920
3.098
3-254
.4542
.5419
.6285
.7384
.7927
.8226
.9058
1.034
1.158
1.172
1.328
1.448
1.502
1-597
1.742
1.825
1.912
2.057
2.128
2.270
2.409
2.420
2.572
2.670
2.741
2.910
2.930
3-044
3.129
3.327
3.504
.4775
.5699
.6612
• 7771
.8344
.8660
• 9539
1.090
.220
.235
.401
.528
.585
.687
.841
• 930
2. 022
2.177
2.253
2.405
2.555
2.567
2.731
2.837
2.914
3.098
3.120
3-244
3.338
3-557
3.755
4.088
.5009
• 5979
.6939
.8158
.8761
.9094
1.002
1. 145
1.283
1.299
1.474
1. 608
1.669
1.776
1-939
2.034
2.132
2.297
2.378
2.541
2.701
2.714
2.890
3.004
3.o87
3.285
3.309
3-444
3.546
3-786
4.005
4.381
.5243
.6260
.7266
.8545
.9178
.9528
1.050
1. 201
1-345
1.362
1.547
1.689
1.752
1.865
2.038
2.138
2.242
2.417
2.503
2.676
2.847
2.861
3-049
3.I7I
3.260
3-473
3-499
3.645
3-755
4.015
4-255
4.673
.5476
.6540
• 7594
.8932
.9595
.9962
.098
.256
.408
.426
.619
.769
.836
• 955
2.137
2.242
2-353
2.538
2.628
2.812
2.993
3.008
3.208
3-338
3-433
3.66i
3.688
3.845
3.963
4-245
4.506
4.965
5-340
}46
%2
Vs
"%2"
3/16
7/32
"ii"'
"%2"
5/16
H32
%
Tfy
%
384 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
I9/16
1%
HVlG
1%
I18/io
1%
I15/16
2
20
19
18
17
16
15
14
13
12
II
IO
9
8
7
6
5
4
3
2
I
.5710
.6820
.7921
• 9320
.001
.040
.146
.312
• 471
.489
.692
.849
• 919
.044
.236
• 347
.463
.658
• 753
2.947
3-139
3-154
3.367
3.504
3.606
3.849
3.878
4-045
4.172
4-474
4.756
5-257
5.674
• 5944
.7101
.8248
.9707
043
083
194
.367
.533
• 552
.765
.929
.003
• 134
• 335
• 451
• 573
• 778
.879
3-083
3.285
3-301
3.526
3-671
3-779
4.036
4-067
4.245
4.381
4.704
5.006
5-549
6.008
.6177
.7381
.8575
1.009
1.085
1.126
1.242
1.422
1-596
1.616
1-838
2.009
2.086
2.223
2.433
2.555
2.683
2.898
3-004
3.219
3-431
3.448
3-684
3.838
3-951
4.224
4-257
4.446
4.589
4-933
5-257
5.841
6.341
6.759
.6411
.7662
.8902
1.048
1.126
1.170
1.290
1.478
1.658
1.679
1.910
2.089
2.169
2.313
2.532
2.660
2.793
3.018
3-129
3-354
3-577
3-595
3.843
4.005
4-124
4.412
4-447
4.646
4.798
5.163
5-507
6.133
6.675
7-134
.6644
.7942
.9229
1.087
.168
.213
.338
• 533
.721
• 743
.983
2.169
2.253
2.402
2.631
2.764
2.903
3.138
3.254
3.490
3.723
3.742
4.002
4.172
4.297
4.600
4.636
4.846
5.006
5.392
5.757
6.425
7.009
7.509
.6878
.8222
.9556
1.126
.210
.257
.386
.589
.784
.806
.056
2.249
2.336
2.492
2.730
2.868
3-013
3.259
3-379
3.625
3.869
3-889
4.161
4.339
4-470
4.787
4.826
5.046
5-215
5.622
6.008
6.717
7-343
7-885
8.344
.7112
.8503
.9883
1.164
1.252
1.300
1.435
1.644
1.846
1.869
2.129
2.329
2.420
2.581
2.829
2.973
3-124
3-379
3.504
3.761
4.015
4-035
4.320
4.506
4.643
4-975
5.015
5-247
5.424
5.851
6.258
7.009
7.676
8.260
8.761
• 7345
.8783
I.O2I
1.203
1.293
1.343
1.483
1.699
1.909
1-933
2.201
2.409
2.503
2.671
2.927
3-077
3-234
3-499
3-630
3.896
4.162
4.182
4-479
4.673
4.816
5.163
5.205
5-447
5.632
6.081
6.508
7-301
8.010
8.636
9.178
9.637
Vie
%2
%
"%2"
"8^6"
%2
"ii"'
%2
%6
%
8,
1/2
9/16
%
J%6
Weight in Pounds per Lineal Foot for Pipe and Tubing 385
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
2%
2V*
2%
2*/2
2%
2%
2%
3
20
19
. 18
17
16
IS
14
13
12
II
10
9
8
7
6
5
4
3
2
I
.7813
• 9344
1. 086
1.280
1.377
1-430
1-579
1.810
2.034
2.060
2.347
2-570
2.670
2.849
3-125
3.285
3-454
3-739
3-88o
4.167
4-454
4.476
4-797
5.oo6
5.162
5-538
5.584
5.847
6.049
6.540
7.009
7-885
8.678
9.387
10.01
10.55
.8280
.9904
.152
.358
.460
.517
.675
.921
2.159
2.186
2.492
2.730
2.837
3-028
3 323
3-494
3.674
3-979
4-130
4.438
4.746
4-770
5.H4
5-340
5.507
5.914
5.963
6.248
6.467
6.998
7.509
8.469
9-345
10.14
10.85
11.47
12. 02
.8747
.047
.217
• 435
• 544
.604
• 771
.032
2.284
2.313
2.638
2.890
3.004
3.207
3-520
3-703
3.895
4.220
4.381
4.709
5.038
5.063
5-432
5.674
5.853
6.289
6.342
6.648
6.884
7-457
8.010
9-053
10.01
10.89
11.68
12.39
13.02
13.56
-9214
I.I03
1.283
I.5I3
1.627
1.690
1.867
2.143
2.409
2.440
2.783
3.050
3-I7I
3.386
3-718
3-9II
4-II5
4.460
4.631
4.980
5-330
5-357
5-750
6.008
6-199
6.665
6.721
7.049
7-301
7.916
8.511
9.637
10.68
11.64
12.52
I3-3I
14.02
14.64
.9682
-159
-348
• 590
.710
• 777
.963
2.253
2.534
2.567
2.929
3.210
3-338
3.565
3.915
4.120
4-335
4-700
4.881
5.251
5.622
5.651
6.067
6.341
6-545
7.040
7.101
7-449
7.718
8.375
9.011
10.22
H.35
12.39
13-35
14-23
15.02
15-73
16.35
1. 015
1. 215
1.414
1.668
1-794
1.864
2.059
2.364
2.660
2.694
3-074
3-371
3.504
3-744
4-II3
4.328
4-555
4-941
5-I3I
5-522
5.914
5-945
6-385
6.675
6.891
7.416
7.48o
7.850
8.135
8.834
9-512
10.81
12.02
13.14
I4.I8
15.14
16.02
16.81
17.52
18.15
I.O62
I.27I
1.479
1-745
1.877
I-95I
2.155
2.475
2.785
2.821
3-220
3.531
3.671
3.923
4.310
4-537
4.776
5.181
5.382
5-793
6.206
6.238
6.703
7.009
7.236
7-791
7-859
8.250
8.552
9-293
10.01
H.39
12.68
13-89
15.02
16.06
17.02
17-90
18.69
19.40
1.108
1.327
1-544
1.822
1.961
2.038
2.252
2.586
2.910
2-947
3.366
3-691
3.838
4-102
4.508
4.746
4.996
5.421
5.632
6.064
6.498
6.532
7.021
7.343
7.582
8.167
8.238
8.651
8.970
9.752
10.51
11.97
13-35
14-64
15.85
16.98
18.02
18.98
19.86
20.65
21.36
Vie
%2
%
"%2"
"%e"
%«
"ii"'
"%3"
5/16
»%•
%
7/i6
4
9/16
%
Hie
S/4
13/16
7/8
15/4e
i
386 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
3Vs
3*4
3%
3V2
3%
33/4
3%
4
18
17
16
15
14
13
12
II
10
9
8
7
6
5
4
3
2
I
"'Vie'
1.610
1.900
2.044
2.124
2.348
2.697
3-035
3-074
3-Sii
3.851
4.005
4.281
4.706
4-954
5.216
5.662
5-882
6.335
6.790
6.826
7.338
7.676
7.928
8.542
8.617
9-061
9.387
10.21
II. 01
12.56
14.02
15.39
16.69
17.90
19.02
20.07
21.03
21.90
22.70
23.40
1.675
1.977
2.128
2. 211
2.444
2.807
3.160
3-201
3.657
4. oil
4.172
4-459
4.903
5.163
5.436
5-902
6.133
6.606
7.082
7.119
7.656
8.010
8.274
8.918
8.996
9-452
9.804
10.67
ii.Si
13.14
14.69
16.15
17.52
18.82
20.03
21.15
22.19
23.15
24.03
24.82
I.74I
2.055
2. 211
2.298
2.540
2.918
3.285
3.328
3.802
4.172
4-339
4-638
5.101
S.37I
5.657
6.142
6.383
6.877
7-374
7-413
7-974
8.344
8.619
9-293
9.376
9.852
IO.22
II. 13
12.02
13-73
15-35
16.90
18.36
19-73
21.03
22.24
23.36
24.41
25-37
26.24
27.03
1. 806
2.132
2.295
2.385
2.636
3.029
3.411
3.455
3.948
4.332
4.506
4.817
5.298
5.580
5.877
6.382
6.633
7.148
7.666
7.707
8.292
8.678
8.965
9.668
9-755
10.25
10.64
11-59
12.52
I4-3I
16.02
17.65
19.19
20.65
22.03
23.32
24-53
25.66
26.70
27.66
28.54
29-33
1.871
2.2IO
2.378
2.471
2.732
3.140
3.536
3.582
4-093
4-492
4.673
4.996
5.496
5.789
6.097
6.623
6.884
7-419
7.958
8.001
8.609
9.011
9-3II
10.04
10.13
10.65
II. 06
12.05
13.02
14.89
16.69
18.40
20.03
21.57
23.03
24.41
25.70
26.91
28.04
29.08
30.04
30.91
1.937
2.287
2.461
2.558
2.828
3-251
3.66i
3.708
4-239
4.652
4.839
5-175
5.694
5-997
6.318
6.863
7-134
7.690
8.250
8.294
8.927
9-345
9.657
10.42
10.51
11.05
n.47
12.51
13.52
15.48
17.36
19 • 15
20.86
22.49
24.03
25-49
26.87
28.16
29-37
30.50
31-54
32.50
33.38
2.002
2.364
2.545
2.645
2.924
3.36i
3-786
3.835
4.384
4.812
5.oo6
5-354
5.891
6.206
6.538
7-103
7.384
7.96i
8.542
8.588
9-245
9.679
IO.OO
10.79
10.89
11.45
11.89
12.96
14.02
16.06
18.02
19.90
21.69
23.40
25.03
26.58
28.04
29.41
30.71
31.92
33-04
34.o8
35-04
35-92
2.068
2.442
2.628
2.732
3.O2I
3-472
3-9II
3.962
4-530
4-973
5-173
5-533
6.089
6.414
6.758
7-344
7.635
8.232
8.834
8.882
9.563
10.01
10.35
11.17
11.27
11.85
12.31
13.42
14.52
16.65
18.69
20.65
22.53
24.32
26.03
27.66
29.20
30.66
32.04
33-33
34-54
35.67
36.71
37-67
"'%i'
'"%"
'"%2
«/16
"'%i'
V4
%2
5/16
%
%
%e
V2
9/16
%
H/16
8/4
13/16
%
15/16
lVl6
iVs
I%6
1%
I5/16
Weight in Pounds per Lineal Foot for Pipe and Tubing 387
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
4Vs
4%
4%
M
4%
43/4
4%
5
18
17
16
15
14
13
12
II
10
9
8
7
6
5
4
3
2
I
'"iie'
2.133
2.519
2.712
2.818
3-H7
3.583
4-036
4.089
4-675
5-133
5-340
5-712
6.286
6.623
6.978
7.584
7-885
8.503
9.126
9-175
9.880
10.35
10.69
11-55
11.65
12.26
12.72
13-88
15.02
17.23
19.36
21.40
23.36
25-24
27.03
28.74
30.37
31.92
33-38
34-75
36.05
37-26
38.38
39-42
40.38
2.199
2.597
2.795
2.905
3-213
3.694
4.162
4.216
4.821
5-293
5.507
5.891
6.484
6.832
7.199
7.824
8.135
8.774
9.418
9.469
O.2O
0.68
1.04
1.92
2.03
2.66
3-14
14-34
15-52
17.81
20.03
22.15
24.20
26.16
28.04
29.83
31.54
33-17
34.71
36.17
37-55
38.84
40.05
41.18
42.22
43-18
2.264
2.674
2.879
2.992
3.309
3.805
4.287
4-343
4-966
5-453
5-674
6.069
6.681
7-040
7.419
8.065
8.386
9-045
9.710
9.763
10.52
II. OI
H-39
12.30
12.41
13-06
13-56
14-80
16.02
18.40
20.69
22.90
25.03
27.08
29.04
30.91
32.71
34.42
36.05
37.59
39.05
40.43
41.72
42.93
44.06
45.10
2.329
2.752
2.962
3-079
3-405
3.915
4.412
4.469
5- H2
5.613
5.841
6.248
6.879
7.249
7.639
8.305
8.636
9.316
IO.OO
10. 06
10.83
11.35
H.73
12.67
12.79
13-46
13.98
15.26
16.52
18.98
21.36
23.65
25-87
27.99
30.04
32.00
33-88
35.67
37.38
39-01
40.55
42.01
43-39
44.68
45.89
47-02
48.06
2.395
2.829
3.046
3.166
3-501
4.026
4-537
4-596
5-257
5-774
6.008
6.427
7-077
7-457
7.860
8-545
8.886
9.587
10.29
10.35
II. 15
11.68
12.08
13.05
13.17
13.86
14-39
15-72
17.02
19-57
22.03
24.41
26.70
28.91
31.04
33.o8
35.04
36.92
38.72
40.43
42.05
43.6o
45.o6
46.43
47-73
48.94
50.06
2.460
2.906
3-129
3-252
3-597
4-137
4.662
4-723
5.403
5-934
6.174
6.606
7-274
7.666
8.080
8.785
9-137
9-858
10.59
10.64
II.47
12.02
12.42
13.42
13.55
14.26
14.81
16.18
17.52
20.15
22.70
25.16
27-53
29-83
32.04
34-17
36.21
38.17
40.05
41.84
43.56
45.18
46.73
48.19
49.56
50.86
52.07
2.526
2.984
3-212
3-339
3.693
4.248
4.787
4.850
5.548
6.094
6.341
6.785
7.472
7.875
8.300
9.026
9.387
10.13
10.88
10.94
11.79
12.35
12.77
13-80
13-93
14.66
15.23
16.64
18.02
20.73
23-36
25.91
28.37
30.75
33-04
35-25
37-38
39-42
41-39
43-26
45-o6
46.77
48.39
49-94
51-40
52.77
54-07
2.591
3.061
3.296
3.426
3.789
4-359
4.912
4.977
5.694
6.254
6.508
6.964
7.669
8.083
8.520
9.266
9.637
10.40
11. 17
11.23
12. IO
12.68
13.11
14.17
14.30
15.06
15.64
17.09
18.52
21.32
24.03
26.66
29.20
31.66
34-04
36.34
38.55
40.68
42.72
44.68
46.56
48.35
50.06
51-69
53.23
54.69
56.07
%2
:::..::
'"%2
8/16
"'7/32'
-%,•
7/16
9/i6
3/f
7/8
15/16
I
388 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table H. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
SVs
5V4
5%
5V2
5%
53/4
5%
6
12
II
10
9
8
7
6
5
4
3
2
I
5.839
6.415
6.675
7.143
7.867
8.292
8.741
9.506
9-887
10.67
11.46
11.52
12.42
13.02
13.46
14.55
14.68
15.46
16.06
17-55
19.02
21.90
24.70
27.41
30.04
32.58
35-04
37.42
39-72
41.93
44-06
46.10
48.06
49-94
51.73
53-44
55-07
56.61
58.07
5.985
6.575
6.842
7-322
8.065
8.500
8.961
9-747
10.14
10.94
H.75
6.130
6.735
7.009
7-501
8.262
8.709
9.181
9.987
10.39
II. 21
12.05
6.276
6.895
7.176
7.680
8.460
8.918
9.401
10.23
10.64
11.48
12.34
6.421
7-055
7-343
7.858
8.657
9.126
9.622
10.47
10.89
11.76
12.63
6.567
7.216
7.509
8.037
8.855
9-335
9.842
10.71
11.14
12.03
12.92
6.712
7.376
7.676
8.216
9-052
9-543
10. 06
10.95
H.39
12.30
13.21
13.29
14-33
15.02
15-53
16.80
16.96
17.86
18.57
20.31
22.03
25.41
28.70
31.92
35-04
38.09
41-05
43-93
46.73
49-44
52.07
54.6i
57-07
59.45
6i.74
63.96
66.08
68.13
70.09
6.858
7.536
7.843
8.395
9.250
9-752
10.28
11.19
11.64
12.57
I3-5I
13.58
14.65
15-35
15-88
17.18
17-34
18.26
18.98
20.77
22.53
25-99
29.37
32.67
35-88
39-01
42.05
45-02
47.89
50.69
53-40
56.03
58.57
61.04
63.41
65.71
67.92
70.05
72.09
%
%2
S/i6
%2
12.74
13-35
13.81
14-93
15.06
15-86
16.48
18.01
19.52
22.49
25.37
28.16
30.87
33.50
36.05
38.51
40.88
43-18
45-39
47.52
49.56
51.52
53-40
55-19
56.91
58.53
60.08
13.06
13-68
I4-I5
15.30
15-44
16.26
16.90
18.47
20.03
23.07
26.03
28.91
31.71
34.42
37.05
39.59
42.05
44.43
46.73
48.94
51.06
53.ii
55-07
56.95
58.74
60.45
62.08
13.38
14.02
14.50
15-68
15-82
16.66
17.31
18.93
20.53
23.65
26.70
29.66
32.54
35-34
38.05
40.68
43-22
45-68
48.06
50.36
52.57
54.69
56.74
58.70
60.58
62.37
64.08
13.69
14-35
14.84
16.05
16.20
17.06
17-73
19.39
21.03
24.24
27-37
30.41
33.38
36.25
39-05
41.76
44.39
46.93
49-40
51.77
54.07
56.28
58.41
6o.45
62.41
64.29
66.08
14.01
14.69
15.19
16.43
16.58
17.46
18.15
19.85
21.53
24.82
28.04
31.16
34.21
37-17
40.05
42.85
45.56
48.19
50.73
53-19
55-57
57-86
60.08
62.20
64.25
66.21
68.09
%
"'%i'
'"&'
H'32
%
%6
%
*%6
%
*%6
%
15/ie
^ie
i%
I3/16
1%
I5/16
1%
I7/16
i%
Weight in Pounds per Lineal Foot for Pipe and Tubing 389
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
61/8
6H
6%
6V2
6%
6%
6%
7
12
10
9
8
7
6
5
4
3
2
I
7.003
7.696
8.010
8.574
9.448
9.960
10.50
n.43
11.89
12.84
13.80
13.87
14.96
15.69
16.23
17-55
17.72
18.66
19.40
21.22
23.03
26.58
30.04
33-42
36.71
39-93
43-05
46.10
49-06
51-94
54-74
57-45
60.08
62.62
65.08
67.46
69.75
71-97
74-09
7-149
7-856
8.177
8.753
9.645
10.17
10.72
11.67
12.14
13- II
14.09
14.17
15.28
16.02
16.57
17-93
18.10
19.06
19.82
21.68
23-53
27.16
30.71
34-17
37-55
40.84
44.06
47.18
50.23
53-19
56.07
58.87
61.58
64.21
66.75
69.21
71-59
73.89
76.10
7-294
8.017
8-344
8.932
9.843
10.38
10.94
11.91
12.39
13.38
14.38
14.46
I5.6o
16.35
16.92
18.30
18.48
19.46
20.23
22.14
24.03
27-74
31-37
34-92
38.38
41.76
45-o6
48.27
51-40
54-44
57-41
60.28
63.08
65.79
68.42
70.96
73-43
75-80
78.10
7.440
8.177
8.511
9.111
10.04
10.59
ii. 16
12.15
12.64
13.65
14.67
14.76
15.92
16.69
17.26
18.68
18.85
19-87
20.65
22.60
24-53
28.33
32.04
35.67
39-22
42.68
46.06
49.35
52.57
55-70
58.74
61.70
64.58
67.38
70.09
72.72
75.26
77-72
80.10
7-586
8.337
8.678
9.290
10.24
10.79
11.38
12.39
12.89
13.92
14-97
15-05
16.23
17.02
17.61
19.06
19.23
20.27
21.07
23.06
25.03
28.91
32.71
36.42
40.05
43-6o
47.06
50.44
53-73
56.95
60.08
63.12
66.08
68.96
71.76
74-47
77.10
79.64
82.10
7-731
8.497
8.845
9.468
10.44
II. OO
ii. 60
12.63
13.14
14.19
15.26
15-34
16.55
17.36
17 .-96
19-43
19.61
20.67
21.49
23.52
25-53
29.50
33.38
37.17
40.88
44-51
48.06
51.52
54-90
58.20
61.41
64.54
67.59
70.55
73-43
76.22
78.93
81.56
84.11
7.877
8.657
9. on
9.647
10.63
II. 21
11.82
12.87
13-39
14-47
15-55
15-64
16.87
17-69
18.30
19.81
19-99
21.07
21.90
23-98
26.03
30.08
34-04
37-92
41.72
45-43
49-06
52.61
56.07
59-45
62.75
65.96
69.09
72.13
75-09
77-97
8o.77
83.48
86.11
8.022
8.818
9.178
9.826
10.83
11.42
12.04
13.11
13-64
14-74
15.84
15-93
17.19
18.02
18.65
20.18
20.37
21.47
22.32
24.44
26.53
30.66
34-71
38.67
42.55
46.35
50.06
53.69
57-24
60.70
64.08
67.38
70-59
73.72
76.76
79-73
82.60
85.40
88.11
%
%2
3Ae
%2
V4
%2
5Ae
7/?6
9Ae
18A6
15Ae
iMe
I%6
390 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
7%
7%
7%
7V2
7%
73/4
77/8
8
10
10.01
10.18
10.36
10.54
10.72
10.90
11.08
11.26
9
11.03
11.23
11.42
11.62
11.82
12.02
12.21
12.41
%2
11.63
11.84
12.05
12.26
12.46
12.67
12.88
13.09
8
12.27
12.49
12.71
12.93
13.15
13-37
13-59
13.81
7
13.35
13-59
13.83
14.07
I4-3I
14-55
14.79
15.03
"'SA'Q'
13.89
14.14
14-39
14.64
14.89
15.14
15-39
15.64
6
15.01
15.28
15-55
15-82
16.09
16.36
16.63
16.90
"'%2'
16.13
16.43
16.72
17.01
17.30
17.60
17-89
18.18
5
16.22
16.52
16.81
17.11
17.40
17.69
17.99
18.28
4
17 51
17.82
18.14
18.46
18.78
19.09
19.41
19-73
V*
18.36
18.69
19.02
19.36
19.69
2O.03
20.36
20.69
3
18.99
19.34
19.68
20.03
20.38
2O.72
21.07
21.41
%2
20.56
20.93
21.31
21.68
22.06
22.43
22.81
23.19
2
20.75
21.13
21.51
21.89
22.27
22.65
23.02
23.40
I
21.87
22.27
22.67
23.07
23.47
23.87
24.27
24.67
5/16
22.74
23.15
23-57
23-99
24.41
24.82
25.24
25.66
Hb
24.90
25-35
25.81
26.27
26.73
27.19
27.65
28.11
%
27.03
27-53
28.04
28.54
29.04
29.54
30.04
30.54
7/ie
31.25
31-83
32.42
33-00
33.58
34.17
34-75
35-34
%
35.38
36.05
36.71
37-38
38.05
38.72
39.38
40.05
9/16
39-42
40.18
40.93
41.68
42.43
43.18
43-93
44-68
%
43-39
44.22
45.06
45.89
46.73
47.56
48.39
49-23
Hie
47.27
48.19
49.10
50.02
50.94
51 86
52.77
53.69
%
5l.o6
52.07
53-07
54-07
55-07
56.07
57-07
58.07
13/16
54.78
55-86
56.95
58.03
59-12
60.20
61.29
62.37
%
58.41
59.58
60.74
61.91
63.08
64.25
65.42
66.58
15/ie
61.95
63.20
64.46
65.71
66.96
68.21
69.46
70.71
i
65.42
66.75
68.09
69.42
70.76
72.09
73-43
74.76
lVl6
68.80
70.21
71.63
73-05
74-47
75.89
77.31
78.72
i%
72.09
73-59
75-09
76.60
78.10
79.6o
81.10
82.60
I3/16
75-30
76.89
78.47
80.06
81.64
83.23
84.82
86.40
m
78.43
80.10
81.77
83.44
85.11
86.78
88.45
90.11
I5/16
81.48
83.23
84.98
86.73
88.49
90.24
91.99
93-74
' 1%
84.44
86.28
88.11
89.95
91.78
93.62
95-45
97-29
I7/16
87.32
89.24
91.16
93.o8
95-00
96.91
98.83
100.8
iy2
90.11
92.12
94.12
96.12
98.12
100. 1
102. 1
104.1
1
Weight in Pounds per Lineal Foot for Pipe and Tubing 391
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
81/8
w
8%
8%
8%
83/4
8%
9
10
11.44
11.62
11.79
H.97
12.15
12.33
12.51
12.69
9
12. 6l
12.81
13.00
13.20
13.40
I3.6o
13-79
13-99
"'%i'
13 30
13.51
13.72
13.92
14.13
14-34
14-55
14.76
8
14.03
14.25
14.47
14.69
14.91
15.13
15.35
15-57
7
15-27
15.51
15-75
15-99
16.23
16.48
16.72
16.96
"'%e'
15.90
16.15
16.40
16.65
16.90
I7-I5
17.40
17-65
6
17.18
17.45
17.72
17.99
18.26
18.53
18.80
19.07
"'%i'
18.47
18.76
19.06
19-35
19.64
19-93
20.22
20.52
5
18.57
18.87
19.16
19-45
19.75
20.04
20.34
20.63
4
20.05
20.37
20.68
21.00
21.32
21.6^
21.95
22.27
'"%"
21.03
21.36
21.69
22.03
22.36
22.70
23.03
23.36
3
21.76
22. IO
22.45
22.8O
23.14
23.49
23.83
24.18
%2
23 56
23-94
24.31
24.69
25.06
25-44
25.81
26.19
2
23.78
24.16
24.54
24.92
25.30
25.68
26.06
26.44
I
25.07
25-47
25.87
7 y
26.27
26.67
27.07
27.47
27.88
'"%e"
26.07
26.49
26.91
27-33
27.74
28.16
28.58
29.00
i*ifo
28.57
29.03
29-49
29-94
30.40
30.86
31.32
31.78
%
31.04
31-54
32.04
32.54
33.04
33-54
34-04
34-54
&
35.92
36.50
37-09
37.67
38.26
38.84
39-42
40.01
V2
40.72
41-39
42.05
42.72
43.39
44-06
44.72
45-39
%6
45.43
46.18
46.93
47-69
48.44
49-19
49-94
50.69
%
50.06
50.90
51-73
52-57
53.40
54-24
55-07
55-90
Hie
54.61
55-53
56.45
57.36
58.28
59-20
60.12
61.04
%
59.07
60.08
61.08
62.08
63.08
64.08
65.08
66.08
!%6
63.46
64.54
65.62
66.71
67.79
68.88
69.96
71.05
%
67 75
68.92
70.09
71.26
72.42
73-59
74.76
75-93
!%6
71.97
73-22
74-47
75-72
76.97
78.22
79.48
80.73
I
76.10
77.43
78.77
80.10
81.44
82.77
84.11
85-44
lVl6
80.14
81.56
82.98
84.40
85.82
87.24
88.65
90.07
i%
84.11
85.61
87.11
88.61
90.11
91.62
93-12
94.62
•i%e
87.99
89.57
91.16
92.74
94.33
95.91
97-50
99.08
i%
91.78
93.45
35-12
96.79
98.46
100. 1
101. 8
103-5
i5/ie
95-50
97.25
99.00
100.8
102.5
104-3
106.0
107.8
i%
99-13
IOI O
102.8
104.6
106.5
108.3
no. i
112. 0
i%e
102.7
104.6
106.5
108.4
iio. 3
112. 3
114.2
116.1
I iy2
106.1
108.1
IIO. I
112. 1
114. 1
116.1
118.1
120.2
392 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
9l/8
9V4
9%
9Va
9%
9%
9%
J!_
10
12.87
13.05
13.23
13.40
13.58
13.76
13-94
14.12
9
14. 19
14 . 39
14.58
14.78
14.98
I5.I8
15.38
15.57
%2
14-97
I5.i8
15.38
15-59
15.80
16.01
16.22
16.43
8
15-79
16.01
16.23
16.45
16.67
16.89
17.11
17.33
7
17.20
17 44
17.68
17 92
18.16
18.40
18.64
18.88
8/16
17.90
18. 15
18.40
18.65
18.90
19.15
19.40
19.65
6
19.34
19.61
19.89
20 16
20.43
20.70
20.97
21.24
7/82
20.81
21.10
21.39
21.68
21.98
22.27
22.56
22.85
5
20.92
21.22
21.51
21.80
22. IO
22.39
22.69
22.98
4
22 . 59
22.91
23.23
23.54
23.86
24.18
24.50
24.81
#
23.70
24.03
24.36
24.70
25.03
25-37
25.70
26.03
3
24.52
24.87
25.22
25.56
25.91
26.25
26.60
26.95
%2
26.56
26.94
27.32
27.69
28.07
28.44
28.82
29.19
2
26.82
27.2O
27.57
27.95
28.33
28.71
29.09
29.47
I
28.28
28.68
29.08
29 48
29.88
30.28
30.68
31.08
5/16
29.41
29.83
30.25
30.66
31.08
3i.5o
31.92
32.33
!%a
32.24
32.70
33.16
33.62
34-07
34-53
34-99
35-45
%
35.04
35-54
36.05
36.55
37-05
37-55
38.05
38.55
%6
40.59
4I.I8
41.76
42.35
42.93
43-51
44.10
44-68
y2
46.06
46.73
47-39
48.06
48.73
49-40
50.06
50.73
9/16
51.44
52.19
52.94
53.69
54-44
55.19
55-95
56.70
%
56.74
57-57
58.41
59.24
60.08
60.91
6i.74
62.58
iVie
61.95
62.87
63.79
64.71
65.62
66.54
67.46
68.38
%
67.08
68.09
69.09
70.09
71.09
72.09
73.09
74-09
l8/le
72.13
73-22
74-30
75.39
76.47
77.56
78.64
79-73
7/8
77.10
78.27
79-43
80.60
81.77
82.94
84.11
85.27
15Ae
81.98
83.23
84.48
85-73
86.98
88.24
89-49
90.74
i
86.78
88.11
89.45
90.78
92.12
93.45
94-79
96.12
itte
91.49
92.91
94.33
95.75
97.16
98.58
IOO.O
101.4
i%
96.12
97.62
99-13
100.6
O2. 1
03.6
105.1
106.6
I%6
100.7
102.3
103.8
105-4
07.0
08.6
IIO. 2
in. 8
1%
105.1
106.8
108.5
IIO. I
II. 8
13-5
115- 1
116.8
I5/16
109.5
HI. 3
II3-0
114.8
16.5
18.3
120.0
121. 8
1%
H3.8
115.6
II7-5
119.3
21.2
23.0
124.8
126.7
I7/16
118.0
H9.9
121.9
123.8
125-7
127.6
129-5
I3i. 5
iy2
122.2
124.2
126.2
128.2
130.2
132.2
134-2
136.2
*.
Weight in Pounds per Lineal Foot for Pipe and Tubing 393
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
*M
10%
10%
I0y2
10%
«4*
10%
II
3/16
19.90
20.15
20.40
20.65
20.90
21.15
21.40
21.65
6
21.51
21.78
22.O5
22.32
22.60
22.87
23.14
23.41
%2
23.14
23-44
23-73
24.O2
24.31
24.60
24.90
25.19
5
23.27
23.57
23.86
24.15
24.45
24.74
25.04
25.33
4
25.13
25-45
25-77
26.08
26.40
26.72
27.04
27.36
•V4
26.37
26.70
27.03
27-37
27.70
28.04
28.37
28.70
3
27.29
27.64
27.98
28.33
28.67
29.02
29-37
29.71
%2
29-57
29-94
30.32
30.70
31-07
31.45
31.82
32.20
2
29-85
30.23
30.6l
30.99
31-37
31.75
32.12
32.50
I
31.48
31-88
32.28
32.68
33-oS
33.48
33.88
34-28
%6
32.75
33-17
33-58
34-00
34-42
34.84
35-25
35.67
1V&2
35.91
36.37
36.83
37-29
37-75
38.20
38.66
39-12
%
39-05
39-55
40.05
40.55
41.05
41.55
42.05
42.55
T/IQ
45-27
45-85
46.43
47-02
47.6o
48.19
48.77
49-35
i&
51.40
52.07
52.73
53-40
54-07
54.74
55-40
56.07
9/16
57-45
58.20
58.95
59-70
6o.45
61.20
61.95
62.70
%
63.41
64-25
65.08
65.92
66.75
67.59
68.42
69.25
ll^g
69.30
70.21
71.13
72.05
72.97
73.88
74.8o
75-72
3/4
75-09
76.10
77-10
78.10
79-10
80.10
81.10
82.10
13/16
80.8l
81.90
82.98
84.06
85-15
86.23
87.32
88.40
%
86.44
87.61
88.78
89.95
91.12
92.28
93-45
94.62
91.99
93-24
94-49
95-75
97.00
98.25
99-50
100.8
I
97.46
98.79
100. 1
101.5
102.8
104.1
105.5
106.8
1 *- '-: •
itte
102.8
108 i
104-3
ioS-7
107.1
108.5
109.9
ill. 3
112. 8
118.6
I3/?6
II3-4
118.5
II4-9
I2O.2
116.5
121. 8
118.1
123.5
119.7
125.2
121. 3
126.8
122.9
128.5
124.4
130.2
I5/16
123.5
125-3
127.0
128.8
130.5
132.3
134-0
135-8
1%
128.5
130.3
132.2
134.0
135.8
137-7
139-5
I4L3
!%6
133-4
135-3
137.2
139 I
141.1
143.0
144.9
146.8
iV2
138.2
140.2
142.2
144.2
146.2 148.2
150.2
152.2
394 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
11%
ni/4
11%
11%
11%
n%
11%
12
8/16
21.90
22.15
22.40
22.65
22.90
23 15
23.40 23.65
6
23.68
23 .95
24 22
24 . 40
24 . 76
%2
25.48
25.77
26^06
26^36
26^65
*J -^O
26.94
•*5 •.}•*• ^o-oo
27-23 27.52
5
25.62
25.92
26.21
26.50
26.80
27 .09
27 . 38 v f\R \
4
27.67
27.99
28.31
28.63
28.94
20. 26
29.58
29.90
V4
29.04
29-37
29.70
30.04
30.37
30.71
31.04
31-37
3
30.06
30.40
30.75
31.09
31.44
31-79
32.13
32.48
'"%2
32.57
32.95
33-32
33.70
34.07
34-45
34.83
35-20
2
32.88
33.26
33.64
34.02
34.40
34.78
35.16
35.54
I
34-68
35.08
35,48
35.89
36.29
36.69
37-09
37-49
'"iie
36.09
36.50
36.92
37.34
37.76
38.17
38.59
39-01
^32
39-58
40.04
40.50
40.96
41.42
41.88
42.33
42.79
%
43-05
43.56
44.06
44.56
45.06
45.56
46.06
46.56
7Ae
49-94
50.52
51. ii
51.69
52.27
52.86
53-44
54-03
y2
56.74
57.41
58.07
58.74
59.41
60.08
60.74
61.41
9/16
63.46
64.21
64.96
65.71
66.46
67.21
67.96
68.71
%
70.09
70.92
71.76
72.59
73.43
74.26
75-09
75-93
!%6
76.64
77-56
78.47
79.39
80.31
81.23
82.15
83-06
%
83.10
84.11
85.11
86.11
87.11
88.11
89.11
90.11
18/ie
89.49
90.57
91.66
92.74
93.83
94.91
96.00
97.08
%
95-79
96.96
98.12
99-29
100.5
ior.6
102.8
104.0
5/16
102.0
103.3
104-5
105.8
107.0
108.3
109.5
no. 8
I08.I
109.5
no. 8
112. 1
II3-5
114.8
116.1
H7.5
Vie
II4.2
115.6
117.0
118.4
119.9
121. 3
122.7
124.1
%
120.2
121. 7
123.2
124.7
126.2
127.7
129.2
130.7
%e
I26.O
127.6
129.2
130.8
132.4
134.0
135-5
I37-I
1/4
I3I.8
133.5
135.2
136.8
138.5
140.2
141.8
143.5
i5/ie
137-5
139.3
141.1
142.8
144.6
146.3
148.1
149.8
i%
143-2
145.0
146.9
148.7
150.5
152.4
154-2
156.0
i7/4e
148.7
150.6
152.6
154.5
156.4
158.3
160.2
162.2
1%
154-2
156.2
158.2
160.2
162.2
164.2
166.2
168.2
' . '
Weight in Pounds per Lineal Foot for Pipe and Tubing 395
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter hi inches
B.W.G
Inches
12%
I2V4
12%
12%
12%
12%
12%
13
8/16
23.91
24.16
24.41
24.66
24.91
25.16
25.41
25.66
6
25.85
26. 12
26.39
26 66
26.93
27.2O
27.47
27.74
7/82
27.82
28.11
28.40
28.69
28.98
29.28
29.57
29.86
5
27.97
28.27
28.56
28.85
29.15
29.44
29-73
30.03
4
30.22
30.53
30.85
31.17
31-49
31.80
32.12
32.44
'"U"
3i.7i
32.04
32.37
32.71
33-04
33.38
33-71
34-04
3
32.82
33-17
33.51
33.86
34-21
34-55
34-90
35.24
'"%2
35-58
35-95
36.33
36.70
37.08
37-45
37.83
38.20
2
35.92
36.29
36 67
37.O5
37-43
37.81
38.19
38.57
I
37.89
38^29
38.69
39-09
39-49
39-89
40.29
40.69
"'%e'
39-42
39.84
4O.26
40.68
41.09
4I.5I
41-93
42.35
!%2
43.25
43-71
44-17
44.63
45-09
45.55
46.01
46.46
%
47.o6
47.56
48.06
48.56
49-06
49.56
50.06
50.56
7/16
54.6i
55-19
55.78
56.36
56.95
57-53
58.12
58.70
%
62.08
62.75
63.41
64.08
64.75
65.42
66.08
66.75
9/i«
69.46
70.21
70.96
71.72
72.47
73-22
73-97
74-73
%
76.76
77.6o
78.43
79-27
80.10
80.94
81.77
82.60
Hie
83.98
84.90
85.82
86.73
87.65
88.57
89.49
90.41
[ -' -&>*|
8/4
91.12
92.12
93.12
94.12
95-12
96.12
97-12
98.12
18/16
98.17
99-25
100.3
101.4
102.5
103.6
104.7
105.8
%
105.1
106.3
107.5
108.6
109.8
III.O
112. 1
II3-3
15/16
112. 0
H3.3
H4.5
115.8
117.0
118.3
II9-5
120.8
I
II8.8
I2O.2
121. 5
122.8
124.2
125-5
126.8
128.2
I Me
125-5
127.0
128.4
129.8
I3L2
132.6
134.0
135.5
i%
132.2
133-7
135.2
136.7
138.2
139-7
I4I.2
142.7
is/ie
138.7
140.3
141.9
143-5
I45-I
146.6
148.2
149-8
1%
145.2
146.9
148.5
150.2
I5I.9
153.5
155-2
156.9
i5/ie
151. 6
153-3
155.1
156.8
158.6
160.3
I62.I
163.8
i%
157-9
159-7
161.5
163.4
165.2
167.0
168.9
170.7
I7/] 6
164.1
166.0
167.9
169.8
171.8
173-7
175.6
177-5
1%
170.2
172.2
174.2
176.2
178.2
180.2
182.2
184.2
396 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
13y8
I3V4
13%
I3V2
13%
I33/4
13%
14
91e
25.91
26.16
26.41
26.66
26.91
27.16
27.41
27.66
6
28.02
28.29
28.56
28.83
29. 10
29.37
29.64
29.91
%2
30.15
30.44
30-74
31.03
31.32
31.61
31.90
32.20
5
30.32
30.62
30.91
31.20
31.50
31.79
32.08
32.38
4
32 76
33.07
33-39
33.71
34.03
34 .'35
34.66
34-98
V4
34.38
34.71
35-04
35.38
35-71
36.05
36.38
36.71
3
35-59
35-94
36.28
36.63
36.97
37.32
37-66
38.01
%2
38.58
38.96
39-33
39.71
40.08
40.46
40.83
41.21
2
38.95
39.33
39.71
40.09
40.47
40.84
41.22
41.60
I
41.09
41.49
41.89
42.29
42.69
43.09
43-49
43.00
5/i«
42.76
43.18
43.6o
44-01
44-43
44.85
45-27
45-68
46.92
47.38
47.84
48.30
48.76
49-22
49-68
50.14
3/8
51.06
51-57
52.07
52.57
53-07
53.57
54.07
54-57
7/ie
59-28
59-87
6o.45
61.04
61.62
62.20
62.79
63.37
67.42
68.09
68.75
69.42
70.09
70.76
71.42
72.09
lie
75-47
76.22
76.97
77-72
78.47
79-23
79.98
8o.73
%
83.44
84.27
85.11
85-94
86.78
87.61
88.45
89.28
l^Q
91.32
92.24
93.i6
94-08
94-99
95-91
96.83
97-75
%
99-13
100. 1
IOI.I
IO2.I
103.1
104.1
105.1
106.1
18/le
106.8
107.9
IOO.O
IIO.I
III. 2
112. 3
113.4
II4-4
%
H4.5
115.6
116.8
118.0
119.2
120.3
121. 5
122.7
15/16
122,0
123-3
124.5
125.8
127.0
128.3
129-5
130.8
I
129.5
130.8
132.2
133-5
134.8
136.2
137-5
138.8
I%8
136.9
138.3
139.7
141.1
142.6
144.0
145-4
146.8
1%
144.2
145-7
147.2
148.7
150.2
151.7
153-2
154-7
I%6
I5I.4
153-0
154-6
156.2
157-7
159.3
160.9
162.5
1%
158.5
160.2
161.9
163-5
165.2
166.9
168.5
170.2
165.6
167.3
169.1
170.8
172.6
174.3
176.1
177.8
1%
172.6
174-4
176.2
178.1
179-9
181.7
183.6
185.4
I7/16
179-4
181.4
183.3
185.2
187.1
189.0
190.9
192.9
186.2
188.2
190.2
192.2
194-2
196.2
198.3
200.3
Weight in Pounds per Lineal Foot for Pipe and Tubing 397
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
141/8
14%
14%
I4V2
14%
14%
14%
15
8/16
27.91
28.16
28.41
28.66
28.91
29.16
29.41
29.66
6
30.18
30.45
30.73
3i.oo
31-27
31-54
3i.8i
32.08
""%*'
32.49
32.78
33-07
33-37
33-66
33-95
34-24
34-53
5
32.67
32.97
33.26
33-55
33-85
34.14
34-43
34-73
4
35.30
35.62
35-93
36.25
36.57
36.89
37.21
37-52
y±
37-05
37.38
37-71
38.05
38.38
38.72
39-05
39.38
3
38.36
38.70
39-05
39-39
39-74
40.08
40.43
40.78
'"%*
41.58
41.96
42.33
42.71
43-09
43.46
43.84
44-21
2
41.08
42.36
42.74
43-12
43-50
43.88
44.26
44.64
I
44-30
44-70
45-10
45-50
45.90
46.30
46.70
47-10
"Vie"
46.10
46.52
46.93
47-35
47-77
48.19
48.60
49-02
*%»
50.60
51.05
51.51
51-97
52.43
52.89
53-35
53-81
%
55.07
55-57
56.07
56.57
57-07
57 57
58.07
58.57
7/16
63.96
64.54
65.12
65.71
66.29
66.88
67.46
68.04
V2
72.76
73-43
74-09
74.76
75-43
76.10
76.76
77.43
%6
81.48
82.23
82.98
83.73
84.48
85.23
85.98
86.73
%
90.11
90.95
91.78
92.62
93-45
94-29
95.12
95-95
iH«
98.67
99.58
100.5
101.4
102.3
103.3
104.2
113. 1
105.1
114. i
13/16
II5-5
116.6
II7-7
118.8
119.9
120.9
122. 0
123.1
%
123.8
125.0
126.2
127-3
128.5
129.7
130.8
132.0
15/16
132.0
133-3
134-5
135-8
137-0
138.3
139-6
140.8
I
140.2
I4I.5
142.8
144-2
145-5
146.9
148.2
149-5
!Vl6
148.2
149.6
I5I.I
152.5
153-9
155-3
156.7
158.2
1%
156.2
157-7
159.2
160.7
162.2
163.7
165.2
166.7
I3/16
164.1
165.7
167.3
168.8
170.4
172.0
173-6
175-2
IV*
171.9
173.6
175-2
176.9
178.6
180.2
I8I.9
183.6
I5/16
179-6
181.4
183.1
184.9
186.6
188.4
I90.I
191.9
1%
187.2
189.1
190.9
192.7
194.6
196.4
198.3
200.1
i7/ie
194-8
196.7
198.6
200.5
202.5
204.4
206.3
208.2
4j
202.3
204.3
206.3
208.3
210.3
212.3
214.3
216.3
398 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
15%
I5H
15%
15%
15% 15%
15%
16
6
5
3/16
29.91
32.35
34-83
35-02
30.16
32.62
35-12
35-32
30.41
32.89
35-41
35.6i
30.66
33-i6
35-70
35-90
30.91
33-44
35-99
36.20
31.16
33.71
36.29
36.49
31.41
33.98
36.58
36.78
31.66
34-25
36.87
37.o8
%2
4
3
'"U"
'"%2'
37-84
39-72
41.12
44-59
38.16
40.05
41-47
44.96
38.48
40.38
41.81
45-34
38.79
40.72
42.16
45-71
39-11
41.05
42.50
46.09
39.43
41.39
42.85
46.46
39.75
41.72
43-20
46.84
40.07
42.05
43-54
47-22
2
I
45- C2
47-50
49-44
54-27
45-39
47.90
49.85
54-73
45-77
48.30
50.27
55.18
46.15
48.70
50.69
55.64
46.53
49.10
51- II
56.10
46.91
49.50
51.52
56.56
47.29
49.90
51.94
57-02
47.67
50.30
52.36
57.48
5/16
*%2
%
7/16
Va
9/16
59-07
68.63
78.10
87.49
59-58
69.21
78.77
88.24
60.08
69.80
79-43
88.99
60.58
70.38
80.10
89.74
61.08
70.96
80.77
90.49
61.58
71.55
81.44
91.24
62.08
72.13
82.10
91.99
62.58
72.72
82.77
92.74
%
m*
%
13/16
96.79
106.0
US. i
124.2
97-62
107.0
116.1
125.3
98.46
107.8
117.1
126.4
99-29
108.8
118.1
127.5
100. 1
109.7
119.2
128.5
IOI.O
no. 6
I2O.2
129.6
101.8
in. 5
121. 2
130.7
102.6
112. 4
122.2
I3I.8
%
15A6
iVlG
133-2
142.1
150.9
159-6
134-3
143-3
152.2
161.0
135-5
144-6
153-5
162.4
136.7
145-8
154-9
163.8
137.8
147.1
156.2
165.3
139.0
148.3
157.5
166.7
140.2
149.6
158.9
168.1
I4I-3
150.8
l6o.2
169.5
H/8
I3/16
1%
I5/16
168.2
176.8
185.2
193.6
169.7
178.4
186.9
195-4
171.2
179-9
188.6
197-1
172.7
181.5
190.2
198.9
174.2
183.1
191.9
2O0.6
175.7
184.7
193.6
202.4
177.2
186.3
195.2
204.1
178.7
187.9
196.9
205.9
1%
IT/10
i%
201.9
2IO.I
218.3
203.8
212. 1
220.3
205.6
214.0
222.3
207.4
215-9
224.3
209.3
217.8
226.3
211. 1
219.7
228.3
212.9
221.7
230.3
214.8
223.6
232.3
',-' ""
.
',
,.
.
Weight in Pounds per Lineal Foot for Pipe and Tubing 399
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
16%
*%
16%
i6y2
16%
i<%
16%
17
3/16
31.92
32.17
32.42
32.67
32.92
33-17
33-42
33.67
6
34.52
34-79
35.06
35-33
35.6o
35 88
36. 15
36.42
%2
37.16
37-45
37-75
38.04
38.33
38.62
38.91
39-21
5
37-37
37-66
37-96
38.25
38.55
38.84
39- 13
39-43
4
40.38
40.70
41.02
41.34
41.65
4I.97
42.29
42.61
Vi
42.39
42-72
43-05
43-39
43.72
44.06
44-39
44-72
3
43.89
44.23
44.58
44-93
45.27
45.62
45.96
46.31
%2
47-59
47-97
48-34
48.72
49-09
49-47
49-84
50.22
2
48.05
48. 43
48.81
49- 19
49.56
49.94
50.32
50. 70
I
50.70
51.10
51-51
51-91
52.31
52.71
53-11
53-51
"'%i'
52.77
53-19
53.6i
54-03
54-44
54.86
55-28
55-70
H'32
57-94
58.40
58.86
59-31
59-77
60.23
60.69
61.15
%
63.08
63.58
64.08
64-58
65.08
65.58
66.08
66.58
Ttti
73-30
73-88
74-47
75-05
75.64
76.22
76.81
77-39
V2
83.44
84.11
84.77
85-44
86.11
86.78
87.44
88.11
9/16
93-49
94.24
95.00
95-75
96.50
97-25
98.00
98.75
%
103-5
104-3
105.1
106.0
106.8
107.6
108.5
109.3
Hie
113- 4
H4-3
115.2
116.1
117.0
117.9
118.9
119-8
8/4
123.2
124.2
125.2
126.2
127.2
128.2
129.2
130.2
13/16
132.9
134-0
135-0
136.1
137-2
138.3
139-4
140.5
%
142.5
143-7
144 8
146.0
147-2
148.4
149-5
150.7
15/16
I52.I
153-3
154-6
155-8
I57-I
158.3
159-6
160.8
I
161.5
162.9
164.2
165-5
166.9
168.2
169.5
170.9
lVl6
170.9
172-3
173.8
175.2
176.6
178.0
179-4
180.9
iVs
180.2
181.7
183.2
184.7
186.2
187.7
189.2
190.7
I3/16
189-4
191.0
192.6
194.2
195-8
197-4
199.0
200.5
1%
198.6
200.3
201.9
203.6
205.3
206.9
208.6
210.3
I5/16
207.6
209.4
211. 1
212.9
214.6
216.4
218.2
219-9
1%
216.6
218.4
220.3
222.1
223.9
225.8
227.6
229.5
I7/16
225-5
227.4
229-3
231.3
233-2
235-1
237.0
238.9
IV2
234-3
236.3
238.3
240.3
242.3
244.3
246.3
248-3
400 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
[nches
ifH
I7V4
17%
I7V2
17%
17%
17%
18
6
5
%6
"'%i'
33-92
36.69
39-50
39-72
34.17
36.96
39-79
40.01
34-42
37-23
40.08
40.31
34-67
37-50
40.37
40.60
34-92
37-77
40.67
40.90
35-17
38.04
40-96
41.19
35-42
38.31
41.25
41.48
35.67
38.59
4L54
41.78
4
3
2
i
'"%"
'"%2
42.92
45-o6
46-65
50.60
51.08
53-91
56.11
61.61
43-24
45.39
47-00
50.97
51.46
54-31
56.53
62.07
43.56
45-72
47.35
5L35
51.84
54-71
56.95
62.53
43-88
46.06
47.69
5L72
52.22
55.ii
57.36
62.99
44.20
46.39
48.04
52.10
52.60
55-51
57-78
63.44
44-51
46.73
48.38
52.47
52.98
55-91
58.20
63.90
44.83
47-06
48.73
52.85
53-36
56.31
58.62
64.36
45-15
47-39
49-07
53-22
53-74
56.71
59-03
64.82
'"%i*
^32
%
%6-
y2
9/16
67.08
77-97
88.78
99-50
67.59
78.56
89-45
100.3
68.09
79-14
90.11
IOI.O
68.59
79-73
90.78
101.8
69.09
80.31
91-45
102.5
69.59
80.89
92.12
103-3
70.09
81.48
92.78
104.0
70.59
82.06
93-45
104.8
%
^6
%
13/10
no. i
120.7
131 2
I4I.6
III.O
121. 6
132.2
142.6
HI. 8
122.5
133-2
143 7
112. 6
123.4
134-2
144-8
II3-5
124.4
135-2
145-9
II4-3
125-3
136.2
147-0
IIS- 1
126.2
137-2
148,1
116.0
127.1
138.2
149- 1
%
15/16
I
lVl6
I5I.9
I62.I
172.2
182.3
153 o
163.3
173-6
183-7
154-2
164.6
174-9
185.1
155-4
165.8
176.2
186.5
156.5
167.1
177-6
187.9
157-7
168.3
178.9
189-4
158.9
169.6
180.2
190.8
160.0
170.8
181.6
192.2
iVs
I8/16
IV4
I5/16
192.2
202.1
2II.9
221.7
193-7
203.7
213.6
223.4
195-2
205.3
215-3
225.2
196.7
206.9
216.9
226.9
198.3
208.5
218.6
228.7
199-8
2IO.I
220.3
230.4
201.3
211. 6
221.9
232.2
202.8
213.2
223.6
233.9
1%
i7/ie
iV2
231.3
240 8
250.3
233-1
242.8
252.3
235-0
244-7
254-3
236.8
246.6
256-3
238.6
248.5
258.3
240.5
250.4
260.3
242.3
252.4
262.3
244.1
254.3
264.3
Weight in Pounds per Lineal Foot for Pipe and Tubing 401
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
18%
i8V4
18%
isi/2
18%
18%
187/8
19
3/16
35-92
36.17
36.42
36.67
36.92
37-17
37-42
37.67
6
38.86
39-13
39-40
39.67
39-94
40.21
40.48
40.75
"'7/32'
41-83
42.13
42.42
42.71
43-00
43-29
43-59
43-88
5
42.07
42.36
42.66
42.95
43-25
43-54
43.83
44.13
4
45-47
45.78
46.10
46.42
46.74
47.o6
47-37
47.69
'"ii"
47-73
48.06
48.39
48.73
49-06
49-40
49-73
50.06
3
49.42
49-77
50.11
50.46
50.80
51.15
51.49
51.84
%2
53.6o
53-97
54-35
54.73
55-10
55.48
55.85
56.23
2
54.11
54-49
54.87
55.25
55.63
56.01
56.39
56.77
I
57.11
57.51
57.91
58.31
58.71
59-11
59-52
59.92
5/16
59-45
59.87
60.28
60.70
61.12
61.54
jy j~
61.95
62.37
H'32
65-28
65.74
66.20
66.66
67.12
67.57
68.03
68.49
%
71.09
71.59
72.09
72.59
73-09
73-59
74-09
74-59
7Ae
82.65
83.23
83.81
84.40
84.98
85.57
86.15
86.73
%
94.12
94-79
95-45
96.12
96.79
97.46
98.12
98.79
9/ie
105-5
106.3
107.0
107.8
108.5
109-3
IIO.O
no. 8
%
116.8
117.6
118.5
II9-3
120.2
121. 0
121. 8
122.7
lVl6
128.0
129.0
129.9
130.8
I3I.7
132.6
133.5
134-5
%
139-2
140.2
141.2
142.2
143-2
144.2
145-2
146.2
13/16
150.2
I5I-3
152.4
153-5
154-6
155-7
156.7
157.8
%
161.2
162.4
163.5
164.7
165.9
167.0
168.2
169.4
15Ae
172.1
173-3
174.6
175-8
I77-I
178.4
179-6
180.9
i
182.9
184.2
185.6
186.9
188.2
189-6
190.9
192.2
I*/16
193-6
I95-I
196.5
197-9
199-3
200.7
202. i
203.5
iVs
204.3
205.8
207.3
208.8
210.3
211. 8
213-3
214.8
I3/16
214.8
216.4
218.0
219.6
221.2
222.7
224.3
225.9
1%
225.3
227.0
228.6
230.3
232.0
233-6
235 3
237.0
I5/i6
235-7
237-4
239.2
240.9
242.7
244.4
246.2
247-9
1%
246.0
247.8
249.6
251.5
253-3
255-2
257 o
258.8
i%e
256.2
258.1
260.0
262.0
263.9
265.8
267.7
269.6
iy2
266.3
268.3
270.3
272.3
274-3
276.3
278.4
280.4
402 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
19%
191/4
19%
191/2
19%
19%
19%
20
3/ie
37.92
38.17
38.42
38.67
38.92
39-17
39-43
39.68
6
41.02
4i.3o
41-57
41.84
42.11
42.38
42.65
42.92
7/
732
44.17
44.46
44-75
45-05
45-34
45.63
45-92
46.21
5
44.42
44-71
45-01
45-30
45-59
45.89
46.18
46.48
4
48.01
48.33
48.64
48.96
49.28
49.60
49.91
So. 23
ii
50.40
50.73
5i.o6
51.40
51-73
52.07
52.40
53.73
3
52. 19
52 53
52.88
53. 22
53-57
53 92
54 . 26
P AT
%2
56.60
56.98
57-35
57-73
58.10
58^8
58.86
5 .uj.
5 23
2
57.15
57-53
57-91
58.29
58.66
59-04
59-42
5 50
I
60.32
60.72
61.12
61.52
6l.92
62.32
62.72
63 12
"'%i'
62.79
63.20
63.62
64.04
64.46
64.87
65.29
65.71
Hb
68.95
69.41
69.87
70.33
70.79
71.25
71.71
72.16
%
75-09
75.6o
76.10
76.60
77-10
77.6o
78.10
78.60
%6
87.32
87.90
88.49
89.07
89.65
90.24
90.82
91.41
%
99.46
IOO.I
100.8
101.5
IO2.I
102.8
102.5
IO4.I
9/16
in. 5
112. 3
113.0
113.8
II4-5
115.3
116.0
II6.8
%
123-5
124.3
125.2
126.0
126.8
127.7
128.5
129.3
*Vi6
135-4
136.3
137-2
138.1
I39-I
140.0
140.9
I4I.8
%
147.2
148.2
149.2
150.2
I5I.2
152.2
153 2
154-2
18/16
158.9
160.0
161.1
162.2
163.2
164.3
165.4
166.5
%
170.5
171.7
172.9
I74-I
175-2
176.4
175-6
178.7
15/16
182.1
183.4
184.6
185.9
I87.I
188.4
189.6
190.9
I
193.6
194-9
196.2
197.6
198.9
200.3
201.6
202.9
iVie
205.0
206.4
207.8
209.2
210.6
212. 1
213.5
214-9
1 1/8
216.3
217.8
219-3
220.8
222.3
223.8
225.3
226.8
I%6
227.5
229.1
230.7
232.3
233-8
235-4
237.0
238.6
1%
238.6
240.3
242.0
243-6
245-3
247-0
248.6
250.3
I5/16
249-7
251.4
253-2
254-9
256.7
258.5
260.2
262.0
1%
260.7
262.5
264.3
266.2
268.0
269.8
271.7
273-5
I%6
271.6
273-5
275.4
277-3
279-2
28I.I
283.1
285.0
i%
282.4
284.4
286.4
288.4
290.4
292.4
294.4 296.4
Weight in Pounds per Lineal Foot for Pipe and Tubing 403
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
2oy8
20%
208/8
20y2
2o5/8
20%
20%
21
8/16
39.93
-40.18
40.43
40.68
40.93
4I.I8
41.43
41.68
6
43.19
43.46
43-73
44.01
44.28
44-55
A A 8?
45 .09
7/32
46.51
46.80
47-09
47.38
47.67
47-97 48.26
48^55
5
46.77
47.06
47.36
47.65
47-94
48.24
48.53
48.83
4
50.55
5O.87
51.19
51.50
51.82
52.14
52.46
52. 77
ii
53.07
53-40
53-73
54.07
54-40
54-74
55-07
55-40
3
54-95
55-30
55.64
55-99
56.34
56.68
57-03
57.37
"'%2'
59.6i
59.98
60.36
6o.73
.61.11
61.48
61.86
62.23
2
60. 18
60.56
60.94
61.32
61.70
62.08
62.46
62.84
I
63 52
63 92
64 32
64 72
65.12
65 52
65 92
66.32
5/16
66.13
66.54
66.96
67.38
67.79
68^21
68^63
69.05
*%2
72.62
73.o8
73-54
'74.00
74.46
74-92
75.38
75-84
%
79-10
79.60
80.10
80.60
81.10
81.60
82.10
82.60
%a
91.99
92.58
93.16
93-74
94-33
94-91
95-50
96.08
y2
104.8
105-5
106.1
106.8
107.5
108.1
108.8
109.5
9/16
H7.5
118.3
119.0
119.8
120.5
121. 3
122.0
122.8
%
130.2
131 • o
131.8
132.7
133.5
134-3
135-2
136.0
!Vl6
142.7
143.6
144.6
145-5
146.4
147-3
148.2
149 -I
3/4
155.2
156.2
157-2
158.2
159-2
160.2
161.2
162.2
13/16
167.6
168.7
169.8
170.8
171.9
173-0
174.1
175.2
7/8
179-9
181.1
182.2
183.4
184.6
185.7
186.9
188.1
15/16
192.1
193-4
194-6
195-9
197.1
198.4
199.6
200.9
I
204.3
205.6
206.9
208.3
209.6
210.9
212.3
213.6
iVio
216.3
217.7
219.2
220.6
222. 0
223.4
224.8
226.2
iVs
228.3
229.8
231.3
232.8
234-3
235-8
237-3
238.8
I3/16
240.2
241.8
243.3
244-9
246.5
248.1
249-7
251.3
il4
252.0
253-7
255-3
257-0
258.7
260.3
262.0
263.7
I5/16
263.7
265.5
267.2
269.0
270.7
272.5
274.2
276.0
1% '
275-3
277.2
279.0
280.9
282.7
284.5
286.4
288.2
I7/l6
286.9
288.8
290.7
292.7
294.6
296.5
298.4
300.3
iy2
298.4
300.4
302.4
304.4
306 4
308.4
310.4
312.4
404 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table H. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
2iVs
2iy4
218/8
2iy2
21%
213/4
21%
22
8/16
41-93
42.18
42.43
42.68
42.93
43-18
43-43
43.68
6
45.36
45.63
45.90
46.17
46.44
46.72
46.99
47.26
'"%i*
48.84
49.13
49.43
49.72
50.01
50.30
50.60
50.89
5
49.12
49.41
49.71
50.00
5O.29
5O.59
50.88
51.18
4
53.09
53.41
53.73
54.05
54.36
54-68
55-00
55-32
'"%"
55-74
56.07
56.40
56.74
57-07
57-41
57-74
58.07
3
57-72
58.06
58.41
58.76
59-10
59-45
59-79
60.14
'"%2
62.61
62.99
63.36
63.74
64.11
64.49
64.86
65.24
2
63 21
63.59
63. 97
64 35
64 73
65 ii
65.49
65.87
I
"%6"
66^72
69.46
67.12
69.88
67^53
7P-30
67.93
70.71
68^33
7I-I3
68^73
71-55
69'i3
71.97
69.53
72.38
%
76.29
76.75
77.21
77.67
78.13
78.59
79-05
79-51
8/8
83.10
83.61
84.11
84.61
85.11
85.61
86.11
86.61
%6
Vo
96.66
IIO. I
97.25
97.83
98.42
99-0
99.58
IOO.2
100.8
72
9/4e
123.5
124.3
125.0
125.8
126.5
127-3
128.0
128.8
%
136.8
137.7
138.5
139-3
140.2
141.0
I4I.8
142.7
i%«
150.1
151.0
I5I-9
152.8
153-7
154-7
155-6
156.5
8/4
163.2
164.2
165 . 2
166.2
167.2
168.2
169.2
170.2
18Ae
176.3
177.3
178.4
179-5
180.6
181.7
182.8
183.9
%
189.2
190.4
I9I.6
192.7
193.9
I9S-I
196.2
197-4
15/ie
2O2.I
203.4
2O4.6
205.9
207.1
208.4
209.6
210.9
i
214-9
216.3
217.6
218.9
220.3
221.6
222.9
224.3
I%8
227.7
229.1
230.5
231-9
233-3
234-8
236.2
237.6
i%
240.3
241.8
243-3
244-8
246.3
247-8
249-3
250.8
I8/16
252.9
254.4
256.0
257-6
259-2
260.8
262.4
264.0
IV4
265.3
267.0
268.7
270.3
272.0
273-7
275-3
277.0
I6/16
277-7
279.5
281.2
283.0
284.7
286.5
288.2
290.0
18/8
290.0
291.9
293-7
295-5
297.4
299-2
301.0
302.9
I%6
302.3
304.2
306.1
308.0
309.9
3H.9
313.8
315.7
iy2
314.4
316.4
318.4
320.4
322.4
324.4
326.4
328.4
Weight in Pounds per Lineal Foot for Pipe and Tubing 405
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
22l/8
2214
223/8
2&/2
225/8
228/4
227/8
23
8/16
43-93
44.18
44-43
44-68
44-93
45.18
45-43
45-68
6
47-53
47.80
48.07
48.34
48.61
48.88
49-15
49-43
'"%2
51.18
51-47
51.76
52.06
52.35
52.64
52.93
53-22
5
51-47
51.76
52.06
52.35
52.64
52.94
53-23
53-52
4
..._.
55.63
55-95
56.27
56.59
56.91
57-22
57-54
57-86
58.41
58.74
59-07
59-41
59-74
60.08
60.41
60.74
3
60.48
60.83
61.18
61.52
61.87
62.21
62.56
62.91
'"%2
65.61
65.99
66.37
66.74
67.12
67.49
67.87
68.24
2
66.25
66.63
67.01
67.38
67.76
68.14
68.52
68.90
I
69.93
7O.33
7O 77
71.13
71-53
71 _ Q^
72.33
72. 73
%6
72.80
73-22
I*-1- 10
73.63
74-05
74-47
74^89
75-30
75-72
Hfal
79-97
80.42
80.88
8i.34
81.80
82.26
82.72
83.18
%
87.11
87.61
88.11
88.61
89.11
89.61
9O.II
90.61
Vl6
101.3
101.9
102.5
103.1
103.7
104.3
104.8
105.4
%
II5-5
116.1
116.8
H7.5
118.1
118.8
II9-5
I2O.2
9/ie
129.5
130.3
131.0
131.8
132.5
133.3
134-0
134-8
%
143-5
144-3
145-2
146.0
146.9
147.7
148.5
149-4
4?«
157-4
158.3
159-2
160.2
161.1
162.0
162.9
163.8
%
171.2
172.2
173-2
174.2
175-2
176.2
177.2
178.2
!%6
184.9
186.0
187.1
188.2
189.3
190.4
I9L5
192.5
%
198.6
199-8
200.9
202.1
203.3
204.4
205.6
206.8
15/ie
212. 1
213-4
214.6
215-9
217.1
218.4
219-7
220.9
i
225.6
227.0
228,3
229.6
231.0
232.3
233.6
235-0
iVie
239-0
240.4
241.8
243-3
244-7
246.1
247-5
248.9
i%
252.3
253-8
255-3
256.8
258.3
259.8
261.3
262.8
I%6
265.5
267.1
268.7
270.3
271.9
273.5
275-1
276.6
*%
278.7
280.4
282.0
283.7
285.4
287.0
288.7
290.4
i5/ie
291.7
293.5
295.2
297.0
298.8
300.5
302.3
304.0
i%
304-7
306.6
308.4
310.2
312. i
313.9
315.7
317 6
I%6
317.6
319.5
321.4
323.4
325.3
327.2
329.1
331.0
iV2
330.4
332.4
334-4
336.4
338.4
340.4
342.4
344-4
406 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table H. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
23Vs
23V4
23%
23V2
23%
23%
23%
24
3/16
45-93
46.18
46.43
46.68
46.93
. 47.18
47-43
47.69
6
49-70
49-97
50.24
50.51
50.78
51.05
51-32
51-59
":%*
53-52
53.81
54.10
54-39
54.68
54.98
55-27
55-56
5
53-82
54-11
54-41
54-70
54-99
55-29
55-58
55-87
4
58.18
58.49
58.81
59-1"
59-45
59.76
60.08
60.40
U
61.08
61.41
6i.74
62.08
62.41
62.75
63-08
63.41
3
63.25
63 60
63.94
64.29
64.63
64.98
65.33
65.67
%2
68.62
68.99
69.37
69.74
70.12
70.50
70.87
71-25
2
69.28
69.66
70.04
70.42
70.80
71. 18
71.56
71 .93
I
73-13
73 53
73-93
74-33
74-73
75 13
75-54
75 -94
5/le
76.14
76.'s6
76.97
77-39
77^81
78^22
78.64
79-06
Wa
83.64
84.10
84.55
85.01
85.47
85.93
86.39
86.85
%
91.12
91.62
92.12
92.62
93-12
93.62
94-12
94.62
7/16
106.0
106.6
107.2
107.8
108.3
108.9
109.5
IIO. I
%
120.8
121. 5
122.2
122.8
123-5
124.2
124.8
125.5
9/16
135-5
136.3
137-0
137.8
138.6
139.3
140.1
140.8
%
150.2
151.0
I5I.9
152.7
153-5
154.4
155-2
156.0
iMe
164.7
165.7
166.6
167.5
168.4
169.3
170.3
171.2
%
179.2
180.2
181.2
182.2
183.2
184.2
185.2
186.2
13/10
193-6
194-7
195-8
196.9
198.0
199.0
200. 1
201.2
%
207.9
209.1
210.3
211.4
212.6
213.8
214.9
216.1
15A6
222.2
223.4
224-7
225.9
227.2
228.4
229.7
230.9
I
236.3
237.6
239.0
240.3
241.6
243.0
244-3
245.6
I%6
250.4
251.8
253.2
254-6
256.0
257.5
258.9
260.3
i%
264.3
265.8
267.3
268.8
270.3
271.8
273-3
274.8
I8/16
278.2
279-8
281.4
283.0
284.6
286.2
287.7
289.3
iV4
2Q2.0
293-7
295-4
297.0
298.7
300.4
302.0
303.7
i5/ie
305.8
307.5
309.3
311.0
312.8
314.5
316.3
318.0
i%
319.4
321.2
323.1
324.9
326.7
328.6
330.4
332.3
I7/16
333.0
334-9
336.8
338.7
340.6
342.6
344-5
346.4
i%
346.4
348.4
350.4
352.4
354-4
356.5
358.5
360.5
Weight in Pounds per Lineal Foot for Pipe and Tubing 407
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
24%
24V4
24%
24V2
24%
248/4
247/8
25
s/le
47.94
48.19
48.44
48.69
48.94
49-19
49-44
49-69
6
51-86
52.14
52.41
52.68
52.95
53-22
53-49
53-76
"'%i'
55.85
56.14
56.44
56.73
57-02
57.31
57.6o
57-90
5
56.17
56.46
56.76
57.05
57 . 34
57.64
57-93
58.22
4
60.72
6l.O4
61.35
61.67
61.99
62.31
62.62
62.94
tt
63-75
64.08
64.41
64.75
65.08
65.42
65-75
66.08
3
66.02
66.36
66.71
67.05
67.40
67.75
68.09
68.44
%2
71.62
72.OO
72-37
72.75
73.12
73.50
73-87
74.25
2
72.31
72.69
73.O7
73-45
73.83
74.21
74-59
74-97
I
76.34
76.74
77-14
77-54
77-94
78.34
78.74
79-14
'"%«•
79.48
79.89
80.31
80.73
81.14
81.56
81.98
82.40
H'82
87-31
87.77
88.23
88.68
89.14
89.60
90.06
00.52
%
95.12
95.62
96.12
96.62
97-12
97.62
98.12
98.62
%e
110.7
ill. 3
in. 8
112.4
113.0
113.6
114.2
114.8
V2
126-2
126.8
127-5
128.2
128.8
129.5
130.2
130.8
9/16
141.6
142.3
I43-I
143.8
144-6
145.3
146.1
146.8
%
156,9
157-7
158.5
159-4
160.2
161.0
161.9
162.7
i%e
172.1
173-0
173-9
174-8
175-8
176.7
177.6
178.5
%
187.2
188.2
189.2
190.2
191.2
192.2
193.2
194.2
1 ,
18/16
202.3
203.4
204.5
205.6
206.6
207.7
208.8
209.9
r 8 • f v '
%
217- ,3
218.4
219.6
220.8
221.9
223.1
224.3
225.5
15Ae
232.2
233-4
234-7
235-9
237-2
238.4
239-7
240.9
i
247-0
248.3
249.6
25I.O
252.3
253-7
255.0
256-3
itte
261.7
263.1
264.5
266.0
267.4
268.8
270.2
271.6
iVs
276.3
277-9
279.4
280.9
282.4
283.9
285.4
286.9
I3/16
290.9
292.5
294.1
295-7
297-3
298.8
300.4
302.0
iH
305.4
307.1
308.7
310.4
312. 1
313-7
315-4
3I7.I
I5/16
319.8
321.5
323.3
325.0
326.8
328.5
330.3
332-0
1%
334-1
335-9
337-8
339-6
341.4
343-3
345-1
346.9
lVl6
348.3
350.2
352.2
354-1
356.0
357-9
359-8
361.7
lV2
362.5
364.5
366.5
368.5
370.5
372.5
374-5
376-5
408 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
25%
25U
25%
25^2
25%
258/i
257/8
26
8/16
49.94
50.19
50.44
50.69
50.94
51.19
51.44
51.69
6
54.03
54-30
54.57
54-85
55-12
55.39
55-66
55-93
'"%2*
58.19
58.48
58.77
59-o6
59.36
59-65
59-94
60.23
5
58.52
58 81
59.ii
59.40
59.69
59-99
60.28
60.57
4
63.26
63.58
63.90
64.21
64.53
64.85
65.17
65.48
V4
66.42
66.75
67.08
67.42
67-75
68.09
68.42
68.75
3
68.78
69. 13
69.47
69.82
70.17
70.51
70.86
71.20
%2
74-63
75-00
75.38
75-75
76.13
76.50
76.88
77-25
2
75-35
75.73
76.11
76.48
76.86
77.24
77.62
78.00
I
79-54
79-94
80 34
80.74
81.14
81.54
81.94
82.34
%6
82.81
83.23
83-65
84.06
84-48
84-90
85-32
85-73
H'32
90.98
91.44
91.90
92.36
92.82
93-27
93-73
94-19
%
99-13
99.63
100 I
100.6
IOI.I
101.6
IO2.I
102.6
7Ae
II5-4
II5-9
116.5
117.1
117.7
118.3
II8.9
119.4
y2
I3I-5
132.2
132.8
133-5
134-2
134-8
135-5
136.2
9/10
147-6
148.3
149-1
149 8
150.6
I5I-3
I52.I
152.8
%.
163.5
164.4
165.2
166.0
166.9
167 7
168.5
169.4
iMe
179-4
180.4
181.3
182 2
183.1
184 o
184.9
185.9
8/4
195-2
196.2
197.2
198.3
199-3
200.3
201.3
202.3
18/46
211. 0
212. 1
213.1
214.2
215-3
216.4
217.5
218.6
%
226.6
227.8
229.0
230.1
231-3
232.5
233.6
234-8
15/i6
242.2
243.4
244-7
245-9
247-2
248.4
249.7
250.9
I
257-7
259.0
260.3
261.7
263.0
264.3
265.7
267.0
1^6
273.1
274-5
275-9
277-3
278.7
280.1
281.6
283.0
iVs
288.4
289.9
291.4
292.9
•294-4
295-9
297.4
298.9
I3/l6
303-6
305.2
306.8
308.3
309-9
3H.5
313.1
314.7
I*/4
318.7
320-4
322.1
323.7
325-4
327-1
328.7
330.4
I%6
333-8
335.5
337-3
339-1
340.8
342.6
344-3
3~46.I
18/8
348.8
350.6
352.4
354-3
356.1
358.0
359-8
361.6
I7/16
363.7
365-6
367.5
369.4
371-3
373-3
375-2
377.1
1%
378.5
380.5
382 5
384-5
3865
388 5
390.5
392.5
Weight in Pounds per Lineal Foot for Pipe and Tubing 409
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
26V8
26U
263/8
26y2
265/8
268/4
267/8
27
8/16
51-94
52.19
52.44
52.69
52.94
53-19
53-44
53.69
6
56.20
56.47
56.74
57-01
57-28
57.56
57-83
58.10
"'7/32'
60.52
60.82
61. ii
61.40
61.69
61.98
62.28
62.57
5
60.87
61.16
6i.45
6i.75
62.04
62.34
62.63
62.92
4
65.80
66.12
66.44
66.75
67.07
67.39
67.71
68.03
%
69.09
69.42
69.75
70.09
70.42
70.76
71.09
71.42
3
7i "»•;
71 .90
72 24
72 59
72.93
73.28
73.62
73-97
%2
/A -00
77.63
78^00
78^38
78^76
79.13
79-51
79-88
80.26
2
78.38
78.76
79-14
79-52
79-90
80.28
80-65
81.03
i
82 74
83 15
83 55
83.95
84 35
84.75
85-15
85.55
5Ae
86^15
86^57
86^98
87.40
87^82
88.24
88.65
89-07
H32
94.65
95.ii
95-57
96.03
96.49
96.95
97-40
97.86
%
103.1
103.6
104.1
104.6
105.1
105.6
106.1
106.6
Vie
I2O.O
120.6
121. 2
121. 8
122.4
122.9
123-5
124.1
¥2
136.8
137-5
138.2
138.8
139-5
140.2
140.8
I4L5
%6
153.6
154-3
155. 1
155-8
156.6
157-3
158.1
158.8
%
170.2
171.0
171.9
172.7
173-6
174-4
175-2
176.1
!M6
186.8
187.7
188.6
189-5
190.4
191.4
192.3
193.2
8/4
203.3
204.3
205.3
206.3
207.3
208.3
209-3
210.3
18Ae
219-7
220.7
211. 8
222.9
224.0
225.1
226.2
227.2
%
236.0
237-1
238.3
239-5
240.6
241.8
243-0
244.1
15/ie
252.2
253-4
254-7
255-9
257-2
258.5
259.7
261.0
i
268.3
269.7
271.0
272.3
273-7
275-0
276.3
277-7
i!/i6
284.4
285.8
287.2
288.7
290.1
29L5
292.9
294-3
i%
300.4
301.9
303.4
304.9
306.4
307.9
309.4
310.9
I3/16
316.3
317.9
319.4
321.0
322.6
324-2
325.8
327.4
1%
332.1
333-8
335-4
337-1
338.8
340.4
342.1
343-8
I5/16
347-8
349-6
351-3
353-1
354-8
356.6
358.3
360.1
1%
363.5
365.3
367.1
369.0
370.8
372.6
374-5
376.3
I%6
379-0
380.9
382.9
384.8
386.7
388.6
390.5
392.5
iy2
394-5
396.5
398.5
400.5
402.5
404.5
406.5
408.5
0 '
410 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
271/8
2774
27%
27V2
27%
27%
27%
28
8/16
53-94
54.19
54-44
54.69
54-94
55.19
55.45
55.70
6
58.37
58.64
58.91
59-18
59-45
59.72
59.99
60.27
%2
62.86
63.15
63.44
63.74
64.03
64.32
64.61
64.90
5
63.22
63.51
63.80
64.10
64.39
64.69
64.98
65.27
4
68.34
68.66
68.98
69.30
69.61
69.93
70.25
70.57
'"ii"
71.76
72.09
72.42
72.76
73.09
73.43
73.76
74.09
3
74.32
74.66
75-01
75-35
75.70
76.04
76.39
76.74
"'%2'
80.63
8l.oi
81.38
81.76
82.14
82.51
82.89
83.26
2
81.41
8i.79
82.17
82.55
82.93
83.31
83.69
84.07]
I
85-95
86.35
86.75
87.15
87-55
87.95
88.35
88.75
"'<H6'
i\Ln
89.49
08 72
89.91
08 78
90.32
90.74
91.16
91.57
91-99
92.41
782
%
yo.«5^
107.1
yo. /o
107.6
99. 24
108.1
99- 7O
108.6
109.1
109.6
IIO. I
no. 6
7/l6
124.7
125-3
125-9
126.5
127.0
127.6
128.2
128.8
V2
142.2
142.8
143-5
144-2
144-8
145.5
146.2
146.9
%6
159-6
160.3
161.1
178 6
161.8
162.6
163.3
164.1
164.8
*&8
176.9
I94-I
177-7
195-0
196.0
179-4
196.9
197^8
198.7
199.6
200.5
%
211. 3
212.3
213-3
214.3
215-3
216.3
217.3
218.3
18/4e
228.3
229.4
230.5
231.6
232.7
233.8
234.8
235.9
%
245.3
246.5
247.6
248.8
250.0
251.2
252.3
253.5
15/ie
262.2
263.5
264.7
266.0
267.2
268.5
269.7
271.0
i
279.0
280.4
281.7
283.0
284.4
285.7
287.0
288.4
lVl6
295.7
297-2
298.6
300.0
301.4
302.8
304.3
305.7
i%
312.4
313 9
315.4
316.9
318.4
319 9
321.4
322.9
I3/16
329.0
330.5
332.1
333-7
335.3
336.9
338.5
340.1
.1%
345.4
347-1
348.8
350.4
352.1
353-8
355.4
357-1
i5/4e
361.8
363.6
365.3
367.1
368.8
370.6
372.3
374.1
i%
378.1
380.0
381.8
383.7
385.5
387.3
389-2
391-0 !
i7/i6
394.4
396.3
398.2
400.1
402.0
404.0
405.9
407.8
i%
410.5
412.5
414.5
416.5
418.5
420.5
422.5
424.5 i
i
• - ' ••'--'.-•• v
Weight in Pounds per Lineal Foot for Pipe and Tubing 411
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
28%
2814
283/8
281/2
285/8
283/4
287/8
29
3/16
55-95
56.20
56.45
56.70
56.95
57-20
57-45
57-70
6
60.54
60. 81
61.08
61.35
61.62
61.89
62.16
62.43
"'7/32'
65.20
65.49
65-78
66.07
66.37
66.66
66.95
67.24
5
65.57
65.86
66.15
66.45
66.74
67.04
67.33
67.62
4
70.89
71.20
71.52
71.84
72.16
72-47
72.79
73-11
'"ii"
74-43
74.76
75-09
75-43
75.76
76.10
76.43
76.76
3
77.08
77«43
77-77
78 12
78.46
78.81
79 16
79.50
%2
83.64
84.01
84.39
84.76
85.14
85.51
85.89
86.27
2
84.45
84.83
85.20
85.58
85.96
86.34
86.72
87.10
I
89.15
89.55
89.95
90.35
90.75
91.16
91.56
91.96
'"%«'
92.83
93.24
93-66
94.08
94-49
94-91
95-33
95-75
11/32
102.0
102.5
102.9
103-4
103.8
104.3
104-7
105.2
%
III. I
in. 6
112. 1
112. 6
113. i
113.6
114. 1
114.6
%6
129.4
130.0
130.5
131. 1
I3I.7
132.3
132.9
133-5
%
147.5
148.2
148.9
149.5
150.2
150.9
I5I-5
152.2
e/16
165.6
166.3
I67.I
167.8
168.6
169.3
I70.I
170.8
%
183.6
184.4
185.2
186.1
186.9
187.7
188.6
189.4
Hie
201.5
202.4
203.3
204.2
205.1
206.1
207.0
207.9
8/i
219-3
220.4
221.3
222.3
223.3
224.3
225.3
226.3
13/16
237-0
238.1
239-2
240.3
241.3
242.4
243-5
244.6
%
254.7
255.8
257-0
258.2
259-3
260.5
261.7
262.8
15/16
272.2
273-5
274-7
276.0
277.2
278.5
279-7
281.0
I
289.7
291-0
292.4
293-7
295.0
296.4
297.7
299.0
iVie
307.1
308.5
309.9
3H.4
312.8
314.2
315.6
317.0
iVs
324-4
325.9
327.4
328.9
330.4
331-9
333.4
334-9
I8/16
341-6
343-2
344.8
346.4
348.0
349-6
351-2
352.7
IV4
358.8
360.5
362.1
363.8
365.5
367.1
368.8
370.5
I5/16
375-8
377-6
379-4
38I.I
382.9
384-6
386.4
388.1
1%
392.8
394-7
396.5
398.3
400.2
402.0
403-8
405.7
I%8
409.7
411.6
413.6
415.5
417-4
419.3
421.2
423.2
i%
426.5
428.5
430.5
432.5
434-5
436.6
438.6
440.6
412 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
291/8
291/4
29%
29%
29%
29%
29%
3o
%6
57-95
58.20
58.45
58.70
58.95
59-20
59.45
59-70
6
62 70
62.98
63 25
63 52
63.79
64.06
64.33
64 60
%2
67^53
67.83
68.12
68.41
68.70
68.99
69.29
69^58
5
67.92
68.21
68.50
68.80
69.09
69.38
69.68
69.97
4
73-43
73-74
74 06
74.38
74-7°
75 02
75-33
75.65
a
77.10
77-43
77.76
78.10
78.43
78.77
79-10
79-43
3
79 85
80.19
80 14
80 89
81.23
81.58
81 92
82.27
9/32
86.64
87.02
w.^H
87.39
87.77
88.14
88.52
88.89
89.27
2
87.48
87.86
88.24
88.62
89.00
89.38
89.75
00.13
I
92.3^
92.76
93-1^
93.56
93.96
94.36
94-7^
95-i6
5/ie
96.16
96.58
97-00
97-41
97.83
98.25
98.67
99.08
H'82
105-7
106.1
106.6
107.0
107-5
108.0
108.4
108.9
%
II5-I
115.6
116.1
116.6
117.1
117.6
118.1
118.6
%6
134-0
134-6
135-2
135.8
136.4
137-0
137-5
138.1
%
152.9
153-5
154-2
154.9
155-5
156.2
156.9
157-5
%6
I7I.6
172.3
I73.I
173.8
174-6
175-3
176.1
176.8
%
190.2
191.1
I9L9
192.7
193.6
194-4
195-2
196.1
»%6
208.8
209.7
210.6
211. 6
212.5
213-4
214-3
215.2
%
227-3
228.3
229.3
230.3
231.3
232.3
233-3
234-3
!%e
245-7
246.8
247-9
248.9
250.0
251.1
252.2
253-3
%
264.0
265.2
266.3
267.5
268.7
269.8
271.0
272.2
15/16
282.2
283.5
284.7
286.0
287.2
288.5
289.7
291.0
I
300.4
301.7
303-0
304.4
305.7
307.1
308.4
309-7
I%8
318.4
319.9
321.3
322.7
324.1
325.5
327.0
328.4
iVs
336.4
337-9
339-4
340.9
342.4
343-9
345-4
346.9
I8/16
354-3
355-9
357.5
359-1
36o.7
362.2
363.8
365.4
1%
372.1
373-8
375-5
377-1
378.8
380.5
382.1
383.8
I5/i6
389.9
391.6
393-4
395-1
396.9
398.6
400.4
402.1
1%
407.5
409.4
411.2
413.0
414.9
416.7
418.5
420.4
iVie
425.1
427.0
428.9
430.8
432.8
434-7
436.6
438.5
i%
442.6
444-6
446.6
448.6
450.6
452.6
454-6
456.6
Weight in Pounds per Lineal Foot for Pipe and Tubing 413
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
30%
3oV4
303/8
3oy2
30%
303/4
30%
31
%e
59-95
60.20
60.45
60.70
60.95
61.20
6i.45
61.70
6
64 87
65.14
65,42
65.69
65.96
66.23
66.50
66.77
7/32
69.87
70.16
70.45
70.75
71.04
71.33
71.62
71.91
5
70.27
70.56
70.85
71.15
71.44
71-73
72.03
72.33
4
75-97
76.29
76.6o
76.92
77.24
77.56
77-88
78.19
H
79-77
80. 10
80.43
80.77
81.10
81.44
81.77
82.10
3
82.61
82.96
83.31
83.65
84.00
84.34
84.69
85.03
%2
89.64
90.02
90.40
90.77
91.15
91.52
91.90
92.27
2
90.51
90.89
91.27
91.65
92.03
92.41
92.79
93-17
I
95.56
95.96
96.36
96.76
97.16
97.56
97-96
98.36
"'%i'
99.50
99.92
100.3
100.8
IOI.2
101.6
102.0
102.4
*%»
109.3
109.8
110.3
110.7
III. 2
in. 6
112. 1
112. 5
%
119.2
119.7
I2O.2
120.7
121. 2
121. 7
122.2
122.7
7/i6
138.7
139-3
139-9
140.5
I4I.I
141.6
142.2
142.8
y2
158.2
158.9
159-5
160.2
160.9
161.5
l62.2
162.9
9/i6
177-6
178.4
I79-I
179-9
180.6
181.4
I82.I
182.9
%
196.9
197-7
198.6
199-4
200.3
2OI.I
201-9
202.8
Hie
216. i
217.1
218.0
218.9
219.8
220.7
221.7
222.6
%
235-3
236.3
237.3
238.3
239-3
240.3
241.3
242.3
18Ae
254-4
255-4
256.5
257-6
258.7
259-8
260-9
262.O
7/s
273-3
274-5
275.7
276.8
278.0
279-2
280.4
281.5
15A6
292.2
293-5
294.7
296.0
297-3
298.5
299-8
301.0
i
3H. I
312.4
313.7
3I5.I
316.4
317.7
3I9.I
320.4
Itte
329.8
331.2
332.6
334-0
335-5
336.9
338.3
339-7
i%
348.4
349-9
351-4
352.9
354-4
355-9
357-5
359-0
I8/16
367.0
368.6
370.2
371-8
373-3
374-9
376.5
378.1
IV4
385.5
387.2
388.8
390.5
392.2
393-8
395-5
397-2
i5Ae
403.9
405.6
407.4
409.1
410.9
412.6
414-4
416.2
i%
422.2
424.0
425.9
427.7
429.5
43L4
433-2
435-0
I7/16
440.4
442.4
444-3
446.2
448.1
450.0
451-9
453 9
iV2
458.6
460.6
462.6
464.6
466.6
468.6
470.6
472.6
414 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
3iVs
3IV4
31%
3iy2
31%
3I3/4
31%
32
SAQ
61.95
62.20
62.45
62.70
62.95
63.20
63.46
63.71
6
67.04
67.31
67.58
67.85
68.13
68.40
68.67
68.94
7/32
72.21
72.50
72.79
73.o8
73-37
73.67
73.96
74-25
5
72.62
72.91
73.20
73-50
73-79
74-08
74-38
74.67
4
78.51
78.83
79-15
79.46
79-78
80.10
80.42
80.74
'"ii"
82.44
82.77
83.10
83-44
83-77
84.11
84.44
84.77
3
85.38
85-73
86.07
86.42
86.76
87.11
87.45
87.80
%2
92.65
93-02
93-40
93-77
94-15
94-53
94-90
95-28
2
93-55
93-92
94-30
94-68
95.o6
95-44
95-82
96.20
I
98.76
99.17
99-57
99-97
100.4
100.8
IOI.2
101.6
5/16
102.8
103-3
103-7
104.1
104-5
104.9
105-3
105.8
H'32
113.0
II3-5
H3-9
114.4
114.8
II5-3
II5-8
116.2
%
123.2
123-7
124.2
124-7
125.2
125-7
126.2
126.7
7/ie
143-4
144-0
144-6
145- 1
145-7
146.3
146.9
147.5
%
163.5
164.2
164.9
165-5
166.2
166.9
167.5
168.2
9/16
183.6
184.4
185.1
185.9
186.6
187.4
188.1
188.9
%
203.6
204.4
205.3
206.1
206.9
207.8
208.6
209.4
Hie
223.5
224.4
225.3
226.2
227.2
228.1
229.0
229.9
%
243-3
244-3
245-3
246.3
247-3
248.3
249-3
250.3
13/10
263.0
264.1
265.2
266.3
267.4
268.5
269.5
270.6
%
282.7
283.9
285.0
286.2
287.4
288.5
289.7
290.9
15/16
302.2
303.5
304.8
306.0
307-3
308.5
309.8
311. 0
I
321-7
323-1
324.4
325.7
327-1
328.4
329-7
331. 1
1^6
341. 1
342.6
344-0
345-4
346.8
348.2
349-6
351. 1
iVs
360.5
362.0
363.5
365.0
366.5
368.0
369.5
371-0
I%0
379-7
38L3
382.9
384.4
386.0
387.6
389-2
390.8
1%
398.8
400.5
402.2
403-8
405.5
407.2
408.9
410.5
I5/16
417.9
419.7
421.4
423.2
424.9
426.7
428.4
430.2
1%
436.9
438-7
440.6
442.4
444-2
446.1
447-9
449-7
i7/i«
455.8
457-7
459-6
461.5
463.5
465.4
467.3
469.2
iy2
474-6
476.6
478.6
480.6
482.6
484.6
486.6
488.6
Weight in Pounds per Lineal Foot for Pipe and Tubing 415
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
32V8
32V4
32%
32l/2
32%
32%
327/8
33
3/16
63.96
. 64.21
64.46
64.71
64.96
65.21
65.46
65.71
6
69.21
69.48
69.75
70.02
70.29
70.56
70.84
71. II
'"%2
74.54
74.83
75-13
75.42
75-71
76.00
76.29
76.59
5
74.97
75.26
75-55
75-85
76.14
76.43
76.73
77-02
4
81.05
81.37
81.69
82.01
82.32
82.64
82.96
83.28
'"%"
85.11
85.44
85.78
86.11
86.44
86.78
87.11
87.44
3
88.15
88.49
88.84
89.18
89.53
89.88
90.22
90.57
'"%2
95.65
96.03
96.40
96.78
97-15
97-53
97.90
98.28
2
96.58
96.96
97-34
97.72
98.10
98.47
98.85
99-23
I
102.0
102.4
102.8
103.2
103.6
104.0
104-4
104.8
"'s/ie'
106.2
106.6
107.0
107.4
107.8
108.3
108.7
109.1
ma
116.7
117.1
117.6
118.1
118.5
119.0
II9.4
119.9
%
127.2
127.7
128.2
128.7
129.2
129.7
130.2
130.7
K«
148.1
148.6
149-2
149-8
150.4
151.0
I5I.6
152.2
%
168.9
169.5
170.2
170.9
171.6
172.2
172.9
173.6
%•
189.6
190.4
191.1
I9I.9
192.6
193-4
I94-I
194-9
%
210.3
211. 1
211.9
212.8
213.6
214-4
215-3
216. i
*M*
230.8
231.8
232.7
233.6
234-5
235-4
236.3
237-3
3/4
251.3
252.3
253-3
254-3
255-3
256.3
257-3
258.3
13/16
271.7
272.8
273.9
275-0
276.1
277-1
278.2
279.3
7/8
292.0
293-2
294-4
295-5
296.7
297.9
299.0
300.2
15/16
312.3
313.5
314.8
316.0
317.3
318.5
319.8
321.0
I
332.4
333-8
335-1
336.4
337-8
339-1
340.4
341.8
!Vl6
352.5
353-9
355.3
356.7
358.2
359-6
361.0
362.4
iVs
372.5
374-0
375.5
377.0
378.5
380.0
381-5
383.0
I3/16
392.4
394-0
395-5
397-1
398.7
400.3
401.9
403.5
IV4
412.2
413.9
415.5
417.2
418.9
420.5
422.2
423.9
I5/16
431.9
433-7
435-4
437.2
438.9
440.7
442-4
444.2
1%
451.6
453-4
455.2
457.1
458.9
460.7
462.6
464.4
I%6
471. 1
473-1
475.0
476.9
478.8
480.7
482.7
484.6
iya
490.6
492.6
494-6
496.6
498.6
500.6
502.6
504.6
416 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
331/8
33V4
33%
33V2
33%
33%
33%
34
8/ie
65.96
66.21
66.46
66.71
66.96
67.21
67.46
67.71
6
71 38
71.65
71.92
72. 19
72.46
72.73
73.00
73 27
7/32
76.88
77-17
77.46
77.75
78.05
78.34
78.63
'X
78.92
5
77.31
77.61
77.90
78.20
78.49
78.78
79.08
79-37
4
83.59
83.91
84.23
84.55
84.87
85.18
85 50
85.82
y*
87-78
88.11
88.45
88.78
89.11
89.45
89.78
90.11
3
90.91
91.26
91.60
91.95
92.30
92.64
92 99
93-33
%2
98.66
99-03
99.41
99.78
IOO.2
100.5
100.9
101.3
IO2 3
I
99- 01
105.2
109-5
99-99
105.6
109.9
106.0
110.3
106.4
no. 8
106.8
III. 2
107.2
in. 6
107 6
112. 0
108.0
112. 4
5/16
HS2
120.3
120-8
121. 3
121. 7
122.2
122.6
123.1
123.6
%
I3L2
131.7
132.2
132.7
133-2
133.7
134 2
134.7
Vie
152.7
153.3
153-9
154-5
155- 1
155.7
156.2
156.8
y2
174.2
174.9
175-6
176.2
176.9
177.6
178 2
178.9
9/16
195.6
196.4
197.1
197.9
198.6
199.4
200.1
200.9
%
216.9
217.8
218.6
219-4
220.3
221. 1
221.9
222.8
*%6
238.2
239.1
240.0
240.9
241.8
242.8
243-7
244.6
%
259.3
260.3
261.3
262.3
263.3
264.3
265.3
266.3
!%6
280.4
281.5
282.6
283.6
284.7
285.8
286 9
288.0
%
301.4
302.5
303.7
304.9
306.1
307.2
308.4
309.6
15/16
322.3
323.5
324.8
326.0
327.3
328.5
329.8
331.0
I
343-1
344.4
345.8
347-1
348.4
349-8
351. 1
352.4
I%6
363.8
365.3
366.7
368.1
369.5
370.9
372.3
373.8
i%
384.5
386.0
387.5
389.0
390.5
392.0
393-5
395-0
I3/16
405.1
406.6
408.2
409.8
411.4
4i3.o
414.6
416.2
*%
425.5
427.2
428.9
430.5
432.2
433-9
435.6
437-2
i5/4e
445-9
447.7
449.4
451.2
452.9
454-7
456.5
458.2
i%
466.3
468.1
469.9
471.8
473-6
475-4
477-3
479.1
I7i6
486.5
488.4
490.3
492.2
494-2
496.1
498.0
499-9
iy2
506.6
508.6
510.6
512.6
514.7
516.7
518.7
520.7
'• '
Weight in Pounds per Lineal Foot for Pipe and Tubing 417
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Continued)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
34Vs
34^4
34%
34%
34%
34%
34%
35
8/16
67.96
68.21
68.46
68.71
68.96
69.21
69.46
69.71
6
73 55
73.82
74.09
74.36
74.63
74 9O
75-17
75 44
7/32
79.21
79-51
79.8o
80.09
80.38
80.67
80.97
81^26
5
79.66
79.96
80.25
80.55
80.84
81.13
81.43
81.72
4
86.14
86.45
86.77
87.09
87.41
87.73
88.04
88.36
V4
90.45
90.78
91.12
91-45
91.78
92.12
92.45
92^78
3
93-68
94.02
94-37
94.72
95.06
95-41
95-75
96. 10
%2
101.7
102.0
102.4
102.8
103.2
103-5
103-9
104.3
2
102.6
103.0
103-4
103.8
104.2
104-5
104.9
105.3
I
108.4
108.8
109.2
109.6
IIO.O
no. 4
no. 8
III. 2
"'%i'
112.9
H3.3
II3-7
114.1
114.5
114.9
iiS-4
II5-8
*%2
124.0
124-5
124.9
125.4
125-9
126.3
126.8
127.2
%
135-2
135-7
136.2
136.7
137-2
137-7
138.2
138.7
7/16
157-4
158.0
158.6
159.2
159-7
160.3
160.9
l6l.5
%
179-6
180.2
180.9
181.6
182.2
182.9
183.6
184.2
9/i6
2OI.6
202.4
203.1
203.9
204.6
205.4
206.1
206.9
%
223.6
224.5
225.3
226.1
227.0
227.8
228.6
229.5
Hie
245.5
246.4
247-4
248.3
249.2
250.1
251.0
251-9
%
267.3
268.3
269.3
270.3
27L3
272.3
273-3
274-3
18/4e
289.1
290.2
291.2
292.3
293.4
294-5
295-6
296.7
%
310.7
3H.9
3I3.I
314.2
315.4
316.6
317.7
318.9
15/16
332.3
333-5
334-8
336.0
337-3
338.6
339-8
341. 1
I
353.8
355.1
356.5
357-8
359-1
360.5
361.8
363.1
lVl6
375-2
376.6
378.0
379-4
380.9
382.3
383.7
385.1
i%
396.5
398.0
399-5
401.0
402.5
404.0
405.5
407.0
i%«
417.7
419.3
420.9
422.5
424.1
425-7
427.2
428.8
IV4
438.9
440.6
442.2
443-9
445-6
447-2
448.9
450.6
I5A6
460.0
461.7
463.5
465.2
467.0
468,7
470.5
472.2
1%
480.9
482.8
484.6
486.4
488.3
490.1
492.0
493.8
I7/16
501.8
503.8
505.7
507.6
509.5
5II-4
513.4
515-3
1%
522.7
524.7
526.7
528.7
530.7
532.7
534-7
536.7
418 Weight in Pounds per Lineal Foot for Pipe and Tubing
Table II. — Weight in Pounds per Lineal Foot for Steel Pipe
and Tubing (Concluded)
Weight i cubic inch Steel = .2833 pound
Wall thickness
Outside diameter in inches
B.W.G.
Inches
35%
35l/4:
35%
351/2 v
35%
35%
35%
36
8/16
69.96
70.21
70.46
70.71
70.96
71.21
71-47
71.72
6
75-71
75.98
76.26
76.53
76.80
77-07
77-34
77.61
%2
Si.55
81.84
82.13
82.43
82.72
83.01
83-30
83-60
5
82.01
82.31
82.60
82.90
83.19
83-48
83.78
84.07
•4
88.68
89.00
89.31
89.63
89.95
90.27
90.58
90.90
V4
93-12
93.45
93-79
94.12
94-45
94-79
95-12
95-45
3
96.45
96.79
97.14
97.48
97-83
98.17
98.52
98.87
%2
104.7
105.0
105.4
105.8
106.2
106.5
106.9
107.3
2
105.7
in . 6
106.1
106.4
106.8
107.2
107.6
108.0
108.3
I
"5/ie'
116.2
116.6
117.0
117.4
117.9
118.3
118.7
II9.I
*%2
127.7
128.2
128.6
129.1
129.5
130.0
130.4
130.9
%
139-2
139-7
140.2
140.7
141.2
141.7
142.2
142.7
7/l6
162.1
162.7
163.2
163.8
164.4
165.0
165.6
166.2
V2
184-9
185.6
186.2
186.9
187.6
188.2
188.9
189.6
%6
207.6
208.4
209.1
209.9
210.6
211. 4
212. 1
212.9
%
230.3
231.1
232.0
232.8
233.6
234.5
235-3
236.1
'VIS
252.9
253-8
254-7
255-6
256.5
257.5
258.4
259-3
3/4
275-3
276.3
277.4
278.4
279.4
280.4
281.4
282.4
13/16
297-8
298.8
299-9
301.0
302.1
303.2
304-3
305.3
%
320.1
321.2
322.4
323.6
324.7
325.9
327.1
328.2
lr>i6
342.3
343-6
344-8
346.1
347.3
348.6
349-8
351. 1
I
364.5
365.8
367.1
368.5
369.8
371- 1
372.5
373.8
lVl6
386.5
387.9
389.4
390.8
392.2
393-6
395-0
396.5
iVs
408.5
410.0
4H.5
4i3.o
414.5
416.0
417.5
419.0
I%6
430.4
432.0
433-6
435.2
436.8
438.3
439-9
44L5
1%
452.2
453-9
455-6
457-2
458.9
460.6
462.3
463.9
I%6
474-0
475.7
477-5
479-2
481.0
482.7
484.5
486.2
1%
495-6
497-5
499-3
SOLI
503.0
504.8
506.6
508.5
lVl6
517.2
5I9.I
521.0
523.0
524.9
526.8
528.7
530.6
iy2
538.7
540.7
.542.7
544-7
546.7
548.7
550.7
552.7
Table of the Properties of Tubes and Round Bars 419
Fig. 133
Fig. 134
TABLE OF THE PROPERTIES OF TUBES AND
ROUND BARS
Plan of Table. This table was planned with a view of stating the
properties of tubes and pipe in the best form for application to practice.
The scheme is based upon the fact
that a hollow cylinder, or tube, may
always be considered as the differ-
ence of two solid cylinders. Thus
the hollow cylinder or tube, Fig.
134, may be considered as result-
ing from the removal of the smaller
cylinder, Fig. 133, from the center
of the larger cylinder, Fig. 132. Fig. 132
In order to be able to
apply this table to the solu-
tion of problems in tubular
mechanics, it will only be
necessary, in addition to
having the above funda-
mental relation clearly in
mind, to remember that
the table states the proper-
ties of a series of solid round bars, each one foot long, whose diameters
advance by .01 inch to 16 inches, and thereafter by % inch.
Calculation of Table. The table was calculated on an eight-slot
Burkhardt machine, making use of the following data:
D = diameter of a round bar in inches.
C = irD = 3.1415927 D = circumference of a cross-section in inches.
A = - D2 = 0.78539816 D2 = area of cross-section in square inches.
4
S = — = — D = 0.26179939 D = cylindrical surface hi square feet per
foot length.
V = 12 A = 3 wD2 = 9.4247780 D2 = volume in cubic inches per foot
length.
W = 0.2833 V = 3.3996 A = 2.6700396 D2 = weight of a round steel bar
in pounds per foot length.
D2
& — ~7 — 0.0625 D2 = radius of gyration of cross-section, squared.
/ = — D4 = 0.049087385 D4= - Z)2 X — = AR2 = moment of inertia of
64 4 16
cross-section.
y = | D = distance of farthest fiber from the axis of a round bar in
inches.
Weight of one cubic inch of steel = 0.2833 pound.
420 Table of the Properties of Tubes and Round Bars
The last value stated in each of the above formulae is the one actually
used in making the calculations.
The machine calculations, except for the moment of inertia, /, were
all carried out to the respective degrees of accuracy indicated by the
constants of the above formulae. Each result was then contracted to
a lesser number of significant figures for the reason explained below. The
moment of inertia, /, was obtained by multiplying the area of cross-sec-
tion, A, by the corresponding radius of gyration squared, R2, both being
taken to six significant figures.
Precision of Tabular Statement. While entering the calculated
values in this table, care was taken to have the precision of state-
ment just sufficient to meet the demands of practice. The number of
significant figures given in the different columns corresponding to any
tabular diameter is based upon the assumption that diameters are meas-
ured to the nearest one-thousandth of an inch, thus involving a possible
error of 0.0005 inch. This error in the diameter of a round bar will
give rise to corresponding errors in its volume, weight, moment of inertia,
and other properties. An investigation has shown these resulting errors
to be as follows: For C, 0.00157 inch; for A, 0.000785 D; for S, 0.000131
square inch; for V, 0.00942 D; for W, 0.00267 D; for R2, 0.0000625 Z>;
for /, 0.000098 Ds', and for y, 0.00025 inch.
Checking of Tabular Values. Each individual entry of this table
has been calculated twice, and wherever a difference was found a third
independent calculation was made to decide which of the two values in
question was in error. The second calculation was made after the table
had been traced, and all errors found were corrected directly on the
tracings. A set of blue-prints was then made, and this was finally
checked by the well-known method of differences.
APPLICATION OF TABLE TO ROUND BARS
For the properties of round bars use the different tabular
values direct. Thus for a round steel bar 6.35 inches in diameter,
turn to the table, page 436, headed / inches, and opposite 6.35,
in column D, take the required properties from the table as follows:
For circumference of cross-section, 19.949 inches; for area of cross-
section, 31.669 square inches; for cylindrical surface, 1.6624 square
feet per foot length; for volume, 380.03 cubic inches per foot length;
for weight of steel bar, 107.66 pounds per foot length; for moment of
inertia of cross-section, 79.81, from which the polar moment of inertia,
being equal to twice the moment of inertia, is 79.81 X 2, or 159.62; for
distance from axis of the bar to the most remote fiber, 3.175 inches;
and for the square of the radius of gyration of cross-section, 2.5202.
The table is applicable to diameters when stated in inches and
hundredths to 16 inches and thereafter when stated in inches and eighths.
When diameters are stated to thousandths of an inch, interpolate in
the usual way as follows: For example, to find the weight in pounds
Application of Table to Tubes and Pipe 421
per lineal foot, of a round steel bar 6.356 inches diameter, add to the
tabular weight corresponding to 6.35, six-tenths of the difference of
weights corresponding to diameters of 6.36 and 6.35; thus, difference of
these weights is 108.00— 107.66 = 0.34; and six-tenths of this difference
is 0.34 X 0.6= 0.204; which added to the weight corresponding to 6.35
diameter gives 107.66+0.204= 107.86 pounds per lineal foot as the
weight of a bar 6.356 inches in diameter. Similarly all the other prop-
erties may be obtained; thus, moment of inertia, /, = 79.81 + 0.6 (80.32 —
79.81) = 79.81 + 0.31 = 80.12.
When diameters are stated to sixteenths, thirty-seconds, or sixty-fourths,
above 16 inches interpolate similarly. Thus the weight of a round
bar i8%2 inches in diameter, since this diameter lies between iSVs
and i8V4, will be (weight for i8V8) + ( %2~Vs ) (weight for 18%-
\ i/i-Vs/
weight for iSVs) or 877.15 + 14 of (889.29 - 877.15) = 877.15 +
3.04 = 880.19 pounds per lineal foot.
To Find Diameter of Bar Corresponding to a Given Property.
This is accomplished by taking the diameter opposite the tabular prop-
erty nearest to that stated. For example, to find what diameter of round
bar will correspond to a moment of inertia of 46, look down column I
of the table until 45.91 is reached, which is the nearest tabular value,
and then read opposite, in column A 5.53 inches as the diameter required.
Similarly a round bar of 15 square inches cross-sectional area will have
a diameter of 4.37 inches, as read opposite 14.999 in column A.
APPLICATION OF TABLE TO TUBES AND PIPE
Let it be required to find the properties of a tube having outside and
inside diameters of 7.62 and 7.02 inches respectively.
It will be observed that according to the plan of this table (see page
419) the different properties of a tube may be grouped as follows:
(1) The circumference, surface, fluid capacity, and distance of the
farthest fiber from the axis are to be used direct
as taken from the table. For the above example
these will be as follows: From the table, col-
umn C, the outside circumference, opposite
7.62, is 23.939 inches; and the inside circum-
ference, opposite 7.02, is 22.054 inches; from
column S, similarly the outside and inside sur-
faces are found to be respectively 1.9949 and
1.8378 square feet per foot length of tube; from
column V, the fluid capacity will be found opposite 7.02, the inside diam-
eter, and is 464.46 cubic inches per foot length; while from column y, the
distance of the farthest fiber from the axis of the tube will be found
opposite the outside diameter, 7.62, and is 3.810 inches.
(2) The area of cross-section, volume of wall, weight, and moment of
inertia for a tube are obtained by taking the difference of the respective
422 Table of the Properties of Tubes and Round Bars
tabular values corresponding to the outside and inside diameters of the
tube. For the above example they will be as follows: From column A,
opposite 7.62, the outside diameter of the tube,
read 45.604, and opposite 7.02, the inside diam-
eter, read 38.705- The difference of these, or
45.604 — 38.705 = 6.899 square inches, is the
required sectional area of tube wall. Similarly
from column V, the volume of the tube wall is
547.24 — 464.46 = 82.78 cubic inches; from col-
umn W, the weight of tube is 155.03 - 131.58 =
23 -45 pounds per foot length; and from column/,
the moment of inertia of cross-section is 165.50 —
119.21=46.29. Note that the polar moment of
inertia, being equal to twice the moment of inertia,
will be 46.29 X 2, or 92.58.
(3) The radius of gyration, squared, for a lube
is obtained by taking the sum of the radii of gyra-
tion, squared, corresponding to the outside and in-
side diameters of the tube. For the above example,
from column R2, opposite 7.62, the outside diam-
eter of the tube, read 3.6290, and opposite 7.02,
the inside diameter, read 3.0800. The sum of
these, or 3.6290 + 3.0800=6.7090 is the square
of the require^! radius of gyration. Note that
the sum is to be taken here, and not the differ-
ence, as in the preceding case.
To Find the Diameters of Tubes Cor-
Fig. 136 responding to Given Properties. This table
may be used for the solution of a great variety
of problems of this character, of which the following is a representative
example:
When one diameter and either the sectional area, weight, or moment of
inertia are given, to find the other diameter and thickness of wall.
Remembering that a tube may be considered as the difference be-
tween two solid cylinders, it is evident that the weight, for example,
of the smaller cylinder will equal the weight of the larger cylinder minus
the weight of the tube, and that the required inside diameter of the tube
is the same as the diameter of the smaller cylinder, we proceed as follows:
For a tube that shall weigh 16 pounds per foot, for example, when the
outside diameter is six inches, we find from the table, opposite 6.00
in column D, 96.12 in column W, which is the weight of a six-inch round
steel bar in pounds per foot length. Subtracting 16.00 pounds, the given
weight of tube per foot, we get 96.12 — 16.00 = 80.12 as the weight per
foot of a round steel bar whose diameter must be the same as the required
inside diameter of the tube. From column W, the nearest tabular weight
is found to be 80. 1 8, opposite which we read, in column D, 5.48 inches
as the inside diameter required. The thickness of wall will then be one-
half the difference of the diameters, or y2 (6.00 - 5.48) = 0.26 inch.
Application of Table to Tubes and Pipe 423
When the inside diameter is given and the outside diameter required,
we must add the weight of the tube to that of the smaller cylinder;
otherwise the two solutions are identical.
In a similar manner to the above we can find the thickness of wall
corresponding to a given sectional area or moment of inertia. For exam-
ple, to find the inside diameter of a six-inch tube that shall have a moment
of inertia of 32, proceed as follows: From column /, opposite 6.00, we read
63.62, which is the moment of inertia of a solid bar six inches in diameter.
Subtracting 32, we get 63.62 - 32 = 31.62 as the moment of inertia of a
solid round bar that would just fill up the interior of the required tube.
The nearest tabular value in column / we find to be 31-67, opposite
which we read 5.04 inches as the required inside diameter of the tube.
The thickness of wall will then be M> (6.00- 5.04) = 0.48 inch.
Weight Factors for Different Materials
In the following formulae V is the tabular volume in cubic inches, and
W the tabular weight for wrought steel.
Weight of wrought iron = V X .278 = W — 2 per cent.
Weight of cast iron = V X .260 = W - 8 per cent.
Weight of wrought copper = V X .320 = W + 13 per cent.
Weight of wrought brass = V X .303 = W + 7 per cent.
Weight of wrought nickel = V X .313 = W + 10% per cent.
Weight of lead = V X .4" = W + 45 per cent.
Weight of tin = V X .267 = W - 6 per cent.
Weight of cast aluminum = V X .092 = W — 6jy2 per cent.
Weight of wrought aluminum = V X .097 = W — 66 per cent.
These multipliers are the weights of a cubic inch of the respective materi-
als. They have been compiled from various sources and may be accepted
as representing good average values for use in case more exact values are not
at hand. The percentage column was calculated from the column of mul-
tipliers here given, and is expressed to the nearest one-half per cent only.
The weight of a cubic inch of soft wrought steel used in the calculation
of the tabular weights, column W, was taken as 0.2833 pound, the value
that is commonly accepted for rolled steel. More exact average values
are 0.2831 for welded steel tubes, and 0.2834 for seamless steel tubes. It
should be noted (i) that the adopted tabular value is the average of
these two, and (2) that the three values are in substantial agreement, so
far as commercial weighing is concerned, the differences being iM? and %
pounds per ton respectively for welded and seamless tubes.
Capacity Factors for Tubes
The different capacities of a tube or pipe per lineal foot may be obtained
by applying the following formulae, where V is the tabular volume in
cubic inches:
Capacity in cubic feet = V -5- 1728 = V X .0005787
Capacity in gallons (U. S.) = V -5- 231 = V X .004329
Capacity in cubic centimeters = V X 16 .387
Capacity in liters. = V X .016387
Capacity in pounds pure water at 39.2° F = V X .03613
Capacity in pounds pure water at 62° F = V X .03609
Capacity in pounds carbonic acid for density of .62 ... = V X .02240
424 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars «06 inch
.50 inch
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
.R2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
7i
S-c
Cir-
Area
Per foot length
Moment
Distance
Radius
Jl
ence in
section
Surface
Volume
Weight,
of
to farth-
tion
" &
inches
sq. in.
sq. ft.
cu. in.
bs. steel
inertia
est fiber
squared
D
C
A
5
V
W
/
y
&
.00
.000
.000000
.0000
.00000
.00000
.0000000000
.000
.0000000
.01
.031
.000079
.0026
.00094
.00027
.0000000005
.005
.0000063
.02
.063
.00031
.0052
.0038
.00107
0000000079
.010
.000025
.03
.094
.00071
.0079
.0085
.00240
000000040
.015
.000056
.04
.126
.00126
.0105
.0151
.0043
000000126
.020
.000100
•05
.157
.00196
.0131
.0236
.0067
00000031
.025
.000156
.06
.188
.00283
.0157
.0339
.0096
.00000064
.030
.000225
.07
.220
.00385
.0183
.0462
.0131
.00000118
-035
.000306
.08
.251
.00503
.0209
.0603
.0171
.00000201
.040
.000400
.09
.283
.00636
.0236
.0763
.0216
.00000322
.045
.000506
.10
.314
.00785
.0262
.0942
.0267
.00000491
.050
.000625
.11
.346
.00950
.0288
.114
.0323
.0000072
.055
.000756
.12
.377
.01131
.0314
.136
.0384
.0000102
.060
.000900
.13
.408
.0133
.0340
.159
.0451
.OOOOI40
.065
.001056
.14
.440
.0154
.0367
.185
.0523
.0000189
.070
.001225
.15
• 471
.0177
.0393
.212
.0601
. 0000248
.075
.001406
.16
.503
.0201
.0419
.241
.0684
.0000322
.080
.00160
.17
.534
.0227
.0445
.272
.0772
.00004IO
.085
.00181
.18
.565
.0254
.0471
• 305
.0865
.0000515
.090
.00203
.19
• 597
.0284
.0497
.340
.0964
.000064O
.095
.00226
.20
.628
.0314
.0524
• 377
.1068
.0000785
.100
.00250
.21
.660
.0346
.0550
.416
.1177
.0000955
.105
.00276
.22
.691
.0380
.0576
.456
.1292
.000115
.110
.00303
.23
.723
.0415
.0602
.499
.1412
.000137
.115
,00331
.24
.754
.0452
.0628
.543
.1538
.000163
.120
.00360
.25
.785
.0491
.0654
.589
.1669
.000192
.125
.00391
.26
.817
.0531
.0681
.637
.1805
. 000224
.130
.00423
.2?
.848
.0573
.0707
.687
.1946
.000261
.135
.00456
.28
.880
.0616
.0733
.739
.2093
.000302
.140
.00490
.29
.911
.0661
.0759
.793
.2246
.000347
.145
.00526
.30
• 942
.0707
.0785
.848
.2403
.000398
.150
.00563
.31
.974
.0755
.0812
.906
.2566
.000453
.155
.00601
.32
1. 005
.0804
.0838
.965
.2734
.000515
.160
.00640
.33
1.037
.0855
.0864
1.026
.2908
.000582
.165
.00681
.34
1. 068
.0908
.0890
1.090
.3087
.000656
.170
.00723
.35
1. 100
.0962
.0916
1. 155
.3271
.000737
.175
.00766
.36
I.I3I
.1018
.0942
1. 221
.3460
.000824
.180
.00810
• 37
1.162
.1075
.0969
1.290
.3655
.000920
.185
.00856
.38
1.194
• 1134
.0995
I.36I
.386
.001024
.190
.00903
.39
1.225
.1195
.1021
1.434
.406
.001136
.195
.00951
.40
1.257
.1257
.1047
1.508
.427
.001257
.200
.01000
.41
1.288
.1320
.1073
1.584
• 449
.001387
.205
.01051
.42
I.3I9
.1385
.IIOO
1.663
.471
.001527
.210
.01103
• 43
1. 351
.1452
.1126
1.743
.494
.001678
.215
.01156
.44
1.382
.1521
.1152
1.825
• 517
. 001840
.220
.OI2IO
• 45
I.4I4
.1590
.1178
1.909
• 541
.002013
.225
.01266
.46
1-445
.1662
.1204
1.994
.565
.002198
.230
.01323
• 47
1.477
.1735
.1230
2.082
• 590
.00240
.235
.01381
.48
1.508
.1810
.1257
2.171
.615
.00261
.240
.01440
.49
1.539
.1886
.1283
2.263
.641
.00283
.245
.01501
.50
1. 571
.1963
.1309
2.356
.668
.00307
.250
.01563
Table of the Properties of Tubes and Round Bars 425
Properties of Tubes and Round Bars (Continued) »5O inch
1.00 inch
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R?, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
el
Circum-
Area
Per foot length
Moment
Distance
Radius
il
in
section
Surface
Volume
Weight,
of
to farth-
01 gyra-
tion
" a
inches
sq. in.
sq.ft.
cu. in.
Ibs. steel 1"cl"lrt
est fiber
squared
zf
C
A
5
V
W I
y
#2
-50
I-57I
.1963
.1309
2.356
.668
.00307
.250
.01563
.51
1.602
.2043
.1335
2.451
.694
.00332
• 255
.01626
.52
1-634
.2124
.1361
2.548
.722
.00359
.260
.Ol600
.53
1.665
.2206
.1388
2.647
• 750
.00387
.265
.01756
.54
1.696
.2290
.1414
2.748
• 779
.00417
.270
.01823
.55
1.728
.2376
.1440
2.851
.808
.00449
.275
.01891
.56
1-759
.2463
.1466
2.956
.837
.00483
.280
.01960
• 57
1.791
.2552
.1492
3.062
.867
.00518
.285
.02031
• 58
1.822
.2642
.1518
3.170
.898
•00555
.290
.02103
• 59
1.854
-2734
• 1545
3.281
.929
.00595
.295
.02176
.60
1.885
.2827
• 1571
3-393
.961
.00636
.300
.02250
.61
1.916
.2922
.1597
3-507
• 994
.00680
.305
.02326
.62
1.948
.3019
. 1623
3.623
.026
.00725
.310
.02403
.63
1.979
-3II7
.1649
3.741
.060
.00773
.315
.02481
.64
2. on
.3217
. . 1676
3.860
.094
.00824
.320
.02560
.65
2.042
-33i8
.1702
3.982
.128
.00876
.325
.02641
.66
2.073
• 3421
.1728
4-105
.163
.00931
• 330
.02723
.67
2.105
.3526
.1754
4.231
.199
.00989
• 335
.02806
.68
2.136
.3632
.1780
4.358
.235
.01050
• -340
.02890
.69
2.168
• 3739
.1806
4.487
.271
.01113
.345
.02976
• 70
2.199
.3848
-I833
4.618
.308
.01179
.350
.03063
• 71
2.231
.3959
.1859
4-751
• 346
.01247
.355
.03151
.72
2.262
.4072
.1885
4.886
.384
.01319
.360
.03240
• 73
2.293
.4185
.1911
5.022
.423
.01394
.365
.03331
• 74
2.325
• 4301
.1937
5.161
.462
.01472
• 370
.03423
• 75
2.356
.4418
.1963
5-301
-502
.01553
-375
.03516
.76
2.388
-4536
.1990
5-444
.542
.01638
.380
.03610
• 77
2.419
.4657
.2016
5.588
.583
.01726
.385
.03706
• 78
2.450
• 4778
.2042
5-734
.624
.01817
• 390
.03803
.79
2.482
.4902
.2068
5.882
.666
.01912
.395
.03901
.80
2.513
.5027
.2094
6.032
.709
.02011
.400
.04000
.81
2.545
.5153,
.2121
6.184
• 752
.02113
• 405
.04101
.82
2.576
.5281
.2147
6.337
• 795
.O22I9
.410
.04203
.83
2.608
• 5411
.2173
6.493
.839
.02330
• 415
.04306
.84
2.639
• 5542
.2199
6.650
.884
.02444
.420
. 04410
.85
2.670
.5675
.2225
6.809
.929
.02562
.425
.04516
.86
2.702
.5809
.2251
6.971
• 975
.02685
• 430
.04623
.87
2.733
• 5945
.2278
7-134
.021
.02812
.435
.04731
.88
2.765
.6082
.2304
7.299
.068
.02944
• 440
.04840
.89
2.796
.6221
.2330
7.465
2. 115
.O3O80
• 445
.04951
• 90
2.827
.6362
.2356
7.634
2.163
.03221
.450
.05063
• 91
2.859
.6504
.2382
7-805
2. 211
.03366
.455
.05176
• 92
2.890
.6648
.2409
7-977
2.260
.03517
.460
.05290
-93
2.922
.6793
.2435
8.151
2.309
.03672
.465
.05406
• 94
2.953
.6940
.2461
8.328
2.359
.03832
• 470
.05523
• 95
2.985
.7088
.2487
8.506
2.410
.03998
.475
.05641
.96
3.016
.7238
.2513
8.686
2.461
.04169
.480
.05760
.97
3-047
• 7390
.2539
8.868
2.512
.04346
.485
.05881
• 98
3-079
• 7543
.2566
9.052
2.564
.04528
.490
.06003
-99
3.110
.7698
.2592
9-237
2.617
.04715
.495
.06126
1. 00
3-142
.7854
.2618
9.425
2.670
.04909
.500
.06250
426 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued) J-gg ^mch
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R?, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
i
Circum-
Area
Per foot length
Moment
Distance
Radius
ii
in
section
Surface
Volume
Weight,
of
to farth-
tion
Q'S
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
tr
C
A
S
V
W
/
y
R*
.00
3.142
.7854
.2618
9-425
2.670
.04909
.500
.06250
.01
3-173
.8012
.2644
9.614
2.724
.0511
.505
.06376
.02
3.204
.8171
.2670
9.806
2.778
.0531
.510
.06503
.03
3.236
.8332
.2697
9.999
2.833
.0552
.515
.06631
.04
3.267
.8495
.2723
10.194
2.888
.0574
.520
.06760
.05
3.299
.8659
.2749
10.391
2.944
.0597
• 525
.06891
.06
3-330
.8825
.2775
10.59
3.000
.0620
• 530
.07023
.07
3.362
.8992
.2801
10.79
3-057
.0643
• 535
.07156
.08
3-393
.9161
.2827
10.99
3.H4
.0668
.540
.07290
.09
3.424
• 9331
.2854
11.20
3.172
.0693
.545
.07426
.10
3.456
.9503
.2880
11.40
3.231
.0719
.550
.07563
.11
3.487
.9677
.2906
ii. 61
3.290
.0745
• 555
.07701
.12
3-519
.9852
.2932
11.82
3-349
.0772
.560
.07840
.13
3-550
.0029
.2958
12.03
3.409
.0800
.565
.07981
.14
3.581
.0207
.2985
12.25
3-470
.0829
• 570
.08123
• IS
3.6i3
.0387
.3011
12.46
3-531
.0859
• 575
.08266
.16
3.644
.0568
.3037
12.68
3-593
.0889
.58o
.08410
.17
3.676
.0751
.3063
12.90
3.655
.0920
.585
.08556
.18
3.707
.0936
.3089
13.12
3.718
.0952
• 590
.08703
.19
3-738
.1122
.3115
13-35
3.781
.0984
• 595
.08851
.20
3-770
.1310
.3142
13-57
3.845
.1018
.600
.09000
.21
3.8oi
.1499
.3168
13.80
3.909
.1052
.605
.09151
.22
3-833
.1690
.3194
14.03
3-974
.1087
.610
.09303
.23
3-864
.1882
.3220
14.26
4.040
.1124
.615
-09456
.24
3.896
.2076
.3246
14-49
4-105
.1161
.620
.09610
.25
3.927
.2272
.3272
14-73
4.172
.1198
.625
.09766
.26
3.958
.2469
.3299
14.96
4-239
.1237
.630
.09923
.27
3-990
.2668
.3325
15.20
4.307
.1277
.635
.10081
.28
4.021
.287
• 3351
15-44
4-375
.1318
.640
. 10240
.29
4-053
.307
• 3377
15-68
4-443
.1359
.645
. 10401
• 30
4.084
• 327
• 3403
15-93
4-512
.1402
.650
. 10563
•31
4.H5
• 348
• 3430
16.17
4.582
. 1446
.655
. 10726
• 32
4-147
.368
.3456
16.42
4-652
.1490
.660
.10890
• 33
4.178
.389
.3482
16.67
4.723
.1536
.665
.11056
.34
4.210
.410
.3508
16.92
4-794
.1583
.670
.11223
• 35
4.241
• 431
• 3534
17.18
4.866
.1630
.675
.11391
.36
4-273
• 453
.3560
17-43
4-939
.1679
.680
.11560
• 37
4.304
• 474
.3587
17.69
5. on
.1729
.685
-II73I
.38
4-335
.496
.3613
17-95
5-085
.1780
.690
.11903
• 39
4.367
.517
.3639
18.21
5.159
.1832
.695
. 12076
• 40
4.398
• 539
.3665
18.47
5-233
.1886
.700
. 12250
• 41
4-430
.561
.3691
18.74
5.308
.1940
-70S
. 12426
• 42
4.461
.584
.3718
19.00
5.384
.1996
.710
.12603
.43
4-492
.606
.3744
19.27
5.46o
.2053
.715
. 12781
• 44
4-524
.629
• 3770
19.54
5-537
.2111
.720
.12960
• 45
4-555
.651
.3796
19.82
5-614
.2I7O
.725
.13141
.46
4.587
.674
.3822
20.09
5.691
.2230
• 730
. 13323
• 47
4.618
.697
.3848
20.37
5-770
.2292
.735
. I35o6
.48
4.650
.720
.3875
20.64
5-848
.2355
• 740
.13690
• 49
4.681
• 744
• 3901
20.92
5.928
.2419
• 745
.13876
• 50
4-712
.767
.3927
21.21
6.008
.2485
• 750
.14063 I
Table of the Properties of Tubes and Round Bars 427
Properties of Tubes and Round Bars (Continued) 1-gO inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
&, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
ii
Circum-
Area
Per foot length
Moment
Distance
from axis
Radius
of gyra-
.£ a
Qa
in
inches
section,
sq. in.
Surface
sq. ft.
Volume
cu. in.
Weight,
Ibs. steel
of
inertia
to farth-
est fiber
tion
squared
D
C
A
5
V
W
I
y
R*
1.50
4.712
1.767
.3927
21.21
6.008
.2485
.750
.14063
1.51
4-744
1.791
.3953
21.49
6.088
.2552
.755
. 14251
• 52
4-775
1.815
.3979
21.78
6.169
.2620
.760
• 14440
• S3
4.807
1.839
.4006
22.06
6.250
.2690
.765
• 14631
• 54
4-838
1.863
.4032
22.35
6.332
.2761
.770
. 14823
.55
4.869
1.887
.4058
22.64
6.415
.2833
.775
. 15016
.56
4.901
1.911
.4084
22.94
6.498
.2907
.780
. 15210
• 57
4-932
1.936
.4110
23.23
6.581
.2982
.785
.15406
.58
4.964
1.961
.4136
23.53
6.665
.3059
• 790
.15603
-59
4-995
1.986
.4163
23.83
6.750
.3137
.795
.15801
.60
5.027
2. Oil
.4189
24.13
6.835
.3217
.800
.1600
.61
5-058
2.036
.4215
24.43
6.921
.3298
.805
.1620
.62
5.089
2.061
.4241
24.73
7.007
.3381
.810
.1640
.63
5- 121
2.087
.4267
25.04
7.094
.3465
.815
.1661
.64
5-152
2. 112
.4294
25.35
7.181
.3551
.820
.1681
.65
5.184
2.138
• 4320
25.66
7-269
.3638
.825
.1702
.66
5-215
2.164
.4346
25.97
7.358
.3727
.830
.1722
.67
5.246
2.190
• 4372
26.28
7.446
.3818
.835
.1743
.68
5.278
2.217
.4398
26.60
7-536
• 3910
.840
.1764
.69
5.309
2.243
• 4424
26.92
7.626
.4004
.845
.1785
.70
5-341
2.270
.4451
27.24
7.7i6
.4100
.850
.1806
• 71
5-372
2.297
• 4477
27.56
7.807
.4197
.855
.1828
• 72
5.404
2.324
.4503
27.88
7.899
.4296
.860
.1849
• 73
5-435
2.351
.4529
28.21
7-991
.4397
.865
.1871
• 74
5.466
2.378
.4555
28.53
8.084
.45oo
.870
.1892
• 75
5.498
2.405
.4581
28.86
8.177
.4604
.875
.1914
• 76
5.529
2.433
.4608
29.19
8.271
.4710
.880
.1936
• 77
5.56i
2.461
.4634
29.53
8.365
.4818
.885
.1958
• 78
5-592
2.488
.4660
29.86
8.460
.4928
.890
.1980
• 79
5.623
2.516
.4686
30.20
8-555
.5039
.895
.2003
.80
5.655
2-545
• 4712
30.54
8.651
.5153
.900
.2025
.81
5.686
2.573
• 4739
30.88
8.747
.5268
.905
.2048
.82
5.7i8
2.602
.4765
31-22
8.844
.5386
.910
.2070
.83
5-749
2.630
• 4791
3L56
8.942
.5505
• 915
.2093
.84
5.78i
2.659
.4817
3L9I
9.040
.5627
.920
.2116
.85
5.812
2.688
.4843
32.26
9.138
.5750
• 925
.2139
.86
5.843
2.717
.4869
32.61
9-237
.5875
• 930
.2162
.87
5.875
2.746
.4896
32.96
9-337
.6003
• 935
.2186
.88
5.9o6
2.776
.4922
33-31
9-437
.6132
• 940
.2209
.89
5.938
2.806
.4948
33.67
9.538
.6263
.945
.2233
.90
5.969
2.835
.4974
34-02
9.639
.6397
.950
.2256
• 91
6.000
2.865
.5000
34-38
9-741
.6533
.955
.2280
• 92
6.032
2.895
.5027
34-74
9.843
.6671
.960
.2304
• 93
6.063
2.926
.5053
35-11
9.946
.6811
.965
.2328
• 94
6.095
2.956
-5079
35-47
10.049
.6953
• 970
.2352
.95
6.126
2.986
.5105
35.84
10.153
.7098
.975
-2377
.96
6.158
3.017
.5131
36.21
10.257
.7244
.980
.2401
• 97
6.189
3.048
.5157
36.58
10.362
.7393
.985
.2426
.98
6.220
3-079
.5184
36.95
10.468
.7544
• 990
.2450
• 99
6.252
3. no
.5210
37-32
10.574
.7698
• 995
.2475
2.00
6.283
3.142
.5236
37-70
10.680
.7854
I. COO
.2500
428 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued) g 00 inches
4.50 inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use ail tabular values direct.
1
Circum-
Area
Per foot length
Moment
Distance
Radius
5 o
.2 3
ference
in
inches
cross
section
sq. in.
Surface
sq. ft.
Volume
cu. in.
Weight,
Ibs. steel
of
inertia
to farth-
est fiber
ot gyra-
tion
squared
zT
C
A
S
V
W
I
y
R*
2.0O
6.283
3.142
.5236
37-70
10.680
.7854
.000
.2500
2.01
6.315
3-173
.5262
38.08
10.787
.8012
.005
.2525
2. 02
6.346
3.205
.5288
38.46
10.895
-8173
.010
.2550
2.03
6.377
3-237
.5315
38.84
11.003
.8336
.015
.2576
2.04
6.409
3.269
.5341
39-22
II. 112
-8501
.020
.2601
2.05
6.440
3-301
.5367
39.61
II. 221
.8669
.025
.2627
2.06
6.472
3-333
-5393
39.99
11.331
.8840
.030
.26=52
2.07
6.503
3.365
.5419
40.38
11.441
-9013
.035
.2678
2.08
6.535
3.398
.5445
40.78
11-552
.9188
.040
.2704
2.09
6.566
3-431
-5472
41.17
11.663
-9366
.045
.2730
2.IO
6.597
3.464
.5498
41.56
11-775
-9547
.050
.2756
2. II
6.629
3-497
.5524
41.96
11.887
-9730
.055
-2783
2.12
6.660
3-530
• 5550
42.36
I2.OOO
-9915
.060
.2809
2.13
6.692
3.563
.5576
42.76
12.114
1.0104
.065
.2836
2.14
6.723
3-597
.5603
43.16
12 . 228
.0295
.070
.2862
2. IS
6.754
3.631
.5629
43-57
12.342
.0489
.075
.2889
2.16
6.786
3.664
.5655
43-97
12.457
.0685
.080
.2916
2.17
6.817
3.698
.5681
44.38
12.573
.088
.085
.2943
2.18
6.849
3-733
.5707
44-79
12.689
.109
.090
.2970
2.19
6.880
3.767
.5733
45-20
12.806
.129
.095
.2998
2.20
6.912
3-801
.576o
45-62
12.923
.150
.100
-3025
2.21
6.943
3-836
-5786
46.03
13.041
.171
-105
.3053
2.22
6.974
3-871
.5812
46.45
13.159
.192
.110
.3080
2.23
7.006
3.906
.5838
46.87
13-278
.214
.115
.3108
2.24
7-037
3-941
-5864
47-29
13-397
.236
.120
.3136
2.25
7.069
3.976
.5890
47-71
13.517
.258
-125
.3164
2.26
7.100
4.011
-5917
48.14
13.637
.281
.130
.3192
2.27
7.I3I
4.047
.5943
48.56
13.758
-303
-135
-3221
2.28
7.163
4-083
.5969
48.99
13.880
-327
.140
-3249
2.2Q
7-194
4-II9
.5995
49-42
14.002
-350
.145
.3278
2.30
7.226
4-155
.6021
49-86
14.125
-374
.150
.3306
2.31
7-257
4.I9I
.6048
50.29
14.248
-398
.155
• 3335
2.32
7.288
4.227
.6074
50.73
14.371
.422
.160
.3364
2.33
7-320
4.264
.6100
5LI7
14-495
• 447
.165
.3393
2.34
7-351
4-301
.6126
5i.6i
14.620
• 472
.170
.3422
2.35
7.383
4-337
.6152
52.05
14-745
-497
.175
.3452
2.36
7.414
4-374
.6178
52.49
14.871
.523
.180
.3481
2.37
7.446
4.412
.6205
52.94
14-997
.549
.185
• 3511
2.38
7-477
4-449
.6231
53-39
15.124
-575
.190
.3540
2.39
7.508
4.486
.6257
53.84
15-252
.602
.195
.3570
2.40
7-540
4.524
.6283
54-29
15-379
.629
.200
.3600
2.41
7.S7I
4.562
.6309
54-74
15.508
.656
.205
.3630
2.42
7.603
4.600
.6336
55-20
15.637
.684
.210
.3660
2.43
7.634
4-638
.6362
55-65
15.766
.712
.215
.3691
2.44
7.665
4-676
.6388
56.11
15.896
-740
.220
.3721
2.45
7.697
4-714
.6414
56.57
16.027
.769
.225
• 3752
2.46
7.728
4-753
.6440
57-03
16.158
.798
.230
.3782
2.47
7.760
4.792
.6466
57-50
16.290
.827
-235
.3813
2.48
7-791
4-831
.6493
57-97
16.422
.857
.240
.3844
2.49
7.823
4.870
.6519
58.43
16.555
.887
.245
.3875
2.50
7-854
4-909
.6545
58.90
16.688
.917
.250
.3906
Table of the Properties of Tubes and Round Bars 429
Properties of Tubes and Round Bars (Continued) 3.50 inches
•3.OO inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
H
Circum-
Area
Per foot length
Moment
Distance
Radius
.$ «
in
section
Surface
Volume
Weight,
of
to farth-
tion
Q'«
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
if
C
A
5
V
W
/
y
R*
2.50
7-854
4.909
.6545
58.90
16.688
1.917
.250
.3906
2.51
7.885
4.948
.6571
59.38
16.822
1.948
.255
• 3938
2.52
7.917
4-988
.6597
59-85
16 . 956
1.980
.260
.3969
2.53
7.948
5.027
.6624
60.33
17.091
2. Oil
.265
.4001
2.54
7.980
5.067
.6650
60.80
17.226
2.043
.270
.4032
2-55
8. on
5.107
.6676
61.28
17.362
2.076
.275
.4064
2.56
8.042
5-147
.6702
6i.77
17.498
2.108
.280
.4096
2.57
8.074
5.187
.6728
62.25
17.635
2.141
.285
.4128
2.58
8.105
5.228
.6754
62.74
7-773
2.175
.290
.4160
2.59
8.137
5.269
.6781
63.22
7.911
2.209
.295
.4193
2.6o
8.168
5.309
.6807
63.71
8.049
2.243
.300
.4225
2.61
8.200
5-350
.6833
64.20
8.189
2.278
.305
.4258
2.62
8.231
5-391
.6859
64.70
8.328
2.313
.310
.4290
2.63
8.262
5-433
.6885
65-19
18.468
2.349
.315
• 4323
2.64
8.294
5-474
.6912
65-69
18.609
2.384
.320
.4356
2.65
8.325
5.515
.6938
66.19
18.750
2.421
.325
.4389
2.66
8.357
5-557
.6964
66.69
18.892
2.458
.330
.4422
2.67
8.388
5-599
.6990
67.19
19.034
2.495
• 335
.4456
2.68
8.419
5.641
.7016
67.69
19.177
2.532
• 340
.4489
2.69
8.451
5.683
.7042
68.20
19.321
2.570
.345
.4523
2.70
8.482
5.726
.7069
68.71
19.465
2.609
• 350
.4556
2.71
8.514
5-768
.7095
69.22
19.609
2.648
.355
• 4590
2.72
8.545
5-8ii
.7121
69.73
19-754
2.687
.360
.4624
2.73
8.577
5.853
.7147
70.24
19.900
2.727
.365
.4658
2.74
8.608
5.896
.7173
70.76
20.046
2.767
• 370
.4692
2.75
8.639
5-940
.7199
71.27
20.192
2.807
.375
.4727
2.76
8.671
5.983
.7226
71.79
20.339
2.848
.380
.476i
2.77
8.702
6.026
.7252
72.32
20.487
2.890
.385
.4796
2.78
8.734
6.070
.7278
72.84
20.635
2.932
• 390
.4830
2.79
8.765
6.114
.7304
73.36
20.784
2.974
.395
.4865
2.80
8.796
6.158
.7330
73-89
20.933
3-017
.400
.4900
2.81
8.828
6.202
.7357
74-42
21.083
3.061
.405
.4935
2.82
8.859
6.246
.7383
74-95
21.233
3-104
.410
.4970
2.83
8.891.
6.29O
.7409
' 75.48
21.384
3-149
.415
.5006
2.84
8.922
6.335
.7435
76.02
21 . 535
3-193
.420
.5041
2.85
8.954
6.379
.7461
76.55
21.687
3-239
.425
.5077
2.86
8.985
6.424
.7487
77.09
21 . 840
3.284
.430
.5112
2.87
9.016
6.469
.7514
77.63
21.993
3-330
.435
.5148
2.88
9.048
6.514
• 7540
78.17
22.146
3-377
.440
-5184
2.89
9.079
6.560
.7566
78.72
22.300
3.424
• 445
.5220
2.90
9. in
6.605
• 7592
79.26
22.455
3-472
• 450
.5256
2.91
9.142
6.651
.7618
79.8i
22.610
3-520
.455
.5293
2.92
9-173
6.697
.7645
80.36
22.766
3.569
.460
.5329
2.93
9.205
6.743
.7671
80.91
22.922
3.6i8
.465
.5366
2.94
9.236
6.789
.7697
81.46
23.079
3.667
.470
.5402
2.95
9.268
6.835
.7723
82.02
23.236
3.718
.475
• 5439
2.96
9.299
6.881
.7749
82.58
23-394
3.768
.480
.5476
2.97
9-331
6.928
.7775
83.14
23.552
3.819
.485
• 5513
2.98
9.362
6.975
.7802
83.70
23.711
3.871
.490
.5550
2.99
9-393
7.022
.7828
84.26
23.870
3.923
• 495
.5588
3.oo
9.425
7.069
.7854
84.82
24.030
3.976
.500
.5625
430 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued) 3.00 inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R?, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
Diam.
in inches
Circum-
ference
in
inches
Area
cross
section
sq. in.
Per foot length
Moment
of
inertia
Distance
from axis
to farth-
est fiber
Radius
of gyra-
tion
squared
Surface
sq. ft.
Volume
cu. in.
Weight,
Ibs. steel
D
C
A
5
V
W
7
y
R*
3-00
9-425
7.069
.7854
84.82
24.030
3.976
.500
.5625
3.01
9.456
7.116
.7880
85.39
24.191
4.029
• 505
.5663
3-02
9.488
7.163
.7906
85.96
24.352
4.083
.510
• 5700
3-03
9-519
7. 211
• 7933
86.53
24.513
4.138
• 515
.5738
3-04
9-550
7.258
.7959
87.10
24 . 675
4.192
.520
.5776
3-05
9-582
7.306
.7985
87.67
24.838
4.248
.525
.5814
3-06
9.613
7-354
.Son
88.25
25.001
4.304
• 530
.5852
3-07
9.645
7-402
.8037
88.83
25.165
4.360
.535
.5891
3.08
9.676
7-451
.8063
89.41
25.329
4.417
• 540
.5929
3-09
9.7o8
7-499
.8090
89.99
25-494
4-475
.545
.5968
3.io
9-739
7.548
.8116
90.57
25.659
4-533 -550
.6006
3. II
9-770
7.596
.8142
91.16
25.825
4.592
.555
.6045
3-12
9.802
7.645
.8168
91-74
25.991
4.651
.560
.6084
3-13
9.833
7.694
.8194
92.33
26.158
4-7II
.565
.6123
3-14
9.865
7-744
.8221
92.92
26.326
4.772
• 570
.6162
3-15
9.896
7-793
.8247
93-52
26.493
4.833
• 575
.6202
3-l6
9.927
7.843
.8273
94.ii
26.662
4.895
.580
.6241
3-17
9-959
7.892
.8299
94-71
26.831
4-957
.585
.6281
3-18
9-990
7-942
.8325
95-31
27.001
5-020
.590
.6320
3-19
10.022
7-992
.8351
95-91
27.171
5.083
• 595
.6360
3-20
10.053
8.042
.8378
96.51
27.341
5.147
.600
.6400
3-21
10.085
8.093
.8404
97-11
27.512
5.212
.605
.6440
3-22
10.116
8.143
.8430
97.72
27.684
5-277
.610
.6480
3 23
10.147
8.194
.8456
98.33
27.856
5-343
.615
.6521
3.24
10.179
8.245
.8482
98.94
28.029
5.409
.620
.6561
3.25
10.210
8.296
.8508
99-55
28 . 202
5-477
.625
.6602
3.26
10.242
8.347
.8535
100.16
28.376
5-544
.630
.6642
3.27
10.273
8.398
.8561
100.78
28.550
5.613
.635
.6683
3.28
10.304
8.450
.8587
101 . 40
28.725
5.682
.640
.6724
3.29
10.336
8.501
.8613
102.01
28.901
5-751
.645
.6765
3-30
10.367
8.553
.8639
102 . 64
29.077
5.821
.650
.6806
3-31
10.399
8.605
.8666
103.26
29.253
5.892
.655
.6848
3.32
10.430
8.657
.8692
103.88
29.430
5.964
.660
.6889
3-33
10.462
8.709
.8718
104.51
29.608
6.036
.665
.6931
3-34
10.493
8.762
.8744
105.14
29.786
6.109
.670
.6972
3-35
10.524
8.814
.8770
105 . 77
29.965
6.182
.675
.7014
3.36
10.556
8.867
.8796
106.40
30.144
6.256
.680
.7056
3.37
10.587
8.920
.8823
107.04
30.323
6.331
.685
.7098
3.38
10.619
8.973
.8849
107.67
30.504
6.407
.690
.7140
3-39
10.650
9.026
.8875
108.31
30.684
6.483
.695
.7183
3-40
10.681
9-079
.8901
108.95
30.866
6.560
.700
.7225
3.41
10.713
9.133
.8927
109-59
31.047
6.637
.705
.7268
3-42
10.744
9.186
.8954
110.24
31.230
6.715
.710
.73io
3-43
10.776
9.240
.8980
110.88
3L4I3
6.794
•715
• 7353
3.44
10.807
9-294
.9006
in. 53
31.596
6.874
.720
.7396
3.45
10.838
9.348
.9032
112.18
31.780
6-954
• 725
.7439
3.46
10.870
9.402
.9058
112.83
31.965
7-035
• 730
.7482
3.47
10.901
9-457
.9084
H3.48
32.150
7.H7
.735
.7526
3-48
10.933
9-5II
.9111
114.14
32.335
7.199
• 740
.7569
3.49
10.964
9-566
• 9137
H4.79
32.521
7.282
.745
.7613
3-50
10.996
9.621
.9163
115-45
32.708
7.366
• 750
.7656
Table of the Properties of Tubes and Round Bars 431
Properties of Tubes and Round Bars (Continued) 3.50 inches
4.00 inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular va ues direct.
[g *
Circum
Area
cross
Per foot length
Moment
Distance
from axis
Radius
.1"|
in
inches
section
sq. in.
Surface
sq. ft.
Volume
cu. in.
Weight,
Ibs. stee
of
inertia
to farth-
est fiber
tion
squared
if
C
A
5
V
W
7
y
R2
3.50
10.996
9.621
.9163
115-45
32.708
7-366
1-750
.7656
3.51
11.027
9.676
.9189
116.11
32.895
7.451
1.755
.7700
3.52
11.058
9-731
.9215
116.78
33.083
7.536
1.760
• 7744
3-53
11.090
9.787
.9242
117.44
33.271
7.622
1.765
.7788
3-54
II. 121
9.842
.9268
Ii8.ii
33.46o
7.709
1.770
.7832
3-55
II. 153
9.898
.9294
118.78
33.649
7.796
1-775
.7877
3-56
11.184
9 954
.9320
119-45
33-839
7-884
1.780
• 7921
3-57
11.215
IO.OIO
.9346
120.12
34-029
7-973
1.785
.7966
3.58
11.247
10.066
• 9372
120.79
34-220
8.063
1-790
.8010
3-59
11.278
10.122
• 9399
121.47
34.412
8.154
1-795
.8055
3.6o
11.310
10.179
.9425
122.15
34.604
8.245
1.800
.8100
3-6i
11.341
10.235
• 9451
122.82
34.796
8.337
1.805
.8145
3-62
H-373
10.292
• 9477
123.51
34.989
8.430
1.810
.8190
3-63
11.404
10.349
• 9503
124.19
35.183
8.523 1.815
.8236
3.64
11-435
10.406
.9529
124.87
35.377
8.617
1.820
.8281
3.65
11.467
10.463
.9556
125.56
35.572
8.712
1.825
.8327
3-66
11.498
10.521
-9582
126.25
35.767
8.808
1.830
.8372
3.67
11-530
10.578
.9608
126.94
35.962
8.905
1.835
.8418
3-68
11.561
10.636
.9634
127.63
36.159
9.002
1.840
.8464
3.69
II-592
10.694
.9660
128.33
36.356
9.101
1.845
.8510
3-70
11.624
10.752
.9687
129.03
36.553
9.200
1.850
.8556
3-71
11.655
10.810
• 9713
129.72
36.751
9-300
1.855
.8603
3-72
11.687
10.869
9739
130.42
36.949
9.400
1. 860
.8649
3-73
11.718
10.927
.9765
131.13
37.148
9-502
1.865
.8696
3-74
11.750
10.986
.9791
131.83
37.347
9.604
1.870
.8742
3-75
11.781
11.045
.9817
132.54
37-55
9.707
1.875
.8789
3.76
11.812
11.104
.9844
133.24
37-75
9.811
I.88o
.8836
3 77
11.844
11.163
.9870
133.95
37-95
9.916
1.885
.8883
3.78
11.875
11.222
.9896
134.66
38.15
O.O22
1.890
.8930
3-79
11.907
11.282
.9922
135.38
38.35
0.128
1.895
.8978
3-80
n.938
11.341
.9948
136.09
38.56
0.235
1.900
.9025
3.8i
11.969
II.4OI
• 9975
136.81
38.76
0.344
1.905
.9073
3-82
12.001
II.46I
.0001
137.53
38.96
0.453
1.910
.9120
3-83
12.032
11.521
.0027
138.25
39.17
0.562
I.9I5
.9168
3-84
12.064
II.58I
• 0053
138.97
39-37
0.673
1.920
.9216
3.85
12.095
11.642
.0079
139.70
39.58
0.785
1.925
.9264
3.86
12.127
11.702
.0105
140.43
39.78
0.897
1.930
• 9312
3-87
12.158
11.763
.0132
141.15
39-99
I. Oil
1-935
.9361
3.88
12.189
11.824
.0158
141 . 88
40.20
1.125
1.940
• 9409
3.89
12.221
11.885
.0184
142 . 62
40.40
1.240
1-945
.9458
3-90
12.252
11.946
.0210
143.35
40.61
1.356
1-950
.9506
3-91
12.284
12.007
.0236
144.09
40.82
1-473
1.955
.9555
3-92
12.315
12.069
.0263
144.82
41.03
I.59I
1.960
.9604
3-93
12.346
12.130
.0289
145.56
41.24
1.710
1.965
.9653
3-94
12.378
12.192
.0315
146.31
41-45
1.829
1.970
.9702
3-95
12.409
12.254
.0341
147.05
41.66
1.950
1.975
• 9752
3.96
12.441
12.316
.0367
147.80
41.87
2.071
1.980
.9801
3-97
12.472
12.379
• 0393
148.54
42.08
2.194
1.985
.9851
3.98
12.504
12.441
.0420
149.29
42.29
12.317
1.990
.9900
3-99
12.535
12.504
.0446
150.04
42.51
12.441
1-995
• 9950
4.00
12.566
12.566
.0472
150.80
42.72
12.566
2.000
I.OOOO
432 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued) |-0g inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R?, and direct tabular values for C, S, y and V (for capacity) . For Round
Bars use all tabular values direct.
. w
S.S
Circum-
Area
Per foot length
Moment
Distance
Radius
rt o
/•> ^
in
section
Surface
Volume
Weight,
of
to farth-
tion
" 3
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
D
C
A
5
V
W
I
y
R*
4.00
12.566
12.566
.0472
150.80
42.72
12.566
2 OOO
I.OOOO
4.01
12.598
12 . 629
.0498
151.55
42.93
12.693
2.005
1.0050
4.02
12.629.
12.692
.0524
152.31
43-15
12.820
2.010
I.OIOO
4.03
12.661
12.756
.0551
153.07
43.36
12.948
2.015
1.0151
4.04
12.692
12.819
• 0577
153.83
43.58
13.077
2. 020
I.02OI
4-05
12.723
12.882
.0603
154-59
43-So
13.207
2.025
1.0252
4.06
12.755
12.946
.0629
155-35
44.01
13.338
2.030
1.0302
4.07
12.786
I3.OIO
.0655
156.12
44-23
13.469
2.035
1.0353
4.08
12.818
13.074
.0681
156.89
44-45
13.602
2.040
1.0404
4.09
12.849
13.138
.0708
157-66
44-66
13.736
2.045
1.0455
4.10
12.881
13.203
.0734
158.43
44-88
13.871
2.050
1.0506
4. ii
12.912
13.267
.0760
159.20
45.10
14.007
2.055
1.0558
4.12
12.943
13.332
.0786
159.98
45-32
14.144
2.060
1.0609
4-13
12.975
13.396
.0812
160.76
45-54
14.281
2.065
I. 0661
4.14
13.006
I3.46I
.0838
161.54
45.76
14.420
2.070
1.0712
4-15
13.038
13.527
.0865
162.32
45.98
14.560
2.075
1.0764
4.16
13.069
13.592
.0891
163.10
46.21
14.701
2.080
i. 0816
4.1?
13.100
13.657
.0917
163.89
46.43
14.843
2.085
1.0868
4.18
13.132
13.723
• 0943
164.67
46.65
14.986
2.090
i . 0920
4.19
13.163
13.789
.0969
165 . 46
46.88
15.130
2.095
I.Q973
4.20
13.195
13.854
.0996
166.25
47-10
15.274
2.IOO
I . 1025
4.21
13 . 226
13.920
.1022
167.05
47-32
15.421
2.105
I . 1078
4.22
13.258
13.987
.1048
167.84
47-55
15.568
2. IIO
1.1130
4.23
13.289
14.053
.1074
168.64
47-77
15.716
2. 115
.1.1183
4.24
13.320
I4.I2O
.1100
169.43
48.00
15.865
2.I2O
1.1236
4-25
13.352
14.186
.1126
170.24
48.23
16.015
2.125
I . 1289
4.26
13.383
14.253
.1153
171.04
48.45
16.166
2.130
I • 1342
4.27
13.415
14.320
.1179
171.84
48.68
16.319
2.135
I • 1396
4.28
13.446
14.387
.1205
172.65
48.91
16.472
2.I4O
i . 1449
4.29
13-477
14-455
.1231
173-45
49-14
16.626
2.145
I . 1503
4-30
13.509
14-522
.1257
174.26
49-37
16.782
2.150
i - 1556
4-31
13.540
14.590
.1284
I75.o8
49-60
16.939
2.155
i . 1610
4-32
13.572
14.657
.1310
175.89
49.83
17.096
2.l6o
1.1664
4-33
13.603
14.725
.1336
176.70
50.06
17.255
2.165
1.1718
4-34
13.635
14-793
.1362
177.52
50.29
17.415
2.170
i . 1772
4-35
13.666
14.862
.1388
178.34
50.52
17.576
2.175
1.1827
4.36
13.697
14.930
.1414
179.16
50.76
17.738
2. .180
1.1881
4-37
13.729
14.999
.1441
179.98
50.99
17.902
2 . 185
i . 1936
4.38
13.760
15.067
.1467
180.81
51.22
18.066
2.190
1.1990
4-39
13.792
15.136
• 1493
181.64
51.46
18.232
2.195
1.2045
4-40
13.823
15.205
.1519
182 . 46
51.69
18.398
2. 2OO
I.2IOO
4.41
13.854
15-275
.1545
183.29
51-93
18.566
2.205
I. 2155
4-42
13.886
15 - 344
.1572
184.13
52.16
18.735
2.210
I . 2210
4-43
13.917
15.413
.1598
184.96
52.40
18.905
2.215
I . 2266
4-44
13-949
15.483
.1624
185.80
52.64
19.077
2.220
I . 2321
4-45
13.980
15-553
.1650
186.63
52.87
19-249
2.225
1.2377
4.46
14.012
15.623
.1676
187.47
53.11
19.423
2.230
1.2432
4-47
14.043
15.693
.1702
188.32
53-35
19.598
2.235
1.2488
4.48
14.074
15.763
.1729
189.16
53-59
19-773
2.240
1.2544
4-49
14 . 106
15.834
.1755
190.00
53-83
I9.95I
2.245
1.2600
4-So
14.137
15.904
.1781
190.85
54-07
20.129
2.250
I . 2656
Table of the Properties of Tubes and Round Bars 433
Properties of Tubes and Round Bars (Continued) 4. 5O inches
5.00 inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
K*, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
el
Circum
Area
Per foot length
Moment
Distance
from axis
Radius
a!
in
inches
section
sq. in.
Surface
sq. ft.
Volume
cu. in.
Weight,
Ibs. steel
of
inertia
to farth-
est fiber
of gyra-
tion
squared
D
C
A
5
V
W
I
y
R*
4-50
14.137
15.904
.1781
190.85
54-07
20.129
2 . 25O . 2656
4-51
14.169
15-975
.1807
191 . 70
54-31
20.309
2.255
• 2713
4-52
14.200
16.046
.1833
192.55
54-55
20.489
2.260
.2769
4-53
14.231
16.117
.1860
193.40
54-79
20.671
2.265
.2826
4-54
14.263
16.188
.1886
194 . 26
55-03
20.854
2.270
.2882
4-55
14.294
16.260
.1912
195.12
55-28
2 .039
2.275
• 2939
4.56
14.326
16.331
.1938
195.98
55-52
2 .224
2.280
.2996
4-57
14-357
16.403
.1964
196.84
55.76
2 .411
2.285
• 3053
4-58
14-388
16.475
.1990
197 - 70
56.01
2 .599
2.29O
.3110
4-59
14.420
16.547
.2017
198.56
56.25
2 .788
2.295
.3168
4.60
I4-45I
16.619
.2043
199 • 43
56.50
2 .979
2.300
.3225
4.61
14.483
16.691
.2069
200 . 30
56.74
22.171
2.305
.3283
4.62
14.514
16.764
.2095
201 . 17
56.99
22.364
2.310
• 3340
4.63
14.546
16.837
.2121
202.04
57-24
22.558
2.315
-3398
4.64
14-577
16.909
.2147
202 . 91
57-48
22.753
2.320
.3456
4.65
14.608
16.982
.2174
203-79
57-73
22.950
2.325
.3514
4.66
14.640
17.055
.2200
204 . 66
57.98
23.148
2.330
• 3572
4-67
14.671
17.129
.2226
205.54
58.23
23-35
2.335
.3631
4.68
14.703
17.202
.2252
206.43
58.48
23-55
2.340
.3689
4.69
14-734
17.276
.2273
207.31
58.73
23-75
2.345
.3748
4.70
14.765
17-349
.2305
208.19
58.98
23-95
2.350
.3806
4-71
14-797
17.423
.2331
209.08
59-23
24.16
2.355
.3865
4-72
14.828
17-497
.2357
209.97
59-48
24.36
2.360
.3924
4-73
14.860
17.572
-2383
210.86
59-74
24-57
2.365
.3983
4-74
14.891
17.646
.2409
2H.75
59-99
24.78
2.370
.4042
4-75
14.923
17.721
• 2435
212.65
60.24
24.99
2.375
.4102
4.76
14-954
17-795
.2462
213.54
60.50
25.20
2.380
.4161
4 77
14.985
17.870
.2488
214.44
60.75
25.41
2.385
.4221
4-78
15.017
17-945
.2514
215-34
61.01
25.63
2.390
.4280
4-79
15.048
18.020
.2540
216.24
61.26
25-84
2.395
• 4340
4.80
15.080
18.096
.2566
217.15
61.52
26.06
2.400
.4400
4.81
15.111
18.171
.2593
218.05
6i.77
26.28
2.405
.4460
4.82
15.142
18.247
.2619
218.96
62.03
26.49
2.410
• 4520
4-83
15.174
18.322
.2645
219.87
62.29
26.72
2.415
.4581
4.84
15.205
18.398
.2671
220 . 78
62.55
26.94
2.420
.4641
4-85
15.237
18.475
.2697
221 . 69
62.81
27.16
2.425
• 4702
4.86
15.268
I8.55I
.2723
222.61
63.07
27-39
2.430
.4762
4.87
15.300
18.627
.2750
223-53
63.33
27.61
2.435
-4823
4.88
I5.33I
18.704
.2776
224-45
63.59
27.84
2.440
.4884
4.89
15.362
18.781
.2802
225-37
63.85
28.07
2.445
.4945
4-90
15-394
18.857
.2828
226.29
64.11
28.30
2.450
.5006
4-91
15.425
18.934
.2854
227.21
64.37
28.53
2.455
.5068
4-92
15-457
19.012
.2881
228 . 14
64-63
28.76
2.460
.5129
4-93
15.488
19.089
.2907
229.07
64.90
29.00
2.465
.5191
4-94
15.519
19.167
.2933
23O.OO
65-16
29.23
2.470
.5252
4-95
I5.55I
19 . 244
.2959
230.93
65.42
29-47
2.475
.5314
4.96
15.582
19.322
.2985
231.86
65.69
29-71
2.480
.5376
4-97
15.614
19.400
.3011
232.80
65-95
29-95
2.485
• 5438
4.98
15.645
19.478
.3038
233-74
66.22
30.19
2.490
.5500
4-99
15.677
19.556
.3064
234-68
66.48
30.43
2.495 .5563
S.oo
15.708
19.635
3090
235.62
66.75
30.68
2.500 .5625
434 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued) 5-00 inches
5. 5O inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R?, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
a!
Circum-
Area
cross
Per foot length
Moment
Distance
Radius
•2 «
in
section
Surface
Volume
Weight,
of
to farth-
oi gyra-
tion
Q'S
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est'fiber
squared
D
C
A
5
V
W
I
y
&
S.oo
15.708
19.635
1.3090
235.62
66.75
30.68
2.500
1.5625
5. oi
15-739
19.714
1.3116
236.56
67.02
30.93
2.505
1.5688
5.02
I5.77I
19.792
.3142
237.51
67.29
3I.I7
2.510
1-5750
5-03
15.802
19.871
.3169
238.46
67.55
31.42
2.515
1.5813
5-04
15.834
19.950
.3195
239.40
67.82
31.67
2.520
1.5876
5-05
15.865
20.030
.3221
240.36
68.09
31-93
2.525
1-5939
S.o6
15.896
20.109
.3247
241.31
68.36
32.18
2.530
1.6002
5-07
15.928
20.189
.3273
242.26
68.63
32.43
2.535
1. 6066
5.o8
15-959
20.268
.3299
243.22
68.90
32.69
2.540
1.6129
S.op
I5.99I
20.348
.3326
244.18
69.18
32.95
2.545
1.6193
S.io
16.022
20.428
• 3352
245.14
69.45
33-21
2.550
I . 6256
5- ii
16.054
20.508
• 3378
246.10
69.72
33-47
2.555
I . 6320
5-12
16.085
20.589
.3404
247.06
69.99
33-73
2.560
1.6384
5-13
16.116
20.669
• 3430
248.03
70.27
34-00
2.565
1.6448
5-14
16.148
20.750
.3456
249.00
70.54
34.26
2.570
1.6512
5-15
16.179
20.831
.3483
249.97
70.82
34-53
2 575
1.6577
5.16
16.211
20.912
.3509
250.94
71.09
34.8o
2.580
1.6641
5.17
16.242
20.993
.3535
251.91
71-37
35-07
2.585
I . 6706
5.18
16.273
21.074
.3561
252.89
71.64
35-34
2.590
I . 6770
5-19
16.305
21 . 156
.3587
253.87
71-9"
35.62
2.595
1.6835
5.20
16.336
21 . 237
.3614
254.85
72.20
35.89
2.600
1.6900
5-21
16.368
21.319
.3640
255.83
72.48
36.17
2.605
1.6965
5.22
16.399
21.401
.3666
256.81
72.75
36.45
2.610
1.7030
5.23
16.431
21.483
.3692
257.80
73-03
36.73
2.615
1.7096
5.24
16.462
21.565
-37I8
258.78
73.31
37.01
2.620
I.7l6l
5.25
16.493
21 . 648
.3744
259-77
73-59
37-29
2.625
1.7227
5.26
16.525
21.730
• 3771
260.76
73.87
37.58
2.630
1.7292
5.27
16.556
21.813
• 3797
261.75
74-15
37-86
2.635
1-7358
5.2S
16.588
21.896
.3823
262.75
74-44
38.15
2.640
1.7424
5.29
16.619
21.979
.3849
263.74
74.72
38.44
2.645
I . 7490
5.30
16.650
22.062
.3875
264.74
75.00
38.73
2.650
I • 7556
5.31
ro.682
22.145
.3902
265.74
75.28
39-03
2.655
1.7623
5.32
16.713
22.229
.3928
266.74
75-57
39-32
2.660
1.7689
5.33
16.745
22.312
.3954
267.75
75.85
39.62
2.665
1.7756
5-34
16.776
22.396
.3980
268.75
76.14
39-92
2.670
I . 7822
5-35
16.808
22.480
.4006
269.76
76.42
40.21
2.675
1.7889
5.36
16.839
22.564
.4032
270.77
76.71
40.52
2.680
1.7956
5-37
16.870
22.648
.4059
271.78
77.00
40.82
2.685
1.8023
5-38
16.902
22.733
.4085
272.79
77-28
41.12
2.690
1.8090
5-39
16.933
22.817
.4111
273.81
77-57
41-43
2.695
1.8158
5-40
16.965
22.902
• 4137
274.83
77-86
41-74
2.700
1.8225
5-41
16.996
22.987
.4163
275.85
78.15
42.05
2.705
1.8293
5.42
17.027
23.072
.4190
276.87
78.44
42.36
2.710
1.8360
5.43
17.059
23.157
.4216
277.89
78.73
42.67
2.715
1.8428
5-44
17.090
23.243
.4242
278.91
79-02
42.99
2.720
1.8496
5-45
17.122
23.328
.4268
279-94
79-31
43-31
2.725
1.8564
5.46
17.153
23.414
.4294
280.97
79.6o
43.63
2.730
1.8632
5.47
17.185
23.500
• 4320
282.00
79.89
43-95
2.735
1.8701
5.48
17.216
23.586
• 4347
283.03
80. 18
44-27
2-740
1.8769
5-49
17.247
23.672
• 4373
284.06
80.48
44-59
2.745
1.8838
5-50
17.279
23.758
.4399
285 . 10
80.77
44-92
2.750
1.8906
Table of the Properties of Tubes and Round Bars 435
Properties of Tubes and Round Bars (Continued) 5.50 inches
o.OO inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R*, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
f • %
Circum-
Area
Per foot length
M
Distance
Radius
8*
in
inches
section
sq. in.
Surface
sq. ft.
Volume
cu. in.
Weight,
Ibs. steel
of
inertia
to farth-
est fiber
01 gyra-
tion
squared
D
C
A
5
V
W
/
y
R*
5-50
17.279
23.758
.4399
285.10
80.77
44.92
2.750
1.8906
5-51
17.310
23.845
.4425
286.14
81.06
45-25
2.755
1.8975
5-52
17.342
23.931
• 4451
287.18
81.36
45-57
2.760
1.9044
5-53
17-373
24.018
.4478
288.22
81.65
45-91
2.765
I.9H3
5-54
17.404
24.105
.4504
289.26
8i.95
46.24
2.770
1.9182
5-55
17.436
24.192
• 4530
290.31
82.24
46.57
2.775
1.9252
5-56
17.467
24.279
.4556
291.35
82.54
46.91
2.780
I.932I
5-57
17-499
24.367
.4582
292.40
82.84
47-25
2.785
I.939I
5-58
17.530
24-454
.4608
293-45
83.14
47-59
2.790
1.9460
5-59
17.562
24-542
.4635
294-51
83.43
47-93
2.795
1-9530
5.6o
17-593
24.630
.4661
295.56
83.73
48.27
2.800
1.9600
5.6i
17.624
24.718
.4687
296.62
84.03
48.62
2.805
1.9670
5-62
17.656
24.806
.4713
297.68
84.33
48.97
2.810
1.9740
5.63
17.687
24.895
• 4739
298.74
84.63
49-32
2.815
1.9811
5-64
17.719
24.983
.4765
299.80
84.93
49.67
2.820
1.9881
5-65
17.750
25.072
• 4792
300.86
85.23
50.02
2.825
1-9952
5-66
17.781
25.161
.4818
301.93
85.54
50.38
2.830
2.OO22
5.6?
17-813
25.250
.4844
303.00
85.84
50.73
2.835
2.0093
5-68
17.844
25-339
.4870
304.07
86.14
51.09
2.840
2.0164
5.69
17.876
25.428
.4896
305.14
86.45
51.45
2.845
2.0235
5-70
17.907
25.518
.4923
306.21
86.75
51.82
2.850
2.0306
5-71
17.938
25.607
• 4949
307.29
87-05
52.18
2.855
2.0378
5-72
17.970
25.697
• 4975
308.36
87.36
52.55
2.860
2.0449
5-73
18.001
25.787
.5001
309.44
87-67
52.92
2.865
2.0521
5-74
18.033
25.877
.5027
310.52
87.97
53-29
2.870
2.0592
5-75
18.064
25.967
.5053
311.61
88.28
53-66
2.875
2.0664
5-76
18.096
26.058
.5080
312.69
88.59
54-03
2.880
2.0736
5-77
18.127
26.148
.5106
313.78
88.89
54-41
2.885
2.0808
5-78
18.158
26.239
.5132
314-87
89.20
54-79
2.890
2.0880
5-79
18.190
26.330
.5158
315.96
89.51
55.17
2.895
2.0953
5.8o
18.221
26.421
.5184
317.05
89.82
55-55
2.900
2.1025
5.8i
18.253
26.512
.5211
318.14
90.13
55-93
2.905
2.1098
5-82
18.284
26.603
.5237
319.24
90.44
56.32
2.910
2.1170
5-83
18.315
26.695
.5263
320.34
90.75
56.71
2.915
2.1243
5.84
18.347
26.786
.5289
321.44
91.06
57-10
2.920
2.1316
5.85
18.378
26.878
• 5315
322.54
91.38
57-49
2.925
2.1389
5.86
18.410
26.970
• 5341
323.64
91.69
57.88
2.930
2.1462
5-87
18.441
27.062
.5368
324.75
92.00
58.28
2.935
2.1536
5-88
18.473
27.155
• 5394
325-86
92.32
58.68
2.940
2.1609
5-89
18.504
27.247
• 5420
326.97
92.63
59.o8
2-945
2.1683
5-90
18.535
27.340
.5446
328.08
92.94
59.48
2.950
2.1756
5.91
18.567
27.432
• 5472
329:19
93.26
59-89
2.955
2.1830
5-92
18.598
27.525
• 5499
330.30
93-58
60.29
2.960
2.1904
5-93
18.630
27.618
.5525
331.42
93.89
60.70
2.965
2.1978
5-94
18.661
27.712
.5551
332.54
94-21
6i.n
2.970
2.2052
5-95
18.692
27.805
• 5577
333-66
94-53
61.52
2.975
2.2127
5.96
18.724
27.899
.5603
334-78
94.84
61.94
2.980
2.2201
5-97
18.755
27.992
.5629
335-91
95.16
62.35
2.985
2.2276
5-98
18.787
28.086
.5656
337-03
95.48
62.77
2.990
2.2350
5-99
18.818
28.180
.5682
338.16
95.8o
63.19
2.995
2.2425
6.00
18.850
28.274
.5708
339-29
96.12
63.62
3.000
2.2500
436 Table of the Properties of Tubes and Round Bars.
Properties of Tubes and Round Bars (Continued)
6.00 inches
6.50 inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
al
Circum-
Area
Per foot length
Moment
Distance
Radius
11
in
inches
section
sq.in.
Surface
sq. ft.
Volume
cu. in.
Weight,
Ibs. steel
of
inertia
to farth-
est fiber
tion
squared
D~
C
A
5
V
W
7
y
&
6.00
18.850
28 . 274
i.57o8
339-29
96.12
63.62
3.000
2.2500
6.01
18.881
28 369
1.5734
340.42
96.44
64.04
3.005
2.2575
6.02
18.912
28.463
i.576o
341.56
96.76
64.47
3.010
2.2650
6.03
18.944
28.558
1.5787
342.69
97-09
64.90
3.015
2 . 2726
6.04
18.975
28.653
1.5813
343-83
97-41
65-33
3.020
2.2801
6.05
19.007
28.748
I 5839
344-97
97-73
65-76
3-025
2.2877
6.06
19.038
28 . 843
1.5865
346.11
98.05
66.20
3-030
2.2952
6.07
19.069
28.938
1.5891
347-26
98.38
66.64
3-035
2.3028
6.08
19.101
29.033
I-59I7
348.40
98.70
67 08
3-040
2.3104
6.09
19-132
29.129
1-5944
349-55
99-03
67.52
3-045
2.3180
6.10
19.164
29.225
1-5970
350.70
99-35
67-97
3-050
2 3256
6. ii
19.195
29.321
1.5996
351-85
99-68
68.41
3-055
2.3333
6.12
19.227
29.417
I. 6022
353-00
IOO.OO
68.86
3.060
2.3409
6.13
19-258
29.513
1.6048
354-15
100.33
69-31
3-065
2.3486
6.14
19.289
29.609
1.6074
355-31
100-66
69.77
3-070
2.3562
6.15
19.321
29.706
I.6ioi
356.47
100.99
70.22
3-075
2.3639
6.16
19.352
29.802
1.6127
357.63
101.32
70.68
3.080
2 3716
6.17
19.384
29.899
I.6I53
358.79
101 65
71.14
3.085
2.3793
6.18
I9-4I5
29.996
I.6I79
359 95
101 98
71.60
3.090
2.3870
6.19
19.446
30.093
I . 6205
361.12
102.31
72.07
3-095
2.3948
6.20
19.478
30.191
I . 6232
362.29
102 64
72.53
3.100
2.4025
6.21
19.509
30.288
I . 6258
363-46
102 97
73.00
3-105
2.4103
6.22
19-541
30.366
1.6284
364-63
103 30
73-47
3.110
2.4180
6.23
19.572
30.484
1.6310
365-80
103 63
73.95
3."5
2.4258
6.24
19-604
30.582
1.6336
366.98
103 96
74-42
3.120
2.4336
6.25
I9-635
30.680
I . 6362
368.16
104.30
74-90
3-125
2.4414
6.26
19.666
30.778
1.6389
369.33
104-63
75-38
3.130
2.4492
6.27
19-698
30.876
1.6415
370.52
104-97
75-86
3-135
2 4571
6.28
19.729
30-975
1.6441
37L70
105-30
76.35
3.140
2.4649
6.29
19-761
31-074
I . 6467
372.88
105-64
76.84
3-145
2.4728
6.30
19.792
31.172
1.6493
374-07
105-97
77-33
3-150
2.4806
6.31
19 823
31.271
I . 6520
375-26
106.31
77-82
3-155
2.4885
6.32
19.855
31 371
1.6546
376.45
106.65
78.31
3.160
2.4964
6.33
19.886
31-470
I 6572
377.64
106.99
78.81
3.165
2.5043
6-34
19.918
31.570
I 6598
378.83
107.32
79-31
3-170
2.5122
6.35
19.949
31.669
I 6624
380.03
107.66
79.81
3-175
2.5202
6.36
19.981
31.769
I 6650
381.23
108 oo
80.32
3.180
2.5281
6.37
20.012
31-869
I 6677
382.43
108.34
80.82
3-185
2.5361
6.38
2O.O43
31.969
I 0703
383-63
108.68
81.33
3.190
2-5440
6-39
20.075
32.069
I 6729
384-83
109.02
81.84
3-195
2.5520
6.40
20.106
32.170
I 6755
386.04
109-36
82.35
3.200
2.5600
6.41
20.138
32.271
I . 6781
387.25-
109.71
82.87
3-205
2.5680
6.42
20.169
32.371
I . 6808
388.46
110.05
83.39
3.210
2.5760
6.43
20.200
32.472
1.6834
389-67
110-39
83 91
3-215
2.5841
6.44
20.232
32.573
I . 6860
390.88
110.74
84-43
3.220
2.5921
6.45
20.263
32.675
I . 6886
392.09
111.08
84.96
3-225
2 60O2
6 46
20.295
32.776
1.6912
393-31
ill. 43
85-49
3.230
2.6o82
6.47
20.326
32.877
1.6938
394-53
111.77
86.02
3.235
2.6l63
6.48
20.358
32.979
1.6965
395-75
112. 12
86.55
3-240
2 . 6244
6-49
20.389
33.o8i
1.6991
396.97
112.46
87.09
3.245
26325
6 50
20 . 420
33-I83
i . 7017
398-20
112-81
87-62
3.250
2-6406
Table of the Properties of Tubes and Round Bars 437
Properties of Tubes and Round Bars (Continued)
6. 50 inches
7.00 inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R?, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
il
Circum
Area
Per foot length
Moment
Distance
Radius
H
in
section
Surface
Volume
Weight,
of
to farth-
ot gyra-
tion
Q o
inches
sq. in.
sq. ft.
cu. in.
Ibs.stee
inertia
est fiber
squared
rf
C
A
5
V
W
7
y
Ri
6.50
20.420
33.183
1.7017
398.20
112.81
87.62
3 250
2 . 6406
6.51
20.452
33.285
1.7043
399-42
113.16
88.16
3-255
2 6488
6.52
20.483
33.388
1.7069
400.65
H3.50
88.71
3.260
2.6569
6-53
20.515
33-490
1.7096
401.88
113-85
89.25
3-265
2.6651
6.54
20.546
33-593
I . 7122
403.11
114.20
89.80
3.270
2.6732
6-55
20.577
33.696
1.7148
404.35
114-55
90.35
3-275
2.6814
6.56
20.609
33-799
I.7I74
405.58
114.90
90.90
3.280
2.6896
6.57
20.640
33-902
1.7200
406.82
115.25
91.46
3-285
2.6978
6.58
20.672
34-005
I . 7226
408.06
115.60
92.02
3.290
2.7060
6-59
20.703
34-io8
I 7253
409.30
"5-95
92.58
3-295
2.7143
6.60
20.735
34-212
I . 7279
410.54
116.31
93-14
3-300
2.7225
6.61
20.766
34-316
1.7305
4H.79
116.66
93-71
3-305
2.7308
6.62
20.797
34.420
I - 7331
413.04
117.01
94-28
3-310
2.7390
6.63
20.829
34.524
1.7357
414-28
117-37
94.85
3.315
2-7473
6-64
20.860
34.628
I 7383
415.53
117.72
95.42
3-320
2.7556
6.65
20 . 892
34.732
1.7410
416.79
118.08
96.00
3.325
2.7639
6.66
20.923
34.837
1.7436
418.04
118.43
96.58
3-330
2.7722
6.67
20.954
34.942
I . 7462
419.30
118.79
97.16
3-335
2.7806
6.68
20.986
35.046
I . 7488
420.56
119.14
97-74
3-340
2.7889
6.69
21.017
35.151
I.75M
421.82
119.50
98.33
3-345
2.7973
6.70
21.049
35.257
I 7541
423.08
119.86
98.92
3-350
2.8056
6.71
21.080
35.362
I 7567
424.34
120.22
99-51
3-355
2 . 8140
6.72
21. 112
35.467
I • 7593
425.61
120.57
IOO . IO
3.36o
2.8224
6.73
21.143
35.573
I . 7619
426.88
120.93
100.70
3.365
2.8308
6-74
21 . 174
35.679
I • 7645
428.15
121.29
101.30
3-370
2.8392
6.75
21.206
35.785
I . 7671
429.42
121.65
101.90
3-375
2.8477
• 76
21.237
35.891
I . 7698
430.69
122.01
102.51
3.38o
2.8561
•77
21.269
35.997
I . 7724
431.96
122.38
103.12
3.385
2.8646
.78
21.300
36.103
I - 7750
433-24
122.74
103.73
3-390
2.8730
•79
21.331
36.210
I . 7776
434-52
123.10
104.34
3-395
2.8815
.80
21.363
36.317
I . 7802
435-8o
123.46
104.96
3-400
2.8900
.81
21.394
36.424
I . 7829
437-08
123.83
105.57
3-405
2.8985
.82
21 . 426
36.531
1.7855
438.37
124.19
106 . 20
3-410
2.9070
• 83
21-457
36.638
I . 7881
439-66
124.55
106.82
3.415
2.9156
.84
21 . 488
36.745
I - 7907
440-94
124.92
107-45
3-420
2.9241
•85
21.520
36.853
I 7933
442.23
125.28
108.08
3.425
2.9327
.86
21.551
36.961
I - 7959
443-53
125.65
108.71
3-430
2.9412
•87
21.583
37.068
1.7986
444-82
126.02
109.34
3-435
2.9498
.88
21 6l4
37.176
1.8012
446-12
126.38
109.98
3-440
2.9584
.89
21 . 646
37.284
I . 8038
447-41
126.75
110.62
3-445
2.9670
.90
21.677
37.393
1.8064
448.71
127.12
111.27
3-450
2.9756
.91
21 . 708
37.501
1.8090
450.02
127.49
111.91
3-455
2.9843
.92
21.740
37.610
1.8117
451.32
127.86
112.56
3.46o
2.9929
•93
21.771
37.719
I 8143
452.62
128.23
113.21
3.465
3.0016
.94
21.803
37.828
I 8169
453-93
128.60
113-87
3-470
3.0102
• 95
21.834
37.937
I 8195
455-24
128.97
114-53
3-475
3.0189
.96
21.865
38.046
I 8221
456.55
129.34
H5.I9
3.480
3.0276
•97
21.897
38.155
1.8247
457-86
129.71
115.85
3.485
3 0363
.98
21.928
38.265
1.8274
459-18
130.09
116.52
3-490
3-0450
• 99
21.960
38.375
1.8300
460.50
130.46
117-19
3-495
3 0538
.00
21.991
38.485
1.8326
461-81
130.83
117-86
3-500
3-0625
438 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued)
7.00 Inches
7. 50 Inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
IP, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
el
Circum
Area
Per foot length
Mom en
Distance
Radius
11
in
section
Surface
Volume
Weight
of.
to farth-
oi gyra
tion
Q.2
inches
sq. in.
sq. ft.
cu. in.
Ibs. stee
inertia
est fiber
squared
D
C
A
5
V
W
7
y
R*
7.00
21.991
38.485
1.8326
461.81
130.83
117.86
3-500
3-0625
7.01
22.023
38.595
1.8352
463.13
131.21
118.53
3.505
3.0713
7.02
22.054
38.705
1.8378
464.46
131.58
119.21
3-Sio
3.0800
7-03
22.085
38.815
1.8404
465-78
131.96
119.89
3.515
3.0888
7.04
22.117
38.926
1.8431
467.11
132.33
120.58
3-520
3.0976
7-05
22.148
39.036
1.8457
468.44
132.71
121.26
3.525
3.1064
7.06
22.180
39-147
1.8483
469.76
133.08
121.95
3-530
3.1152
7 07
22.211
39.258
1.8509
471.10
133.46
122.64
3-535
3.1241
7.08
22.242
39.369
1.8535
472.43
133.84
123-34
3-540
3.1329
7.09
22.274
39.48o
i . 8562
473-77
134.22
124.04
3-545
3.1418
7.10
22.305
39-592
1.8588
475.10
134.60
124-74
3.550
3.1506
7. II
22.337
39.704
1.8614
476.44
134.98
125-44
3-555
3.1595
7.12
22.368
39.815
1.8640
477.78
135.36
126.15
3.56o
3.1684
7-13
22.400
39.927
1.8666
479-13
135-74
126.86
3.565
3-1773
7-14
22.431
40.039
1.8692
480.47
136.12
127-57
3-570
3.1862
7-lS
22.462
40.152
1.8719
481.82
136.50
128.29
3-575
3.1952
7.16
22.494
40.264
1.8745
483.17
136.88
129.01
3.58o
3-2041
7-17
22.525
40.376
1.8771
484-52
137.26
129.73
3.585
3.2131
7.18
22.557
40.489
1.8797
485-87
137.65
130.46
3.590
3.2220
7.19
22.588
40.602
1.8823
487.22
138.03
131.19
3-595
3.2310
7.20
22.619
40.715
1.8850
488.58
138.41
131.92
3.600
3.2400
7.21
22.651
40.828
1.8876
489.94
138.80
132.65
3.605
3.2490
7-22
22.682
40.942
1.8902
491-30
I39.I8
133-39
3.610
3.2580
7-23
22.714
41.055
1.8928
492.66
139-57
I34-I3
3.6iS
3.2671
7.24
22.745
41.169
1-8954
494-02
139.96
134.87
3.620
3.2761
7-25
22.777
41.282
1.8980
495-39
140.34
135.62
3-625
3.2852
7-26
22.808
41.396
1.9007
496.76
140.73
136.37
3.630
3.2942
7.27
22.839
4I.5H
1.9033
498.13
141.12
137.12
3.635
3-3033
7.28
22.871
41.625
1.9059
499-50
141.51
137.88
3.640
3.3124
7.29
22.902
41-739
1.9085
500.87
141.90
138.64
3.645
3.3215
7-30
22.934
41.854
1.9111
502.25
142.29
139.40
3.650
3.3306
7 31
22.965
41.969
I.9I38
503-62
142.68
140.17
3-655
3.3398
7-32
22.996
42.084
1.9164
505-00
143-07
140.93
3.66o
3.3489
7.33
23.028
42.199
1.9190
506.38
143-46
141.71
3.665
3.3581
7-34
23-059
42.314
1.9216
507.77
143.85
142.48
3.670
3.3672
7-35
23.091
42.429
1.9242
509.15
144.24
143.26
3.675
3.3764
7-36
23.122
42.545
1.9268
510.54
144-63
144.04
3-680
3.3856
7-37
23.154
42.660
1.9295
511-92
145 03
144.82
3-685
3.3948
7.38
23.185
42.776
1.9321
513-31
145-42
145.61
3.690
3.4040
7.39
23.216
42.892
1-9347
514.71
145-82
146.40
3.695
3.4133
7 40
23.248
43.oo8
1-9373
516 10
146 21
147-20
3.7oo
3.4225
7-41
23.279
43-125
1-9399
517.50
146 61
147-99
3.705
3.4318
7-42
23.311
43-241
1.9426
518.89
147 00
148.79
3-710
3.4410
7-43
23.342
43 358
1.9452
520.29
147.40
149.60
3.715
3.4503
7-44
23-373
43-475
1.9478
521.70
147 80
150.40
3.720
3.4596
7-45
23.405
43-592
1.9504
523-10
148.19
151 . 22
3.725
3.4689
7.46
23.436
43.709
1-9530
524-50
148.59
152.03
3-730
3.4782
7-47
23.468
43-826
1.9556
525.91
148.99
152.85
3-735
3.4876
7-48
23-499
43 943
1.9583
527-32
149-39
153.67
3-740
3.4969
7-49
23.531
44.061
1.9609
528.73
149 79
154.49
3-745
3.5063
7 So
23.562
44-179
1.9635
530.14
150 19
155 32
3-750
3.5156
Table of the Properties of Tubes and Round Bars 439
Properties of Tubes and Round Bars (Continued) g'oolSches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
HI
Q""1 -S
Circum-
ference
in
Area
cross
section
Per foot length
Moment
of
Distance
from axis
to farth-
Radius
of gyra-
tion
Surface
Volume
Weight,
0
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia,
est fiber
squared
D
C
A
5
V
W
7
y
/?»
7-50
23.562
44-179
1.9635
530.14
150.19
155-32
3-750
3.5156
7-51
23-593
44-297
1.9661
531.56
150.59
156.15
3-755
3.5250
7-52
23.625
44.415
1.9687
532.97
150.99
156.98
3.760
3-5344
7-53
23.656
44-533
I.97I3
534-39
151.39
157.82
3.765
3.5438
7-54
23.688
44.651
1.9740
535.81
151-80
158.66
3-770
3-5532
7-55
23.719
44-770
1.9766
537.24
152.20
159-50
3-775
3.5627
7.56
23.750
44-888
1.9792
538.66
152.60
160.35
3.78o
3-5721
7-57
23.782
45-007
1.9818
540.09
153-01
161 . 20
3.785
3.5816
7.58
23.813
45.126
1.9844
541-51
I53-4I
162.05
3-790
3-5910
7-59
23.845
45-245
1.9871
542.94
153-82
162.91
3.795
3.6005
7.60
23.876
45.365
1.9897
544.38
154-22
163.77
3.800
3.6100
7.61
23.908
45.484
1.9923
545.81
154.63
164.63
3.805
3.6195
7.62
23 939
45.604
1.9949
547 24
155-03
165.50
3.810
3.6290
7-63
23.970
45.723
1-9975
548.68
155-44
166.37
3.815
3.6386
7.64
24.002
45.843
2.0001
550.12
155.8s
167.24
3.820
3-6481
7-65
24-033
45.963
2.OO28
551.56
156.26
168.12
3.825
3.6577
7.66
24.065
46.084
2.0054
553-00
156.67
169.00
3.830
3.6672
767
24.096
46.204
2.0080
554-45
I57.o8
169.88
3.835
3.6768
7.68
24.127
46.325
2.0106
555-90
157.49
170.77
3.840
3.6864
7.69
24.159
46.445
2.0132
557-34
157.90
171.66
3.845
3.6960
7-70
24.190
46.566
2.0159
558.8o
158.31
172.56
3.850
3.7056
7.71
24.222
46.687
2 0185
560.25
158.72
173.46
3.855
3.7153
7-72
24-253
46.808
2 0211
561.70
159.13
174.36
3.860
3.7249
7 73
24.285
46.930
2 0237
563.16
159-54
175.26
3.86s
3.7346
7-74
24.316
47-051
2.0263
564.62
159-96
176.17
3.870
3-7442
7-75
24-347
47-173
2.0289
566.08
160.37
177.08
3.875
3-7539
7-76
24-379
47-295
2.0316
567.54
160.78
178.00
3.880
3.7636
7-77
24.410
47.417
2.0342
569.00
161.20
178.92
3.885
3-7733
7-78
24.442
47-539
2.0368
570.47
161.61
179.84
3.890
3.7830
7-79
24-473
47-661
2.0394
571-93
162.03
180.77
3-895
3.7928
7.80
24.504
47.784
2.0420
573-40
162.45
181 . 70
3.900
3.8025
7.81
24.536
47.906
2.0447
574.87
162.86
182.63
3.905
3.8123
7.82
24.567
48.029
2.0473
576.35
163.28
183.57
3.9io
3.8220
7-83
24-599
48.152
2.0499
577-82
163.70
184.51
3.915
3.8318
7.84
24.630
48.275
2.0525
579-30
164.12
185.45
3.920
3.8416
7.85
24.662
48.398
2.0551
580.78
164.53
186.40
3.925
3.8514
7.86
24.693
48.522
2.0577
582.26
164.95
187.35
3-930
3.8612
7-87
24.724
48.645
2.0604
583.74
165.37
188.31
3-935
3.87H
7.88
24.756
48.769
2.0630
585-23
165.79
189.27
3-940
3.8809
7.89
24.787
48.893
2.0656
586.71
166.22
190.23
3-945
3-8908
7-90
24.819
49-017
2.0682
588.20
166.64
191.20
3-950
3.9006
7-91
24.850
49.141
2.0708
589-69
167.06
192.17
3-955
3-9105
7-92
24.881
49.265
2.0735
591 . 18
167.48
193.14
3.96o
3.9204
7-93
24.913
49-390
2.0761
592.68
167.91
194.12
3.965
3-9303
7-94
24.944
49.5U
2.0787
594-17
168.33
195.10
3-970
3-9402
7-95
24.976
49.639
2.0813
595.67
168.75
196.08
3-975
3-9502
7.96
25.007
49.764
2.0839
597.17
169.18
197.07
3.98o
3.96oi
7-97
25.038
49-889
2.0865
598.67
169.60
198.06
3.985
3-9701
7-98
25.070
50.014
2.0892
600.17
170.03
199-06
3-990
3.98oo
7-99
25 . 101
50.140
2.0918
601.68
170.46
200.06
3-995
3-9900
8.00
25.133
50.265
2.0944
603.19
170.88
201.06
4.000
4.0000
440 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued) 8. 00 inches
O.5O inches
For Tubes use differences for A, W, 7 and V (for volume of wall only), sum for
R2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
a|j
Circum-
Area
Per foot length
Moment
Distance
Radius
.$%
Q'S
in
inches
section
sq. in.
Surface
sq. ft.
Volume
cu. in.
Weight,
Ibs. steel
of
inertia
to farth-
est fiber
or gyra-
tion
squared
D
C
A
5
V
W
7
y
7?2
8.00
25.133
50.265
2.0944
603.19
170.88
201.06
4.000
4.0000
8.01
25.164
50.391
2.0970
604.69
171.31
202.07
4-005
4.0100
8.02
25.196
50.517
2.0996
606.21
171-74
203.08
4.010
4.0200
8.03
25 . 227
50.643
2 . 1022
607.72
172.17
204.10
4.015
4.0301
8.04
25.258
50.769
2.1049
609.23
172.60
205.11
4.020
4.0401
8.05
25.290
50.896
2.1075
610.75
173.03
206.14
4-025
4.0502
8.06
25.321
51.022
2.IIOI
612.27
173.46
207.16
4-030
4.0602
8.07
25 - 353
5I.I49
2.II27
613.79
173-89
208.19
4-035
4.0703
8.08
25.384
51-276
2.II53
615.31
174-32
209.23
4.040
4.0804
8.09
25.415
51-403
2.1180
616.83
174-75
210.26
4.045
4.0905
8.10
25-447
51.530
2.1206
618.36
I75.I8
211.31
4-050
4.1006
8. II
25.478
51.657
2.1232
619.89
I75.6i
212.35
4-055
4.1108
8.12
25.510
51.785
2.1258
621 . 42
176.05
213.40
4.060
4.1209
8.13
25-541
51.912
2.1284
622.95
176.48
214.45
4-065
4.1311
8.14
25-573
52.040
2.1310
624 . 48
176.92
215.51
4.070
4.1412
8.15
25.604
52.168
2.1337
626.02
177-35
216.57
4.075
4.1514
8.16
25.635
52.296
2.1363
627.55
177-79
217.64
4.080
4.1616
8.17
25-667
52.424
2.1389
629 . 09
178.22
218.71
4-085
4-1718
8.18
25.698
52.553
2.1415
630.63
178.66
219.78
4.090
4.1820
8.19
25.730
52.681
2.1441
632.18
179.10
220.85
4-095
4.1923
8.20
25.761
52.810
2.1468
633.72
179 53
221.93
4.100
4.2025
8.21
25.792
52.939
2.1494
635.27
179-97
223.02
4.105
4.2128
8.22
25.824
53.o68
2.1520
636.82
180.41
224.11
4.110
4.2230
8.23
25.855
53-197
2.1546
638.37
180.85
225 . 20
4-II5
4-2333
8.24
25.887
53.327
2 . 1572
639.92
181 . 29
226.30
4.120
4.2436
8.25
25.918
53.456
2.1598
641 . 47
181.73
227.40
4.125
4-2539
8.26
25-950
53-586
2.1625
643.03
182.17
228.50
4.130
4 . 2642
8.27
25.981
53.7i6
2.I65I
644.59
182.61
229.61
4-135
4.2746
8.28
26.012
53.846
2.1677
646.15
183.05
230.72
4.140
4 . 2849
8.29
26.044
53.976
2.1703
647 71
183.50
231.84
4-145
4-2953
8.30
26.075
54.io6
2.1729
649.27
183.94
232.96
4.150
4.3056
8.31
26.107
54-237
2.1756
650.84
184.38
234.09
4-155
4.3i6o
8.32
26.138
54.367
2.1782
652.41
184.83
235.21
4.160
4.3264
8.33
26.169
54.498
2.1808
653.97
185.27
236.35
4.165
4.3368
8.34
26.201
54.629
2.1834
655.55
185.72
237.48
4.170
4-3472
8.35
26.232
54.760
2.l86o
657.12
186.16
238.63
4-175
4-3577
8.36
26.264
54.891
2.1886
658.69
186.61
239.77
4.180
4-3681
8.37
26.295
55.023
2.I9I3
660.27
187.05
240.92
4.185
4-3786
8.38
26.327
55-154
2.1939
661.85
187.50
242.07
4.190
4-3890
8.39
26.358
55.286
2.1965
663.43
187.95
243.23
4-195
4-3995
8.40
26.389
55.418
2.I99I
665.01
188.40
244.39
4.200
4.4100
8.41
26.421
55-550
2.2017
666.60
188.85
245.56
4.205
4.4205
8.42
26.452
55.682
2.2044
668.18
189.30
246.73
4.210
4-4310
8.43
26.484
55.814
2 . 2070
669.77
189.75
247.90
4.215
4.4416
8.44
26.515
55-947
2.2096
671.36
190.20
249.08
4.220
4-4521
8.45
26.546
56.079
2.2122
672.95
190.65
250.26
4-225
4.4627
8.46
26.578
56.212
2.2148
674.55
191.10
251.45
4.230
4-4732
8.47
26.609
56.345
2.2174
676.14
I9I-55
252.64
4-235
4-4838
8.48
26.641
56.478
2.2201
677.74
192.00
253.84
4.240
4.4944
8.49
26.672
56.612
2.2227
679.34
192.46
255.04
4-245
4.5050
8.50
26.704
56.745
2.2253
680.94
192.91
256.24
4.250
4.5156
Table of the Properties of Tubes and Round Bars 441
Properties of Tubes and Round Bars (Continued) 8. 50 inches
9. OO inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R*, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
al
Circum-
Area
Per foot length
Moment
Distance
Radius
11
in
inches
section
sq. in.
Surface
sq. ft.
Volume
cu. in.
Weight,
Ibs. steel
of
inertia
to farth-
est fiber
01 gyra-
tion
squared
D
C
A
5
V
W
/
y
R>
8.50
26 . 704
56.745
2.2253
680.94
192.91
256.24
4.250
4.5156
8.51
26.735
56.879
2.2279
682.54
193.36
257-45
4.255
4.5263
8.52
26.766
57-012
2.2305
684.15
193-82
258.66
4.260
4.5369
8.53
26.798
57.146
2.2331
685.76
194.27
259-88
4.265
4.5476
8.54
26.829
57.28o
2.2358
687.36
194-73
261 . 10
4.270
4.5582
8.55
26.861
57.415
2.2384
688.97
195.19
262.32
4.275
4.5689
8.56
26 . 892
57-549
2.2410
690.59
195.64
263.55
4.280
4.5796
8.57
26.923
57.683
2.2436
692.20
196.10
264.79
4-285
4.5903
8.58
26.955
57.8i8
2 . 2462
693.82
196.56
266.02
4.290
4.6010
8.59
26.986
57-953
2.2489
695.44
197.02
267.27
4-295
4.6118
8.60
27.018
58.088
2.2515
697-06
197.48
268.51
4-300
4.6225
8.61
27.049
58.223
2.2541
698.68
197-94
269.76
4.305
4.6333
8.62
27.081
58.359
2.2567
700.30
198.40
271.02
4-310
4.6440
8.63
27.112
58.494
2.2593
701.93
198.86
272 . 28
4.315
4.6548
8.64
27-143
58.630
2.2619
703.56
199.32
273.54
4.320
4.6656
8.65
27.175
58.765
2.2646
705.19
199-78
274.81
4.325
4.6764
8.66
27 . 206
58.901
2.2672
706.82
200.24
276.08
4-330
4.6872
8.67
27-238
59.038
2.2698
708.45
200.70
277.36
4-335
4.6981
8.68
27.269
59-174
2.2724
710.09
201 . 17
278.64
4-340
4.7089
8.69
27.300
59-310
2.2750
711.72
201 . 63
279-93
4-345
4.7198
8.70
27-332
59-447
2.2777
713.36
202.10
281.22
4-350
4.7306
8.71
27-363
59.584
2.2803
7i5.oo
202.56
282.52
4-355
4.7415
8.72
27 395
59-720
2.2829
716.65
203.03
283.82
4.360
4.7524
8.73
27.426
59.857
2.2855
718.29
203.49
285.12
4.365
4.7633
8.74
27.458
59-995
2.2881
719.94
203.96
286.43
4-370
4-7742
8.75
27.489
60.132
2.2907
721.58
204.42
287.74
4-375
4.7852
8.76
27-520
60.270
2.2934
723.23
204 . 89
289.06
4.38o
4.7961
8-77
27.552
60.407
2.2960
724.89
205.36
290.38
4.385
4.8071
8.78
27-583
60.545
2.2986
726.54
205.83
291 . 71
4-390
4.8180
8.79
27.615
60.683
2.3012
728 . 20
206.30
293-04
4-395
4.8290
8.80
27 . 646
60.821
2.3038
729.85
206.77
294-37
4.400
4.8400
8.81
27.677
60.960
2.3065
731.51
207.24
295.72
4.405
4.8510
8.82
27.709
61.098
2.3091
733.18
207.71
297.06
4.4io
4.8620
8.83
27-740
61.237
2.3II7
734.84
208.18
298.41
4.415
4.8731
8.84
27 772
61-375
2.3143
736.50
208.65
299.76
4.420
4.8841
8.85
27.803
61.514
2.3169
738.17
209.12
301 . 12
4.425
4.8952
8.86
27.835
61.653
2.3195
739.84
209.60
302.49
4-430
4.9062
8.87
27-866
61.793
2.3222
74L5I
210.07
303.85
4-435
4 9173
8.88
27.897
61.932
2.3248
743-19
210.54
305.23
4-440
4.9284
8.89
27.929
62.072
2.3274
744-86
211.02
306.60
4-445
4-9395
8.90
27.960
62.211
2.3300
746.54
211.49
307.99
4-450
4.95o6
8.91
27.992
62.351
2.3326
748.22
211.97
309.37
4-455
4.9618
8.92
28.023
62 . 491
2.3353
749-90
212.45
310.76
4.460
4.9729
8.93
28.054
62.631
2.3379
751.58
212.92
3I2.I6
4.465
4.9841
8.94
28.086
62.772
2.3405
753.26
213.40
313.56
4.470
4-9952
8.95
28.117
62.912
2.3431
754-95
213.88
314.97
4-475
5.0064
8.96
28 149
63.053
2.3457
756.64
214.36
316.37
4.480
5.0176
8.97
28 180
63.194
2.3483
758.33
214.83
317 79
4.485
5.0288
8.98
28 212
63.335
2 35io
760.02
215-31
319-21
4-490
5 0400
8.99
28.243
63.476
2.3536
761.71
215-79
320 63
4-495
5.0513
9.00
28.274
63,617
2.3562
763.41
216,27
322.06
4-500
5.0625
442 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued)
9.00 inches
9.50 inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
K*, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
p
Circum-
Area
Per foot length
Moment
Distance
Radius
si
in
inches
section
sq. in.
Surface
sq. ft.
Volume
cu. in.
Weight,
Ibs. steel
of
inertia
to farth-
est fiber
01 gyra-
tion
squared
D
C
A
S
V
W
I
y
&
9.00
28.274
63.617
2.3562
763.41
216.27
322.06
4-500
5-0625
9.01
28.306
63.759
2.3588
765 . 10
216.75
323.50
4.505
5.0738
9.02
28.337
63.900
2.3614
766.80
217.24
324.93
4-510
5-0850
9.03
28.369
64.042
2.3640
768.50
217.72
326.38
4.515
5-0963
9.04
28.400
64.184
2.3667
770.21
218.20
327.83
4.520
5-1076
9.05
28.431
64.326
2.3693
77I.9I
218.68
329.28
4.525
5-1189
9.06
28.463
64-468
2.3719
773-62
219.17
330.74
4-530
5-1302
9.07
28.494
64.611
2.3745
775-33
219.65
332.20
4-535
5.1416
9.08
28.526
64.753
2.3771
777-04
220.14
333-67
4-540
5.1529
9.09
28.557
64.896
2.3798
778.75
220.62
335.14
4-545
5-1643
9.10
28.588
65.039
2.3824
780.47
221. II
336.62
4-550
5 . 1756
9. II
28.620
65.182
2.3850
782.18
221.59
338.10
4-555
5-1870
9.12
28.651
65.325
2.3876
783.90
222.08
339-59
4.56o
5-1984
9-13
28.683
65.468
2.3902
785.62
222.57
34i.o8
4.565
5-2098
•9.14
28.714
65.612
2.3928
787.34
223.05
342.57
4-570
5.2212
9-15
28 . 746
65.755
2.3955
789.07
223.54
344.o8
4-575
5.2327
9.16
28.777
65.899
2.3981
790.79
224.03
345-58
4.58o
5.2441
9-17
28.808
66.043
2.4007
792.52
224.52
347-09
4.585
5.2556
9.18
28.840
66.187
2.4033
794-25
225.OI
348.61
4-590
5.2670
9-19
28.871
66.332
2.4059
795.98
225.50
350.13
4-595
0.2785
9.20
28.903
66.476
2.4086
797-71
225-99
351-66
4.600
5-2900
9.21
28.934
66.621
2.4112
799-45
226.48
353.19
4.605
5.3015
9.22
28.965
66.765
2.4138
801.19
226.98
4.610
5.3130
9-23
28.997
66.910
2.4164
802.92
227.47
356.27
4.6i5 .
5.3246
9-24
29.028
67.055
2.4190
804.66
227.96
357.81
4.620
5.3361
9-25
29.060
67 . 201
2.4216
806.41
228.46
359-37
4.625
5-3477
9.26
29.091
67.346
2.4243
808.15
228.95
360.92
4.630
5-3592
9.27
29.123
67.492
2.4269
809.90
229.44
362.48
4.635
5.3708
9.28
29.154
67.637
2.4295
811.65
229.94
364-05
4.640
5-3824
9.29
29.185
67.783
2.4321
813.40
230-44
365-62
4 645
5-3940
9-30
29.217
67.929
2-4347
815-15
230.93
367.20
4.650
5-4056
9-31
29.248
68.075
2-4374
816.90
23L43
368.78
4.655
5-4173
9-32
29.280
68.222
2.4400
818.66
231.93
370.37
4.660
5.4289
9-33
29.311
68.368
2.4426
820.42
232.42
37L96
4-665
5.4406
9-34
29.342
68.515
2.4452
822.18
232.92
373.56
4.670
5-4522
9-35
29-374
68.661
2.4478
823.94
233.42
375.16
4.675
5.4639
9.36
29.405
68.808
2.4504
825.70
233.92
376.77
4.680
5.4756
9-37
29-437
68.956
2.4531
827.47
234.42
378.38
4-685
5-4*73
9-38
29.468
69.103
2.4557
829.23
234-92
380.00
4.690
5-4990
9-39
29.500
69.250
2.4583
831.00
235.42
381.62
4.695
5.5108
9.40
29.531
69.398
2.4609
832.77
235.92
383.25
4.700
5.5225
9 41
29.562
69.546
2.4635
834-55
236.43
384.88
4.705
5-5343
9-42
29-594
69.693
2 . 4662
836.32
236.93
386.52
4.710
5.546o
9 43
29.625
69.841
2.4688
838.10
237-43
388.17
4.715
5.5578
9-44
29.657
69.990
2.4714
839.88
237-94
389-81
4.720
5.5696
9-45
29.688
70.138
2.4740
841.66
238.44
391-47
4.725
5.5814
9.46
29.719
70.287
2.4766
843.44
238.95
393-13
4-730
5-5932
9-47
29.751
70.435
2.4792
845.22
239-45
394-79
4-735
5 6051
9.48
29.782
70.584
2.4819
847.01
239.96
396.46
4-740
5.6169
9-49
29.814
70.733
2.4845
848.80
240.46
398.14
4-745
5.6288
9-50
29.845
70.882
2.4871
850.59
240.97
399-82
4-750
5.6406
Table of the Properties of Tubes and Round Bars 443
Properties of Tubes and Round Bars (Continued)
9. 50 inches
10. OO inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R?t and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
si
Circum-
Area
Per foot length
Moment
Distance
Radius
ll
in
section
Surface
Volume
Weight,
of.
to farth-
tion
Q.s
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
D
C
A
5
V
W
/
y
R*
9-50
29.845
70-882
2.4871
850.59
240.97
399.82
4-750
5.6406
9-51
29.877
71.031
2.4897
852.38
241.48
401.51
4-755
5-6525
9-52
29.908
71.181
2.4923
854.17
241.99
403.20
4.76o
5.6644
9-53
29-939
7I-33I
2.4949
855.97
242.50
404.89
4.765
5.6763
9-54
29.971
71.480
2.4976
857.76
243.00
406.60
4.770
5.6882
9-55
30.002
71-630
2.5002
859.56
243.51
408.30
4-775
5-7002
9.56
30.034
71.780
2.5028
861.36
244.02
410.02
4.78o
5-7I2I
9-57
30.065
7L93I
2.5054
863.17
244-54
411.74
4.785
5.7241
9.58
30.096
72.081
2.5080
864.97
245.05
413.46
4-790
5.736o
9-59
30. 128
72.232
2.5107
866.78
245.56
4I5.I9
4-795
5.748o
9.60
30.159
72-382
2.5133
868.59
246.07
416.92
4.800
5.7600
9.61
30.191
72.533
2.5159
870.40
246.58
418.66
4.805
5.7720
9.62
30.222
72.684
2.5185
872.21
247.10
420.41
4.810
5.7840
9.63
30.254
72.835
2.5211
874.02
247.61
422 . 16
4.815
5.7961
?.64
30.285
72.987
2.5237
875.84
248.13
423.91
4.820
5.8081
9.65
30.316 1 73.138
2.5264
877-66
248.64
425.68
4-825
5.8202
9.66 30.348
73.290
2.5290
879.48
249.16
427.44
4.830
5.8322
9.67 30.379
73-442
2.5316
881.30
249.67
429.22
4.835
5.8443
9.68
30.411
73-594
2.5342
883.12
250.19
430.99
4.840
5.8564
9-69 30.442
73.746
2.5368
884.95
250.71
432.78
4.845
5.8685
9.70 30-473
73.898
2.5395
886.78
251.22
434-57
4.850
5.8806
9.71
30.505
74-051
2.5421
888.61
251 • 74
436.36
4-855
5.8928
9.72
30.536
74.203
2.5447
890.44
252.26
438.16
4.860
5.9049
9-73
30.568
74.356
2.5473
892.27
252.78
439-97
4-865
5.9I7I
9-74
30.599
74.509
2.5499
894.11
253-30
441.78
4.870
5.9292
9-75
30.631
74-662
2.5525
895.94
253.82
443.6o
4.875
5.9414
9.76 30.662
74.815
2.5552
897.78
254-34
445-42
4.880
5.9536
9-77! 30.693
74.969
2.5578
899-62
254-86
447-25
4-885
5.9658
9.78
30.725
75-122
2.5604
901.46
255-39
449.o8
4.890
5.978o
9-79
30.756
75.276
2.5630
903.31
255.91
450.92
4.895
5-9903
9.80
30.788
75.430
2.5656
905.16
256.43
452.77
4.900
6.0025
9.81
30.819
75.584
2.5683
907.00
256.95
454.62
4-905
6.0148
9.82
30.850
75.738
2.5709
908.85
257.48
456-47
4.910
6.0270
9.83
30.882
75.892
2.5735
910.71
258.00
458.34
4.915
6.0393
9.84
30.913
76.047
2.5761
912.56
258.53
460.20
4.920
6.0516
9-85
30-945
76.201
2.5787
914.42
259-05
462.08
4.925
6.0639
9.86
30.976
76.356
2.5813
916.27
259.58
463.96
4-930
6.0762
9.87
31.008
76.511
2.5840
918.13
260.11
465.84
4-935
6.0886
9.88
31.039
76.666
2.5866
919.99
260.63
467.73
4-940
6.1009
9-89
31.070
76.821
2.5892
921.86
261 . 16
469.63
4-945
6. H33
9.90
31 . 102
76.977
2.5918
923.72
261.69
471-53
4-950
6 . 1256
9-91
31 • 133
77.132
2.5944
925.59
262.22
473-44
4-955
6.1380
9.92
31 • 165
77.288
2.5970
927.46
262.75
475-35.
4.960
6.1504
9-93
31.196
77-444
2.5997
929.33
263.28
477-27
4.965
6.1628
9-94
31.227
77.600
2.6023
931.20
263.81
479-20
4.970
6.1752
9-95
31.259
77.756
2.6049
933-08
264.34
481 . 13
4-975
6.1877
9.96
31.290
77.913
2.6075
934-95
264.87
483.07
4-980
6.2OOI
9-97
31.322
78.069
2.6101
936.83
265.40
485.01
4.985
6.2126
9.98
3L353
78.226
2.6128
938.71
265.94
486.96
4-990
6.2250
9-99
3L385
78.383
2.6154
940.59
266.47
488.91
4-995
6.2375
10.00
3I.4I6
78.540
2. 6l8o
942.48
267.00
490.87
5.000
6.2500
444 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued) 10.00 inches
10. 5O inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
.R2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
dl
Circum-
Area
Per foot length
Moment
Distance
from axis
Radius
•sj
in
section
Surface
Volume
Weight,
of
to farth-
of gyra-
tion
Q'3
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
D
C
A
5
V
W
/
y
J&
IO.OO
31.416
78.540
2.6180
942.48
267.00
490.87
5.000
6.2500
IO.OI
31-447
78.697
2.6206
944.36
267.54
492.84
5.005
6.2625
IO.O2
31-479
78.854
2 . 6232
946.25
268.07
494-Si
5.010
6.2750
10.03
3i.5io
79.012
2.6258
948.14
268.61
496.79
5.015
6.2876
10.04
31.542
79.169
2.6285
950.03
269.14
498.78
5.020
6.3001
10.05
31.573
79-327
2.63H
951-93
269.68
500.77
5.025
6.3127
10. 06
31.604
79.485
2.6337
953-82
270.22
502.76
5.030
6.3252
10.07
31.636
79.643
2.6363
955-72
270.76
504.76
5-035
6.3378
10.08
31.667
79.801
2.6389
957.62
271 . 29
506.8
5.040
6.3504
10.09
31.699
79.960
2.6416
959-52
271.83
508.8
5-045
6.3630
10.10
31.730
80.118
2.6442
961.42
272.37
510.8
5.050
6.3756
IO.II
31.762
80.277
2.6468
963.33
272.91
512.8
5-055
6.3883
10.12
31-793
80.436
2.6494
965.23
273-45
514.9
5.o6o
6.4009
10.13
31.824
8o.595
2.6520
967.14
273-99
516.9
5.065
6.4136
10.14
31-856
8o.754
2.6546
969.05
274-53
518.9
5.070
6.420
IO.I5
31.887
80.914
2.6573
970.96
275.07
521.0
5-075
6.4389
10.16
31.919
81 .073
2.6599
972.88
275.62
523.1
5.080
6.4516
10.17
31.950
81.233
2.6625
974-79
276.16
525.1
5.085
6.4643
10.18
31.981
81.393
2.6651
976.71
276.70
527.2
5.090
6.4770
10.19
32.013
81.553
2.6677
978.63
277.25
529.3
5.095
6.4898
IO.20
32.044
8i.7i3
2.6704
980.55
277.79
531-3
5.100
6.5025
IO.2I
32.076
81.873
2.6730
982.48
278.34
533-4
5.105
6.5153
IO.22
32.107
82.034
2.6756
984.40
278.88
535-5
5. no
6.5280
10.23
32.138
82.194
2.6782
986.33
279-43
537-6
5.II5.
6.5408 |
IO.24
32.170
82.355
2.6808
988.26
279.97
539-7
5-120
6.5536 !
10.25
32.201
82.516
2.6834
990.19
280.52
541-8
5.125
6.5664 j
IO.26
32.233
82.677
2.6861
992.12
281.07
544.0
5.130
6.5792
10.27
32.264
82.838
2.6887
994.06
281 . 62
546.1
5.135
6.5921
10, 28
32.296
83.000
2.6913
996.00
282.17
548.2
5.140
6.6049
10.29
32.327
83.161
2.6939
997-93
282.71
550.3
5-145
6.6178
10.30
32.358
83-323
2.6965
999.87
283.26
552.5
5.150
6.6306
10.31
32.390
83.485
2.6992
1001.82
283.81
554-6
5.155
6.6435
10.32
32.421
83 647
2.7018
1003 . 76
284.37
556.8
5-i6o
6.6564
10.33
32.453
83.809
2.7044
1005 . 71
284.92
558.9
5.165
6.6693
10.34
32.484
83-971
2.7070
1007 . 66
285.47
561.1
5.170
6.6822
10.35
32.515
84.134
2.7096
1009.61
286.02
563.3
5-175
6.6952
10.36
32.547
84.296
2.7122
1011.56
286.57
565.5
5.180
6.7081
10.37
32.578
84.459
2.7149
1013.51
287.13
567.7
5.185
6.7211
10.38
32.610
84.622
2.7175
1015.47
287.68
569-8
5.190
6.7340
10.39
32.641
84-785
2.7201
1017.42
288.24
572.0
5-195
6.7470
10.40
32.673
84.949
2.7227
1019.38
288.79
574-3
5.200
6.7600
10.41
32.704
85.112
2.7253
1021.35
289.35
576.5
5.205
6.7730
10.42
32.735
85.276
2.7279
1023.31
289.90
578.7
5-210
6.7860
10.43
32.767
85.439
2.7306
1025.27
290.46
580.9
5.215
6.7991
10.44
32.798
85.603
2.7332
1027.24
291.02
583.1
5-220
6.8121
10.45
32.830
85-767
2.7358
1029.21
291.57
585.4
5-225
6.8252
10.46
32.861
85.932
2.7384
1031 . 18
292.13
587.6
5.230
6.8382
10.47
32.892
86.096
2.7410
1033.15
292.69
589.9
5-235
6.8513
10.48
32.924
86.261
2.7437
1035.13
293.25
592.1
5.240
6.8644
10.49
32.955
86.425
2.7463
1037.10
293.81
594-4
5-245
6.8775
10.50
32.987
86.590
2.7489
1039.08
294-37
596.7
5.250
6.8906
Table of the Properties of Tubes and Round Bars 445
Properties of Tubes and Round Bars (Continued) }9'ooJSches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
3
Circum-
Area
Per foot length
Moment
Distance
Radius
.11
in
section
Surface
Volume
Weight,
of
to farth-
of gyra-
tion
Q'ja
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
D
C
A
5
V
W
7
y
R*
0.50
32.987
86.590
2.7489
1039.08
294.37
596.7
5.250
6.8906
0.51
33 018
86.755
2.7515
1041.06
294-93
598.9
5-255
6.9038
0.52
33 050
86.920
2.7541
1043.04
295-49
601.2
5.260
6.9169
0.53
33 081
87.086
2.7567
1045.03
296.06
603.5
5-265
6.9301
o.54
33.H2
87-251
2.7594
1047.01
296.62
605.8
5.270
6.9432
0.55
33.144
87.417
2 . 7620
1049.00
297.18
608. i
5-275
6.9564
0.56
33-175
87-583
2 . 7646
1050.99
297-75
610.4
5.280
6.9696
0.57
33-207
87.749
2.7672
1052.98
298.31
612.7
5-285
6.9828
0.58
33.238
87.915
2.7698
1054.98
298.87
615.1
5.290
6.9960
0.59
33 269
88.081
2.7725
1056.97
299-44
617.4
5.295
7.0093
0.60
33-301
88.247
2.7751
1058.97
300.01
619.7
5-300
7 0225
0.61
33-332
88.414
2.7777
1060 . 97
300.57
622.1
5.305
7.0358
0.62
33.364
88.581
2.7803
1063.0
301 . 14
624.4
5-310
7.0490
0.63
33-395
88.748
2.7829
1065.0
301.71
626.8
5.315
7.0623
0.64
33.427
88.915
2.7855
1067.0
302.27
629.1
5-320
7.0756
0.65
33.458
89.082
2.7882
1069.0
302.84
631.5
5.325
7.0889
0.66
33.489
89.249
2.7908
1071.0
303.41
633.9
5-330
7.1022
0.67
33.521
89.417
2.7934
1073.0
303.98
636.2
5-335
7.1156
0.68
33-552
89.584
2.7960
1075.0
304-55
638.6
5-340
7.1289
0.69
33.584
89.752
2.7986
1077.0
305.12
641.0
5-345
7.1423
0.70
33 615
89.920
2.8013
1079.0
305-69
643.4
5-350
7.1556
0.71
33.646
90.088
2.8039
1081.1
306.26
645.8
5-355
7.1690
0.72
33 678
90.257
2.8065
1083.1
306.84
648.3
5.36o
7.1824
0.73
33-709
90.425
2.8091
1085.1
307.41
650.7
5.365
7.1958
0.74
33-741
90.594
2.8117
1087.1
307.98
653.1
5-370
7.2092
0.75
33-772
90.763
2.8143
1089.2
308.56
655.5
5-375
7.2227
0.76
33.804
90.932
2.8170
1091.2
309.13
658.0
5.38o
7.2361
0.77
33-835
91.101
2.8196
1093.2
309.71
660.4
5.385
7.2496
0.78
33.866
91.270
2.8222
1095.2
310.28
662.9
5-390
7.2630
o.79
33.898
91-439
2.8248
1097-3
310.86
665.4
5-395
7.2765
0.80
33.929
91.609
2.8274
1099-3
311-43
667.8
5-400
7.2900
0.81
33.961
91.779
2.8301
HOI. 3
312.01
670.3
5.405
7.3035
0.82
33-992
91.948
2.8327
1103.4
312.59
672.8
5-410
7.3170
0.83
34.023
92.118
2.8353
1105.4
313.17
675.3
5.415
7.3306
0.84
34-055
92.289
2.8379
1107.5
313.74
677-8
5-420
7-3441
0.85
34-086
92.459
2.8405
1109.5
314.32
680.3
5.425
7-3577
0.86
34.H8
92.630
2.8431
IIII. 6
314.90
682.8
5-430
7-3712
0.87
34-149
92.800
2.8458
1113.6
315.48
685.3
5-435
7.3848
0.88
34 181
92.971
2.8484
1115.7
316.06
687.8
5-440
7.3984
0.89
34-212
93.142
2.8510
1117.7
316.65
690.4
5-445
7.4120
0.90
34.243
93.313
2.8536
1119.8
317.23
692.9
5-450
7.4256
0.91
34-275
93.484
2.8562
II2I.8
3I7.8I
695.5
5-455
7-4393
0.92
34.306
93.656
2.8588
1123.9
318.39
698.0
5.460
7.4529
0.93
34-338
93.828
2.8615
1125.9
318.98
700.6
5.465
7.4666
0.94
34.369
93-999
2.8641
1128.0
319.56
703.1
5-470
7.4802
0-95
34-400
94.171
2.8667
1130.1
320.14
705.7
5-475
7-4939
0.96
34-432
94-343
2.8693
1132.1
320.73
708.3
5.48o
7.5076
10.97
34.463
94.516
2.8719
1134.2
321.31
710.9
5.485
7.5213
10.98
34-495
94.688
2.8746
1136.3
321.90
713-5
5-490
7-5350
10.99
34.526
94.860
2.8772
1138.3
322.49
716.1
5-495
7.5488
11.00
34-558
95.033
2.8798
1140.4
323.07
718.7
5-500
7.5625
446 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued) 11-00 }nc£es
11.5O Inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R?, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
P
Circum-
ference
in
Area
cross
section
Per foot length
Moment
of
inot-f 10
Distance
from axis
to farth-
Radius
of gyra-
tion
Surface
Volume
Weight,
P a
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
D
C
A
5
V
W
7
y
JK*
11.00
34-558
95-033
2.8798
1140.4
323.07
718.7
5-500
7.5625
II. OI
34.589
95.206
2.8824
1142.5
323.66
721.3
5-505
7.5763 -
II 02
34 620
95-379
2.8850
H44-5
324.25
723.9
5-Sio
7-5900
II.O3
34.652
95-552
2.8876
1146.6
324.84
726.6
5.515
7-6038
11.04
34.683
95.726
2.8903
1148.7
325.43
729.2
5-520
7.6176
II.O5
34-715
95.899
2.8929
1150.8
326.02
731-8
5.525
7-6314
II. 06
34.746
96.073
2.8955
1152.9
326.61
734-5
5-530
7.6452
II.O7
34-777
96.247
2.8981
H55- o
327.20
737-2
5-535
7.6591
II.08
34.809
96.421
2.9007
II57-0
327.79
739-8
5-540
7.6729
II.O9
34.840
96.595
2.9034
1159.1
328.38
742.5
5-545
7.6868
II. 10
34.872
96.769
2.9060
1161.2
328.98
745-2
5-550
7.7006
II. II
34.903
96.943
2.9086
1163.3
329.57
747-9
5-555
7.7145
II. 12
34-935
97.118
2.9112
1165.4
33o.i6
750.6
5.56o
7.7284
II. 13
34.966
97-293
2.9138
1167.5
330.76
753-3
5.565
7.7423
II. 14
34 997
97-468
2.9164
1169.6
331-35
756.0
5-570
7.7562
II. 15
35-029
97.643
2.9191
1171.7
331-95
758.7
5 575
7.7702
II. 16
35.o6o
97.818
2.9217
1173.8
332.54
761.4
5.58o
7.7841
11.17
35.092
97-993
2.9243
1 175 --9
333-14
764.2
5.585
7.7981
11.18
35-123
98.169
2.9269
1178.0
333-73
766.9
5-590
7.8120
11. 19
35-154
98.344
2.9295
1180.1
334-33
769.6
5-595
7.8260
11.20
35-186
98.520
2.9322
1182.2
334-93
772.4
5.6oo
7.8400
II. 21
35-217
98.696
2.9348
1184.4
335-53
775-2
5.605
7.8540
11.22
35-249
98.873
2.9374
1186.5
336.13
777-9
5.6io
7.8680
11.23
35.28o
99-049
2.9400
1188.6
336.73
780.7
5.615
7.8821
11.24
35-312
99-225
2.9426
1190.7
337-33
783.5
5.620
7.8961
11.25
35-343
99-402
2.9452
1192.8
337-93
786.3
5.625
7.9102
11.26
35-374
99-579
2.9479
II94-9
338.53
789.1
5-630
7.9242
11.27
35.4o6
99.756
2.9505
II97-I
339-13
791.9
5.635
7.9383
11.28
35-437
99.933
2.9531
1199.2
339-73
794-7
5-640
7-9524
11.29
35.469
100. 110
2.9557
1201 . 3
340.33
797-5
5.645
7.966s
11.30
35-500
100.287
2.9583
1203.4
340.94
800.4
5-650
7.9806
11.31
35-531
100.465
2.9610
1205.6
341-54
803.2
5.655
7.9948
11.32
35.563
100.643
2.9636
1207.7
342.15
806.0
5.66o
8.0089
11.33
35-594
100.821
2.9662
1209.8
342.75
808.9
5-665
8.0231
11.34
35.626
100.999
2.9688
I2I2.0
343.36
811.8
5.670
8.0372
11.35
35.657
101.177
2.9714
I2I4.I
343.96
814.6
5-675
8.0514
11.36
35-688
101.355
2.9740
I2I6.3
344-57
817.5
5.68o
8.0656
H.37
35-720
101.534
2.9767
I2I8.4
345-17
820.4
5.685
8.0798
11.38
35-751
101 . 713
2.9793
1220.6
345.78
823.3
5.690
8.0940
11.39
35.783
101.891
2.9819
1222.7
346.39
826.2
5.695
8.1083
11.40
35.814
102.070
2.9845
1224.8
347-00
829.1
5.700
8.1225
11.41
35.846
102 . 249
2.9871
1227.0
347-61
832.0
5-705
8.1368
11.42
35.877
102.429
2.9897
I229.I
348.22
834.9
5-710
8.1510
11-43
35.908
102.608
2.9924
I23I.3
348.83
837-8
5-715
8.1653
11.44
35-940
102.788
2.9950
1233-5
349-44
840.8
5.720
8.1796
11.45
35-971
102.968
2.9976
1235-6
350.05
843.7
5-725
8.1939
11.46
36.003
103.148
3.0002
1237-8
350.66
846.7
5-730
8.2082
11.47
36.034
103.328
3.0028
1239-9
351.27
849.6
5-735
8.2226
11.48
36.065
103.508
3-0055
I242.I
351.89
852.6
5-740
8.2369
11.49
36.097
103.688
3.0081
1244-3
352.50
855-6
5-745
8.2513
H.50
36.128
103.869
3-0107
1246.4
353.ii
858.5
5-750
8.2656 j
Table of the Properties of Tubes and Round Bars 447
Properties of Tubes and Round Bars (Continued) 1 |-gO j^hes
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
ii
Circum-
erence
Area
Per foot length
Moment
Distance
°rom axis
Radius
of gyra-
11
section
Surface
Volume
Weight,
of
to farth-
tion
Q.2
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
D
C
A
5
V
W
/
y
/?2
11.50
36.128
103.869
3.0107
1246.4
353-11
858.5
5-750
8.2656
11.51
36.160
104.050
3.0133
1248.6
353-73
861.5
5-755
8.2800
11.52
36.191
104.231
3-0159
1250.8
354-34
864.5
5.760
8.2944
H.53
36.223
104.412
3.0185
1252.9
354.96
867.5
5-765
8.3088
11-54
36.254
104-593
3.0212
1255.1
355-57
870.6
5-770
8.3232
H.55
36.285
104.774
3.0238
1257.3
356.19
873.6
5-775
8.3377
11.56
36.317
104.956
3.0264
1259.5
356.81
876.6
5.78o
8.3521
H.57
36.348
105.137
3.0290
1261.6
357-42
879-6
5.785
8.3666
11.58
36.380
105.319
3.0316
1263.8
358.04
882.7
5.790
8.3810
H.59
36.411
105.501
3.0343
1266.0
358.66
885.7
5-795
8.3955
ii. 60
36.442
105.083
3.0369
1268.2
359-28
888.8
5.8oo
8.4100
n. 61
36.474
105.865
3-0395
1270.4
359-90
891.9
5.805
8.4245
11.62
36.505
106.048
3.0421
1272.6
360.52
894.9
5.8io
8.4390
11.63
36.537
106.231
3-0447
1274.8
36i . 14
898.0
5.815
8.4536
11.64
36.568
106.413
3-0473
1277.0
361 . 76
901.1
5.820
8.4681
11.65
36.600
106.596
3.0500
1279.2
362.38
904.2
5.825
8.4827
11.66
36.631
106.779
3.0526
1281.4
363-01
907.3
5.830
8.4972
11.67
36.662
106.963
3.0552
1283.6
363.63
910.4
5.835
8.5118
11.68
36.694
107.146
3.0578
1285.8
364.25
913.6
5.840
8.5264
11.69
36.725
107.329
3.0604
1288.0
364.88
916.7
5.845
8.5410
11.70
36.757
107.513
3.0631
I2OO.2
365.50
919.8
5.850
8.5556
11.71
36.788
107.697
3.0657
1292.4
366.13
923-0
5.855
8-5703
11.72
36.819
107.881
3.0683
1294.6
366.75
926.1
5.86o
8.5849
H.73
36.851
108.065
3.0709
1296.8
367.38
929.3
5-865
8.5996
n. 74
36.882
108 . 250
3-0735
1299-0
368.01
932.5
5.870
8.6142
H.75
36.914
108.434
3.0761
1301 . 2
368.63
935-7
5.875
8.6289
11.76
36.945
108.619
3.0788
1303.4
369.26
938.9
5.88o
8.6436
11.77
36.977
108.803
3.0814
1305.6
369.89
942.1
5-885
8.6583
11.78
37.oo8
108.988
3.0840
1307.9
370.52
945-3
5.890
8.6730
H-79
37-039
109.174
3.0866
I3IO.I
37LI5
948.5
5.895
8.6878
il.8o
37-071
109-359
3.0892
I3I2.3
37L78
951-7
5-900
8.7025
II.8I
37.102
109.544
3.0919
I3I4.5
372.41
954-9
5.905
8.7173
11.82
37.134
109.730
3-0945
I3I6.8
373-04
958.2
5-910
8.7320
11.83
37.165
109.916
3.0971
I3I9.0
373.67
961.4
5.915
8.7468
11.84
37.196
IIO. 102
3-0997
1321 . 2
374-30
964.7
5.920
8.7616
11.85
37.228
110.288
3.1023
1323.5
374-93
967.9
5.925
8.7764
11.86
37-259
H0.474
3-1049
1325.7
375.57
971.2
5-930
8.7912
11.87
37.291
110.660
3.1076
1327.9
376.20
974-5
5-935
8. 8061
11.88
37-322
110.847
3 1 102
1330.2
376.83
977-8
5 940
8.8209
11.89
37-354
in. 033
3.1128
1332.4
377-47
981.1
5-945
8.8358
11.90
37.385
III. 220
3.1154
1334-6
378.10
984.4
5.950
8.8506
11.91
37.4i6
III.407
3.1180
1336.9
378.74
987.7
5-955
8.8655
11.92
37.448
HI. 594
3.1206
1339 I
379.38
991.0
5.96o
8.8804
11-93
37-479
111.782
3-1233
I34L4
380.01
994-3
5.965
8.8953
H.94
37-511
111.969
3-1259
1343-6
380.65
997-7
5-970
8.9102
11.95
37-542
112. 157
3.1285
1345-9
381.29
IOOI.O
5-975
8.9252
11.96
37-573
H2.345
3.I3H
I348.I
381.93
1004.4
5.98o
8.9401
11.97
37-605
H2.533
3-1337
1350.4
382.57
1007.7
5.985
8.9551
11.98
37.636
112.721
3.1364
1352.6
383-21
ion. i
5-990
8.9700
H-99
37-668
112.909
3.1390
1354.9
383.85
1014.5
5-995
8.9850
12.00
37.699
113.097
3.I4I6
1357-2
384.49
1017.9
6.000
9.0000
448 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued)
12. 00 inches
12. 50 inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
Rz, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
_•!
Circum-
Area
Per foot length
Moment
Distance
from axis
Radius
.2 g
in
section
Surface
Volume
Weight,
of.
to farth-
tion
P'«
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
b
C
A
5
V
W
7
y
R*
12.00
37.699
113.097
3.1416
1357-2
384.49
1017.9
6.000
9.0000
12. OI
37-731
113.286
3.1442
1359-4
385.13
021.3
6.005
9.0150
12.02
37.762
113-475
3.1468
1361.7
385.77
024.7
6.010
9.0300
I2.O3
37-793
113.664
3.1494
1364.0
386.41
028.1
6.015
9.0451
12.04
37.825
113.853
3.1521
1366.2
387.05
031.5
6.020
9.0601
12.05
37.856
114.042
3-1547
1368.5
387.70
034.9
6.025
9.0752
12. 06
37-888
114.231
3-1573
1370.8
388.34
038.4
6.030
9.0902
12.07
37.919
114.421
3-1599
1373-0
388.98
1041.8
6.035
9-1053 1
12. 08
37-950
114.610
3.1625
1375-3
389.63
1045.3
6.040
9.1204
12.09
37.982
114.800
3.1652
1377-6
390.27
1048.8
6.045
9-1355
12.10
38.013
114.990
3.1678
1379-9
390.92
1052.2
6.050
9-1506
12. II
38.045
115.180
3.1704
1382.2
391-57
1055.7
6.055
9 1658
12.12
38.076
115.371
3.1730
1384.4
392.21
1059.2
6.060
9.1809
12.13
38.108
115.561
3.1756
1386.7
392.86
1062.7
6.065
9.1961
12.14
38.139
115.752
3.1782
1389.0
393-51
1066.2
6.070
9.2112
12.15
38.170
115.942
3.1809
I39L3
394-16
1069.7
6.075
9.2264
i 12:16
38.202
116.133
3.1835
1393 6
394 81
1073.3
6.080
9.2416
12.17
38.233
116.324
3.1861
1395-9
395.46
1076.8
6.085
9.2568
12.18
38.265
116.516
3.1887
1398.2
396.11
1080.3
6.090
9.2720
12.19
38.296
116.707
3.1913
1400.5
396.76
1083.9
6.095
9.2873
12.20
38.327
116.899
3.1940
1402.8
397-41
1087.5
6.100
9.3025
12.21
38.359
117.090
3.1966
1405.1
398.o6
1091.0
6.105
9.3178
12.22
38.390
117.282
3.1992
1407.4
398.71
1094.6
6.110
9-3330
12.23
38.422
117-474
3.2018
1409.7
399-37
1098.2
6.115
9.3483
12.24
38.453
117.666
3.2044
1412.0
400.02
1101.8
6.I2O
9.3636
12.25
38.485
117.859
3.2070
I4I4.3
400.67
1105.4
6.125
9.3789
12.26
38.516
118.051
3.2097
1416.6
401.33
1109.0
6.130
9-3942
12.27
38.547
118.244
3.2123
1418.9
401.98
III2.6
6.135
9.4096
12.28
38.579
118.437
3.2149
1421.2
402.64
1116.3
6.140
9.4249
12.29
38.610
118.630
3-2175
1423-6
403.29
1119.9
6.145
9.4403
12.30
38 642
118.823
3.2201
1425.9
403.95
1123.5
6.150
9.4556
12.31
38.673
119.016
3.2228
1428.2
404.61
1127.2
6.155
9.4710
12.32
38.704
119.210
3.2254
1430.5
405.27
1130.9
6.160
9.4864
12.33
38.736
119.403
3.2280
1432.8
405.92
1134.5
6.165
9.5018
12.34
38.767
119-597
3.2306
1435.2
406.58
1138.2
6.170
9.5172
12.35
38.799
119.791
3.2332
1437-5
407.24
1141.9
6.175
9.5327
12.36
38.830
119.985
3-2358
1439.8
407.90
1145.6
6.180
9.5481
12.37
38.862
120.179
3-2385
1442.2
408.56
1149.3
6.185
9-5636
12.38
38 893
120.374
3.2411
1444 • 5
409.22
1153.1
6.190
9-5790
12.39
38.924
120.568
3-2437
1446.8
409.88
1156.8
6.195
9 5945
12.40
38.956
120.763
3.2463
1449-2
410.55
1160.5
6.200
9.6100
12.41
38.987
120.958
3.2489
I45I-5
411.21
1164.3
6.205
9 6255
12.42
39-019
121. 153
3.2515
1453-8
411.87
1168.0
6.210
9.6410
12.43
39-050
121.348
3.2542
1456.2
412.53
1171.8
6.215
9 6566
12-44
39.o8i
121.543
3-2568
1458.5
413.20
1175.6
6.220
9.6721
12.45
39.H3
121.739
3-2594
1460.9
413.86
1179.4
6.225
9.6877
12.46
39 • 144
121.934
3.2620
1463.2
414.53
1183.2
6.230
9.7032
12.47
39.176
122.130
3.2646
1465.6
415.19
1187.0
6.235
9.7188
12.48
39-207
122.326
3.2673
1467.9
415.86
1190.8
6.240
9-7344
12.49
39.238
•122.522
3.2699
1470.3
416.53
1194.6
6.245
9.7500
12.50
39.270
122.718
3.2725
1472.6
417.19
1198.4
6.250
9.7656
Table of the Properties of Tubes and Round Bars 449
Properties of Tubes and Round Bars (Continued)
12.50 inches
13. 00 inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
Rt, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
w
si
Circum-
Area
Per foot length
Moment
Distance
Radius
1.1
in
section
Surface
Volume
Weight,
of
to farth-
tion
Q'S
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
D
C
A
5
V
W
I
y
R*
12.50
39.270
122.718
3.2725
1472.6
417.19
1198.4
6.250
9.7656
12.51
39-301
122.915
3-2751
1475-0
417-86
1202.3
6.255
9.7813
12.52
39-333
123.111
3-2777
1477-3
418.53
1206. i
6.260
9.7969
12.53
39.364
123.308
3.2803
1479-7
419.20
I2IO.O
6.265
9.8126
12.54
39.396
123.505
3 2830
1482.1
419.87
I2I3.8
6.270
9.8282
12.55
39.427
123 . 702
3.2856
1484 . 4
420.54
I2I7.7
6.275
9 8439
12.56
39.458
123 . 899
3 . 2882
1486 . 8
421.21
I22I.6
6.280
9.8596
12.57
39-490
124.097
3-2908
1489.2
421.88
1225.5
6.285
9-8753
12.58
39-521
124.294
3-2934
I49I.5
422.55
1229.4
6.290
9.8910
12.59
39-553
124.492
3.2961
1493 9
423.22
1233-3
6.295
9.9068
12.60
39.584
124.690
3-2987
1496.3
423.90
1237.2
6.300
9.9225
12. 6l
39.615
124.888
3 3013
1498.7
424.57
I24I.2
6.305
9.9383
12.62
39.647
125.086
3.3039
1501.0
425.24
I245.I
6.310
9-9540
12.63
39.678
125.284
3.3065
1503.4
425.92
I249.I
6.315
9.9698
12.64
39-710
125.483
3.3091
1505.8
426.59
1253-0
6.320
9.9856
12.65
39-741
125.681
3.3H8
1508.2
427.27
1257-0
6.325
10.0014
12.66
39-773
125.880
3.3144
I5I0.6
427.94
I26l.O
6.330
10.0172
12.67
39.804
126.079
3.3170
I5I2.9
428.62
I265.O
6.335
0.0331
12.68
39-835
126 . 278
3.3196
I5I5.3
429-30
1269.0
6.340
0.0489
12.69
39.867
126.477
3-3222
I5I7.7
429.97
1273-0
6.345
0.0648
12.70
39.898
126.677
3.3249
1520.1
430.65
1277.0
6.350
0.0806
12.71
39-930
126.876
3.3275
1522.5
431-33
I28I.O
6.355
0.0965
12.72
39.961
127.076
3-3301
1524.9
432.01
1285.0
6.360
0.1124
12.73
39-992
127.276
3.3327
1527.3
432.69
I289.I
6.365
0.1283
12.74
40.024
127.476
3-3353
1529.7
433-37
I293-I
6.370
0.1442
12.75
40.055
127 . 68
3-3379
I532.I
434-05
1297.2
6-375
0.1602
12.76
40.087
127.88
3.3406
1534-5
434-73
I30I.3
6.380
0.1761
12.77
40.118
128.08
3-3432
1536.9
435-41
1305.4
6.385
0.1921
12.78
40.150
128.28
3-3458
1539-3
436.09
1309.5
6.390
0.2080
12.79
40.181
128.48
3.3484
I54L7
436.78
I3I3.6
6-395
0.2240
12.80
40.212
128.68
3-3510
1544-2
437.46
I3I7.7
6.400
0.2400
12. 8l
40.244
128.88
3-3537
1546.6
438.14
I32I.8
6.405
0.2560
12.82
40.275
129.08
3.3563
1549-0
438.83
1325.9
6.410
10.2720
12.83
40.307
129.28
3.3589
I55I-4
439-51
I330.I
6.415
10.2881
12.84
40.338
129.49
3.3615
1553-8
440 . 20
1334-2
6.420
10.3041
12.85
40.369
129.69
3.3641
1556.2
440.88
1338.4
6.425
10.3202
12.86
40.401
129.89
3.3667
1558.7
441-57
1342.6
6.430
10.3362
12.87
40.432
130.09
3.3694
1561 . I
442.26
1346.7
6.435
10.3523
12.88
40.464
130.29
3.3720
1563.5
442.94
1350.9
6.440
10.3684
12.89
40-495
130.50
3.3746
1565.9
443.63
I355-I
6-445
10.3845
12.90
40.527
130.70
3-3772
1568.4
444 • 32
1359-3
6.450
10.4006
12.91
40.558
130.90
3.3798
1570.8
445-01
1363.6
6.455
10.4168
12.92
40.589
131.10
3.3824
1573.2
445-70
1367.8
6.460
10.4329
12.93
40.621
131.31
3.3851
1575-7
446.39
1372.0
6.465
10.4491
12.94
40.652
131.51
3.3877
I578.I
447.08
1376.3
6.470
10.4652
12.95
40.684
131.71
3.3903
1580.6
447-77
1380.5
6.475
10.4814
12.96
40.715
131.92
3.3929
1583.0
448.46
1384.8
6.480
10.4976
12.97
40.746
132.12
3-3955
1585.4
449.16
I389.I
6.485
10.5138
12.98
40.778
132.32
3.3982
1587.9
449.85
1393-4
6.490
10.5300
12.99
40.809
132.53
3.4008
1590.3
450.54
1397-7
6.495
10.5463
13-00
40.841
132.73
3.4034
1592.8
451 . 24
I402.O
6.500
10.5625
450 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued)
13.00 inches
13. 50 inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R?, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
el
Circum-
ference
Area
cross
Per foot length
Moment
Distance
Radius
11
in
section
Surface
Volume
Weight,
of
to farth-
tion
Q 2
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
D
C
A
5
V
W
7
y
R2
13.00
40.841
132.73
3.4034
1592.8
451-24
1402.0
6.500
0.5625
13.01
40.872
132.94
3.4060
1595-2
451-93
1406.3
6.505
0.5788
13.02
40.904
133.14
3.4086
1597-7
452.63
1410.6
6.510
o.595o
13.03
40-935
133-35
3.4112
1600. i
453-32
1415.0
6.515
0.6113
13.04
40.966
133-55
3.4139
1602.6
454-02
1419.3
6.520
0.6276
13.05
40.998
133.76
3.4165
1605.1
454.71
1423.7
6.525
0.6439
13.06
41.029
133.96
3.4I9I
1607.5
455-41
1428.0
6.530
0.6602
13.07
41.061
134-17
3.4217
1610.0
456.11
1432.4
6.535
0.6766
13.08
41.092
134-37
3.4243
1612.5
456.81
1436.8
6.540
0.6929
13.09
41.123
134.58
3.4270
1614.9
457-51
1441.2
6.545
0.7093
13.10
4LI55
134.78
3.4296
1617.4
458.21
1445.6
6.550
0.7256
13.11
41.186
134.99
3-4322
1619.9
458.91
1450.0
6.555
0.7420
13 12
41.218
I35-I9
3.4348
1622.3
459.6i
1454-5
6.560
0.7584
13.13
41.249
135.40
3-4374
1624.8
460.31
1458.9
6.565
0.7748
13.14
41.281
I35.6i
3-4400
1627.3
461.01
1463.4
6.570
0.7912
13.15
41.312
I35.8I
3.4427
1629.8
46i . 71
1467.8
6.575
0.8077
I3.I6
41-343
136.02
3-4453
1632.2
462.41
1472.3
6.580
0.8241
I3-I7
41.375
136.23
3-4479
1634.7
463.12
1476.8
6.585
0.8406
13.18
41.406
136.43
3-4505
1637.2
463.82
1481.3
6.590
0.8570
13.19
4L438
136.64
3-4531
1639.7
464 • 52
1485.8
6.595
0.8735
13-20
41.469
136.85
3-4558
1642.2
465.23
1490.3
6.600
0.8900
13-21
41.500
137.06
3.4584
1644.7
465.93
1494-8
6.605
0.9065
13-22
4L532
137.26
3.4610
1647.2
466.64
1499-3
6.610
0.9230
13.23
41-563
137-47
3.4636
1649.6
467.34
1503.9
6.615
0.9396
13.24
41-595
137.68
3-4662
1652.1
468.05
1508.4
6.620
10.9561
13.25
41.626
137-89
3.4688
1654.6
468.76
1513-0
6.625
10.9727
13.26
41.658
138.09
3.4715
1657.1
469.47
1517-6
6.630
10.9892
13.27
41.689
138.30
3-4741
1659.6
470.18
1522.1
6.635
11.0058
13.28
41.720
138.51
3.4767
1662.1
470.88
1526.7
6.640
11.0224
13.29
4L752
138.72
3-4793
1664.6
471-59
I53I-3
6.645
11.0390
13.30
41.783
138.93
3.4819
1667.1
472.30
1535-9
6.650
11.0556
13.31
41.815
I39-I4
3.4845
1669.7
473-01
1540.6
6.655
11.0723
13-32
41.846
139-35
3.4872
1672.2
473-72
1545.2
6.660
11.0889
13-33
41.877
139.56
3.4898
1674.7
474-44
1549-9
6.665
11.1056
13-34
41.909
139-77
3.4924
1677.2
475-15
1554-5
6.670
I I. 1222
13-35
41.940
139.98
3-4950
1679.7
475-86
1559-2
6.675
11.1389
13.36
41.972
140.19
3.4976
1682.2
476.57
1563.8
6.680
11.1556
13-37
42.003
140.40
3.5003
1684.7
477-29
1568.5
6.685
11.1723
13.38
42.035
140.61
3.5029
1687.3
478.00
1573-2
6.690
II.I890
13-39
42.066
140.82
3.5055
1689.8
478.72
1578.0
6.695
11.2058
13.40
42.097
141-03
3.5o8i
1692.3
479-43
1582.7
6.700
11.2225
13.41
42.129
141.24
3.5107
1694.8
480.15
1587.4
6.705
11.2393
13.42
42.160
141.45
3.5133
1697.4
480.86
1592.1
6.710
I .2560
13-43
42.192
141.66
3.5i6o
1699.9
481.58
1596.9
6.715
I .2728
13-44
42.223
141.87
3-5186
1702.4
482.30
1601.6
6.720
I .2896
13-45
42.254
142.08
3-5212
1705.0
4^j ~>2
1606.4
6.725
I .3064
13.46
42.286
142.29
3.5238
1707.5
483.74
1611.2
6.730
I .3232
13-47
42.317
142.50
3.5264
1710.0
484.45
1616.0
6.735
I -3401
13.48
42.349
142.72
3.5291
1712.6
485.17
1620.8
6.740
11.3569
13-49
42.380
142.93
3.5317
1715.1
485.89
1625.6
6.745
11.3738
13-50
42.412
143.14
3-5343
1717.7
486.61
1630.4
6.750
11.3906
Table of the Properties of Tubes and Round Bars 451
Properties of Tubes and Round Bars (Continued) J?*58{[|dI2
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
Fit
Circum-
Area
cross
Per foot length
Moment
Distance
from axis
Radius
11
in
section
Surface
Volume
Weight,
of
to farth-
01 gyra-
tion
Q g
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
D
C
A
5
V
W
/
y
R*
13.50
42.412
143.14
3-5343
1717.7
486.61
1630.4
6.750
11.3906
I3.5I
42.443
143-35
3.5369
1720.2
487.34
1635.3
6.755
11.4075
13.52
42.474
143.56
3-5395
1722.8
488.06
1640.1
6.760
11.4244
13-53
42.506
143.78
3-5421
1725.3
488.78
1645.0
6.765
H.44I3
13-54
42.537
143-99
3.5448
1727.9
489-50
1649.8
6.770
11.4582
13-55
42.569
144.20
3-5474
1730.4
490.23
1654.7
6.775
H.4752
13.56
42.600
I44-4I
3.55oo
1733-0
490.95
1659.6
6.780
11.4921
13-57
42.631
144.63
3.5526
1735-5
491.67
1664.5
6.785
11.5091
13.58
42.663
144-84
3-5552
1738.1
492.40
1669.4
6.790
11.5260
13-59
42.694
145.05
3-5579
1740.6
493-12
1674.4
6.795
11.5430
13.60
42.726
145.27
3.5605
1743.2
493.85
1679.3
6.800
11.5600
13.61
42.757
145.48
3.5631
1745-8
494.58
1684.2
6.805
11.5770
13.62
42.788
145.69
3.5657
1748.3
495-30
1689.2
6.810
11.5940
13.63
42.820
I45.9I
3.5683
1750.9
496.03
1694.2
6.815
11.6111
13.64
42.851
146.12
3.5709
1753-5
496.76
1699.1
6.820
11.6281
13.65
42.883
146.34
3.5736
1756.0
497-49
1704.1
6.825
11.6452
13.66
42.914
146.55
3.5762
1758.6
498.22
1709.1
6.830
11.6622
13.67
42.946
146.77
3.5788
I76l . 2
498.95
1714.1
6.835
11.6793
13-68
42-977
146.98
3.5814
1763.8
499.68
1719.1
6.840
11.6964
13.69
43.oo8
147.20
3.5840
1766.4
500.41
1724.2
6.845
11-7135
13.70
43.040
I47.4I
3.5867
1768.9
501.14
1729.2
6.850
11.7306
I3.7I
43-071
147.63
3.5893
I77L5
5oi . 87
1734-3
6.855
n.7478
13.72
43-103
147-84
3.5919
I774.I
502.60
1739-3
6.860
11.7649
13-73
43-134
148.06
3-5945
1776.7
503.34
1744-4
6.865
11.7821
13-74
43.165
148.27
3-5971
1779-3
504.07
1749-5
6.870
11.7992
13-75
43-197
148.49
3-5997
I78I.9
504.80
1754-6
6.875
11.8164
13.76
43.228
148.71
3.6024
1784.5
505.54
1759-7
6.880
11.8336
13-77
43.260
148.92
3.6050
I787.I
506.27
1764 . 8
6.885
11.8508
13.78
43.291
149.14
3.6076
1789.7
507.01
1770.0
6.890
11.8680
13-79
43.323
149-35
3.6102
1792.3
507.75
I775-I
6.895
11.8853
13.80
43-354
149-57
3.6128
1794-9
508.48
1780.3
6.000
11.9025
13.81
43.385
149-79
3.6154
1797-5
509.22
1785.4
6.905
11.9198
13.82
43.417
150.01
3.6181
ISOO.I
509.96
1700.6
6.910
11.9370
13.83
43.448
150.22
3.6207
1802.7
510.70
1795-8
6.915
11-9543
13.84
43.48o
150.44
3.6233
1805.3
5H.43
1801.0
6.920
11.9716
13.85
43-511
150.66
3.6259
1807.9
512.17
1806.2
6.925
11.9889
13.86
43-542
150.87
3.6285
I8l0.5
512.91
1811.4
6.930
12.0062
13.87
43-574
151.09
3.6312
I8I3.I
513.65
1816.7
6.935
12.0236
13.88
43.605
151.31
3.6338
I8I5.7
514.39
1821.9
6.940
12.0409
13.89
43.637
151.53
3.6364
I8l8.3
515.14
1827.2
6.945
12.0583
13.90
43.668
151-75
3.6390
I82I.O
515.88
1832.4
6.950
12.0756
13.91
43.700
151.97
3.6416
1823.6
516.62
1837.7
6.955
12.0930
13.92
43-731
152.18
3.6442
1826.2
517.36
1843.0
6.960
12.1104
13-93
43.762
152.40
3.6469
1828.8
5i8. II
1848.3
6.965
12.1278
13-94
43-794
152.62
3.6495
I83I.5
518.85
1853.6
6.970
12.1452
13.95
43.825
152.84
3.6521
I834.I
519.60
1858.9
6.975
12.1627
13.96
43.857
153-06
3.6547
1836.7
520.34
1864.3
6.980
12.1801
13-97
43.888
153.28
3.6573
1839.3
521.09
1869.6
6.985
12.1976
13.98
43.919
153-50
3.6600
1842.0
521.83
1875.0
6.990
12.2150
13-99
43-951
153-72
3.6626
1844.6
522.58
1880.4
6.995
12.2325
'14.00
43.982
153.94
3.6652
1847 3
523.33
1885.7
7.000
12.2500
452 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued) iJ'SjiJIIdles
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
jR2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
3
Circum-
Area
Per foot length
Moment
Distance
Radius
§1
in
section
Surface
Volume
Weight,
of
to farth-
01 gyra-
tion
P'3
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
zf
C
A
5
V
W
/
y
R*
14.00
43.982
153-94
3 6652
1847-3
523.33
1885.7
7.000
2.2500
14.01
44.014
154-16
3-6678
1849-9
524.08
1891.1
7.005
2.2675
14.02
44-045
154-38
3-6704
1852.5
524-82
1896.5
7.010
2 . 2850
14.03
44-077
I54.6o
3.6730
1855.2
525.57
1902.0
7.015
2 . 3O26
14.04
44-108
154-82
3.6757
1857-8
526.32
1907.4
7.020
2.3201
14.05
44-139
155-04
3-6783
1860.5
527.07
1912.8
7.025
2.3377
14.06
44.171
155-26
3.6809
1863.1
527.82
1918.3
7.030
2.3552
14.07
44.202
155-48
3.6835
1865.8
528.57
1923-7
7.035
2.3728
14.08
44-234
155-70
3.6861
1868.4
529.33
1929.2
7.040
2.3904
14.09
44.265
155.92
3-6888
1871.1
530.08
1934-7
7.045
2.4080
14.10
44.296
156.15
3.6914
1873-7
530.83
1940.2
7.050
2.4256
14.11
44.328
156.37
3.6940
1876.4
531-58
1945-7
7.055
2.4433
14.12
44-359
156.59
3.6966
1879-1
532.34
1951-2
7.060
2.4609
14.13
44-391
156.81
3-6992
1881.7
533-09
1956.8
7.065
2.4786
14.14
44-422
157.03
3.7oi8
1884.4
533-85
1962.3
7.070
2.4962
14.15
44-454
157.25
3.7045
1887.1
534-6o
1967.9
7.075
2.5139
14.16
44.485
157.48
3.7071
1889.7
535.36
1973-4
7.080
2.5316
14.17
44.516
157-70
3.7097
1892.4
536.11
1979.0
7.085
2.5493
14.18
44-548
157.92
3.7123
1895.1
536.87
1984.6
7.090
2.5670
14.19
44-579
158.14
3.7149
1897-7
537.63
1990.2
7.095
2.5848
14.20
44.611
158.37
3.7176
1900.4
538.39
1995.8
7.100
2.6025
14.21
44.642
158.59
3-7202
1903.1
539 15
2001.5
7.105
2 . 6203
14.22
44.673
158.81
3-7228
1905.8
539 90
2007.1
7.110
2.6380
14.23
44.705
159-04
3.7254
1908.5
540.66
2OI2 . 8
7.115
2.6558
14.24
44.736
159.26
3.7280
1911.1
541.42
2018.4
7.120
2.6736
14.25
44.768
159.48
3.7306
1913.8
542.18
2O24 . I
7.125
2.6914
14.26
44-799
I59.7I
3-7333
1916.5
542.95
2029.8
7.130
2.7092
14.27
44.831
159-93
3-7359
1919.2
543-71
2035-5
7.135
2.7271
14.28
44.862
160.16
3.7385
1921.9
544-47
2041.2
7.140
2 . 7449
14.29
44.893
160.38
3 7411
1924.6
545-23
2046 . 9
7.145
2.7628
14.30
44.925
160.61
3-7437
1927.3
546.00
2052.6
7.150
2.7806
14.31
44-956
160.83
3.7463
1930.0
546.76
2058.4
7.155
2.7985
14.32
44-988
161.06
3-7490
1932.7
547-52
2064 . 2
7.160
2.8164
.14.33
45-019
161 . 28
3.7516
1935-4
548.29
2069.9
7.165
2.8343
14.34
45.050
161.51
3-7542
1938.1
549.o6
2075-7
7.170
2.8522
14.35
45-082
161.73
3.7568
1940.8
549.82-
2081.5
7.175
2.8702
14^36
45-113
161.96
3-7594
1943-5
550.59
2087.3
7.180
2.8881
14.37
45 • 145
162.18
3.7621
1946.2
551-35
2093-1
7.185
2.9061
14.38
45.176
162.41
3.7647
1948.9
552.12
2099-0
7.190
2.9240
14.39
45.208
162.63
3.7673
1951-6
552.89
2104.8
7.195
2.9420
14.40
45-239
162.86
3.7699
1954-3
553-66
2IIO.7
7.200
2.9600
14.41
45-270
163.09
3-7725
1957-0
554-43
2II6.5
7.205
2.9780
14.42
45-302
163.31
3-7751
1959-8
555-20
2122.4
7.210
2.9960
14.43
45-333
163.54
3-7778
1962.5
555-97
2128.3
7-215
3.0141
14.44
45.365
163.77
3-7804
1965.2
556.74
2134-2
7.22-0
3-0321
14.45
45.396
163.99
3.7830
1967.9
557-51
2I40.I
7-225
3.0502
14.46
45-427
164 . 22
3.7856
1970.6
558.28
2I46.I
7-230
3.0682
14.47
45-459
164.45
3.7882
1973.4
559.o6
2152.0
7-235
3-0863
14.48
45-490
164.67
3.7909
1976.1
559-83
2158.0
7.240
3-1044
14.49
45-522
164.90
3-7935
1978 . 8
560.60
2163.9
7-245
3.1225
14.50
45-553
165.13
3.7961
1981.6
561.38
2169 9
7.250
3-i4o6
Table of the Properties of Tubes and Round Bars 453
Properties of Tubes and Round Bars (Continued)
14.50 inches
15.00 inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
I&, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
il
Circum-
ference
Area
Per foot length
Moment
Distance
from axis
Radius
la
in
section
Surface
Volume
Weight,
of
inertia,
to farth-
tion
P a
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
est fiber
squared
D
C
A
5
V
W
/
y
&
14.50
45-553
165.13
3.796i
1981.6
561.38
2169.9
7.250
13.1406
14.51
45.585
165.36
3.7987
1984.3
562.15
2175-9
7.255
13.1588
14.52
45.616
165-59
3-8013
1987.0
562.93
2181.9
7.260
13.1769
14-53
45-647
165.81
3.8039
1989.8
563-70
2187.9
7.265
I3.I95I
14-54
45.679
166.04
3.8066
1992.5
564.48
2193-9
7.270
13-2132
14-55
45.7io
166.27
3.8092
1995.2
565-25
22OO.O
7.275
13.2314
14.56
45-742
166.50
3.8118
1998.0
566.03
22O6.0
7.280
13-2496
14-57
45-773
166.73
3-8144
2000.7
566.81
2212. I
7.285
13.2678
14.58
45.804
166.96
3-8170
2003,5
567.59
2218.2
7.200
13.2860
14-59
45.836
167.19
3.8197
2006.2
568.37
2224.3
7-295
13.3043
14.60
45.867
167.42
3-8223
2009.0
569-15
2230.4
7.300
13.3225
14.61
45.899
167.64
3.8249
2011.7
569.93
2236.5
7.305
13.3408
14.62
45-930
167.87
3.8275
2014.5
570.71
2242 . 6
7.310
13.3590
14.63
45.962
168.10
3.8301
2017.3
571-49
2248 . 8
7.315
13.3773
14.64
45-993
168.33
3.8327
2020.0
572.27
2254.9
7.320
13.3956
14.65
46.024
168.56
3.8354
2O22 . 8
573-05
2261 . i
7-325
13.4139
14.66
46.056
168.79
3.8380
2025.5
573.83
2267.3
7.330
13.4322
14.67
46.087
169.02
3.8406
2028.3
574.62
2273-5
7-335
13.4506
14.68
46.119
169.26
3.8432
2031 . I
575-40
2279.7
7-340
13.4689
14.69
46.150
169.49
3.8458
2033-8
576.18
2285.9
7-345
13.4873
14.70
46.181
169.72
3.8485
2036.6
576.97
2292 . i
7-350
13.5056
14.71
46.213
169.95
3-8511
2039-4
577-75
2298.4
7-355
13-5240
14.72
46.244
170.18
3.8537
2042 . I
578.54
2304.6
7.36o
13-5424
14-73
46.276
170.41
3-8563
2044.9
579-33
2310.9
7.365
13.5608
14-74
46.307
170.64
3.8589
2047.7
580.11
2317.2
7-370
13.5792
14-75
46.338
170.87
3.8615
2050.5
580.90
2323.5
7-375
13-5977
14.76
46.370
171.10
3.8642
2053-3
581.69
2329.8
7.38o
13.6161
14-77
46.401
I7L34
3.8668
2056.0
582.48
2336.1
7.385
13.6346
14.78
46.433
I7L57
3-8694
2058.8
583.27
2342.4
7-390
13.6530
14-79
46.464
171.80
3.8720
2061 . 6
584.06
2348.8
7-395
13.6715
14.80
46.496
172.03
3.8746
2064 . 4
584 . 85
2355-1
7.400
13-6900
14.81
46.527
172.27
3.8772
2067 . 2
585.64
2361.5
7.405
13.7085
14.82
46.558
172.50
3-8799
2070.0
586.43
2367.9
7.410
13.7270
14.83
46.590
172.73
3.8825
2072.8
587.22
2374-3
7-415
13.7456
14.84
46.621
172.96
3.8851
2075.6
588.01
2380.7
7-420
13.7641
14-85
46.653
173.20
3.8877
2078 . 4
588.80
2387-1
7-425
13.7827
14.86) 46.684
173-43
3.8903
2081 . 2
589.60
2393-6
7-430
13.8012
14.87
46.715
173-66
3-8930
2084.0
590.39
2400.0
7-435
13.8198
14.88
46.747
173.90
3.8956
2086.8
591 . 19
2406.5
7-440
13-8384
14.89
46.778
174.13
3.8982
2089.6
591.98
2412.9
7-445
13.8570
14.90
46.810
174-37
3.9oo8
2092.4
592.78
2419.4
7-450
13.8756
14.91
46.841
174.60
3.9034
2095-2
593-57
2425.9
7-455
13.8943
14.92
46.873
174.83
3.9o6o
2098.O
594-37
2432.5
7.460
13 9129
14-93
46.904
175.07
3.9087
2100.8
595.16
2439-0
7.465
I3.93I6
14-94
46.935
175.30
3.9H3
2103.6
595.96
2445-5
7-470
13 9502
14-95
46.967
175-54
3.9139
2106.5
596 76
2452 . i
7-475
13-9689
14.96
46.998
175-77
3.9165
2109.3
597-56
2458 . 6
7.48o
13.9876
14-97
47.030
176.01
3.9I9I
2II2.I
598.36
2465 . 2
7.485
14.0063
14.98
47.061
176.24
3 92i8
2II4.9
599-16
2471-8
7-490
14.0250
14.99
47.092
176.48
3.9244
2II7-7
599.96
2478.4
7-495
14.0438
15-00
47.124
176.71
3.9270
2120.6
600 76
2485.1
7.500
14.0625
454 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued) J£-?8!nc!?es
15. 50 inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
.R2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
'1
Circum-
Area
Per foot length
Moment
Distance
Radius
JS
in
section
Surface
Volume
Weight,
of
to farth-
tion
Q S
inches
sq. in.
sq. ft.
cu. in.
Ibs. steel
inertia
est fiber
squared
D_
C
A
5
V
W
7
y
R*
15.00
47-124
176.71
3.9270
2120.6
600.76
2485.1
7.500
14.0625
15.01
47-155
176.95
3.9296
2123-4
601.56
2491.7
7-505
14.0813
15.02
47-187
177.19
3.9322
2126.2
602.36
2498.3
7-510
14.1000
15.03
47-218
177.42
3.9348
2I29.I
603.16
2505.0
7.515
14,1188
15.04
47-250
177-66
3-9375
2I3I.9
603.97
2511.7
7.520
14-1376
15.05
47.281
177.89
3-9401
2134-7
604.77
2518.4
7.525
14-1564
15.06
47-312
178.13
3.9427
2137-6
605.57
2525.0
7-530
14-1752
15.07
47-344
178.37
3-9453
2140.4
606.38
2531.8
7-535
14.1941
15.08
47-375
178.60
3-9479
2143-3
607.18
2538.5
7-540
14.2129
15.09
47.407
178.84
3.9506
2I46.I
607.99
2545.2
7-545
14.2318
15.10
47.438
179-08
3-9532
2148.9
608.80
2552.0
7-550
14.2506
15.11
47.469
179.32
3.9558
2I5I.8
609.60
2558.7
7-555
14-2695
15.12
47-501
179-55
3.9584
2154-6
610.41
2565.5
7.500
14.2884
15-13
47-532
179-79
3.9610
2157-5
611.22
2572.3
7.565
14-3073
15.14
47.564
180.03
3.9636
2160.3
612.03
2579-1
7-570
14.3262
I5.I5
47-595
180.27
3.9663
2163.2
612.83
2586.0
7-575
14.3452
15.16
47.627
180.50
3.9689
2I66.I
613.64
2592.8
7.58o
14.3641
15-17
47.658
180.74
3.9715
2168.9
6i4.45
2599-6
7.585
14-3831
15.18
47-689
180.98
3-9741
2I7I.8
615.26
2606.5
7-590
14.4020
15-19
47.721
181.22
3.9767
2174-6
616.07
2613.4
7-595
14.4210
15.20
47-752
181.46
3-9794
2177-5
616.89
2620.3
7.600
14.4400
15.21
47.784
181.70
3.9820
2180.4
617.70
2627.2
7.605
14-4590
15.22
47.815
181.94
3.9846
2183.2
618.51
2634.1
7.610
14.4780
15.23
47.846
182.18
3.9872
2I86.I
619.32
2641.0
7.615 .
14-4971
IS 24
47.878
182.41
3.9898
2189.0
620.14
2648.0
7.620
14 5161
15.25
47.909
182.65
3.9924
2I9I.8
620.95
2654.9
7-625
14-5352
15.26
47-941
182.89
3-9951
2194-7
621.77
2661.9
7-630
14-5542
15.27
47-972
183.13
3-9977
2197-6
622.58
2668.9
7.635
14-5733
15.28
48.004
183.37
4.0003
2200.5
623.40
2675.9
7.640
14.5924
15.29
48.035
183.61
4.0029
2203.4
624.21
2682.9
7.645
14.6115
15.30
48.066
183.85
4.0055
2206.2
625.03
2689.9
7.650
14.6306
I5.3I
48.098
184.09
4.0081
22O9 . I
625.85
2696.9
7.655
14.6498
15.32
48.129
184.33
4.0108
2212.0
626.66
2704.0
7.660
14.6689
15-33
48.161
184.58
4-0134
2214.9
627.48
2711.1
7-665
14.6881
15-34
48 . 192
184.82
4.0160
2217.8
628.30
2718.1
7-670
14.7072
15-35
48.223
185.06
4.0186
2220.7
629.12
2725.2
7-675
14.7264
15.36
48.255
185.30
4.0212
2223.6
629.94
2732.3
7.680
14.7456
15-37
48.286
185.54
4.0239
2226.5
630.76
2739-5
7-685
14.7648
15.38
48.318
185.78
4.0265
2229-4
631.58
2746.6
7.690
14.7840
15-39
48.349
186.02
4.0291
2232.3
632.40
2753-8
7.695
14-8033
15.40
48.381
186.27
4.0317
2235-2
633.23
2760.9
7,700
14.8225
I5.4I
48.412
186.51
4-0343
2238.1
634.05
2768.1
7.705
14.8418
15.42
48.443
186.75
4.0369
224I.O
634.87
2775-3
7.710
14.8610
15 43
48.475
186.09
4.0396
2243.9
635.70
2782.5
7.715
14.8803
15-44
48.506
187.23
4.0422
2246.8
636.52
2789.7
7.720
14.8996
15-45
48.538
187.48
4.0448
2249.7
637.35
2797.0
7.725
14.9189
15.46
48.569
187.72
4.0474
2252.6
638.17
2804.2
7-730
14.9382
15-47
48.600
187.96
4.0500
2255-5
639.00
2811.5
7-735
14.9576
15.48
48.632
188.21
4.0527
2258.5
639.82
2818.7
7-740
14.9769
15-49
48.663
188.45
4-0553
2261 . 4
640.65
2826.0
7-745
14.9963
15-50
48.695
188.69
4 0579
2264.3
641.48
2833.3
7 750
15.0156
Table of the Properties of Tubes and Round Bars 455
15. 50 inches
16. 00 inches
Properties of Tubes and Round Bars (Continued)
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
.ft2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
il
Circum-
Area
Per foot length
Moment
Distance
from axis
Radius
of gyra-
.11
Q'S
in
inches
section,
sq. in.
Surface
sq. ft.
Volume
cu. in.
Weight,
Ibs. steel
of
inertia
to farth-
est fiber
tion
squared
D
C
A
5
V
W
7
y
R*
15.50
48.695
188.69
4-0579
2264.3
641.48
2833.3
7-750
15.0156
15.51
48.726
188.94
4.0605
2267.2
642.30
2840.6
7-755
15.0350
15-52
48.758
189.18
4.0631
2270.2
643.13
2848.0
7.76o
15.0544
15-53
48.789
189.42
4-0657
2273.1
643.96
2855.3
7.765
15.0738
15-54
48.820
189.67
4.0684
2276.0
644.79
2862.7
7.770
15.0932
iS-55 48.852
189.91
4.0710
2278.9
645 • 62
2870.1
7-775
15.1127
15-56
48.883
190.16
4.0736
2281.9
646.45
2877.5
7.78o
15.1321
iS-57
48.915
190.40
4.0762
2284.8
647.28
2884.9
7.785
15.1516
15.58
48.946
190.64
4.0788
2287.7
648.12
2892.3
7-790
15-1710
15-59
48.977
190.89
4.0815
2290.7
648.95
2899.7
7-795
15.1905
15.60 49.009
191.13
4.0841
2293.6
649.78
2907.1
7.800
15.2100
15.61 49.040
191.38
4.0867
2296.6
650.61
2914.6
7.805
15.2295
15.62 49-072
191 . 62
4.0893
2299.5
6SI.4S
2922.1
7.810
15.2490
15.63 49.103
191.87
4.0919
2302.4
652.28
2929.6
7-815
15.2686
15.64 49-135
192.12
4-0945
2305.4
653.12
2937-1
7.820
15.2881
15.651 49-166
192.36
4.0972
2308.3
653.95
2944.6
7-825
15.3077
15-66
49.197
192.61
4.0998
2311.3
654.79
2952.1
7.830
15.3272
15.67
49.229
192.85
4 . 1024
2314.2
655.63
2959-7
7.835
15.3468
15.68
49.260
193.10
4 • 1050
2317.2
656.46
2967.3
7-840
15.3664
15.69
49-292
193-35
4 . 1076
2320.2
657.30
2974-8
7.845
15.3860
15.70
49.323
193-59
4.1103
2323.1
658.14
2982.4
7-850
15.4056
15.71
49-354
193.84
4.1129
2326.1
658.98
2990.0
7.855
15.4253
15.72
49-386
194-09
4-II55
2329.0
659-82
2997.6
7.860
15-4449
15-73
49-417
194-33
4.1181
2332.0
660.66
3005.3
7.865
15.4646
iS-74
49.449
194.58
4.1207
2335-0
661.50
3012.9
7-870
15.4842
is.75
49-480
194-83
4-1233
2337-9
662.34
3020.6
7.875
15.5039
15-76
49.512
195.08
4.1260
2340.9
663.18
3028.3
7.880
15.5236
15-77
49-543
195.32
4.1286
2343-9
664.02
3036.0
7-885
15-5433
15.78
49-574
195-57
4.I3I2
2346.8
664.86
3043.7
7.890
15.5630
iS-79
49.606
195-82
4.1338
2349-8
665.71
305L4
7.895
15.5828
15.80
49.637
196.07
4.1364
2352.8
666.55
3059.1
7.900
15.6025
15.81
49.669
196.32
4.1390
2355-8
667.39
3066.9
7.905
15-6223
15.82
49.7oo
196.56
4 • I4I7
2358.8
668.24
3074.6
7.910
15.6420
15.83
49-731
196.81
4-1443
2361 . 7
669.08
3082.4
7-915
15.6618
15.84
49.763
197.06
4.1469
2364.7
669.93
3090.2
7.920
15.6816
15.85
49-794
I97.3I
4-1495
2367.7
670.77
3098.0
7.925
15.7014
15.86
49 . 826
197.56
4.I52I
2370.7
671.62
3105.9
7-930
15.7212
15.87
49.857
197.81
4.1548
2373-7
672.47
3H3.7
7-935
I5.74H
15.88
49-888
198.06
4-1574
2376.7
673.32
3121.6
7-940
15.7609
15.89
49.920
198.31
4.1600
2379-7
674.16
3129.4
7-945
15.7808
15.90
49 951
198.56
4.1626
2382.7
675.01
3137.3
7-950
15.8006
15.91
49.983
198.81
4.1652
2385.7
675.86
3145.2
7-955
15.8205
15.92
50.014
199.06
4-1678
2388.7
676.71
3I53.I
7.960
15.8404
15.93
50.046
I99.3I
4.1705
2391 • 7
677.56
3161.1
7.965
15.8603
15.94
50.077
199.56
4.I73I
2394-7
678.41
3169.0
7-970
15.8802
j 15-95
50.108
199.81
4-1757
2397.7
679 . 26
3177.0
7-975
15.9002
15.96
50.140
200.06
4.1783
2400.7
680.12
3184.9
7.980
15.9201
15-97
50.171
200.31
4.1809
2403.7
680.97
3192.9
7.985
15 . 9401
15.98
50.203
200.56
4.1836
2406.7
681.82
3200.9
7-990
15.9600
15.99
50.234
200.81
4.1862
2409.7
682.68
3209.0
7-995
15.9800
16.00
50.265
201.06
4.1888
2412.7
683.53
3217.0
8.000
16.0000
456 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued) |6 {™*
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
J?2, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
1
jta
°:§
D
Circum-
ference
in
inches
C
Area
cross
section
sq. in.
A
Per foot length
Moment
of
inertia
/
Distance
from axis
to farth-
est fiber
y
Radius
of gyra-
tion
squared
&
Surface
sq. ft.
5
Volume
cu. in.
V
Weight,
Ibs. steel
W
16
50.265
201.06
4.1888
2412.7
683-53
3217.0
8.000
16.000
Vs
50.658
204 . 22
4.2215
2450.6
694.25
3318.7
8.063
16.251
V4
51.051
207.39
4.2542
2488.7
705.06
3422.8
8.125
16.504
%
51-444
210.60
4.2870
2527.2
715.95
3529.4
8.188
16.759
V2
51.836
213.82
4-3197
2565.9
726.92
3638.4
8.250
17.016
%
52.229
217.08
4.3524
2604.9
737-97
3749-9
8.313
17.274
%
52.622
220.35
4-3851
2644.2
749-11
3863.9
8.375
17-535
7/8
53-014
223.65
4.4179
2683.9
760.34
398o.6
8.438
17.798
17
53.407
226.98
4.45o6
2723-8
771.64
4099-8
8.500
18.063
y8
53.8oo
230.33
4.4833
2764.0
783-03
4221.7
8.563
18.329
¥4
54.192
233.71
4.5i6o
2804.5
794-50
4346.4
8.625
18.598
%
54.585
237.10
4-5488
2845.3
806.06
4473-7
8.688
18.868
y2
54.978
240.53
4.5815
2886.3
817.70
4603. z
S.75Q
19.141
%
55-371
243.98
4.6142
2927.7
829.42
4736.8
8.813
19.415
8/4
55.763
247.45
4.6469
2969.4
841.23
4872.6
8.875
19.691
%
56.156
250.95
4.6797
3011.4
853-12
50H.3
8.938
19-970
iS.'1
56.549
254.47
4.7124
3053.6
865.09
5153.0
9.000
20.250
Vs
56.941
258.02
4-7451
3096.2
877-15
5297.6
9.063
20.532
V4
57-334
261.59
4.7778
3i39.o
889.29
5445-3
9-125
20.816
8/8
57.727
265.18
4.8106
3182.2
901.51
5596.0
9.188
21.103 |
%
58.119
268.80
4.8433
3225.6
913.82
5749-9
9.250
21.391
%
58.512
272.45
4.8760
3269.4
926.21
5906.8
9.313
21.681
3/4
58.905
276.12
4.9087
3313.4
938.69
6067.0
9-375
21.973
%
59.298
279.81
4.9415
3357-7
95L24
6230.4
9.438
22.267
19
59.690
283.53
4-9742
3402.3
963.88
6397.1
9-500
22.563
Vs
60.083
287.27
5.0069
3447-3
976.61
6567.2
9.563
22.860
V4
60.476
291 .04
5.0396
3492.5
989.42
6740.5
9-625
23.160
%
60.868
294.83
5.0724
3538.0
1002.31
6917.3
9.688
23.462 |
%
61 . 261
298.65
5-I05I
3583.8
1015.28
7097.5
9-750
23.766
5/8
61.654
302.49
5.1378
3629.9
1028 . 34
7281.3
9-813
24.071
8/4
62.046
306.35
5-1705
3676.3
1041.48
7468.6
9.875
24-379
7/8
62.439
310.24
5.2033
3722.9
1054.71
7659.5
9-938
24.688
20
62.832
314 16
5-2360
3769.9
1068.02
7854-0
o.ooo
25.000
Vs
63.225
318.10
5-2687
3817.2
1081.41
8052.2
0.063
25.313
V4
63.617
322.06
5-3014
3864.7
1094.88
8254.1
0.125
25 629
8/8
64.010
326.05
5.3342
3912.6
1108.44
8459.8
0.188
25.946
V2
64.403
33o.o6
5.3669
3960.8
I 122. 08
8669.3
0.250
26.266
%
64.795
334-10
5.3996
4009.2
H35.8I
8882.7
0.313
26.587
8/4
65.188
338.16
5.4323
4058.0
IT49.62
9100.0
0.375
26.910
%
65.581
342.25
5.4^51
4107.0
1163 51
9321.3
0.438
27.235
21
65.973
346.36
5.4978
4156.3
1177.49
9546.6
10.500
27.563
Table of the Properties of Tubes and Round Bars 457
Properties of Tubes and Round Bars (Continued) laches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R*, and direct tabular values for C, S, y and V (for capacity;. For Round
Bars use all tabular values direct.
. Diam.
° in inches
Circum-
ference
in
inches
C
Area
cross
section
sq. in.
A
Per foot length
Moment
of
inertia
I
Distance
from axis
to farth-
est fiber
y
Radius
of gyra-
tion
squared
R*
Surface
sq.ft.
Volume
cu. in.
V
Weight,
Ibs. steel
W
21
i
%
65.973
66.366
66.759
67.152
346.36
350.50
354-66
358.84
5.4978
5.5305
5.5632
5.596o
4156.3
4206.0
4255.9
43o6.i
1177-49
H9I.55
1205.69
1219.92
9546.6
9775-9
10009.3
10247.0
10.500
10.563
10.625
10.688
27.563
27.892
28.223
28.556
%
%
8/4
7/8
67.544
67.937
68.330
68.722
363-05
367.28
371-54
375-83
5.6287
5.6614
5.6941
5.7269
4356.6
4407.4
4458.5
4509.9
1234.23
1248.62
1263.10
1277.66
10488.7
10734.8
10985
11240
10.750
10.813
10.875
10.938
28.891
29.228
29.566
29.907
22
Vs
y±
%
69.115
69.508
69.900
70.293
380.13
384.46
388.82
393-20
5.7596
5-792.3
5.8250
5.8578
4561 . 6
4613.6
4665.9
47i8.4
1292.30
1307.03
1321.84
1336.73
II 499
11763
12031
12303
II.OOO
11.063
11.125
11.188
30.250
30.595
30.941
31.290
%
%
SA
%
70.686
71.079
71.471
71.864
397.61
402.04
406.49
410.97
5.8905
5.9232
5-9559
5.9887
4771-3
4824.5
4877.9
4931-7
1351.71
1366.77
1381.91
1397.14
12581
12862
I3I49
13440
11.250
11.313
11.375
11.438
31.641
31.993
32.348
32.704
23
Vs
y±
%
72.257
72.649
73.042
73-435
415.48
420.00
424.56
429.13
6.0214
6.0541
6.0868
6.1196
4985.7
5040.0
5094.7
5149.6
1412.45
1427.85
1443.32
1458.88
13737
14038
14344
14655
11.500
11.563
11.625
11.688
33.063
33.423
33.785
34-149
%
%
3/4
%
73.827
74.220
74.613
75.oo6
433-74
438.36
443-01
447.69
6.1523
6.1850
6.2177
6.2505
5204.8
5260.4
53i6.2
5372.3
1474-53
1490.26
1506.07
1521.96
I497I
15292
15618
15949
11.750
11.813
n.875
n.938
34.5i6
34.884
35.254
35.626
24
i
%
75.398
75-791
76.184
76.576
452.39
457.ii
461.86
466.64
6.2832
6.3159
6.3486
6.3814
5428.7
5485.4
5542.4
5599-6
1537-94
1554-00
1570.15
1586.38
16286
16628
16975
17328
I2.OOO
12.063
12.125
12.188
36.000
36.376
36.754
37.134
&
%
8/4
%
76.969
77.362
77-754
78.147
471-44
476.26
481.11
485.98
6.4141
6.4468
6.4795
6.5123
5657.2
57I5.I
5773-3
583L7
1602.69
1619.09
1635.57
1652.13
17686
18050
18 419
18794
12.250
12.313
12.375
12.438
37.516
37.899
38.285
38.673
25
y8
%
%
78.540
78.933
79.325
79.718
490.87
495.79
500.74
505.71
6.5450
6.5777
6.6104
6.6432
5890.5
5949.5
6008.9
6068.5
1668.77
1685.50
1702.32
1719.21
19 175
19561
19953
20351
12.500
12.563
12.625
12.688
39.063
39-454
39.848
40.243
y2
%
8/4
! 7/8
80. in
80.503
80.896
81 . 289
5I0.7I
515.72
520.77
525.84
6.6759
6.7086
6.7413
6.7741
6128.5
6188.7
6249.2
6310.0
1736.19
1753.26
1770.40
1787.63
20755
21 165
21 581
22003
12.750
12.813
12.875
12.938
40.641
41.040
41.441
41.845
!26
81.681
530.93
6.8068
637L2
1804.95
22432:
13.000
42.250
458 Table of the Properties of Tubes and Round Bars
Properties of Tubes and Round Bars (Continued) 2? inches
ol incnes
For Tubes use differences for A , W, I and V (for volume of wall only) , sum for
]&, and direct tabular values for C, S, y and V (for capacity). For Round
Bars use all tabular values direct.
il
Circum-
Area
Per foot length
Moment
Distance
1
Radius
SJ
in
section
Surface
Volume
Weight,
of
to farth-
tion
.s
inches
sq. in.
sq. ft.
cu. in.
Ibs. stee
inertia
est fiber
squared
D
C
A
5
V
W
1
y
R2
26
81.681
530-93
6.8068
6371.2
1804.95
22432
13.000
42.250
%
82.074
536-05
6.8395
6432.6
1822.34
22866
- 13-063
42.657
y*
82.467
54I-I9
6.8722
6494.3
1839.82
23307
13-125
43.o66
82.860
546.35
6.9050
6556.3
1857.39
23754
13.188
43.478
Va
83.252
551-55
6.9377
6618. 6
1875.04
24208
13.250
43-891
%
83.645
556.76
6.9704
6681 . i
1892.77
24668
13.313
44.306
8/4
84.038
562.00
7-0031
6744.0
1910.58
25 134
13 375
44.723
84.430
567-27
7-0359
6807.2
1928.48
25607
13.438
45.142
27
84.823
572.56
7.0686
6870.7
1946.46
26087
13.500
45.563
Vs
85.216
577.87
7.1013
6934.4
1964.52
26574
13.563
45.985
85.608
583-21
7-1340
6998.5
1982 . 67
27067
13.625
46.410
%
86.001
588.57
7.1668
7062.8
2000.90
27567
13.688
46.837
Va
86.394
593.96
7-1995
7127.5
2019.22
28074
13.750
47.266
%
86.786
599-37
7.2322
7192.4
2037.62
28588
13-813
47.696
%
87.179
604.81
7.2649
7257.7
2056 . 10
29 109
13-875
48.129
%
87.572
610.27
7.2977
7323.2
2074 . 66
29637
13.938
48.563
28
87.965
615.75
7.3304
7389.0
2093-31
30172
14.000
49.000
Vs
88.357
621 . 26
7.3631
7455-1
2112.04
30714
14.063
49.438
88.750
626.80
7.3958
7521.6
2130.86
31 264
14.125
49.879
%
89.143
632.36
7.4286
7588.3
2149.76
31 821
14.188
50.321
Va
89-535
637.94
7.4613
7655.3
2168 . 74
32385
14-250
50.766
89.928
643.55
7.4940
7722.6
2187.81
32957
14.313
51.212
%
90.321
649.18
7.5267
7790.2
2206 . 95
33537
14-375
51.660
90.713
654.84
7-5595
7858.1
2226.19
34 124
14.438
52.110
29
91 . 106
660.52
7-5922
7926.2
2245.50
34719
14.500
52.563
91.499
666.23
7.6249
7994-7
2264.90
35321
14-563
53-017
•Vi
91.892
671.96
7.6576
8063.5
2284.39
35931
14-625
53-473
%
92.284
677.71
7.6904
8132.6
2303.95
36550
14.688
53-931
Va
92.677
683.49
7.7231
8201 . 9
2323.60
37 176
14.750
54-391
%
93-070
689.30
7.7558
8271.6
2343-34
378io
14-813
54-853
%
93.462
695.13
7.7885
834L5
2363.15
38452
14-875
55.3i6
%
93-855
700.98
7.8213
8411.8
2383.05
39102
14.938
55.782
30
94.248
706.86
7.8540
8482.3
2403.04
3976i
15.000
56.250
Vs
94.640
712.76
7.8867
8553-1
2423.10
40428
15.063
56.720
95-033
718.69
7.9194
8624.3
2443-25
41 103
15.125
57.I9I
8/8
95.426
724-64
7-9522
8695.7
2463.49
41786
15.188
57.665
Va
95.819
730.62
7.9849
8767.4
2483.80
42479
15.250
58.141
%
96.211
736.62
8.0176
8839.4
2504.21
43 179
15.313
58.618
96.604
742.64
8.0503
8911.7
2524-69
43888
15-375
59-098
%
96.997
748.69
8.0831
8984.3
2545.26
44606
15.438
59-579
31
97.389
754-77
8.1158
9057.2
2565.91
45333
15.500
60.063
Table of the Properties of Tubes and Round Bars 459
Properties of Tubes and Round Bars (Concluded) 31 inches
36 inches
For Tubes use differences for A, W, I and V (for volume of wall only), sum for
R2, and direct tabular values for C, S, y and V (for capacity) . For Round
Bars use all tabular values direct.
P
Circum
Area
Per foot length
Momen
of
inertia
I
Distance
from axis
to farth-
est fiber
y
Radius
of gyra-
tion
squared
•S.g
b
31
%
H
8/8
in
inches
C
section
sq. in.
A
Surface
sq. ft.
5
Volume
cu. in.
V
Weight
Ibs. stee
W
97.389
97.782
98.175
98.567
754-77
760.87
766.99
773-14
8.1158
8.1485
8.1812
8.2140
9057.2
9130.4
9203.9
9277.7
2565.91
2586.64
2607.46
2628.36
45333
46069
46813
47567
15.500
15.563
15.625
15.688
60.063
60.548
61.035
61.524
%
98.960
99-353
99.746
100.138
779-31
785.51
791 . 73
797.98
8.2467
8.2794
8.3121
8.3449
9351 . 7
9426.1
9500.8
9575-7
2649.35
2670.42
2691.57
2712.80
48329
49 ioi
49882
50672
15.750
15.813
15.875
15.938
62.016
62.509
63.004
63.501
32 ^
8/8
100.531
100.924
101.316
ioi . 709
804 . 25
810.54
816.86
823.21
8.3776
8.4103
8.4430
8.4758
9651.0
9726.5
9802.4
9878.5
2734.12
2755.52
2777.01
2798.58
51 472
52281
53099
53927
16.000
16.063
16.125
16.188
64.000
64.501
65.004
65.509
1/2
%
102.102
102 . 494
102.887
103.280
829.58
835.97
842.39
848.83
8.5085
8.5412
8-5739
8.6067
9954-9
10031 . 6
10108.7
10186.0
2820.23
2841.97
2863.78
2885.69
54765
55612
56470
57337
16.250
16.313
16.375
16.438
66.016
66.524
67.035
67.548
33 '.
v!
103.673
104.065
104.458
104.851
855.30
861.79
868.31
874.85
8.6394
8.6721
8.7048
8.7376
10263.6
10341.5
10419.7
10498 . 2
2907.67
2929.74
2951.90
2974.13
58214
59 ioi
59998
60905
16.500
16.563
16.625
16.688
68.063
68.579
69.098
69.618
1/2
%
7/8
105.243
105 . 636
106.029
106.421
881.41
888.00
894 . 62
901.26
8.7703
8.8030
8.8357
8.8685
10577.0
10656.0
10735-4
I08I5.I
2996.45
3018.86
3041.34
3063.91
61 823
62751
63689
64638
16.750
16.813
16.875
16.938
70.141
70.665
71.191
71.720
34 /
8
106.814
107 . 207
107 . 600
107.992
907.92
914.61
921.32
928.06
8.9012
8.9339
8.9666
8.9994
10895.0
10975-3
II055-9
III36.7
3086.57
3109.30
3132.12
3155.03
65597
66567
67548
68539
17.000
17-063
17.125
17.188
72.250
72.782
73.316
73-853
%
7/8
108.385
108.778
109.170
109.563
934.82
941-61
948.42
955-25
9.0321
9.0648
9-0975
9.1303
II2I7.8
II299.3
1I38I.O
H463.0
3178.01
3201.09
3224.24
3247.48
69542
70555
7i58o
72615
17.250
I7-3I3
17-375
17.438
74-391
74-931
75-473
76.017
135
Vs
1/4
8/8
109.956
110.348
110.741
III. 134
962.11
969.00
975-91
982.84
9.1630
9-1957
9.2284
9.2612
II545-4
II628.0
II7I0.9
II794-I
3270.80
3294.20
3317.69
3341.26
73662
74720
75789
76870
17.500
17.563
17.625
17.688
76.563
77-110
77-660
78.212
%
7/8
III.527
111.919
112.312
112.705
989.80
996.78
003.79
010.82
9-2939
9.3266
9-3593
9-3921
II877.6
II96I.4
12045.5
I2I29.8
3364.92
3388.66
3412.48
3436.38
77962
79066
80182
81309
17.750
17.813
17.875
17.938
78.766
79-321
79.879
80.438
36
"3.097
017.88
9.4248
I22I4.5
3460.37
82448
18.000
81.000
460
The Metric System
THE METRIC SYSTEM
(Extract from tables of equivalents published by the Department of Commerce
and Labor, Bureau of Standards.)
The fundamental unit of the metric system is the METER (the unit of
length).
From this the units of mass (GRAM) and capacity (LITER) are derived.
All other units are the decimal subdivisions or multiples of these.
These three units are simply related, so that for all practical purposes
the volume of one kilogram of water (one liter) is equal to one cubic
decimeter.
Prefixes
Meaning
Units
Milll-
=one thousandth .001
IOOO
Centi-
=one hundredth — .01
IOO
METER for length
Deci-
=one tenth . i
10
unit
=one i.
GRAM for mass
Deka-
10
=ten 10.
i
Hecto-
=one hundred — 100.
i
LITER for capacity
Kilo-
, IOOO
= one thousand 1000.
i
The metric terms are formed by combining the words "Meter,"
'Gram" and "Liter" with the six numerical prefixes.
Length
10 milli-meters (mm) = i centi-meter (cm).
10 centi-meters = i deci-meter (dm).
10 deci-meters = i METER (about 40 inches) (m).
10 meters = i deka-meter (dkm).
10 deka-meters = i hecto-meter (hm).
10 hecto-meters = i kilo-meter (about % mile) (km).
Mass
10 milli-grams (mg) = i centi-gram (eg).
10 centi-grams = i deci-gram (dg).
10 deci-grams = i GRAM (about 15 grains) (g).
10 grams = i deka-gram (dkg).
10 deka-grams = i hecto-gram (hg).
10 hecto-grams = i kilo-gram (about 2 pounds) (kg).
Capacity
10 milli-liters (ml) = i centi-liter (cl).
10 centi-liters = i deci-liter (dl).
10 deci-liters = i liter (about i quart) (1).
10 liters = i deka-liter (dkl).
10 deka-liters = i hecto-liter (about a barrel) (hi).
10 hecto-liters = i kilo-liter (kl).
Equivalents 461
The square and cubic units are the squares and cubes of the linear
units.
The ordinary unit of land area is the Hectare (about 2^2 acres).
For ordinary mental comparison it is convenient to know the approxi-
mate relations; e.g., i meter = 40 inches; 3 decimeters = i foot; i deci-
meter = 4 inches; i liter = i liquid quart; i kilogram = 2^ pounds;
30 grams = i avoirdupois ounce; i metric ton = i gross ton (see
tables).
Equivalents
All lengths, areas and cubic measures in the following tables are
derived from the international meter, the legal equivalent being i
METER = 39.37 INCHES (law of July 28, 1866). In 1893 the United
States Office of Standard Weights and Measures was authorized to derive
the yard from the meter, using for the purpose the relation legalized in
1866, i YARD EQUALS METER. The customary weights are like-
3937
wise referred to the kilogram. (Executive order approved April 5,
1893.) This action fixed the values, inasmuch as the reference standards
are as perfect and unalterable as it is possible for human skill to make
them.
All capacities are based on the practical equivalent i cubic decimeter
equals i liter. The decimeter is equal to 3.937 inches in accordance
with the legal equivalent of the meter given above. The gallon referred
to in the tables is the United States gallon of 231 cubic inches. The
bushel is the United States bushel of 2150.42 cubic inches. There
units must not be confused with the British units of the same name,
which differ from those used in the United States. The British gallon
is approximately 20 per cent larger, and the British bushel 3 per cent
larger, than the corresponding units used in this country.
The customary weights derived from the international kilogram are
based on the value i avoirdupois pound = 453.5924277 grams. This
value is carried out farther than that given in the law, but is in accord
with the latter as far as it is there given. The value of the troy pound
is based upon the relation just mentioned, and also the equivalent
7000
avoirdupois pound equals i troy pound.
Length
Centimeter = 0.3937 inch.
Meter =3.28 feet.
Meter = 1.094 yards.
Kilometer = 0.621 statute mile.
Kilometer = 0.5396 nautical mile.
Inch = 2.540 centimeters.
Foot = 0.305 meter.
Yard = 0.914 meter.
Statute mile = 1.61 kilometers.
Nautical mile = 1.853 kilometers.
462
Equivalents
Square centimeter
Square meter
Square meter
Hectare
Square kilometer
Square inch
Square foot
Square yard
Acre
Square mile
Cubic centimeter
Cubic meter
Cubic meter
Cubic inch
Cubic foot
Cubic yard
Milliliter
Milliliter
Liter
Liter
Liter
Dekaliter
Hectoliter
U. S. liquid ounce
U. S. apothecaries' dram
U. S. liquid quart
U. S. dry quart
U. S. liquid gallon
U. S. peck
U. S. bushel
Gram
Gram
Gram
Gram
Gram
Kilogram
Kilogram
Metric ton
Metric ton
Grain
U. S. apothecaries' scruple
U. S. apothecaries' dram
Avoirdupois ounce
Troy ounce
Avoirdupois pound
Troy pound
Gross or long ton
Short or net ton
Area
= 0.155 square inch.
= 10.76 square feet.
= 1.196 square yards.
= 2.47 acres.
= 0.386 square mile.
= 6.45 square centimeters.
= 0.0929 square meter.
= 0.836 square meter.
= 0.405 hectare.
= 2.59 square kilometers.
Volume
= 0.0610 cubic inch.
= 35-3 cubic feet.
= 1.308 cubic yards.
= 16.39 cubic centimeters.
= 0.0283 cubic meter.
= 0.765 cubic meter.
Capacity
= 0.0338 U. S. liquid ounce.
= 0.2705 U. S. apothecaries' dram.
= 1.057 U. S. liquid quarts.
= 0.2642 U. S. liquid gallon.
= 0.908 U. S. dry quart.
= 1.135 U. S. pecks.
= 2.838 U. S. bushels.
= 29.57 milliliters.
= 3.70 milliliters.
= 0.946 liter.
= i.ioi liters.
= 3.785 liters.
= 0.881 dekaliter.
= 0.3524 hectoliter.
Weight
= 15.43 grains.
= 0.772 U. S. apothecaries' scruple.
= 0.2572 U. S. apothecaries' dram.
= 0-0353 avoirdupois ounce.
= 0.03215 troy ounce.
= 2.205 avoirdupois pounds.
= 2.679 troy pounds.
= 0.984 gross or long ton.
= 1. 102 short or net tons.
= 0.0648 gram.
= 1.296 grams.
= 3-89 grams.
= 28.35 grams.
= 31.10 grams.
= 0.4536 kilogram.
= 0.373 kilogram.
= i .016 metric tons.
= 0.907 metric ton.
Comparison of
Customary and
Metric Units
463
Comparison of Customary and Metric Units from i to 10
Lengths
Inches meters
I»'hes ££1.
Feet Meters
0
0
03937= i
07874= 2
0
0
3937= I
7874= 2
i
2
=0
=o
304801
609601
0
n8n
= 3
I
= 2.54001
3
= 0
914402
0
15748
= 4
I
1811= 3
3-
28083= I
0
19685
= 5
I
5748= 4
4
= 1
219202
o
23622
= 6
I
9685= 5
5
= 1
524003
o
27559
= 7
2
= 5 08001
6
= 1
828804
0.31496
= 8
2
3622= 6
6.
56167=2
0
35433
= 9
2
7559= 7
7
= 2
133604
I
= 25.4001
3
= 7.62002
8
= 2
438405
2
= 50.8001
3
1496= 8
9
= 2
743205
3
= 76.2002
3
5433= 9
9-
84250 = 3
4
= 101.6002
4
= 10 16002
13-
12333=4
5
= 127.0003
5
= 12.70003
16.
40417 = 5
6
= 152.4003
6
= 15 24003
19.
68500=6
7
= 177.8004
7
= 17-78004
22.
96583=7
8
= 203-2004
8
= 20.32004
26.
24667=8
9
= 228.6005
9
= 22.86005
.9.
52750=9
u. s. Meters
U.S.
Kilo-
miles
meters
I
= 0
914402
0.62137=
i
I
.093611 = 1
i =
i . 60935
_ t '2
= 1
828804
1.24274=
2
L *•_*• j
.187222=2
1.86411 =
3
:i;03
= 2
743205
2
3.21869
3
.280833=3
2.48548 =
4
4
= 3
657607
3
4 82804
4
.374444 = 4
3-10685 =
5
5
= 4
572009
3.72822 =
6
5
.468056 = 5
4
6.43739
6
= 5
486411
4 34959 =
7
6
.561667=6
4. 97096 =*
8
7
=6.400813
5 =
8.04674
i
7
.655278=7
5.59233=
9
8
= 7
3I52I5
6
9 . 65608
8
.748889 = 8
7 =
11.26543
9
= 8
229616
8
12.87478
f
.842500=9
9 =
14.48412
464 Comparison of Customary and Metric Units
Comparison of Customary and Metric Units from i to 10 (Continued)
Areas
Square S^e
->- meter;
Square Squf.re
-h- meters
Square Square
feet meters
0.00155= I
0.003IO= 2
o 00465= 3
0.00620= 4
0.1550= i
O.3IOO= 2
0.4650= 3
0.6200= 4
i =0.09290
2 =0.18581
3 =0.27871
4 =0.37161
o.oo775= 5
0.00930= 6
0.01085= 7
0.01240= 8
o-oi395= 9
0.7750= 5
0.9300= 6
i = 6.452
1.0850= 7
1.2400= 8
5 =0.46452
6 =0.55742
7 =0.65032
8 =0.74323
9 =0.83613
I = 645.16
2 =1290.33
3 =1935-49
4 =2580.65
1.3950= 9
2 =12.903
3 =19-355
4 =25.807
10 764=1
21 528 = 2
32 292=3
43 055 = 4
5 =3225.81
6 =3870.98
7 =4516.14
8 =5161.30
9 =5806.46
5 =32.258
6 =38.710
7 =45.i6i
8 =51.613
9 =58.065
53 8i9=5
64 583=6
75 347 = 7
86 m = 8
96 875=9
Square Square
yards meters
•as 3E
Acres Hectares
i =0.8361
1.1960=1
2 =1.6723
2.3920=2
0.3861= I
0.7722= 2
I = 2.5900
1.1583= 3
i =0.4047
2 =0.8094
2.471 = 1
3 =1.2141
3 =2.5084
3.588o=3
4 =3-3445
4-7839 = 4
5 =4.1807
1.5444= 4
1.9305= 5
2 = 5.1800
2.3166= 6
2.7027= 7
4 =1.6187
4.942=2
5 =2.0234
6 =2.4281
7 =2.8328
5 9799=5
6 =5.0168
7 =5.8529
7 1759=6
3 = 7.7700
3.0888= 8
3.4749= 9
4 =10.3600
7-413=3
8 =3-2375
9 =3.6422
9-884=4
8 =6.6890
8.3719=7
9 =7-5252
9-5679=8
10 7639=9
5 =12.9500
6 =15.5400
7 =18.1300
8 =20.7200
9 =23.3100
12-355=5
14.826=6
17.297=7
19.768=8
22.239=9
Comparison of Customary and Metric Units 465
Comparison of Customary and Metric Units from i to 10 (Continued)
Volumes
Cubic Cubic
'«*« Tetlrs
Cubic ^
-hes rSrs
Cubic Cubic
feet meters
Cubic Cubic
yards meters
O.O0006l = I
0-000122 = 2
0' 000183 =3
0.000244=4
0.0610= i
O.I22O= 2
0.1831= 3
0.2441= 4
i =0.02832
2 =0.05663
3 =0.08495
4 =0.11327
i =0.7645
1.3079=1
2 =1.5291
2.6159=2
0.000305=5
0.000366=6
0.000427=7
0.000488=8
o.ooo549=9
0.3051= 5
0.3661= 6
0.4272= 7
0.4882= 8
0.5492= 9
5 =0.14159
6 =0.16990
7 =0.19822
8 =0.22654
9 =0.25485
3 =2.2937
3-9238=3
4 =3-0582
5 =3.8228
5.2318=4
I = 16387-2
2 = 32774-3
3 =49 161.5
4 = 65548.6
I = 16.3872
2 = 32.7743
3 = 49-1615
4 = 65-5486
35-314 = 1
70.629=2
105-943=3
141-258=4
6 =4.5874
6.5397=5
7 =5.3519
7.8477=6
5 = 81935-8
6 =98 323.0
7 =114710.1
8 =131097-3
9 =147484-5
5 = 81.9358
6 = 98.3230
7 =114.7101
8 =131.0973
9 =147-4845
176.572 = 5
211.887=6
247-201 = 7
282.516=8
317-830=9
8 ,=6.1165
9 =6.8810
9.1556=7
10.4635=8
11.7715=9
466 Comparison of
Customary and Metric Units
Comparison of Customary and Metric Units from i to 10 (Continued)
Capacities
F' Sj Milliliters
liqmd (cc.)
ounces
drams ^°
U. S. M'lniters
apothecaries' / %
scruples
0.03381= i
0.2705= i
0.8115= i
0.06763= 2
0.5410= 2
i = 1.2322
0.10144= 3
0.8115= 3
1.6231= 2
0.13526= 4
I = 3.6967
2 = 2.4645
' ' 1
0.16907= 5
1.0820= 4
2.4346= 3
0.20288= 6
1.3525= 5
3 = 3.6967
0.23670= 7
1.6231 = 6
3.2461= 4
0.27051= 8
1.8936= 7
4 = 4.9290
0.30432= 9
2 = 7-3934
4-0577= 5
I = 29.574
2.1641= 8
4.8692= 6
2 = 59-147
2.4346= 9
5 = 6.1612
3 = 88.721
3 =11.0901
5.6807= 7
4 =118.295
4 =14.7869
6 = 7-3934
5 =147-869
5 =18.4836
6.4923= 8
6 = 177 . 442
6 =22.1803
7 = 8.6257
7 =207.016
7 =25.8770
7.3038= 9
8 =236.590
8 =29.5737
8 = 9-8579
9 =266.163
9 =33.2704
9 =11.0901
U.S.
U.S.
liquid Liters
liquid Liters
quarts
gallons
I =0.94636
0.26417= i
1.05668=1
0.52834= 2
2 =1.89272
0.79251= 3
2.11336=2
i = 3.78543
3 =2.83908
1.05668= 4
3.17005=3
1.32085= 5
4 =3.78543
1.58502= 6
4.22673 = 4
1.84919= 7
5 =4-73179
2 = 7.57087
5.28341=5
2.11336= 8
6 =5.67815
2.37753= 9
6.34009=6
3 =11.35630
7 =6.62451
4 =15.14174
7 39677 = 7
5 =18.92717
8 =7.57o88
6 =22.71261
8.45345=8
7 =26.49804
9 =8.51723
8 =30.28348
9.51014=9
9 =34-06891
Comparison of
Customary and
Metric Units 467
Comparison of Customary and Metric Units from i to 10 (Continued)
Capacities (Concluded)
- UqUSarr "ters
pUecks Liters
U. S. Deka-
pecks liters
0.908l = I
0
H33i= i
i =0.8810
I =1.1012
0
22702= 2
i.i35i = i
I.8l62 = 2
0.34053= 3
2 =1.7620
2 =2.2025
0
45404= 4
2.2702=2
2.7242=3
0
56755= 5
3 =2.6429
3 =3.3037
o
68106= 6
3.4053=3
3.6323=4
0
79457= 7
4 =3.5239
4 =4.4049
0
90808= 8
4.5404=4
4.5404=5
I
= 8.80982
5 =4.4049
5 =5.5o6i
I
02157= 9
5.6755=5
5.4485=6
2
= 17.61964
6 =5.2859
6 =6.6074
3
= 26.42946
6.8106=6
6.3565 = 7
4
= 35.23928
7 =6.1669
7 =7.7o86
5
= 44.04910
7-9457 = 7
7.2646=8
6
= 52.85892
8 =7-0479
8 =8.8098
7
=61.66874
9 =7-9288
8.1727=9
8
= 70.47856
9.0808=8
9 =9.9110
9
= 79-28838
10.2159=9
U. S. Hecto-
bushels liters
KU'A Hectoliters
P™P- hectare
i =0.35239
i =0.87078
2 =0.70479
1.14840=1
2.83774=1
2 =1.74156
3 =1.05718
2.29680 = 2
4 =1.40957
3 =2.61233
5 = I . 76196
3.44519=3
5.67548=2
4 =3.48311
6 =2.11436
4-59359 = 4
7 =2.46675
5 =4.35389
8 =2.81914
5.74199=5
8.51323=3
6 =5.22467
9 =3.17154
6.89039=6
11.35097=4
7 =6.09545
14.18871=5
8 =6.96622
17.02645=6
8.03879=7
19.86420=7
9 =7.83700
22.70194 = 8
9.18719=8
25.53968=9
io.33558=9
468 Comparison of
Customary and Metric Units
Comparison of Customary and Metric Units from i to 10 (Concluded)
Masses
Grains Grams
i^ Grams
£%. Grams
i =0.06480
2 =0.12960
3 =0.19440
4 =0.25920
0.03527= i
0.07O55= 2
0.10582= 3
0.14110= 4
0.03215= I
0.06430= 2
0.09645= 3
0.12860= 4
5 =0.32399
6 =0.38879
7 =0.45359
8 =0.51839
9 - =0.58319
0.17637= 5
0.21164= 6
0.24692= 7
0.28219= 8
o.3i747= 9
0.16075= 5
0.19290= 6
0.22506= 7
0.25721= 8
0.28936= 9
IS 4324=1
30.8647 = 2
46.2971=3
61.7294=4
I = 28.3495
2 = 56.6991
3 = 85.0486
4 =H3.398l
I =31
2 =62
3 =93
4 =124
10348
20696
31044
41392
77-1618=5
92.5941 = 6
108.0265 = 7
123.4589 = 8
138.8912=9
5 =141.7476
6 =170.0972
7 =198.4467
8 =226.7962
9 =255.1457
5 =155.51740
6 =186.62088
7 =217.72437
8 =248.82785
9 =279.93133
Avoirdupois Kilo-
pounds grams
Troy Kilo-
pounds grams
i =0.45359
2 =0.90718
2.20462 = 1
3 =1.36078
i =0.37324
2 =0.74648
2.67923=1
3 =1.11973
4 =i.8i437
4.40924=2
5 =2.26796
6 =2.72155
6.61387=3
4 =1.49297
5 =1.86621
5.35846=2
6 =2.23945
7 = 2 . 61269
7 =3.17515
8 =3.62874
8.81849=4
9 =4.08233
8 =2.98593
8 03769 = 3
9 =3 359i8
10.71691=4
11.02311=5
13.22773=6
15.43236=7
17.63698=8
19.84160=9
13.39614=5
16 07537=6
18.75460=7
21.43383 = 8
24.11306=9
Lengths — Millimeters to Decimals of an Inch 469
Lengths — Hundredths of an Inch to Millimeters
(From i to 100 hundredths.)
Hun-
dredths of
an inch
o
I
2
3
4
10
20
30
40
50
60
70
80
90
0
2.540
5.080
7.620
10.160
12.700
15-240
17.780
20.320
22.860
.254
2.794
5-334
7.874
10.414
12.954
15-494
18.034
20.574
23.114
.508
3.048
5-588
8.128
10.668
13.208
15.748
18.288
20.828
23.368
.762
3.302
5.842
8.382
10.922
13.462
16.002
18.542
21.082
23.622
1.016
3.556
6.096
8.636
11.176
13.716
16.256
18.796
21.336
23.876
Hun-
dredths of
an inch
5
6
7
8
9
10
20
30
40
I
70
80
90
1.270
3.8io
6.350
8.890
11.430
13-970
16.510
19.050
21.590
24.130
i 524
4.064
6.604
9.144
11.684
14.224
16.764
19 304
21.844
24.384
1.778
4.318
6.858
9.398
11.938
14.478
17.018
19-558
22.098
24.638
2.032
4.572
7. 112
9.652
12.192
14.732
17.272
19.812
22.352
24.892
2.286
4.826
7.366
9.9o6
12.446
14.986
17-526
20.066
22.606
25.146
Lengths — Millimeters to Decimals of an Inch
(From i to 100 units.)
Milli-
meters
0
i
2
3
4
10
20
3o
40
So
60
70
80
90
0
•39370
. 78740
1.18110
i.5748o
1.96850
2.36220
2.75590
3.i496o
3 54330
.03937
.43307
.82677
1.22047
1.61417
2.00787
2.40157
2.79527
3-18897
3.58267
.07874
•47244
.86614
1.25984
1.65354
2.04724
2.44094
2.83464
3.22834
3 . 62204
.11811
.51181
.90551
I 29921
I . 69291
2.08661
2.48031
2.87401
3.26771
3.66141
.15748
.55118
.94488
1.33858
1.73228
2.12598
2.51968
2.91338
3.30708
3.70078
Milli-
meters
5
6
7
8
9
10
20
30
40
So
60
70
80
90
.19685
.59055
.98425
1-37795
I.77I65
2.16535
2.55905
2.95275
3.34645
3.74015
. 23622
.62992
1.02362
I.4I732
1.81102
2.20472
2.59842
2.99212
3.38582
3-77952
.27559
.66929
1.06299
1.45669
1.85039
2.24409
2.63779
3.03149
3.42519
3.81889
.31496
.70866
1.10236
1.49606
1.88976
2. 28346
2.67716
3.07086
3-46456
3.85826
•35433
.74803
I.I4I73
1-53543
I.929I3
2.32283
2.71653
3-H023
3 50393
3.89763
470 Lengths — Inches and Millimeters
Lengths — Inches and Millimeters. — Equivalents of Decimal and
Common Fractions of an Inch in Millimeters
(From %4 to i inch.)
V2's
V4'S
8ths
i6ths
32nds
64ths
Milli-
meters
Decimals
of an inch
i
2
3
4
5
6
7
8
9
10
ii
12
13
14
15
16
17
18
19
20
21
22
23
24
25
26
27
28
29
30
31
32
= .397
= .794
= 1.191
= 1.588
= 1.984
= 2.381
= 2.778
= 3-175
= 3-572
= 3.969
= 4.366
= 4.763
= 5-159
= 5-556
= 5-953
= 6.350
= 6.747
= 7.144
= 7-541
= 7-938
= 8.334
= 8.731
= 9.128
= 9.525
= 9-922
= 10.319
= 10.716
= II.H3
= 11-509
= 11.906
= 12.303
= 12.700
015625
03125
046875
.0625
I
.078125
•09375
• 109375
.1250
. 140625
- 15625
I7I875
1875
.203125
.21875
• 234375
.2500
265625
. 28125
.296875
.3125
328125
34375
.359375
3750
.390625
.40625
421875
-4375
453125
.46875
.484375
.5
i
i
2
3
i
2
4
5
3
6
7
I
2
4
8
9
5
10
ii
3
6
12
13
7
14
IS
i
2
4
8
16
i inch = .02540 meter. 4 inches = . 10160 meter.
2 inches == .05080 meter. 5 inches = . 12700 meter.
3 inches = .07620 meter. 6 inches = .15240 meter.
Lengths — Inches and Millimeters 471
Lengths — Inches and Millimeters. — Equivalents of Decimal and
Common Fractions of an Inch in Millimeters (Concluded)
(From %£ to i inch.)
Inch
w*
tt's
8ths
i6ths
32nds
64ths
Milli-
meters
Decimals
of an inch
33
34
35
36
37
38
39
40
41
42
43
44
45
46
47
48
49
50
51
52
53
54
55
56
57
58
59
60
61
62
63
64
= 13.097
= 13-494
= 13.891
= 14.288
= 14.684
= 15.081
= 15.478
= 15.875
= 16.272
= 16.669
= 17.066
= 17.463
= 17.859
= 18.256
= 18.653
= 19.050
= 19.447
= 19.844
= 20.241
= 20.638
= 21.034
= 21.431
= 21.828
= 22.225
= 22.622
= 23.019
= 23.416
= 23.813
= 24.209
= 24.606
= 25.003
= 2^.400
.515625
. 53125
.546875
.5625
- 578125
•59375
.609375
.625
.640625
.65625
.671875
.6875
.703125
.71875
.734375
• 75
.765625
.78125
.796875
.8125
.828125
.84375
.859375
.875
.890625
.90625
.921875
• 9375
.953125
.96875
.984375
1. 000
17
'"is"
9
19
5
10
20
21
ii
22
23
3
6
12
24
25
13
26
27
7
14
28
29
IS
30
31
i
2
4
8
16
32
7 inches = . 17780 meter. 10 inches = . 25400 meter.
8 inches = . 20320 meter. 1 1 inches = . 27940 meter.
9 inches = .22860 meter. 12 inches = .30480 meter.
472 Comparison of Tons and Pounds
Comparison of the Various Tons and Pounds in Use in the
United States
(From i to 10 units.)
Long tons
Short
tons
Metric
tons
Kilograms
Avoirdupois
pounds
Troy pounds
.00036735
.00041143
.00037324
.37324
.822857
i
.00044643
.00050000
.00045359
.45359
i
1.21528
.00073469
.00082286
.00074648
.74648
1.64571
2
.00089286
.00100000
.00090718
.90718
2
2.43056
.00098421
.00110231
.00100000
2.20462
2.67923
.00110204
.00123429
.00111973
•I 1973
2.46857
3
.00133929
.00150000
.00136078
.36078
3
3.64583
.00146939
.00164571
.00149297
.49297
3.29143
4
.00178571
.00200000
.00181437
.81437
4
4.86111
.00183673
.00205714
.00186621
.86621
4.11429
5
.00196841
.00220462
.00200000
2
4.40924
5.35846
.00220408
.00246857
.00223945
2.23945
4.93714
6
.00223214
.00250000
.00226796
2.26796
5
6.07639
.00257143
.00288000
.00261269
2 . 61269
5.76000
7
.00267857
.00300000
.00272155
2.72155
6
7.29167
.00293878
.00329143
.00298593
2.98593
6.58286
8
.00295262
.00330693
.00300000
3
6.61387
8.03769
.00312500
.00350000
.00317515
3.I75I5
7
8.50694
.00330612
.00370286
.00335918
3.35918
7.40571
9
.00357143
.00400000
.00362874
3.62874
8
9.72222
.00393683
.00440924
.00400000
4
8.81849
10.71691
.00401786
.00450000
.00408233
4.08233
9
10.93750
.00492103
.00551156
.00500000
5
11.0231
13.39614
.00590524
.00661387
.00600000
6
13.2277
16.07537
.00688944
.00771618
.00700000
7
15.4324
18.75460
.00787365
.00881849
.00800000
8
17.6370
21.43383
.00885786
.00992080
.00900000
9
19.8416
24.11306
.89287
i
.90718
907.18
2 OOO.OO
2430.56
.98421
i . 10231
I OOO.OO
2 204.62
2679.23
i
I. 12000
.01605
I 016.05
2 24O.OO
2 722.22
1.78571
2
.81437
I 814.37
4 ooo.oo
486l.II
1.96841
2.20462
2000.00
4 409.24
5358.46
2
2.24000
.03209
2032.09
4480.00
5444-44
2.67857
3
•72155
2721.55
6 ooo.oo
7 291.67
2.95262
3.30693
3
3 ooo.oo
6613.87
8037.69
3
3.36ooo
3.04814
3048.14
6 720.00
8 166.67
3.57143
4
3.62874
3628.74
8 ooo.oo
9722.22
3.93683
4.40924
4
4 ooo.oo
8818.49
10 716.91
4
4.48000
4.06419
4064.19
8960.00
10888.89
4.46429
5
4.53592
4535.92
10 ooo.oo
12 152.78
4.92103
5.5JI56
5
5 ooo.oo
11023.11
13396.14
5
S.TOooo
5.08024
5080.24
ii 200.00
I36lI.II
5.35714
6
5.443H
5443.li
12 OOO.OO
14 583.33
5.90524
6.61387
6
6 ooo.oo
13227.73
16075.37
6
6.72000
6.09628
6096.28
13 440.00
16333.33
6.25000
7
6.35029
6350.29
14000.00
17013.89
6.88944
7.71618
7
7 ooo.oo
15 432.36
18754-60
7
7.84000
7.11232
7 112.32
15 680.00
19055.56
7.14286
8
7.25748
7 257.48
16 ooo.oo
19 444-44
7.87365
8.81849
8
8000.00
17 636.98
21 433.83
8
8.96000
8.12838
8 128.38
17 920.00
21 777.78
8.03571
9
8.16466
8164.66
18 ooo.oo
21 875.OO
8.85786
9.92080
9
9 ooo.oo
19 841.60
24 113.06
9
10.08000
9.14442
9 144.42
20 IOO.OO
24 500.00
Table of Centigrade to Fahrenheit 473
Centigrade to Fahrenheit
Temperature Fahrenheit = f Temperature Centigrade +32
Cent.
Fahr.
Cent.
Fahr.
Cent.
Fahr.
Cent.
Fahr.
Cent.
Fahr.
—273.00
—460.7
Zero
+32.0
46
114.8
470
878
930
1706
—260.00
-436.0
+i
+33-8
47
116.6
480
896
940
1724
—250.00
—418.0
2
35.6
48
118.4
490
914
950
1742
—240.00
—400.0
3
37-4
49
120.2
500
932
960
1760
—230.00
—382.0
4
39.2
50
122. 0
5io
950
970
1778
—220.00
—364.0
5
41.0
60
140.0
520
968
980
1796
— 2IO.OO
—346.0
6
42.8
70
158.0
530
986
990
1814
—200.00
-328.0
7
44-6
80
176.0
540
1004
1000
1832
— IQO.OO
—310.0
8
46.4
90
194.0
550
1022
1010
1850
— iSo.OO
—292.0
9
48.2
100
212.0
560
1040
IO2O
1868
— 170.00
-274-0
10
50.0
no
23O.O
570
1058
1030
1886
— l6o.OO
—256.0
ii
51.8
120
248.0
58o
1076
1040
1904
— 150.00
—238.0
12
53-6
130
266.0
590
1094
1050
1922
— I4O.OO
— 220.0
13
55-4
140
284.0
600
III2
1060
1940
— 130.00
— 202.0
14
57-2
150
302.0
610
1130
1070
1958
— 120. OO
— 184.0
15
59-0
160
320.0
620
1148
1080
1976
— IIO.OO
-166.0
16
60.8
170
338.0
630
1166
1090
1994
— 100. OO
— 148.0
17
62.6
180
356.0
640
1184
1 100
2012
— 9O.OO
— 130 o
18
64.4
190
374-0
650
1 202
IIIO
2O3O
— SO.OO
— 112. 0
19
66.2
200
392.0
660
1220
1120
2048
— 70.OO
— 94.0
20
68.0
210
410.0
670
1238
1130
2066
— 60.00
— 76.0
21
69.8
22O
428.0
680
1256
1140
2084
— 50.00
- 58.0
22
71.6
230
446.0
690
1274
1150
2102
— 4O.OO
— 40.0
23
73-4
240
464.0
700
1292
1160
2I2O
— 30.00
— 22. 0
24
75-2
250
482.0
710
1310
1170
2138
— 20.00
- 4.0
25
77-0
260
500.0
720
1328
1180
2156
— I9.OO
— 2.2
26
78.8
270
5i8.o
730
1346
1190
2174
- 18.00
- 0.4
27
80.6
280
536.0
740
1364
I2OO
2192
- 17-77
Zero
28
82.4
290
554-0
750
1382
I2IO
2210
— 17.00
+ 1-4
29
84.2
300
572.0
760
1400
1220
2228
— 16.00
+ 3-2
30
86.0
3io
590.0
770
1418
1230
2246
— 15.00
+ 5.o
31
87.8
320
608.0
780
1436
1240
2264
— 14.00
+ 6.8
32
89.6
330
626
790
1454
1250
2282
— 13.00
+ 8.6
33
91.4
340
644
800
1472
1260
2300
— 12.00
4- 10.4
34
93-2
350
662
810
1490
1270
2318
— 11.00
+ 12.2
35
95-0
360
680
820
1508
1280
2336
— 10. OO
+ 14-0
36
96.8
370
698
830
1526
1290
2354
— 9.00
+ 15.8
37
98.6
38o
716
840
1544
1300
2372
- 8 oo
+ 17-6
38
100.4
390
734
850
1562
1310
2390
- 7-00
+ 19-4
39
IO2.2
400
752
860
1580
1320
2408
— 6.00
+ 21.2
40
I04.O
410
770
870
1598
1330
2426
- 5.00
+ 23.0
41
105.8
420
788
880
1616
1340
2444
— 4.00
+ 24.8
42
107.6
430
806
890
1634
1350
2462
- 3.00
+ 26.6
43
109.4
440
824
900
1652
1360
2480
— 2.00
+ 28.4
44
III. 2
450
842
910
1670
1370
2498
— I.OO
4- 30.2
45
II3.0
460
860
920
1688
1380
2516
474 Table of Fahrenheit to Centigrade
Centigrade to Fahrenheit (Concluded)
Cent.
Fahr.
Cent.
Fahr.
Cent.
Fahr.
Cent.
Fahr.
Cent.
Fahr.
1390
2534
1550
2822
1710
3110
1870
3398
2030
3686
1400
2552
1560
2840
1720
3128
1880
34i6
2040
3704
1410
2570
1570
2858
1730
3146
1890
3434
2050
3722
1420
2588
1580
2876
1740
3164
1900
3452
2060
3740
1430
2606
1590
2894
1750
3182
1910
3470
2070
3758
1440
2624
1600
2912
1760
3200
1920
3488
2080
3776
1450
2642
1610
2930
1770
3218
1930
35o6
2090
3794
1460
2660
1620
2948
1780
3236
1940
3524
2IOO
3812
1470
2678
1630
2966
1790
3254
1950
3542
21 IO
3830
1480
2696
1640
2984
1800
3272
1960
356o
2120
3848
1490
2714
1650
3002
1810
3290
1970
3578
2130
3866
1500
2732
1660
3020
1820
3308
1980
3596
2140
3884
1510
2750
1670
3038
1830
3326
1990
3614
2150
3902
1520
2768
1680
3056
1840
3344
20OO
3632
2l6o
3920
1530
2786
1690
3074
1850
3362
2010
3650
2l8o
3956
1540
2804
1700
3092
1860
338o
202O
3668
2200
3992
Fahrenheit to Centigrade
Temperature Centigrade = | (Temperature Fahrenheit — 32)
Fahr.
Cent.
Fahr.
Cent.
Fahr.
Cent.
Fahr.
Cent.
Fahr.
Cent.
-5
-20.55
ii
-11.66
27
-2.77
43
6. ii
59
15.00
~4
—20.00
12
— ii. ii
28
— 2.22
44
6.66
60
15.55
-3
-19.44-
13
-10.55
29
-1.66
45
7.22
61
16.11
— 2
-18.88
14
— 10. OO
30
—i. ii
46
7-77
62
16.66
_!
-18.33
15
- 9.44
31
- .55
47
8.33
63
17.22
Zero
-17-77
16
- 8.88
32
Zero
48
8.88
64
17.77
+i
— 17.22
17
- 8.33
33
+ -55
49
9-44
65
18.33
2
-16.66
18
- 7-77
34
I. II
50
IO.OO
66
18.88
3
— i6.n
19
- 7-22
35
1.66
51
10.55
67
19.44
4
-15-55
20
- 6.66
36
2.22
52
II. II
68 20.00
5
— 15.00
21
- 6. ii
37 '
2.77
53
11.66
69 20.55
6
-14.44
22
- 5-55
38
3-33
54
12.22
7o
21. II
7
-13.88
23
- 5-00
39
3-88
55
12.77
71
21.66
8
-13-33
24
- 4-44
40
4-44
56
13-33
72
22.22
9
-12.77
25
- 3.88
41
S.oo
57
13-88
73
22.77
10
— 12.22
26
- 3-33
42
5-55
58
14.44
74 23.33
Table of Fahrenheit to Centigrade 475
Fahrenheit to Centigrade (Concluded)
Fahr.
Cent.
Fahr.
Cent.
Fahr.
Cent.
Fahr.
Cent.
Fahr.
Cent.
75
23.88
121
49-44
167
75.00
213
100.55
259
126.11
76
24-44
122
50.00
168
75-55
214
IOI.II
260
126.66
77
25.00
123
50.55
169
76.11
215
101.66
261
127.22
78
25-55
124
Si- ii
170
76.66
216
102.22
262
127-77
79
26.11
125
51.66
171
77.22
217
102.77
263
128.33
80
26.66
126
52.22
172
77-77
218
103-33
264
128.88
8l
27.22
127
52.77
173
78.33
219
103.88
265
129.44
82
27.77
128
53-33
174
78.88
220
104.44
266
130.00
83
28.33
129
53.88
175
79-44
221
105.00
267
130.55
84
28.88
130
54-44
176
80.00
222
105-55
268
131-11
85
29.44
131
55-00
177
80.55
223
io6.n
269
131.66
86
30.00
132
55-55
178
8i.ii
224
106.66
270
132.22
87
30.55
133
56.11
179
81.66
225
107.22
271
132.77
88
31.11
134
56.66
180
82.22
226
107.77
272
133- 33
89
31-66
135
57-22
181
82.77
227
108.33
273
133-88
90
32.22
136
57-77
182
83.33
228
108.88
274
134-44
9i
32.77
137
58.33
183
83.88
229
109.44
275
135-00
92
33-33
138
58.88
184
84.44
230
110.00
276
135.55
93
33-88
139
59 44
185
85.00
231
110.55
277
136. n
94
34-44
140
60.00
186
85-55
232
in. n
278
136.66
95
35-00
141
6o.55
187
86.il
233
in. 66
279
137.22
96
35-55
142
6i.n
188
86.66
234
112.22
280
137-77
97
36.11
143
61.66
189
87.22
235
112.77
281
138.33
98
36.66
144
62.22
190
87.77
236
113-33
282
138-88
99
37.22
145
62.77
I9i
88.33
237
113.88
283
139-44
100
37-77
146
63.33
192
88.88
238
H4-44
284
140.00
101
38.33
147
63.88
193
89-44
239
115.00
285
140.55
102
38.88
148
64.44
194
90.00
240
115-55
286
141.11
103
39-44
149
65.00
195
90.55
241
ii6.ii
287
141.66
104
40.00
ISO
65.55
196
91.11
242
116.66
288
142.22
105
40-55
I5i
66.11
197
91.66
243
117.22
289
142.77
106
41.11
152
66.66
198
92.22
244
H7.77
290
143.33
107
41.66
153
67.22
199
92.77
245
118.33
291
143-88
108
42.22
154
67.77
200
93-33
246
118.88
292
144-44
109
42.77
155
68.33
201
93-88
247
119.44
293
145-00
no
43-33
156
68.88
202
94-44
248
I2O.OO
294
145-55
III
43-88
157
69.44
203
95-00
249
120.55
295
146.11
112
44.44
158
70.00
204
95-55
250
121. II
296
146.66
113
45-00
159
70.55
205
96.11
251
121.66
297
147-22
H4
45.55
160
71.11
206
96.66
252
122.22
298
147-77
H5
46.11
161
71.66
207
97.22
253
122.77
299
148.33
116
46.66
162
72.22
208
97-77
254
123-33
300
148.88
117
47.22
163
72.77
209
98.33
255
123-88
400
204.44
118
47-77
164
73-33
2IO
98.88
256
124.44
600
315.55
H9
48.33
165
73-88
211
99-44
257
125.00
800
426.66
1 20
48.88
166
74-44
212
100. OO
258
125-55
1000
537-77
476
Conversion Chart
Conversion Chart for Lengths, Weights and Temperatures
a- -•»»'"
C4
a--
Glossary of Terms Used in the Pipe and Fitting Trade 477
GLOSSARY OF TERMS USED IN THE PIPE AND
FITTING TRADE
ABBREVIATIONS
A.I. = All iron (use limited to valves and cocks).
B.D. = Brass disc (use limited to valves).
Bd. = Beaded (use limited to malleable fittings).
~F _ ( (i) Blank flange.
~ I (2) Blind flange.
( (i) Ball joint.
B J. = < (2) Brass jacket.
( (3) Bump joint.
B. & L. = Ball and lever (use limited to valves).
B.L. = Bill of lading.
B.M. = Brass mounted.
B.O.C. = Back outlet central (use limited to fittings).
B.O.E. = Back outlet eccentric (use limited to fittings).
B P = I ^ Brass plug (use limited to cocks).
{ (2) By-pass (use limited to valves).
Br. = Brass.
B. & S. = Bell and spigot.
B w _ i (J) Butt weld (use limited to pipe).
~ I (2) Brass washer (use limited to cocks).
C.D. = Copper disc (use limited to valves).
C. & F. = Cost and freight.
C.I. = Cast iron.
C.I.F. = Cost, insurance and freight.
C.J. = Converse joint.
( (i) Carload lots.
C.L. = < (2) Center line.
( (3) Cut lengths.
C.P. = Close pattern (use limited to return bends).
C.S. = Countersunk.
D S _ J (*) Double screen (use limited to well points-).
( (2) Double sweep (use limited to tees).
D.W. = Drive well (use limited to drive well points or supplies).
E.A. = Ends a-nnealed (use limited to pipes and tubes).
E. to E. = End to end.
Ex. Hvy. = Extra heavy.
F.A.S. = Free alongside steamer.
F. & D. = Faced and drilled.
F.E. = Flanged ends.
F. to F. = Face to face.
F.H. = Flat head (use limited to cylinders and cocks).
F.O. = Faced only.
f.o.b. = Free on board.
F.O.R. = Free on rails.
478 Glossary of Terms Used in the Pipe and Fitting Trade
F.P.
F. &R.
F.W.
G. &D.
H.D.M.
H.E.
I.E.
I.D.
I.P.
J.D.
KJ.
L.
L.C.L.
L.H.
L.R.
L.S.
L.W.
Mall.
M. &F.
M.I.
MJ.
m.m.
M.M.A.
M.P.
M.S.
M.S.F.Std,
N.P.
N.P.A.O.
N.P.T.
N.R.S.
O.D.
O.H.S.
O.P.
O.S. & Y.
P.C.
P.E.
P.E.N.R.
P.E.R.
P.F.
PI.
P. &R.
Q.O.
R.B.
R. &D.
R.H.
R. &L.
Fire plug.
Feed and return (use limited to radiators).
Full or card weight pipe.
Galvanized and dipped.
High duty metal (use limited to valves).
Hub end.
Iron body (use limited to valves).
Inside diameter.
Briggs' Standard Threads (poor usage).
Jenkins disc (use limited to valves).
Kimberley joint.
Elbow.
Less carload lots.
(1) Left hand.
(2) Lever handle (use limited to cocks).
= Long radius.
_ \ (i) Lock shield '(use limited to valves and cocks).
~~ | (2) Long sweep (use limited to fittings).
= Lap weld.
= Malleable.
= Male and female.
= Malleable iron.
= Matheson joint.
= Millimeter.
= Master Mechanics Association.
_ j (i) Medium pattern (use limited to return bends).
\ (2) Medium pressure.
= Medium sweep (use limited to fittings).
= Master Steam Fitters' standard.
= Nickel plated (use limited to valves).
= Nickel plated all over (use limited to valves).
= Nickel plated trimmings (use limited to radiator valves) .
= Nonrising stem (use limited to valves).
= Outside diameter.
= Open hearth steel.
= Open pattern (use limited to return bends).
= Outside screw and yoke (use limited to valves).
= Pump column.
= Plain end.
= Plain end not reamed.
= Plain end reamed (use limited to nipples).
= Plain face.
= Plain (use limited to fittings).
= Plugged and reamed = R. and D.
= Quick opening (use limited to valves)
= Rough body (use limited to valves).
= Reamed and drifted = P. & R.
= Right hand.
= Right and left.
Definitions 479
S.C. = Service clamp.
S.E. = Screwed ends.
~ ~ _ j (i) Side outlet (use limited to fittings).
~ { (2) Single opening (use limited to radiators).
Sq. H. = Square head.
S. & S. = Screw and socket = T. & C.
c c _ J (*) Single screened (use limited to well points).
"~ I (2) Single sweep (use limited to tees).
Std. = Standard.
T. = Tee.
T. & C. = Threads and couplings = S. & S.
T. & G. = Tongue and groove — not understood as male and female.
T.H. = Tee handle (use limited to cocks).
T.noC. = Threads no couplings.
W.I. = Wrought iron.
W.W. = Wood wheel (use limited to valves).
X.H. = Extra heavy.
X.S. = Extra strong.
X.X.H.= Double extra heavy.
X.X.S. = Double extra strong.
Y. = Wye.
Y.T. = Yoke top (use limited to valves).
DEFINITIONS
(Definitions marked * are taken from Hawkins' Mechanical Dictionary.)
Ammonia Cock Thread. — Ammonia cock thread is usually larger and
has more taper than Briggs' Standard thread. It lacks uniformity
and is made to suit customers' requirements.
Ammonia Fitting. — A fitting whose material is especially homogeneous,
which usually has its mouth countersunk and both the mouth and
thread tinned.
Ammonia Joint. — All joints should be made of wrought iron or steel,
as ammonia attacks and eats away copper and its alloys, brass and
gun-metal. In consequence of the penetrating nature "of ammonia,
all flanges should be screwed and then soldered on the pipes. Lead
washers should be used for gaskets on all flange joints. Lead or
white metal packing must also be used for all valves.*
Angle Gate Valve. — A gate valve with an elbow cast on one end integral
with body.
Angle Valve. — A stop-valve whose outlet is at right angles to its inlet
branch, thus combining in itself a valve and an elbow. It must not
be confused with angle gate valve.
Angus Smith Composition. — A protective coating for valves, fittings,
and pipe used for underground work. It is composed of coal tar,
tallow, rosin and quicklime and must be applied hot.
480 Glossary of Terms Used in the Pipe and Fitting Trade
Annealed End Tube. — A tube whose ends have been annealed. For
annealing to be effective, it is necessary to heat above the critical
temperature, and this is higher as the carbon contents are less, so
that with the soft steel of which pipe and tubes are made, anneal-
ing must be done at a high heat, 1750 to 1800 degrees Fahrenheit,
which is a bright orange in shop daylight. The piece may be
allowed to cool in the air after being thoroughly heated to this
temperature.
Armstrong Joint. — Designed by Sir W. Armstrong. It is a two bolt,
flanged or lugged connection for high pressures. The ends of the
pipes are peculiarly formed to properly hold a gutta-percha ring.
It was originally made in cast iron pipe. The two bolt feature has
much to commend it. There are various substitutes for this old,
high-class joint; the commonest employ rubber in place of gutta-
percha; others employ more bolts in the endeavor to cheapen.
Artesian Joint. — See Cressed Artesian Joint.
Asphalted. — Coated with asphalt literally, but usually some of the
special compositions such as California Oil (which has an asphaltic
base), coal tar, mineral wax or Gilsonite or Elaterite are added to
give the right consistency to suit the average temperature which
prevails when the coating is used.
Attemper -ator. — A coil of pipe, sometimes working on a swivel or hinge,
through which refrigerated brine, or other liquor, is passed. Used
to cool vessels containing warm liquids, such as fermenting vats.*
B
Back Outlet Central. — Meaning that such outlet is placed centrally or
at mid length. (Use limited to fittings.)
Back Outlet Eccentric. — Meaning that back outlet of tee, elbow, etc.,
is not placed at center. (Use limited to fittings.)
Back Outlet Ell. — An ell with an outlet in the same plane as the run
and on the outside of the curve.
Back Pressure Valve. — A valve that usually is made like a low pressure
safety valve but capable of being opened independently of the
pressure, thereby giving free exhaust. They are usually employed
on non-condensing engines when it is desired to use all or part of
the exhaust steam for heating, etc. The back pressure maintained
by them is usually between one and ten pounds.
Balling. — Nearly the same as peening.
Ball Joint. — A flexible joint made in the shape of a ball or sphere.
Many forms of joint employ such spherical surfaces.
Bar. — See Sinker and Water Bar.
Barrel. — See Working Barrel.
Bead. — When applied to fittings means the slight reinforcing ring on
the end. A circular molding.
Beaded Tube. — The ends of boiler tubes, after being expanded, are
beaded or rounded with a beading tool, just as rivet heads are
finished with a die or snap. The process is termed beading.*
Definitions ' L 481
Beading. — The name given to the slight flanging of the end of a boiler
tube over a tube sheet, or of the pipe, over a peened flange.
Bell. — (i) In pipe fitting, the recessed or enlarged female end of a
pipe into which the male end of the next pipe fits; also called hub.
(2) In plumbing, the expanded female portion of a wiped joint.*
Bell and Spigot Joint. — (i) The usual term for the joint in cast iron
pipe. Each piece is made with an enlarged diameter or bell at one
end into which the plain or spigot end of another piece is inserted
when laying. The joint is then made tight by cement, oakum,
lead, rubber, or other suitable substance which is driven in or
calked into the bell and around the spigot. When a similar joint
is made in wrought pipe by means of a cast bell (or Hub) it is at
times called hub and spigot joint (poor usage). Matheson Joint is
the name applied to a similar joint in wrought pipe which has the
bell formed of the pipe.
(2) Applied to fittings or valves, means that one end of the run is a
"bell," and the other end is a "spigot," similar to those used on
regular cast iron pipe.
Bell Mouthed. — A term used to signify the open end of a vessel or
pipe when it expands or spreads out with an increasing diameter,
thus resembling a bell. Also called trumpet mouthed.*
Bend. — (i) A curved length of pipe struck to a larger radius than the
elbow.
(2) Pipe bent to 45, 90 or 180 degrees is often specified as Vs, Vt or
1/2 bends.
(3) A slight bend is often called a spring. (Poor usage.)
See Close Return, Cross Over, Double, Eighth, Goose Neck, Open
Return, Pipe, Return, and Y Bend.
Bibb. — A cock or valve with bent outlet; strictly the bent outlet.
Blank Flange. — (i) A flange that is not drilled but which is otherwise
complete.
(2) At times used to signify a blind flange (this is poor usage). Com-
pare blind flange.
(3) At times used to signify a pipe flange that is not threaded, but
which is otherwise complete (this is bad usage).
Blanking Flange. — A blind flange, which see (poor usage).
Bleeder. — A small cock or valve to draw off water of condensation
from a range of piping.*
Blind Flange. — (i) A flange used to close the end of a pipe. It pro-
duces a blind end which is also called a dead end.
(2) It is at times used erroneously to designate a blank flange.
(3) Compare blanking flange.
Block Joint. — A joint used by plumbers in which an inserted joint is
combined with a wide flange; used for wiped joints on heavy verti-
cal pipes.*
Boiler Flange. — See Saddle Flange.
Boiler Thimble. — A ring placed between a boiler tube and the tube sheet
or header. The term is more often used in connection with loco-
motive and marine than stationary boilers. (Poor usage.)
482 Glossary of Terms Used in the Pipe and Fitting Trade
Boiler Tube. — One of the tubes by which heat from the furnace is dif-
fused through the water in a steam boiler. The tubes may contain
water and be surrounded by the furnace gases as in a water tube
boiler or they may act as flues and be surrounded by water as in a
tubular boiler. The usual sizes of boiler tubes are 2 to 4 inches.
Bonnet, (i) A cover used to guide and enclose the tail end of a valve
spindle.
(2) A cap over the end of a pipe. (Poor usage.)
Bowl. — See Bell.
Box. — See Service and Valve Box.
Box Coil. — An arrangement of heating pipes made up in the form of a
rectangular box.
Boyle Union. — Essentially a tongue and groove flange connection in
which the tongue is a separate piece placed between two grooved
flanges. Usually the groove extends to the threads so that the
gasket material seals that point and permits use of flanges that are
not screwed very tight.
Bracket Coil. — A heating pipe usually one or two pipes wide, supported
by hooks or expansion plates.
Bracket Valve. — A stop-valve with a bracket cast upon its body, so
that it may serve as an anchorage or support for the piping which
it controls.*
Branch. — The outlet or inlet of a fitting not in line with the run but
which may make any angle. See H and Y Branch.
Branch Ell. — (i) Used to designate an elbow having a back outlet in
line with one of the outlets of the run. It is also at times called a
heel outlet elbow.
(2) Incorrectly used to designate side outlet or back outlet elbow.
Branch Pipe. — A very general term used to signify a pipe either cast
or wrought, that is equipped with one or more branches. Many
such pipes are used so frequently that they have acquired common
names such as tees, crosses, side or back outlet elbows, manifolds,
double branch elbows, etc.
The term branch pipe is generally restricted to such as do not con-
form to usual dimensions.
Branch Tee. — Header. — A tee having many side branches. See Manifold.
Brass Mounted. — When used to describe a globe, angle, or cross valve,
it usually means that the valve has a brass bonnet, stem, seat,
ring and disc. When used to describe gate valves, usually means
brass stem, seat, ring and wedge or disc ring.
Brazed. — Connected by hard solder which usually is copper and zinc —
half and half. Such solder requires a full red heat and is commonly
used with Borax flux.
Breeches Pipe. — A Y-shaped pipe used for many purposes, especially
in locomotives, leading the exhaust from the two cylinders to the
blast nozzle.*
Brick Arch Tube. — One of a series of curved iron tubes, used to sup-
port the fire-box arch in certain locomotives, also providing in-
creased heating surface and promoting circulation.*
Definitions 483
Briggs' Standard. — A list of pipe sizes, thicknesses, threads, etc., com-
piled by Robert Briggs about 1862 and subsequently adopted as a
standard.
Bucket. — The piston of a well pump. It always contains a valve. It
is connected to and operated by the sucker rods.
Bull Head Tee. — A tee whose branch is larger than the run.
Bumped. — Convex when applied to cylinder heads.
Bumped Joint. — One having the end of one pipe so expanded that
the end of another may be driven in until the rivet holes register.
By slightly tapering both ends it is practical to increase the ease of
erection and lessen the calking required.
Bushing. — A pipe fitting for the purpose of connecting a pipe with a
fitting of larger size, being a hollow plug with internal and external
threads to suit the different diameters.* See Flush Bushing.
Butted and Strapped Joint. — A joint where the ends of two pieces of
pipe are united by a sleeve and riveted thereto. The strap may be
inside or outside and may be single or double riveted.
Butterfly. — (i) The name applied to certain valves made after the
design of a damper in a stove pipe.
(2) In pumps this term signifies a double clack valve whose flaps
work on a diametral hinge, like the wings of a butterfly.
Butt-weld. — Welded along a seam that is butted and not scarfed or
lapped.
By-Pass. — A small passage to permit equalizing the pressure on the
two sides of a large valve so that it may be readily opened (or
closed).
By-Pass Valve. — A small pilot valve used in connection with a larger
valve to equalize the pressure on both sides of the disc of the
larger valve before the larger valve is opened.
Caliber. — An expression which is often used to mean the inner diameter
or bore.
Calking. — (i) In iron working, the calking consists of striking a chisel,
or calking tool with a hammer, making a slight indentation along
the seam. The effect of this is to force the edge of one plate hard
against the other, and thus fill up any slight crevice between the
plates which the rivets failed to close.*
(2) The term is used in connection with lead joints or bell and spigot
joints in which case the lead is calked.
Calking Recess. — A counterbore or recess in the back of the flange
into which lead may be calked for water, or copper for steam.
Calking Tool. — Calking Iron. — A blunt ended chisel used in calking.
Cap. — A fitting that goes over the end of a pipe to close it, producing
a dead end.
Card Weight Pipe. — A term used to designate Standard or Full .Weight
Pipe, which is the Briggs' Standard thickness of pipe.
484 Glossary of Terms Used in the Pipe and Fitting Trade
Casing. — A term applied to pipe when used to case an oil or gas well
It is usually characterized by light weight and fine threads.
Casing Dog. — In boring, a fishing instrument provided with serrated
pieces or dogs sliding on a wedge, to grip severed casing.*
Casing Elevator. — A well-boring device consisting of two semi-circular
clamps with a chain-link on either, which are hinged together
at one end, and secured by a latch at the other. This affords a
quickly applied and released attachment for casing to the lifting
tackle.*
Casing Fitting. — A fitting threaded with a casing thread.
Ca-sing Head. — (i) A fitting used at top of casing of a well to separate
oil and gas, to allow pumping, and cleaning out well, etc. There
are many forms.
(2) In well-boring, a heavy mass of iron screwed into the top of a
string of casing to take the blows produced by driving the pipe
home.*
Casing Shoe. — In well-boring, a ring or ferrule of hard steel with a
sharp edge, screwed or shrunk on to the bottom of a string of cas-
ing, to cut its way through the formation as the casing is forced
down.*
Chain Tongs. — A pipe-fitter's tool; a lever with a serrated end pro-
vided with a chain to enlace the pipe. The chain is wrapped
around the pipe to hold the lever in place, and the teeth on the
end of the latter grip into the pipe, thus affording a powerful lever-
age to screw or unscrew the joints.*
Chamfer. — To cut at an angle or bevel.
Chasing. — A term that designates the operation of cutting a thread in
a lathe, either with hand tools or by power feed. A single cutting
point is usually employed, but some mechanics finish by use of a
comb or chaser. Pipe threads are seldom chased but are usually
cut by taps, dies, etc.
Check. ' — (i) To prevent flow except in one direction — applied to
valves.
(2) To prevent rotation except to full open and full closed — applied
to cocks.
Check Valve. — An automatic non-return valve; or a valve which per-
mits a fluid to pass m one direction, but automatically closes when
the fluid attempts to pass in the opposite direction.
C.IJ?. — A commercial transportation term meaning Cost, Insurance
and Freight. It is intended to cover the cost of certain goods at
point of destination; an expression of similar usage to F.O.B. but
C.I.F. is applied to ocean shipments.
Circular Flange. — A curved or saddle flange.
Circular Weld. — Safe end weld. — A weld extending around a girth
seam. Such welds are sometimes butted, but frequently are
scarfed.
Clamp. — See Leak, Pipe, Pouring, Service and Water Pipe Clamp.
Clean Out Fitting. — One that is equipped with hand hole and cover so
that pipes may be cleaned.
Definitions 485
Close Nipple. — One whose length is about twice the length of a stand-
ard pipe thread and is without any shoulder.
Close Return Bend. — A short cast or malleable iron U-shaped fitting
for uniting two parallel pipes. It differs from the open return bend
in having the arms joined together.
Coal Tar. — A by-product of the destructive distillation of soft or
bituminous coal.
Coating for Pipe. — Usually a coal tar composition sometimes called
asphalt. There are many on the market, such as *'Sarco," Mineral
Rubber Asphalt, California Asphalt, Trinidad Asphalt, Elaterite,
Gilsonite and Dr. Angus Smith's Composition. A well refined coal
tar pitch, softening at 60 degrees Fahrenheit and melting about no
degrees Fahrenheit, is one of the best and most durable coatings
known, when properly applied. See Angus Smith Composition,
Asphalted, Galvanizing, Kalameined and Smith's Coating.
Cock. — A device for regulating or stopping the flow in a pipe, made by
a taper plug that may be rotated in a body having ports corre-
sponding to those in the plug. See Bibb, Bleeder, Corporation,
Four- way, Gage, Pet, Plug, and Telegraph Cock.
Coil. — A number of turns of piping or series of connected pipes in
rows or layers for the purpose of radiating or absorbing heat.* See
Box, Bracket and Expansion Coil.
Cold Drawn. — Drawn cold. — See "Drawn."
Collar. — (i) A term used in place of a coupling in such connections
as "Kimberley Collars." (Also used to mean threaded pipe coup-
ling.)
(2) The sleeve in the back of certain styles of flanges, such as a
riveted flange, is called a collar.
(3) Again, certain styles of flanges attached by peening and beading
are known as "Collar Flanges."
Collar Flange. — One having sufficient collar on its back to allow it to
be securely attached to pipe by peening or riveting.
Common Thread. — In machinery, an ordinary standard machine
thread, as distinguished from a pipe thread.*
Conduit Pipe. — Wrought pipe used as armor for electric wires.
Converged End. — A term used to signify the beveling in or converging
of the ends of certain styles of cylinders, as those used for anhy-
drous ammonia. Primarily intended to aid in handling by prevent-
ing fingers from slipping.
Converse Lock Joint. — A joint for wrought pipe which is made up
with a cast iron hub. The joint is made by placing rivets in
the ends of the pipe which, in turn, lock in slots in the cast iron
hub. The lock is so shaped as to have a wedging action in drawing
the pipe tight against a ring in the center of the hub, after which
the pipe is leaded in place and calked.
Corporation Cock. — (i) A term usually applied to the cock attached to
a street main, owned and operated by or under the supervision of
a supply corporation. It is distinct from the more accessible curb
cock which is placed in the service line for convenience.
486 Glossary of Terms Used in the Pipe and Fitting Trade
(2) Its essential peculiarities are usually that it has one threaded
end, a heavy body and a plug large enough to permit a drill to be
operated through it — the diameter of the drill being the nominal
size of the cock.
Corrugated Joint. — A short length corrugated like an accordion or
corrugated fire box. It allows a limited movement but requires
great force to distort, unless made so thin that it requires hooping
for ordinary pressures.
Counterbored. — Bored to a diameter larger than the adjacent hole.
See Recessed.
Countersink. — (i) A tool used to chamfer the mouth of a hole.
(2) The operation that uses a countersink tool.
Countersunk. — (i) Having the shape given by the use of a countersink.
(2) Also applied to certain type of plug which has an opening de-
pressed to receive square wrench.
(3) When applied to fittings means chamfered at an angle of 45° at the
tapped opening.
Coupling. — A threaded sleeve used to connect two pipes. Commer-
cial couplings are threaded inside to suit exterior thread of pipe.
The term coupling is occasionally used to mean any jointing device
and may be applied to either straight or reducing sizes. See Pipe,
Socket, Steam and Union Coupling.
Cressed. — Reduced about Vs inch in diameter for a short distance at
ends. A foreign term used on artesian- well casing.
Cressed Artesian Joint. — A British term used to describe a joint that
requires unusual perfection of workmanship. It may be specified
thus: — Ends of pipe cressed exactly one-half length of coupling;
pipe threaded straight and exactly true to general axis thereof;
end of pipe faced true to same axis; vanish of thread (or lead of
dies) ground to exactly same taper as countersink of coupling;
coupling tapped straight and countersunk each end, same as lead
of dies; coupling nicely beveled at long taper so that there is no
shoulder at joint; ends must butt at same time as vanish screws
home.
Cross. — A pipe fitting with four branches arranged in pairs, each pair
on one axis and the axes at right angles. When the outlets are
otherwise arranged the fittings are branch pipes or specials.
Cross-Over. — A small fitting like a double offset or the letter "U"
with ends turned out. It is only made in small sizes and used to
pass the flow of one pipe past another when the pipes are in the
same plane.
Cross-Over Bend. — A bent pipe used for the same purpose as the cross-
over fitting.
Cross-Over Tee. — A fitting made along lines similar to the cross-over,
but having at one end two openings in a tee head whose plane is at
right angles to the plane of the cross-over bend.
Cross-Tube. — In boiler making, a coned or Galloway water tube
placed transversely across a firebox or furnace flue to increase the
heating surface and improve circulation.*
Definitions 487
Cross Valve. — (i) A valve fitted on a transverse pipe so as to open
communication at will between two parallel lines of piping. Much
used in connection with oil and water pumping arrangements, espe-
cially on ship board.*
(2) Usually considered as an angle valve with a back outlet in the
same plane as the other two openings.
Crotch. — A fitting that has the general shape of the Roman letter " Y. "
Caution should be exercised not to confuse the crotch and wye.
Crushing Test. — A term describing test applied to tubes whose mate-
rial is tested the same as the "bending test" for plates and bars.
When applied to tubes, it is customary to take a ring or crop end
from the tube and crush, so that the weld comes at the points of
shortest radius of curvature, which is usually specified to be equal
to three (3) times the thickness — under which condition the weld
must not open nor material crack.
Cup and Ball Joint. — In gas fitting, a ball and socket joint fitted to
hanging gas chandeliers. It allows the chandelier to turn freely
without escape of gas.*
Cup Joint. — In plumbing, a lead joint in which one pipe is tapered to
fit into a flared out cup on the other, and the joint soldered.*
Cupping. — Means nearly the same as flanging a head, but the cupping
process forms a flat disc into a flanged head and then, by repeating
the operation and giving draft (drawing the metal), forms a deep
head; then a cup; then a deep cup; then a tube which, by repeat-
ing the process a sufficient number of times, becomes a long, thin
pipe.
Curved Flange. — See Saddle Flange.
Cut Length. — A term used to signify that the pipe is cut to length
ordered.
Cylinder. — A term used to designate any tank, drum, retort, receiver
or reservoir, etc., that is made of pipe and closed at both ends,
except such test hole as must always be allowed. See Converged
End, Dished Head, Drum and Flat Head.
Dead End of a Pipe. — The closed end of a pipe or system of pipes.*
Die. — The name of a tool used for cutting threads usually at one pas-
sage. The essential distinctive feature of a die is its multiple cut-
ting edges, while a chasing or threading tool usually has one, or,
at most, only a few cutting edges. Some dies are highly complex
and ingenious pieces of mechanism, equipped to trip after cutting a
certain predetermined number of threads. See Master and Pipe Die.
Dip Pipe. — A valve in a gas main, so arranged as to dip into water
and tar, and thus form a seal. Called also a seal pipe.*
Dished. — Concave when applied to cylinder heads.
Dog. — See Casing Dog, Dog Guard, Pipe Dog and River Dog.
Dog Guard. — The name used to designate the sleeve that is frequently
swaged and shrunk about an electric line pole, for a short distance
488 Glossary of Terms Used in the Pipe and Fitting Trade
above and below the ground line, in order to prevent corrosion of
the pole at the ground line. It is the ordinary name of the "Patent
Protecting Sleeve" applied to electric line poles.
Double Bend. — A pipe or fitting shaped like the letter S in outline.
Double Branch Elbow. — A fitting that, in a manner, looks like a tee or
as though two elbows had been shaved and then placed together,
forming a shape something like the letter Y or a crotch.
Double Extra Strong. — The correct term or name of a certain class of
very thick pipe, which is often, less correctly, called double extra
heavy pipe.
Double Sweep Tee. — A tee made with easy curves between body and
branch, i.e., the center of curve between run and branch lies outside
the body. This is in contradistinction to the short fillet between
body and branch of standard tees.
Drainage Fittings. — Those that have their interior flush with I.D. of
pipe, thereby securing an unobstructed surface for the passage of
solid matter.
Drawn. — The term applied to that style of forging by which the
thickness is reduced and also, at times, the diameter — by pushing
or pulling the material through a die and over a mandrel or plug
at the same time. In some cases the mandrel is long and moves
at nearly the same speed as the tubes, but in other cases, the man-
drel is anchored so as to hold it within the die. When there is no
inside mandrel, it is not called drawn product. See Cold and Hot
Drawn.
Dresser Joint. — A peculiar form of Normandy Joint. There are vari-
ous styles.
Drifted. — (i) Having had a drift or short mandrel passed through the
pipe in order to be certain that there are no inside irregularities or
that they have thereby been removed. It is also, but less correctly,
called plugged.
(2) Enlarged by forcing through a tapered mandrel. This meaning
of the word is uncommon in the pipe trade.
Drill. — See Pole and Shot Drill.
Drilled. — Used in connection with flanges to indicate that the bolt
holes have been made by a drill, i.e., not made by cores.
Drilling Machine. — A name often applied to a tapping machine be-
cause many machines drill and tap.
Drive Head. — Protecting end attached to the top of drive pipe and cas-
ing, etc. Also called Drive Caps.
Drive Pipe. — A pipe which is driven or forced into a bored hole, to
shut off water courses, or prevent caving.
Drive Pipe Joint. — A threaded joint in which the pipe butts in the
center of the coupling.
Drive Pipe Ring. — A device for holding drive pipe while being pulled
from well. It means nearly the same as elevator but the device
is very different.
Drive Shoe. — A protecting end attached to" the bottom of drive pipe
and casing.
Definitions 489
Drop Elbow. — A small sized ell that is frequently used where gas is put
into a building. These fittings have wings cast on each side. The
wings have small countersunk holes so that they may be fastened
by wood screws to ceiling or wall or framing timbers.
Drop Tee. — One having the same peculiar wings as the drop elbow.
Drum. — (i) Package used in shipping fittings and valves.
(2) A short cylinder of large diameter having flat heads, but often
used for a cylinder of any style.
Dry Joint. — One made without gasket or packing or smear of any
kind, e.g., Ground Joint.
Dry Pipe. — A slotted or perforated steam collecting pipe within a
boiler, insuring dryness.*
Eccentric Fitting. — One having its openings on center lines that are not
concentric, usually arranged so that the interior walls of one side
are in one plane. So arranged for draining condensation.
Eckert Joint. — A special design of a form of Armstrong Joint.
Eduction Pipe. — The exhaust pipe from the low pressure cylinder to
the condenser.*
Eighth Bend. — (i) A bent pipe whose curved portion deflects the line
one-eighth of a circle to (36o°/8 = 45°).
(2) At times applied to the cast fitting which is more properly called
a 45° elbow.
Elbow. — Ell. — A fitting that makes an angle between adjacent pipes.
The angle is always 90 degrees, unless other angle is stated.
See Back Outlet, Branch, Double Branch, Drop, Heel Outlet, Reducing
Taper, Return, Service, Side Outlet, Street, Three Way and Union
Ell.
Elevator. — A device for raising or lowering tubing, casing or drive pipe
from or into well. See Casing Elevator.
Ell. — See Elbow.
End. — See Plain and Safe End.
Exhaust Relief Valve. — Nearly the same meaning as a check valve.
They are used with condensing engines to allow atmospheric ex-
haust when condenser is not working. They may be loaded so as
to act as back pressure valves.
Expanded End Tube. — Swelled end tube. — These terms are used in-
terchangeably. See Swelled.
Expanded Joint. — A term at times applied to the joint used on casing
and which is correctly called "Inserted Joint."
Expansion Coil. — The series or coils of pipe placed in a refrigerating
box or brine tank, in which the ammonia vaporizes after passing
through an expansion valve.*
Expansion Diaphragm. — An expansion joint of very limited travel
which it obtains by buckling the diaphragm. If the diaphragms
are corrugated, it is capable of greater motion.
Expansion Joint. — (i) A device used in connecting up long lines of
pipe, etc., to permit linear expansion or contraction as the tempera-
490 Glossary of Terms Used in the Pipe and Fitting Trade
ture rises or falls. Usually patterns consist of a sleeve secured to
one length of pipe, which works within a stuffing box attached to
the next length.*
(2) There are several, such as slip, swing, balanced, diaphragm, loop,
swivel, etc. All are intended to accommodate the change in length
due to changes in temperature.
Expansion Loop. — Either a bend shaped like the letter "U" or a coil
like a "pig tail."
Expansion Pipes. — In cold storage, those pipes within the refrigeration
chambers in which the ammonia or other agent changes into a
gas under release of pressure, drawing heat in the process from its
surroundings.*
Expansion Ring. — A hoop or ring of U section used to join lengths of
pipe together so as to permit of expansion, as the well known
Bowling hoop for boiler furnace flues.*
Expansion Valve. — (i) A valve used to control flow of ammonia (or
other refrigerant). Usually capable of fine adjustment.
(2) The valve of a steam engine that determines the point of cut-off
i.e., point at which steam starts to work expansively.
Extension Piece. — Usually a malleable iron nipple with male and
female thread.
Extra Heavy. — When applied to pipe means pipe thicker than Stand-
ard Pipe; when applied to valves and fittings is to indicate goods
suitable for a working pressure of 250 pounds per square inch.
Extra Strong. — The correct term or name of a certain class of pipe,
which is heavier than standard pipe and not as heavy as double
extra strong pipe. Often less correctly called extra heavy pipe.
F
Faced After. — A term used on flanged work to mean that flanges are
faced after they are attached to pipe and that ends of pipe are
faced flush with flange, both being at right angles to general axis
of pipe.
Faucet. — (i) A device to control the flow of liquid. Originally a hol-
low plug with a transverse hole in which was placed the spigot.
This latter was later bored and equipped with a handle now made
in great variety of forms. Commonly called a tap and used in
house plumbing to draw water.
(2) Enlarged end of a pipe to receive the spigot end of another pipe,
i.e., a bell end.
Ferro Steel. — A special grade of steel that is intermediate in strength
between cast iron and cast steel.
Ferrule. — A short piece of steel or copper pipe placed between tubes
and tube sheet of boiler. At times they are welded to tube. See
Tube Ferrule.
Field Joint. — (i) For poles is made by swaging the inserted end to a
uniform taper, about y& inch in 18 inches, and then swaging the
exterior pipe so that its interior has same taper and size, due allow-
Definitions 491
ance being made for shrinkage. It is assembled by placing the
two sections accurately in line, but separated a few inches, the
lighter section being on rollers. The bell end is then heated by
wood fire to a full red heat, and the other end slid in and the whole
allowed to cool.
(2) The joint in a pipe line which is made in the field.
Field Tube. — An arrangement of two concentric tubes, which greatly
improves the circulation and steaming capacity of a vertical boiler;
the heated water rises in the annulus between the inner tube and
the exterior heating surface, while the cold water circulates down the
inner tube.*
Fire Hydrant. — A hydrant suitable for serving fire hose or engines.
Fire Plug. — See Fire Hydrant.
Fillings. — A term used to denote all those pieces that may be attached
to pipes in order to connect them or provide outlets, etc. — except
that couplings and valves are not so designated.
See Ammonia, Back Outlet Ell, Branch Ell, Branch Tee, Bull Head
Tee, Bushing, Cap, Casing, Clean Out, Cross, Cross Over, Cross
Over Tee, Crotch, Double Branch Ell, Double Sweep Tee, Drainage,
Drop Elbow, Drop Tee, Eccentric, Elbow, Four- way Tee, H Branch,
Heel Outlet Elbow, Increaser, Inverted, Kewanee, Lateral, Long
Turn, Manifold, Pipe, Plug, Railing, Reducer, Reducing Taper El-
bow, Reducing Tee, Return Bend, Return Elbow, Saddle, Service
Ell, Service Tee, Siamese Connection, Side Outlet Ell, Side Outlet
Tee, Street Elbow, Tee, Three-way Elbow, Union, Union Ell, Union
Tee, Wye, and Yoke.
Flange. — A projecting rim, edge, lip or rib. See Blank, Blanking, Blind,
Boiler, Circular, Collar, Curved, Internal, Peened, Pressed, Rein-
forced Pump Column, Riveted, Rolled Steel, Saddle and Spun
Flange.
Flanged. — (i) When applied to a fitting it is used to distinguish from
screwed fittings which are always furnished, unless flanges or other
style of joint is specified.
(2) When applied to pipe it means fitted with flanges.
Flanged Joint — A joint in pipes made by flanges bolted together.
Flanged Pipe. — Pipe provided with flanges so that the ends can be held
together by means of bolts.
Flange Union. — A fitting consisting of a pair of flanges and bolts to con-
nect them for use on threaded pipe. Compare union and lip union.
Flat Head. — (i) Term applied to heads of cylinders meaning that they
are neither convex nor concave.
(2) Meaning shape of head when applied to brass or iron cocks.
Flexible Joint. — Any joint between two pipes that permits one of them
to be deflected without disturbing the other pipe.
Flue. — A British term used in the same sense as the term "tube" is
used in America.
Flue Boiler. — A boiler having smoke flues which pass through the water.
When there are many flues of small size the term "tubular boiler" is
more usual.
492 Glossary of Terms Used in the Pipe and Fitting Trade
Flue Cleaner. — Tube cleaner. — Frequently a wire brush or soot
scraper. At times called a "flue brush."
Flush Bushing. — A fitting intended to reduce the opening of a given
fitting by screwing in flush with the face of the fitting.
Flush Joint. — A threaded joint made by turning off nearly half the
thickness of the pipe at one end and boring in same manner at the
other end, and then threading with a fine thread.
Follower. — A half coupling or lock nut used on a long screw. See Long
Screw.
Four-Way Cock. — A cock so designed that the body has four passages
and the plug has two passages. It may serve to control the flow
of both a supply and exhaust.
Four-Way Tee. — A side outlet tee. (Poor usage.)
Free on Rails. — Signifying that all charges save those of railway trans-
portation are paid by the vender.
Full Way Valve. — (i) A sluice or gate valve for steam, etc., contrived
to give a full bore opening of the same area as the pipe.*
(2) Used in error at times to signify a straight way valve.
Full Weight Pipe. — A term used to designate Standard or Card Weight
Pipe, which is the Briggs' standard thickness of pipe.
Gage. — The main gages used in the pipe trade are threaded plug and
ring gages.
Gage Cock. — A small cock in a boiler at water line, to determine the
water level.
Gage Length. — (i) The distance gage goes on threaded end of pipe by
hand.
(2) Used synonymously for cut lengths.
Gage Ring. — A ring used for gaging the thread on pipe.
Galvanizing. — The process by which the surface of iron and steel is
covered with a layer of zinc.
Gasket. — A thin sheet of composition or metal used in making a joint.
Gas Thread. — Briggs' Standard in America; but in England, use is
indefinite, though it usually means Whitworth thread on 4 inches
and under.
Gate Valve. — A sluice valve; one having two inclined seats between
which the valve wedges down in closing, the passage through the
valve being in an uninterrupted line from one end to the other,
while the valve, when opened, is drawn up into a dome or recess,
thus leaving a straight passage the full diameter of the pipe.*
Globe Valve. — A valve having a round, ball-like shell; it is much in use
for regulating or controlling the flow of gases or steam.
Go Devil. — (i) A scraper with self-adjusting spring blades, inserted in a
pipe line, and carried forward by the fluid pressure, clearing away
accumulations of paraffin, etc., from the walls of the pipe.*
(2) In the oil well country this term is applied to a device for explod-
ing the nitroglycerine used to "shoot" an oil well.
Definitions 493
Goose Neck. — A return or 180 degree bend having one leg shorter than
the other.
Ground Joint. — See Dry Joint.
Grummet or Grommet. — A "cow tail" (frayed end of a piece of rope or
twine) smeared with red lead in oil and used about the threads to
make a tight joint in British pipe fitting practice.
H
Half Turn Socket. — In oil well drilling, a fishing tool having jaws bent
around in an incomplete circle, to embrace lost tools lying against
the side of the well.*
Hand Tight. — (i) Tightened by hand with such effort as an average
man can continuously exert. It does not refer to such forcing as
can be done by a man picked for his strength.
(2) The standard gages are correct as to size when put on hand tight.
Hard Solder. — Brazing Solder. It usually is copper and zinc —
half and half by weight. Other alloys are used for special work;
frequently, pure copper is used. The usual flux is Borax.
Hazelton Head. — One formed by swaging the end of a pipe nearly to a
point, and then welding up the end, either alone or after insertion
of rivet or button. The head, when finished, is nearly hemi-
spherical.
H Branch. — In plumbing, a pipe fitting having a branch parallel and
close to the main line.*
Head. — See Bumped, Casing, Dished, Drive, Flat, Hazelton, and Pat-
terson Head.
Header. — A large pipe into which one set of boilers are connected by
suitable nozzles or tees, or similar large pipes from which a number
of smaller ones lead to consuming points. Headers are often used
for other purposes, such as heaters or in refrigeration work. Headers
are essentially branch pipes with many outlets, which are usually
parallel. Largely used for tubes of water tube boilers.
Heel Outlet Elbow. — See Branch Ell.
Horn Socket. — In well boring, an implement to recover lost tools,
especially broken drill poles, etc. It consists of a conical socket,
the larger end downwards, which slides over the broken part, a
spring latch gripping it when entered. Frequently a flaring mouth-
piece is riveted to the horn socket, making it a bell mouth socket.*
Hot Drawn. — A term used to signify the product of drawing, when the
operation is performed on material that is hot — usually red hot,
e.g. — hot drawn seamless tubes. The term is sometimes applied
to the Mannesmann product that has not been drawn.
Hot Tube. — A tube or pipe lined inside with porcelain, to enable it to
withstand firing through without excessive oxidization.*
Hub. — (i) Usually means a cast iron outside ring or collar used to
join two pipes.
(2) Bell end of cast iron pipe, or similar end in fitting or valve.
(3) Collar of a flange.
494 Glossary of Terms Used in the Pipe and Fitting Trade
Hydrant. — An outlet placed at or near a main, and provided with a
valve to control flow, and with an end suited to attach hose. Those
made to serve fire hose, or engines in cold climates, usually have the
valve below the frost line, and are so arranged, that when the flow
is shut off, the hydrant will drain to prevent freezing up.
Hydraulic Main. — In gas making, the large pipe, partly filled with
water, into which the dip pipes discharge the gases, etc., coming
from the retorts.*
Hydrostatic Joint. — Used in large water mains, in which sheet lead is
forced tightly into the bell of a pipe by means of the hydrostatic
pressure of a liquid, preferably tar.*
Increaser. — (i) In plumbing, a fitting to join the female end of a small
pipe to the male end of a larger pipe.
(2) This is the name applied, at times, to a special type of reducer,
whose large end may be a male end for any type of joint and whose
small end is always female and tapped for Standard Pipe. (Poor
usage.)
Indicator. — A device placed at a valve or fire hydrant and so arranged
that it shows whether the valve is open or closed.
Inserted Joint. — The correct name of the joint which at times is called
"expanded joint" or "swelled joint." The joints are formed by
expanding one end of each pipe so that, when threaded on their in-
terior, they permit screwing in the exteriorly threaded ends that
have not been expanded. It is employed mostly on casing.
Internal Feed Pipe. — A pipe perforated at the end, leading the feed
water from the check valve opening through the hotter portions
of the boiler to the coldest, thus assisting circulation, and gradu-
ally introducing the feed water without shock.*
Internal Flange. — A flange that projects from the inner surface toward
the center. Used in contradistinction to external flange, which is
always meant when the word flange is used without qualification.
Inverted Fitting. — In plumbing, a fitting reversed in order of position
— upside down — turned in contrary direction.
Jars. — In well boring, a connection between the sinker bars and the
poles or cables, made in the form of two links, having a slide on each
other of about two feet. The jars permit the tools to fall on the
downward stroke, but on the upward jar them, or give them a sharp
pull, tending to loosen them from any crevices or cavings that may
hold them; a drill jar.*
Joint. — In the pipe trade, applies to the means used to connect pipes to
each other or to fittings.
See Ammonia, Armstrong, Artesian, Ball, Bell and Spigot, Block,
Bumped, Butted and Strapped, Converse Lock, Corrugated, Cressed
Definitions 495
Artesian, Cup, Cup and Ball, Dresser, Drive Pipe, Dry, Eckert,
Expanded, Expansion, Field, Flanged, Flexible, Flush, Ground,
Hydrostatic, Inserted, Kimberley, Knock-off, Lead, Lead and Rub-
ber, Line Pipe, Matheson, National, Normandy, Peened Flangod,
Perkins, Petit's, Pope, Pressure, Riedler, Rust, Shrunk, Siemens,
Slip, Socket, Spigot, Swing, Swivel, Thimble, Union, Van Stone,
Walker, Welded Flange and Wiped Joints.
Jointer. — (i) A pipe trade term used to express a random length com-
posed of two pieces coupled together. Custom of the pipe trade
is that shipments include a small proportion of such lengths.
(2) The term jointer also is applied to very small style of flanges
that are suitable for connecting pipes to each other, but not suitable
for connecting to fittings.
Kalameined. — Coated in a manner similar to galvanizing, but using a
composition of lead, tin and antimony.
"Kewanee." — As applied to fittings and valves this word indicates that
the "Kewanee" Union principle is involved.
Kewanee Union. — A patented pipe union having one pipe end of brass
and the other of malleable iron, with a ring or nut of malleable iron,
in which the arrangement and finish of the several parts is such as
to provide a non-corrosive ball and socket joint at the junction of
the pipe ends, and a non-corrosive connection between the ring and
brass pipe end.
Kimberley Joint. — Originally a joint of English manufacture exten-
sively used in the South African Mining District. It consists of an
outer wrought sleeve or ring belled out on the ends to form a suit-
able lead recess for calking, the pipes butting in the center of the
sleeve.
Knock Of Joint. — In well drilling, a joint used in the rods of deep well
pumps. The jointed ends of the rods are enlarged to a square
section and scarfed and notched to fit against one another, and are
confined by a clasp or bridle embracing them. The joint is ta-
pered lengthwise and the hole in the clasp is tapered to correspond,
so that the tendency is always for the clasp to tighten around the
joint.*
L
Laid Length. — (i) The length measured after pipe is placed in posi-
tion. It is not the same as the "shipped length," which latter is
measured over all as shipped, and it is greater than the " cut length,"
which applies to length of tubular goods only. The laid length
includes such items as gaskets or space between ends of pipe in
coupling or the insertion of bell and spigot joint or the central
ring of C. J. hub.
(2) Laid length is never considered unless order clearly refers to it.
To specify it on an order or a drawing always delays execution,
unless every essential detail is given.
496 Glossary of Terms Used in the Pipe and Fitting Trade
Lap-weld. — Welded along a scarfed longitudinal seam in which one
part is overlapped by the other.
Laterals. — See Wye.
Lead. — The advance made by one turn of a screw. Often confused
with pitch of thread, but not the same, unless in the case of a single
thread. With a double thread the lead is twice as much as the
pitch.
Lead and Rubber Joint. — (i) The ordinary name for any joint in which
lead and rubber are employed.
(2) The combination of Matheson Joint and Dresser Clamp is not
usually called by this name but acts in the same manner.
Lead Joint. — (i) Generally used to signify the connection between
pipes which is made by pouring molten lead into the annular space
between a bell and spigot — and then making the lead tight by
calking.
(2) Rarely used to mean the joint made by pressing the lead between
adjacent pieces as when lead gasket is used between flanges.
Lead Joint Runner. — See Pouring Clamp.
Lead Lined Pipe. — A wrought pipe having a continuous interior lining
of lead. When used on flanged pipe the lining is often brought out
over the face of the flanges. The lead lining is usually as thick as
the same size of lead pipe. It is useful for conducting certain cor-
rosive fluids.
Lead Wool. — A material used in place of melted lead for making pipe
joints. It is lead fiber, about as coarse as fine excelsior and when
made in a strand it can be calked into the joints making them very
solid.
Leak Clamp. — Packing Clamp — Half Dresser Joint. — Usually super-
posed on some other joint as that made with a coupling.
Line Pipe. — Special brand of pipe that employs recessed and taper
thread couplings, and usually greater length of thread than Briggs'
Standard. The pipe is also subjected to higher test.
Line Pipe Joint. — The screwed joint used on line pipe.
Lip Union. — (i) A special form of union characterized by the lip that
prevents the gasket from being squeezed into the pipe so as to ob-
struct the flow.
(2) It is a ring union, unless flange is specified.
Lock Nut. — (i) A nut placed on a parallel threaded portion of pipe at a
joint in order to stop leaks by means of a grummet, gasket or packing.
(2) Also used to make a joint where the long screw or lock nut
nipple has been run through the tank, the lock nuts being used to
wedge up against the tank on either side.
Long Length. — A length of pipe greater than can ordinarily be made
from one length of plate. The long length is made by uniting two
pipes by a circular or safe end weld. Long lengths — less than
40 feet — can be produced in one piece, without weld, by certain
processes.
Long Screw. — A short length of pipe having ordinary thread on one end,
and the other end threaded for such distance as will allow a lock
Definitions 497
nut and a coupling to be screwed by hand without overhanging the
end of pipe. It is used in making up connections or joining lines
in place.
Long Screw Follower. — A half coupling or lock nut used on a long screw.
Long Turn Fitting. — A term variously employed to mean long sweep,
long radius or an angular branch, e.g., a long turn branch may be
one whose branch makes about 45° with the run, but end of branch
is sharply turned to 90° to run.
Loop. — See Expansion Loop.
M
Male and Female. — (i) Sometimes called recessed; usually written
M. & F. It means that one flange of a pair is faced so as to pro-
duce a flat, depressed face, extending from inside of pipe nearly
to bolt holes. The other flange is faced so as to have a raised
portion at same place and only slightly less diameter. The object
is to prevent the gasket from blowing out.
(2) Also means Male and Female thread.
Malleable Iron. — Cast iron made from pig iron of the proper kind, so
treated as to render it capable of being bent or hammered to a
limited extent without breaking, that is, it is malleable. Its
strength is above that of cast iron. The treatment is known as
annealing.
Mandrel Socket. — A well tool for straightening out the top of casing,
etc., within a well, consisting of a lemon-shaped swage within a
cone or bell-mouth, by means of which the casing is worked to a
circular shape. Also useful for straightening a lost sand pump, etc.,
so that the dogs may enter.*
Manifold. — (i) A fitting with numerous branches used to convey fluids
between a large pipe and several smaller pipes. See Branch Tee.
(2) A header for a coil.
Mannesmann. — A name applied to the product of tube making proc-
ess, invented by Herr Mannesmann.
Master Die. — A die made standard and used only for reference pur-
poses or for threading taps.
Master Tap. — A tap cut to standard dimensions and used only for
reference purposes or for tapping master dies.
Matheson and Dresser Joint. — A combination joint in which a Dresser
leak clamp of special form is used to reinforce a Matheson joint.
Its special advantage is that it allows repair without shutting off
the service pressure. Much used on Natural Gas lines on service
pressures up to 250 pounds and at times up to 500 pounds, and on
pipes 1 6 inches outside diameter and less — and even on 20 inches
outside diameter.
Matheson Joint. — A wrought pipe joint made by enlarging the one end
of the pipe to form a suitable lead recess, similar to the bell end of
a cast iron pipe, and which receives the male or spigot end of the
next length. Practically the same style of a joint as used for cast
iron pipe.
498 Glossary of Terms Used in the Pipe and Fitting Trade
Measurement equals weight. — A commercial transportation term indi-
cating that the specific weight is high enough to secure the freight
tariff that is based on weight under steamer's measurement for
ocean transit.
Medium Pressure. — When applied to valves and fittings, means good
for a working pressure of 125 to 175 pounds per square inch.
Melting Furnace. — A small portable furnace (some designs are mounted
on wheels) used for melting lead for lead joint pipe.
Mounted. — When applied to pipe fittings, valves, etc., in such expres-
sions as brass-mounted, nickel-mounted, etc., means having the
rubbing or wearing surfaces composed of the material named.
N
National Joint. — A bell and spigot joint whose bell is contracted at its
mouth, so as to retain self tightening (U shaped) ring of rubber or
other pliable material.
National Pole Socket. — An extension piece for repairing wooden poles
that have rotted at ground line. It is a piece of pipe suitably
shaped to hold the tapered lower end of upper portion of such
pole.
Needle Valve. — At times called a needle point valve. A valve provided
with a long tapering point in place of the ordinary valve disc. The
tapering point permits fine graduation of the opening.
Nested. — Having one piece placed within another (i.e., telescoped) . A
thing that is done with pipes and fittings at times, to get a required
weight into a given space. See Steamer's Measurements.
Nipple. — (i) A tubular pipe fitting usually threaded on both ends and
under 12 inches in length. Pipe over 12 inches long is regarded as
cut pipe. See Close, Long Screw, Short, Shoulder, Space, Sub and
Swaged Nipple. v.
(2) Boss or Pop — A thickened or raised place outside or inside of
pipe made by welding on a button or pop. It is used on a thin wall
when it is desired to tap a hole. These reinforcements are usually
flush inside or outside as specified.
Non-Return Valve. — A stop valve whose disc may move independently
of the stem so that valve may act as a check. Such valves are
largely used between boilers and headers to prevent accidents.
Normandy Joint. — A joint by which the plain ends of two pipes are
connected by means of a sleeve whose ends are made tight by
rings of packing, compressed between bolting rings and sleeve.
There are many similar joints or modifications such as Dayton,
Dresser, Hammond, etc.
Nozzle. — (i) A short piece of pipe with a flange on one end and a
saddle flange on the other end. May be made of cast iron, cast
steel or wrought steel.
(2) A side outlet attached to a pipe by such means as riveting, braz-
ing or welding.
Nut. — See Lock Nut.
Definitions 499
Offset Pipe. — (i) A pipe bent so as to offset a line, i.e., move the line
to a position parallel to, but not in alignment with, balance of the
pipe.
(2) A fitting to accomplish the same.
(3) Erroneously used for crossover.
(4) Erroneously used for bend.
(5) Erroneously used for branch pipe.
Open Return Bend. — A short cast or malleable iron U-shaped tube for
uniting two parallel pipes. It differs from a close return bend in
having the arms separated from each other.
Oval Socket. — In well boring, a fishing tool used to slip over the ends
of broken and lost poles, to grip so as to recover them.*
Packer. — A device used in an oil or gas well to stop flow in or around
the casing or tubing. See Water Packer.
Packing. — (i) A general term relating to yielding material employed
to effect a tight joint. A common example is the sheet rubber used
for gaskets. The term is also applied to the braided hemp or
metallic rings used in some joints, that allow considerable or in-
cessant motion. The British grummet is another example.
(2) Any material used in packing stuffing boxes of valves.
Patterson Head. — One that has the pipe reduced or swaged to about
half its diameter and then a flat head welded in.
Peened Flange Joint. — A term used to indicate that the flanges are
attached to the pipe by peening — just as welded flange, riveted
flange or screwed flange are terms that indicate the method of
attachment of flange to pipe. Many designs — or almost any
design — can be so attached. The flanges usually depend in part
upon beading of pipe at face, although some designs require grooves
inside of collar flange, into which grooves the metal is forced by
the peening.
Peening. — The act or process of hammering sheet metals with the
peen of a hammer, either to straighten them or to impart a desired
curvature.*
Penstock. — (i) The conductor between forebay and turbine casing.
At times that portion of a forebay that is subject to hydrostatic
pressure — used for any type of water wheels.
(2) A railroad term applied to the pipe for supplying water to loco-
motive tenders.
Perforated. — That in which holes have been bored or pierced. In
pipe it is usually accomplished by drilling holes, but the same
result can be accomplished cheaply by punching.
Perkins Joint. — One made up with threaded pipe and coupling, both
threaded straight (no taper). The one end of the pipe is left
square and the other is beveled to a knife edge at mid-thickness.
Has been used in Baku oil region.
500 Glossary of Terms Used in the Pipe and Fitting Trade
Pet Cock. — A small cock used to drain a cylinder, fitting, etc. The
term means nearly the same as drip or drain cock.
Petit' 's Joint. — One constructed with a double male and female in
which a round rubber is used.
Pilot. — A small valve to operate or relieve pressure on a larger valve.
Pipe. — A long conducting passage, usually a line of tubes; any long
tube or hollow body; especially one that is used as a conductor of
water or other fluids, as a drain pipe, water pipe, etc.*
See Branch, Breeches, Card Weight, Conduit, Converse Lock Joint,
Dip, Double Extra Strong, Drive, Dry, Eduction, Expansion, Extra
Strong, Flanged, Full Weight, Internal Feed, Kimberley Joint, Lead
Lined, Line, Matheson Joint, Offset, Plug, Reamed and Drifted,
Rifled, Riser, Service, Signal, Siphon, Socket, Soil, S, Stand, Stand-
ard, Tail, Tin Lined and Tuyere Pipe.
Pipe Bend. — A bent pipe in contradistinction to a bend, which may
be a casting. See Bend.
Pipe Bending Machine. — An apparatus by which pipe of any ductile
metal may be bent or coiled as desired. Some use rollers and internal
mandrels or coils, but the most usual type uses formers and saddles
and operates without internal mandrel or fitting. The necessity
for internal mandrel or fitting is determined mostly by the ratio of
the thickness to the diameter. Where the wall is relatively thin
something inside appears obligatory to prevent buckling, crumpling
or collapsing.
Pipe Clamp. — A metallic strap or band, made to fit around a pipe,
gripping it closely, for the purpose of stopping leaks, etc., a piece
of jointing material being usually compressed between the clamp
and the pipe.*
Pipe Coupling. — A sleeve or socket of cylindrical form with female
threads, which receives the ends of two adjacent pipe lengths.*
Pipe Covering. — A jacket of non-conducting material placed around
steam (or other) pipes to prevent loss of heat.
Pipe Cutter. — An instrument for cutting off wrought pipes. A com-
mon type is made with a hook-shaped frame on whose stem a slide
can be moved by a screw. On the slide or frame one or more cut-
ting discs are mounted, and forced into the metal as the whole
appliance is rotated about the pipe.
Pipe Die. — A tool for cutting external threads on pipes. Many types
are composite with inserted cutters.
Pipe Dog. — A hand tool that is much used to rotate a pipe whose end
is accessible. It is simply a small short steel bar whose end is bent
at right angles to the handle, and then quickly returned leaving only
enough space between the jaws to slip over the wall of pipe.
Pipe Fittings. — Connections, appliances and adjuncts, designed to be
used in connection with pipes, such as elbows and bends to alter
the direction of a pipe; tees and crosses to connect a branch with a
main; plugs and caps to close an end; bushings, diminishers or re-
ducing sockets to couple two pipes of different dimensions, etc.*
See Fittings.
Definitions 501
Pipe Grip. — In steam and pipe fitting, an implement consisting of an
iron bar. with a curved end and provided with a chain of square
links to hook on to the jaws of the curved end.* See Chain Tongs.
Pipe Hanger. — A suspension link or band (often split) used to support a
pipe without interfering with its expansion and contraction.
Pipe Line. — (i) A line of pipe used for the transporting of liquids or
gases.
(2) It has an entirely different meaning from "Line Pipe," which
see.
Pipe Roller. — In construction work, these are made of different lengths
of wrought pipes to suit the work, and used as rollers for moving
heavy articles and machinery.
Pipe Stay. — A pipe hanger — an unusual term.
Pipe Stock. — A holder for dies by means of which threads are cut on
pipes by hand.*
Pipe Thread. — A thread employed in connection with wrought pipe.
The standard thread is the Briggs', which has an angle of 60 degrees
between its sides, slightly rounded at top and bottom, and which
has a taper. See Briggs' Standard.
Pipe Tongs. — A hand tool for gripping or rotating pipe. It is fre-
quently made like a large pair of pliers one of whose noses is hook-
shaped and the other is made shorter and sharpened so as to dig
into the pipe. Chain tongs and pipe wrenches are used for about
the same purpose.
Pipe Unions. — Erroneously used, at times, to signify pipe joints.
Pipe Vise. — A special type of vise usually attached to a work bench.
It is frequently made with three serrated jaws, one of which moves
between the other two and may be forced against the pipe by
screw or toggle. At times made with an open or latching side to
permit rapid work.
Pipe Wrench. — A wrench whose jaws are usually serrated and arranged
to grip with increasing pressure as the handle is pulled. There are
many forms such as the Alligator, Stillson, Trimo, etc.
Piping. — In plumbing, steam and gas fitting, the whole system of
pipes in a factory, mill or house; the act of laying a pipe system.*
Pitch. — (i) The distance measured on a line parallel to the axis, be-
tween two adjacent threads or convolutions of a screw.
(2) The distance between the centers of holes, as of rivet holes in
boiler plates.*
Plain End. — Usually contracted to P.E. — Used to signify pipe cut
off and not threaded, i.e., ends left as cut.
Plug. — (i) When used without qualification, it always means, in the
pipe trade, the ordinary plug or pipe plug that has an exterior
pipe thread and a projecting head (usually square), by which it
is screwed into the opening of a fitting, etc.
(2) Compare countersunk plug.
(3) The movable part of a tap, cock or faucet.*
(4) Colloquially used for hydrant, penstock, standpipe, water plug,
etc. See Socket, Tap, Tube and Water Plug.
502 Glossary of Terms Used in the Pipe and Fitting Trade
Plug Cock. — Usually called a cock. All cocks are essentially plug cocks.
Plug Gage. — A plug or internal gage for measuring inside dimensions.
Plug Pipe. — A short piece of pipe, screwed with a male thread at one
end and closed or welded at the other, used as a plug to close an-
other pipe or an opening in a fitting, when a proper plug is not
obtainable.*
Plug Tap. — A tap with threaded portion straight or without lead,
used for bottoming.
Pole Drill. — In well boring, a system where a rigid connection is used
between the drilling tools and the reciprocating beam.*
Pop. — (i) A spring loaded safety valve.
(2) A boss or nipple cast on a fitting or welded to a pipe.
Pope Joint. — A joint very similar to the Van Stone. In one form the
flange is separately formed and welded to the pipe.
Pouring Clamp. — Lead Joint Runner — Some forms are made of metal,
others of rubber and others of asbestos. The commonest make-
shift is a piece of frayed rope smeared with clay. All styles serve
to guide the lead into space provided for it in lead joint pipe.
Pressed Flange. — Usually signifies a light style of flange, made from
plate steel by press forging or forming. When the flange is so
made of heavy stock, whose thickness is changed by the forging,
it is better to call the product Press Forged. Some flanges are
Press Forged part way and then rolled. See Rolled Flanges.
Pressed Forged. — A term used to indicate the operation of forming by
steady pressure as distinguished from forging by hammering or
rolling or drawing. The distinction between "Press Forging" and
"Press Forming" is that the former changes the thickness or sec-
tion materially, while the latter only changes the form and may
incidentally change the section or thickness.
Pressure Joint. — A term used by British trade to signify that the
threads of both pipe and coupling are tapered. It closely corre-
sponds to American joints used on Line Pipe, Casing or Tubing, etc.
Protector. — A ring threaded on its inside and used to protect threaded
end of pipe during transit.
Pump Column Flange. — See Reinforced Pump Column Flange.
Radiator. — That which radiates or sends forth heat, as by a coil of
steam or hot water heating pipes.
Radiator Valve. — An angle valve such as is fitted to a steam or hot
water heating radiator.
Radius of Bend. — (i) The distance measured always from the center
of curvature to the center of the pipe or fitting. The relation be-
tween length of radius and size of pipe is modified by the ratio of
the pipe's thickness to its diameter; in general the thinner the pipe
the longer the radius.
(2) The radial distance from the center line of a fitting to the center
of curvature, about which the body of a fitting is struck or swept.
Definitions 503
Railing Fittings. — Those used on hand rails. There are various
styles. To the trade, rail fittings are understood to be globe
shaped in the body, with ends reduced to take thread.
Raised Face. — A term used to indicate that flanges are faced l/32 inch
or so higher inside of the bolt circle.
Random Length. — The " catch length" or length of good quality pipe,
made from any piece of plate skelp after its ends have been
trimmed. For Butt and Lap Weld pipes usually about 20 feet or
less.
Reamed. — In pipe trade, means having the burr from cutting off tool
removed from inside, at ends, by a slight countersinking.
Reamed and Drifted. — Usually contracted to R. & D. See the separate
terms.
Receiver Filling Valve. — A valve of peculiar construction for the ad-
mission of compressed gas to the receiver, so that it can be trans-
mitted to the regulator for consumption.
Recessed. — (i) Counterbored for a short distance when applied to
couplings.
(2) Counterbored or provided at back with a calking recess when
applied to flanges.
(3) Erroneously applied, at times, to flanges to mean M. & F. to dis-
tinguish them from T. & G. or P. F.
Reducer. — (i) A fitting having a larger size at one end than at the
other. Some have tried to establish the term "increaser" —
thinking of direction of flow, but this has arisen from a misunder-
standing of the trade custom of always giving the largest size of
run of a fitting first; hence, all fittings having more than one size
are reducers. They are always inside thread, unless specified flanged
or for some special joint.
(2) Threaded type is made with abrupt reduction.
(3) Flanged pattern has taper body.
(4) Flanged eccentric pattern has taper body, but flanges at 90 de-
grees to one side of body.
(5) Misapplied at times, to a reducing coupling.
Reducing Taper Elbow. — A reducing elbow whose curved body uni-
formly decreases in diameter toward the small end.
Reducing Tee. — Any tee having two different sizes of openings. It
may reduce on the run or branch.
Reducing Valve. — (i) A spring or lever loaded valve similar to a safety
valve, whereby a lower and constant pressure may be maintained
beyond the valve.
(2) A valve for reducing the pressure of air admitted to a train signal
pipe below that maintained in the brake pipe and main reservoir.
Reflux Valve. — In hydraulics, a flap valve used for the purpose of taking
off the pressure of a head of water acting in a backward direction
against a set of pumps.*
Reinforced Pump Column Flange. — A flange that is secured to, or fas-
tened to, pipe by rivets in addition to being peened and beaded.
Reservoir. — An incorrectly used term to denote a cylinder.
504 Glossary of Terms Used in the Pipe and Fitting Trade
Return Bend. — 180 degree bend. — Usually a fitting having inside
threads. Often applied to a bent pipe. Always means the fitting
unless otherwise specified.
Return Bend with Back Outlet. — (i) A crotch having parallel outlet.
(2) A return bend with a back or outlet in line with one of the main
outlets.
Return Elbow. — A return or U bend of small radius.
Ribbed Tube. — In steam engineering, the ribbed tube introduced with
a view to improving the heating surface of the tubes of feed water
heaters. The tubes are simply rolled with internal deep ribs running
transversely. They are made in iron, steel, copper and brass. Also
called corrugated tubes.*
Riedler Joint. — One in which a cup leather is used as packing or gasket.
Useful for high pressure.
Rifled Pipe. — A pipe used for conveying heavy oils. The pipe is
rifled with helical grooves which make a complete turn through
360 degrees in about 10 feet of length.
Ring. — See Drive Pipe, Expansion and Gage Ring.
Ring Union. — The ordinary union used to connect pipes. The term
is used in contradistinction to flange union.
Riser Pipe. — A pipe extending vertically and having side branches.
River Dog. — A device to hold a pipe line on a river bottom.
River Sleeve. — A long sleeve used over other joints to prevent injury to
joints laid on river bottom or under water. An excellent form
requires sleeves to be about six (6) diameters long and fit as neatly
as possible to the outside of the central joint. It is so made to
prevent bending or springing of the pipe, which might injure or
loosen the joint.
Riveted Flange. — One whose collar is attached to pipe by rivets. The
pipe usually is not brought flush with face of flange, but stops about
iH inches to i% inches from center of rivets where it is calked.
One special design brings pipe flush with face of flange and another
design has end of pipe beaded into a recess.
Rod. — See Sucker Rod.
Rolled Steel Flange. — One that is forged from a steel bloom and then
rolled to shape by a mill similar to that used for rolling locomo-
tive or wheel tires. Some small sizes are drop forged, hammer
forged, or press forged. These processes are all considered to
yield rolled flanges, if the product is the required shape. See
Pressed Flange.
Run. — (i) A length of pipe that is made of more than one piece of pipe.
(2) The portion of any fitting having its ends "in line" or nearly so,
in contradistinction to the branch or side opening as of a tee.
The two main openings of an Ell also indicate its run, and when
there is a third opening on an ell, the fitting is a "side outlet" or
"back outlet" elbow, except that when all three openings are in one
plane and the back outlet is in line with one of the run openings,
the fitting is a "heel outlet elbow" or a " single sweep tee " or some-
times (less correctly) a "branch tee."
Definitions 505
Rust Joint. — Employed to secure rigid connection. It generally can-
not be separated except by destroying some of the pieces. It is
made by packing an intervening space tightly with a stiff paste
which oxidizes the iron, the whole rusting together and hardening
into a solid mass. One recipe is 80 pounds cast iron borings or
filings, i pound sal-ammoniac, 2 pounds flowers of sulphur, mixed to
a paste with water.
Saddle. — Strictly the saddle piece, which, assembled with the strap, or
straps, makes a service clamp.
Saddle Flange. — In pipe fitting, a curved flange hollowed out to fit a
boiler, a pipe, or other cylindrical vessel.*
Safe End. — A short piece of boiler tube of high quality that is, at times,
welded to a body of less quality or lighter gage or to old boiler
tubes whose ends have been injured.
Sand Line. — In well boring, a wire line used to lower and raise the bailer
or sand pump, which frees the bore hole from cuttings.*
Sand Pump. — A well drilling tool used for bailing out the muck pro-
duced by drilling.
Scarf Weld. — A joint that is made by overlapping and welding to-
gether the scarfed ends or edges of metal sheets.
Screw. — See Long and Temper Screw.
Screw Down Valve. — A valve which is opened and closed against a
seat by means of a screw. A term little used in America, but usual,
colloquially, with British workmen. Familiar examples are the
needle and globe valves. The term is not commonly applied to
slide or sluice valves.
Screwed. — Threaded.
Seamless. — Without seam, especially without a welded seam. Pipes
and tubes are made seamless by the cupping, Mannesmann or
Stiefel processes.
Setters Thread. — The standard screw thread of the United States,
having an angle of 60 degrees between the threads, and one-eighth
flattened at top and at bottom. It is also known as United States
Standard Thread and as the Franklin Institute Standard Thread.
Semi Steel. — See Ferro Steel.
Service Box. — Small Valve Box — Service Box is the name usually
employed for those boxes used with corporation or curb cocks.
Service Clamp. — A clamp applied to a main at a point of connection
for such use as a house service. It is also, but less correctly, called
"pipe saddle."
Service Ell. — An elbow having an outside thread on one end. Also
known as street ell.
Service Pipe. — A pipe connecting mains with a dwelling; as, in gas
pipes and the like.*
Service Tee. — A tee having inside thread on one end and on branch,
but outside thread on other end of run. Also known as street
tee.
506 Glossary of Terms Used in the Pipe and Fitting Trade
Sherardizing. — A process in which clean surface of iron or steel is
coated with a zinc-iron alloy to protect against rust.
Shoe. — See Casing and Drive Shoe.
Short Nipple. — One whose length is a little greater than that of two
threaded lengths or somewhat longer than a close nipple. It
always has some unthreaded shoulder between the two threads.
Shot Drill. — An earth boring drill using shot as an abrasive, somewhat
after the manner of a diamond drill.*
Shoulder Nipple. — A nipple of any length, which has a shoulder of pipe
between two pipe threads. As generally used, however, it is a
nipple about half way between the length of a close nipple and a
short nipple.
Shrunk Joint. — (i) A joint secured in place by shrinking a larger pipe
on a smaller one.
(2) A term at times applied to a form of collar flange that is attached
by shrinking the flange on the pipe and then expanding the pipe
to a trumpet mouth. This expanded mouth is its distinctive
feature.
Siamese Connection. — A crotch fitting, usually arranged with union
inlets for fire hose.
Side Outlet Ell. — An ell with an outlet at right angles to plane of run.
Side Outlet Tee. — The same as four-way tee.
Siemens Joint. — One for high pressure hydraulic work designed by
Dr. Siemens. It is extensively employed on the steam chests of
locomotives. Its essential feature is a soft copper wire in a groove.
Signal Pipe. — (i) Pipe made to the Signal Association Standard as to
size, thread, coupling, weight, etc., but not equipped with plugs
and rivets.
(2) Special pipe used on interlocking switches and their signals on
railroads. It has a peculiar joint, that is both threaded and con-
nected by a plug riveted to the pipe.
Signal Thread. — The thread used on Signal Pipe. Usually longer
than Briggs' Standard and of less taper.
Sinker Bar. — A heavy bar of round iron which goes to make up the
weight in a string of well boring tools. The sinker connects the
drill bit with the jars, and is sometimes made in two lengths on
account of easy handling; in such a case, the upper half is some-
times known as the sinker and the lower part as the auger stem.*
Siphon. — (i) A pipe bent in the form of U or D acting on the principle
of the hydrostatic balance so that the pressure of water in one leg
always tends to equalize that in the other.
(2) A bent tube or pipe with limbs of unequal length for transferring
liquids from a barrel or other receptacle. The action of the in
strument is due to the difference in weight of the liquid in the two
legs.
(3) A U shaped tube fitted to steam gages, etc., so that nothing but
water shall enter the gage.
(4) In railways, the curved pipe of gradually increasing section which
leads from a water scoop into the tender.*
Definitions 507
Siphon Pipe. — A bent tube with unequal limbs by means of which
liquids are drawn from a vessel; the shortest limb being placed in
the liquid to be drawn off; it is set in action by exhausting the air
from the longer.*
Skelp. — A piece of plate prepared by forming and bending, ready for
welding into a pipe. Flat plates when used for butt-weld pipe are
called skelp.
Sleeve. — A coupling, collar or hub — Also a special form of Converse
Joint Hub that omits the central ring and permits the rivets to
pass clear through. See River Sleeve.
Slip Joint. — An inserted joint in which the end of one pipe is slipped
into the flared or swaged end of an adjacent pipe. The two pipes are
often soldered together.
Smith's Coating. — Dr. Angus — See Angus Smith.
Socket. — (i) A recess or piece furnished with a recess, into which
some other piece may be inserted and securely held; as, a socket in
the ground for the reception of a post or pole.*
(2) The British term for what is called a coupling in America.
(3) The enlarged and recessed end of a cast iron pipe into which the
opposite end of another pipe is inserted. See Half Turn, Horn,
Mandrel, National Pole, Oval and Wide Mouth Sockets.
Socket Coupling. — British term for what is known in America as a
coupling.
Socket Iron. — A bar from which pipe couplings are made.
Socket Joint. — The British equivalent of the American term Coupling
Joint.
Socket Pipe. — In pipe fitting, a cast iron pipe which is provided with a
socket at one end and a spigot at the other. The sockets of wrought
pipes are couplings, and are screwed over the ends on the outside
diameter.*
Socket Plug. — In steam fitting, a plug for stopping the ends of pipes
or openings in pipe fittings. It differs from the ordinary plug, in
that it is provided with a recess into which a wrench fits.
Soft Solder. — Tin and lead alloy. The first grade is half and half by
weight, which melts at a lower temperature than either lead or
tin.
Soil Pipe. — In plumbing, a pipe which conveys away the waste from
water closets, etc., usually made of cast iron.
Solder. — An alloy used for connecting two pieces that are less easily
melted. See Hard and Soft Solder.
Space Nipple. — A nipple with a shoulder between the two threads. It
may be of any length long enough to allow a shoulder.
Special Product. — Not Standard. Also used to mean a product that
is not made to any of the regular lists of goods.
Spellerizing. — The method of treating metal, which consists in sub-
jecting the heated bloom to the action of rolls having regularly
shaped projections on their working surfaces, then subjecting the
bloom to the action of smooth faced rolls, and repeating the opera-
tion, whereby the surface of the metal is worked to produce a uni-
508 Glossary of Terms Used in the Pipe and Fitting Trade
formly dense texture, better adapted to resist corrosion, especially
in the form of pitting.
Spigot. — (i) The end of a pipe, fitting or valve that is inserted into the
bell end.
(2) The tapered male part of an inserted joint, as in plumbers*
wiped joint.*
(3) A cock, tap or faucet used to draw water, etc.
Spigot Joint. — A pipe joint made by tapering down the end of one
piece and inserting it into a correspondingly widened opening in
the end of another piece. Also called faucet joint (unusual).
Spinning. — The operation of changing the shape of a rapidly revolving
plate or tube by the action of a spinning tool. In light work the
tool is usually similar to a burnishing point, but on heavy work a
wheel or revolving head is often used. At times the work is sta-
tionary and the tool moves. The product is called "Spun Work."
— See Spun Flange.
5 Pipe. — In pipe fitting, a pipe whose outline is roughly that of the
letter S, used for connecting parallel lengths of straight piping.
Also called offset elbow or offset bend.*
Spot Faced. — A term used to indicate that an annular facing has been
made about a bolt hole, to allow a nut or head to seat evenly.
Spring. — A pipe bent to a small angle. (Poor usage.)
Spud. — (i) Oil Well Fishing Tool. In well boring, a tool shaped like
a spade, for freeing lost or broken tools by digging around them.*
(2) A bushing or coupling, by which the hole of a sink or water cooler
drip is connected with the drain or drain pipe.
Spun Flange. — A flange formed from the material of the pipe by
spinning, e.g. — A Van Stone flange may be made by press forming,
peening, or by spinning.
Squib. — A detonator; in well boring, a vessel containing the explosive
and fitted with a time fuse which is lowered down a well to detonate
the nitroglycerin used to torpedo it.*
Standard Pipe.-(i) The standard adopted by the Wrought Pipe
makers in 1886. The Briggs' standard runs to 10 inch size inclu-
sive, and by extension the pipe sizes embrace the nominal sizes
11-12-13-14 and 15 inches. For the n and 12 inch sizes the out-
side diameters are 11.75 and 12.75 inches, while for 13-14 and
15 inches the outside diameters are one inch larger than the nominal
diameter. By later agreement 9 inch size was changed from Briggs'
size to 9.625 inches outside diameter. The thickness of all sizes
10 inches and under is determined by Briggs' rule; above 10 inches
it is 0.375 inch thick.
(2) Standard is a term frequently but unfortunately used to indicate
a regular or common product.
Standard Pressure. — A term applied to valves and fittings good for a
working steam pressure of 125 pounds per square inch.
Stand Pipe. — (i) In hot water heating, an upright pipe having its
top connected to the expansion tank to afford room for expan-
sion.
Definitions 509
(2) A vertical pipe arrangement, often of great size, at pumping
stations into which water is pumped.*
Stay. — (i) In the pipe trade, stay tube or upset tube.
(2) A bolt from tube sheet to tube sheet. This is also called a lon-
gitudinal or through stay.
(3) In boilers there are many different kinds of stays used, at times,
and their special names amply describe them, as crown, diagonal,
radial, girder gusset sling, cross, bolt, etc. See Tube Sheet Stay.
Stay Tube. — A boiler tube, stouter than the others, which is threaded
at each end and screwed through both tube plates to brace them
together. The ends are either beaded over, or else secured with
lock nuts. The threads are usually plus and minus; that is, the
thread at the front is larger than the outside diameter of the tube,
while that at back is the same diameter as the tube. Upset tubes
are often used as stays.*
Steam Coupling. — The word steam, when used in such phrase, means
that the coupling is threaded to suit Standard Pipe.
Steamer's Measurement. — The cubic space obtained from the greatest
width, length and height; used in determining ocean freight
which is based on 56 pounds = one cubic foot, or 40 cubic feet =
one ton (2240 pounds).
Stiefel Process. — A parallel process to Mannesmann or a modification
thereof — The product is seamless tubes or pipe.
Stove. — Stoved — Upset.
Straight Way. — (i) A term applied to valves to signify that the fluid
passes through without deviation. Such valves offer the least resist-
ance to flow, and permit the passage of such tools as "Go Devils."
(2) Full bore, straight flow, full way, full area are terms that at times
have been proposed to signify the same thing.
Street Elbow. — Service Ell.
Strum. — A strainer, or the like, to prevent the entrance of solid matter
into a pump chamber or suction pipe.
Sub Nipple. — Substitute nipple; that is, a short piece of pipe having
different styles of thread on its ends.
Sucker Rod. — In bored or drilled wells, the jointed pump rod, which
carries the bucket at its lower end, and is actuated by the walking
beam at its upper.*
Swaged. — Reduced in diameter by use of blacksmith's swages or
swedges, hence the name. This is a hammering process, but the
same result may be attained by press forging or spinning.
Swaged Nipple. — A nipple that has one end smaller than the other; a
reducing nipple.
Sweated. — A term used synonymously with tinned, that is, coated with
soft solder or tin. It is usual in making sweated joints on pipe to
sweat both the pipe and the fitting or socket separately before
sweating them assembled.
Sweep. — A term used to convey the idea that the curvature is not
abrupt: — i.e., that the flow may take place easily and without the
formation of eddies.
510 Glossary of Terms Used in the Pipe and Fitting Trade
Swelled. — Enlarged. Swelled end tubes usually have their ends en-
larged for a short distance. Also see Inserted Joint.
Swing Joint. — One made like a cock, except with only one outlet in the
body, and another outlet from the plug at right angle to axis of
plug.
Switch Valve. — A device for conducting exhaust steam into the smoke-
stack or atmosphere. A three-way cock.*
Swivel. — (i) In oil well drilling, a short piece of casing having one end
belled over a heavy ring, then a large hole through both walls, the
other end being threaded.
(2) Any device that prevents longitudinal motion but allows axial
rotation. See Water Swivel.
Swivel Joint. — One that rotates about an axis without decreasing its
efficiency as a joint.
Symbols. — See Abbreviations.
Tail Pipe. — The suction pipe of a pump. It communicates with the
pump stock through a clack or check valve, and in the case of metal
pumps is in two parts, the upper one of which has a screw thread
at its lower-end, by which it is secured to the lower part, the latter
being cut to a suitable length.*
Tank. — Often applied to a cylinder having closed ends. (Poor usage.)
Tap. — A tool used for cutting internal threads. Small sizes are usually
made solid, but larger sizes are often made with inserted cutters,
so that they can be withdrawn from the work, without stopping,
when the desired threads are cut. See Master and Plug Tap.
Tapped. — (i) The operation of making an internal thread by means
of taps.
(2) Often used loosely, to mean chased or threaded.
(3) In the pipe trade it means threaded regardless of the method of
production.
Tapping Machine. — A machine for cutting and tapping a small hole
in a pipe (as a street main), that is either empty or carrying pressure.
Two classes of tapping machines are made, designated as "pres-
sure" and "dry" tapping machines. They are sometimes called
drilling machines.
Tee. — A fitting, either cast or wrought, that has one side outlet at right
angles to the run. A single outlet branch pipe. See Branch,
Bull Head, Cross-over, Double Sweep, Drop, Four-way, Reducing,
Service, Side Outlet and Union Tee.
Telegraph Cock or Faucet. — A self-closing cock, the lever of which
resembles the key of a telegraph instrument. When the water
enters the cocks horizontally they are called horizontal telegraph
cocks, when it enters vertically they are called vertical telegraph
cocks.
Telescoped. — (i) When one pipe is slid inside of another, it is said to be
telescoped. When the term telescoped is applied to pipe, it means
Definitions 511
that two pipes have been separately made, and then telescoped,
and then welded together so as to form one pipe. This is usually
done so perfectly that it is difficult to see the weld, except by special
or destructive treatment.
(2) Nested (poor usage).
Temper Screw. — Part of a drilling rig used to regulate the force of
blow of the drill bit.
Templet. — (i) A gage ring for thread.
(2) A drilling jig for holes in flanges.
Thimble. — See Boiler Thimble.
Thimble Joint. — A sleeve joint packed to allow longitudinal expansion.
A slip expansion joint.
Threads. — See Ammonia Cock, Briggs', Common, Gas, Pipe, Sellers,
Signal, V, Vanishing, Whitworth and Wine Bore Threads.
Three Way Elbow. — A double branch elbow (poor usage).
Tin Lined Pipe. — A wrought pipe lined with block tin. Tin lining of
lead pipe was introduced by Anderson in 1804.
Tongs. — See Chain Tongs, Pipe Grip, Pipe Tongs and Pipe Wrench.
Tong Tight. — An expression used to indicate that coupling, flange or joint
has been tightened by tongs, frequently in a threading machine.
Tongue and Groove. — Usually applied to flange connections by forming
a tongue on one flange and a groove on the other flange. Usually
placed about midway between bolts and inside diameter of pipe.
The gasket is placed in the groove. The male dimensions should
be equal to the depth of the groove. The depth of the groove
should equal the thickness of the gasket plus Me inch.
Trailing Water. — The operation of drawing water a long distance
through pipes, by means of suction. As long as the total height
lifted, plus the friction in the pipe, does not exceed a head of 25 to
26 feet, water can be trailed a very great distance. The only
difficulty is possible leakage at the pipe joints, which impairs the
vacuum.*
Tube. — (i) In America, means a boiler tube whose outside diameter
is its nominal size. In England, tubes mean tubular goods, whether
tubes, pipe or casing.
(2) In a steam boiler, the pipes, tubes, or flues employed for con-
ducting the products of combustion from the fire box to the chim-
ney, taking heat from them during their passage and transferring it
to the water in the boiler. The tubes are fitted into holes in the tube
sheet at each end of the boiler, being expanded or beaded therein,
or occasionally fastened with a copper or iron ferrule. The tubes
of water tube boilers usually extend between headers, legs, or drums,
into which they are secured as into tube sheets, but the tubes may
be made with closed ends, and circulation secured by special devices.
In water tube boilers, the water is inside the tubes and the hot
gases outside. See Annealed End, Beaded, Boiler, Brick Arch,
Cross, Expanded End, Field, Hot, Ribbed and Stay Tubes.
Tube Cleaner. — (i) A stiff wire brush or metallic scraper attached to
the end of a rod and used to remove soot or scale from boiler tubes.
512 Glossary of Terms Used in the Pipe and Fitting Trade
(2) A steam jet may serve for tubes through which the furnace gases
pass.
(3) Some cleaners for removing hard scale from the interior of tubes
are highly ingenious pieces of mechanism.
Tube Expander. — A tool for expanding boiler tubes within the tube
sheet, causing them to hold firmly. A center piece is fitted with
cylindrical rollers, and inserted within the tube end. A long taper
pin is placed between the rollers and rotated; as it revolves, it
turns the rollers around and forces the material of the tube into
a tiny ridge on each side of the plate, thus gripping it and pre-
venting leaks.*
Tube Ferrule. — A ring of hard wood, used for holding condenser tubes
to their plates. The ferrule fits between the outside of the tube
and the hole in the plate, and being swelled by the action of the
water, renders the tubes water-tight.*
Tube Packing. — A bag of flaxseed, or ring of rubber made to occupy
the space between the tube of an oil well and the bored hole, to
prevent access of water to the oil bearing stratum.*
Tube Plug. — A tube stopper, to be used in case of leak of a boiler
tube. It usually consists of a double wooden plug with a smaller
central part. The plug is forced into the tube until the small
part is opposite the leak; the plug is then in equilibrium and will
not blow out, while the wood rapidly expands and fills the tube.
This device is rarely used, a special stopper being more frequently
applied in cases of emergency, or the tubes are cut off altogether,
when conditions permit, by means of a disc on either tube plate,
held together by a through stay.*
Tube Sealer. — A tool for removing scale and other incrustation from
the inside of steam boilers. See Tube Cleaner.
Tube Scraper. — An instrument or appliance for removing soot and
ashes from the interior of boiler tubes.*
Tube Sheet. — One of the sheets of a boiler, condenser, etc., which is
drilled with holes for the reception and support of the tubes.
Each sheet is defined according to its position; as, fire box tube
sheet, middle condenser tube sheet, etc.
Tube Sheet Cutter. — A trepanning tool, having a spindle guided by a
central hole, while a cranked tool cuts out a disc, corresponding
to the hole required for the reception of a boiler tube.
Tube Sheet Stay. — A rod extending through a boiler from tube sheet to
tube sheet, and having heads or nuts on the exterior of the sheets.
It ties the tube sheets together so as to prevent disruption by steam
pressure. Another form of stay is riveted to the shell and to the
tube sheet. See also Stay, Stay Tube and Upset.
Tubing. — A special grade of high test pipe fitted with threads and
couplings of special design. Tubing is made to the same outside
diameters as Standard Pipe. It is similar to what is known in
Europe as hydraulic pressure pipe.
Tubing Catcher. — A device to prevent tubing from slipping back into
an oil well when it is being pulled.
Definitions 513
Tuyere. — (i) Tuyere pipe is the name applied to pipe of special quality.
It is used in making tuyere coolers, cinder monkeys, etc. It is only
made in small sizes.
(2) The name of the nozzle used where a blast of air is forced into a
furnace of fire such as that used by blacksmiths.
Under Reamer. — An oil well tool used for enlarging the hole below a
drive shoe, etc.
Union. — (i) The usual trade term for a device used to connect pipes.
It commonly consists of three pieces which are, first, the thread end
fitted with exterior and interior threads, second, the bottom end
fitted with interior threads and a small exterior shoulder and third,
the ring which has an inside flange at one end while the other end has
an inside thread like that on the exterior of the thread end. In use a
gasket is placed between the thread and bottom ends which are drawn
together by the ring. Unions are very extensively used because they
permit connecting with little disturbance of the pipe positions.
(2) The Kewanee Union is made with the thread end of brass, and
the thread and bottom ends are ground together so that no gasket
is required.
(3) The act of joining or uniting two or more things. The joint or
connection thereby made. Rarely used in this sense in the pipe
trade.
(4) There are many types of unions. See Boyle, Flange, Kewanee,
Lip, Pipe and Ring Union.
Union Coupling. — A term sometimes applied to a right and left handed
turn buckle, or sleeve nut, whereby two parts might be connected
and drawn together without turning anything but the coupling.*
Union Ell. — An ell with a male or female union at one end.
Union Joint. — A pipe coupling usually threaded which permits dis-
connection without disturbing other sections.*
Union Tee. — A tee with male or female union at connection on one
end of run.
Upset. — The product of any cold or hot forming of material in which
the metal is thickened by being forced back into itself. It is usu-
ally done at a red heat by hammering or press forging. Upset tubes
are those whose ends have their walls so thickened for a short
distance; usually to such extent that the threading leaves as
great a thickness of metal below roots of threads as in main body
of tubes. Upset tubes are much used as stay tubes ; they are some-
times called stoved tubes.
Valve. — A device used for regulating or stopping flow in a pipe, etc.
The form that allows an opening the full inside diameter of the
pipe is usually known as a Gate Valve or Straight Way Valve.
The same result is obtained in some forms of cocks. The essential
514 Glossary of Terms Used in the Pipe and Fitting Trade
difference between a valve and a cock is that the closure of the
latter is invariably accomplished by rotating a taper plug, which
has ports or holes in it that correspond to holes in the body. See
Angle, Angle Gate, Back Pressure, Bracket, Butterfly, By-pass,
Check, Cross, Exhaust Relief, Expansion, Fullway, Gate, Globe,
Needle, Non-return, Pop, Radiator, Receiver Filling, Reducing,
Reflux, Screw Down, Straight Way, Switch, Wedge Gate, and
Wheel Valve.
Valve Box. — A pipe placed over a buried valve to allow access to the
valve stem or wheel for opening or closing. The top of the pipe is
usually closed by a plate or cap to exclude dirt, that would interfere
with operation. There are many designs, the most usual being
adjustable within limited range, to suit the depth planted, and are
called Extension Valve Boxes, Street Boxes or Service Boxes.
Valve Seat. — A flat or conical fixed surface on which a valve rests, or
against which it presses.
Valve Stem. — A rod attached to a valve by which the latter is moved;
it is also called a valve spindle.
Vanishing Thread. — A pipe so threaded that the reaming or counter-
sinking of the coupling is at the same angle as the lead of the dies
that thread the pipe. The pipe is so threaded that the taper
comes into contact at same time as the threads tighten. The
term "Vanishing" comes from the peculiar bore of coupling.
Van Stone Joint. — A flanged joint, in which the pipe itself is flanged
out over the face of the bolting ring.
V Thread. — (i) A screw thread formed by means of a sharp pointed
tool, as contrasted with a square thread.
(2) A standard thread for pipes, tubing, etc., with an angle of 60
degrees between the sides.* See Briggs' Standard.
V Welding. — In boiler making, a mode of welding the plates of boiler
flues in which there is neither butt nor lap properly so called, but
in which a strip of square rod is inserted angle ways between the
nearly abutting edges of the plate, so that it unites the edges upon
two sides of the rod.*
W
Walker Joint. — One form of a flexible joint that is made with spherical
mating surfaces, and which permits a few degrees flexure in any
direction.
Water Arch. — (i) In a steam boiler, a chamber of plates or of pipes
within a furnace, replacing the ordinary fire brick bridge, or arch,
or the deflecting arch over the firedoor of externally fired boilers.
The same as water table.
(2) A locomotive fire box arch, suspended by tubes, which adds to
the heating surface and promotes circulation.*
Water Bar. — A tube serving as a fire bar in a water grate.*
Water Column. — A special fitting connected to a boiler above and below
the water line. To it are usually connected the water gage and
gage cocks.
Definitions 515
Water Flush. — A system of well boring, in which percussive drills are
used in connection with water forced down to the bottom of the
hole through the drill rods. This water jet makes the tools cut
better, and washes the detritus up out of the hole. Its great
objections are, the great probability of waterlogging the surround-
ing territory, and the pressure of water forcing back bodies of oil,
which have only a small force behind them, thus leading to the
passing by of possibly valuable oil-bearing territory.*
Water Gage. — A glass pipe connected to a boiler above and below water
line so as to see the water level.
Water Grate. — When, as in certain steam boilers, to increase the
heating surface, hollow water tubes are used for grate bars, the
arrangement is termed a water grate.*
Water Hammer. — The shock or blow struck by water whose flow in a
pipe is suddenly arrested, e.g., sudden closure of a faucet often
causes shocks that so shake the pipes that a clanking noise is pro-
duced. The term is more used in connection with steam piping,
where the condensed steam (water) is forced ahead by the steam
rushing into a cold empty pipe with such high velocity, that it
slams the water against bends, elbows, valves, etc., with terrific
force or shock. It is peculiarly violent when steam is admitted
suddenly to a cold vacuous pipe, because there is no air to cushion
the blow; but even air will not ordinarily eliminate its destructive
and dangerous violence. The main remedies are easy bends and
slow closure of the valve for liquids, and for vapors (steam, etc.),
slow admission until all pipes are brought to temperature.
Water Packer. — A device intended to cut off water from the lower
levels of an oil well, or to separate two distinct flows of oil from
different strata; more especially in fountaining wells. It consists
essentially of two tubes sliding within one another, the inner tube
being swathed with rubber rings or with canvas and rope yarn, for
some length between its own upper socket and the socket on top of
the larger tube. The whole is lowered into the well, on the tubing,
until the perforated anchor pipe, connected with the outer tube,
rests on the bottom. The whole weight of the string of tubing
then rests upon the inner tube of the packer, compressing the
packing outward against the casing of the well, so that the upper
strata are cut off from communication with the lower.*
Water Pipe Clamps. — A term used to indicate service clamps (poor usage).
Water Plug. — It means stand pipe or penstock, or hydrant. Water plug
is the more general colloquial term used on railroads.
Water Swivel. — In well boring, a combined universal joint and hose
coupling, forming the connection between the water supply pipe
and the drill rods, and permitting complete rotation of the tools.*
Water Tube Boiler. — A steam boiler in which the boiler tubes contain
water. Used in contradistinction to the older type of boiler, in
which the tubes were used as flues and surrounded by water.
Wedge Gate Valve. — A gate valve having inclined seats; usually a wedge
shaped disc is pressed down between these inclined seats.
516 Glossary of Terms Used in the Pipe and Fitting Trade
Weight. — A term that by trade custom has come to be frequently
attached to various tubular products. It has grown out of the
need in the trade for several thicknesses of the same outside diam-
eter and the practice of determining the thickness by the average
weight per foot. See Card and Full Weight.
Weld. — See Butt, Circular, Lap, Safe End, Scarf and V Weld.
Welded Flange Joint. — A joint made by flanges attached to pipe by
welding; for this it is necessary that material of flange be capable
of being welded (e.g., soft steel or wrought iron). The best known
style is made by slipping the end of pipe throug.li. the flange ring
forgings, and then bringing all to a welding .heat -and hammering
or pressing together. Another style uses a collar on the flange;
the collar is attached to flange by a circular or safe end weld.
Wheel Valve. — A stop or gate valve opened by means of a hand. wheel
and screw, as distinguished from those- patterns of gate valves hi
which the valves are opened or closed quickly by means of levers,
or the many types of butterfly and other throttle valves.*
Whitworth Thread. — The standard thread for screws, employed in
England and her colonies, and on the European Continent. The
angle of the thread is 55 degrees, one-sixth being rounded off at
top and bottom.*
Widemouth Socket. — A well borer's fishing tool, in which the socket is
fitted with a bellmouth, nearly the full bore of the casing, thus
making it easy to grip the ends of broken poles or the like, when
lost at the bottom of a well.*
Wine Bore. — A term used to indicate standard pipe thread (rare and
poor usage).
Wiped Joint. — A lead joint in which the molten solder is poured upon
the desired place, after scraping and fitting the parts together, and
the joint is wiped up by hand with a moleskin or cloth pad while the
metal is in a plastic condition; it makes a neat and reliable connec-
tion in the pipe.*
Working Barrel. — The body of a pump used in oil wells.
Wye. — Y. — A fitting either cast or wrought that has one side outlet
at any angle other than 90 degrees. Usually set 45 degrees, and
always so set unless angle is specified. It is usually indicated by
letter " Y."
Y
Y.— Wye. — Which see.
Y Base. — The same as a crotch or back outlet return bend, except
that the horns are parallel.
Y Bend. — Y. — Wye.
Y Branch. — (i) A wye.
(2) Sometimes used to designate a fitting whose shape is nearly like
that of a single sweep tee.
Yoke. — (i) In a rising stem valve, the portion of the bonnet that
supports the nut, hand wheel, etc.
(2) A pipe with two branches; as, for hot and cold water, uniting
them to form one stream.*
INDEX
Abbreviations of Terms Used
in the Pipe and Fitting
Trade 477~479
Absolute Zero 328
Absorption of Gases by Liquids . 316
Accuracy of Cut Length 21
Acid, Carbonic, Cylinders 15
Carbonic, Physical Proper-
ties of 209
Cylinders, Carbonic 15
in Boiler Water 276
Acre-foot 312
Acre-inch . 312
Acres to Hectares 462, 464
Adiabatic Compression of Air,
Work of 356
Compression of Natural
Gas (.324,32$
Expansion and Compression
of Air 35S,3S6
Advantages of Superheating. . . . 338
Advisable Radii for Wrought
Pipe Bends 162
Upsets for Lap-welded and
Seamless Tubes 160-161
After, Faced (Definition) 490
Air 351-364
Adiabatic Expansion and
Compression of 355, 356
Atmospheric Pressure 352
Bound Pipes, Obstruction to
Flow 284
Composition of 352
Compressed (see Compressed
Air) 360
Effects of Bends and Fit-
tings 364
Flow of, in Pipes 360
Flow of, Tables 361-364
Loss of Pressure in Trans-
mission 360
Velocity of Efflux, Tables. . 357
Compression and Expansion.. 355
Corrosion by, in Feed Water. . 277
Discharge from Pipes 358, 359
Coefficients of through an
Orifice 358
Air, Effect of Bends and
Fittings on Flow of in
Pipes 364
Expansion and Compression . 355
Flow 357-364
Affected by Bends and
Fittings 364
Coefficients of Discharge. . . 358
Compressed 360-364
Efflux 357-358
Hawksley's Rule 359
Loss of Pressure 359-364
Under Pressure from Ori-
fices into the Atmos-
phere 357
Sturtevant Rule 359
Weisbach's Rule 359
Index 351
in Feed Water 277
Isothermal Compression of,
Work of 356
Isothermal Expansion and
Compression of 356
Line Pipe, Section of Joint. . . 80
Test Pressures 73
Weights and Dimensions. . . 36
Loss of Pressure in Pipes. . .359-364
Pipe, Galvanized 364
Pressure 273, 352
Pressure, Volume and Tem-
perature of 352
Properties of 352-356
Relation of Pressure, Volume
and Temperature 352
Specific Heat of 355
Tables (Weight of Air at Vari-
ous Pressures and Tem-
peratures) 353, 354
Velocity in Pipes 359, 360
Velocity of Efflux of Com-
pressed 357
Volume 352
Weight of 352-354
Work of Adiabatic Compres-
sion of 356
Work of Isothermal Compres-
sion of 356
517
518
Index
Allison Vanishing Thread
Tubing 33
Ends Upset, Section
of Joint 81
Ends Upset, Test Pres-
sure of 75
Ends Upset, Weights
and Dimensions of 33
Not Upset, Section of
Joint 81
Not Upset, Test Pres-
sure of 75
Not Upset, Weights
and Dimensions of . . 33
Allowances for Machining to
size Cream Separator Bowls 104
Aluminum, Weight of 423
American Soc. Mech. Engrs.
Pipe Thread Comm 209
Standard Flange. . . .169, 176
Steel Manufacturers' Gages . . 369
American Wire Gage 369
Ammonia, Absorption by
Water 316
Cock Thread (Definition) 479
Fitting (Definition) 479
Joint (Definition) 479
Pipe, Specifications for
Special 98
Analysis of Bessemer Pipe
Steel '. .10
of Open Hearth Pipe Steel. ... 10
of Shelby Seamless Steel
Tubes 16, 18, 19
Anchor Poles 109
Angle Valves 169, 170, 479
Angle Gate Valve (Definition) . . 479
Angular Section Specialties,
Shelby Seamless Steel 196
Angus Smith Composition
(Definition) 479
Animal Oils in Boiler Water,
Effect of 276
Annealed End Tube (Definition) 480
Annealing and Welding 10, 20
Pots, Heads for 190
Anneal of Shelby Seamless Steel
Tubes 17-19
Apothecaries drams to milli-
liters 462, 466
scruples to milliliters 466
Applicability of Barlow's For-
mula 224
Application of Table to Round
Bars 420, 421
Tubes and Pipe 421, 422
Approximate Formula for Flow
of Water in Pipes , 280-281
Arch Tube, Brick (Definition) . . 482
Arch, Water (Definition) 514
Area, Circular 419-459
Comparison of Customary and
Metric Units 463-472
Cross Section of Pipes,
58-65, 419-459
Square Pipes 66
Rectangular Pipes .... 67
Shelby Tubing 200-201
Factors for Tubes 373~37S
Measures in Metric Equiva-
lents 462, 464
Surface of Pipe 57
Armstrong Joint (Definition) . . . 480
Artesian Joint, Cressed (Defi-
nition) 486
Artesian Joint (Definition) 480
Assembling Bump Joints 166
Butted and Strapped Joints . . 165
Pole Joints in Field 115
Association of Steel Mfgr's.
Gages 369
Asphalted (Definition) 480
Atmosphere, Flow of Air
into 357.- 358
Flow of Steam into 341
Pressure of 273, 352
Table for Readings of Barom-
eter , 352
Atmospheric Pressure 352
Attemperator (Definition) 480
Automobile Specialties, Shelby
Seamless Steel 193
Avogadro's Law of Gases 314
Avoirdupois Weight Equiva-
lents 462, 468, 472
Axles for Automobiles 193
B
Back Outlet, Central (Defini-
tion) 480
Back Outlet, Eccentric (Defini-
tion) 480
Back Outlet Ell (Definition) 480
Back Pressure Valve (Defini-
tion) 480
Ball and Cup Joint (Defini-
tion) 487
Balling (Definition) 480
Ball Joint (Definition) 480
Banded Fittings 168
Bar (Definition) 480
Bar, Sinker (Definition) 506
Index
519
Bare Steam Pipes, Condensa-
tion in 348
Loss of Heat from 348, 349
Barlow's Formula,
214, 218-219, 223-226
Applicability of 224
Barometer Pressure 352
Barrels, Number of, in Cisterns
and Tanks 304-305
Working 187, 188, 516
Bars, Round, Properties of. . .419, 459
Application of Table to 420
Water (Definition) 514
Base Y (Definition) 516
Bead (Definition) 480
Beaded Boiler Tubes, Holding
Power of 210
Fittings 168
Tube (Definition) 480
Beading (Definition) 481
Beam and Column Sections,
Properties of (Tables) . . . 264-267
Beams, Bending Moment of.. 252, 253
Comparative Stiffness of 255
Comparative Strength of. ... 254
Cdrnpressive Stress in 250
Deflection of 251
Elastic Curve of 251
Elastic Deflection of 251
Elasticity 254-255
Equal Loading in any Direc-
tion 256
Formula for Flexure of 256-263
Loading of 256-263
Mechanical Properties of,
Solid and Tubular 250
Minimum Weight of 255
Modulus of Elasticity 255, 257
Moment of Inertia 254
Neutral Surface 250
of Uniform Cross Section, Me-
chanical Properties of 256-263
Properties of 250-263
Properties of Sections 264-267
Properties of Solid and Tubu-
lar 250-263
Reactions of Supports 252
Rectangular Pipe 67
Resisting Moment of 253
Section Modulus of 254
Sections of for Minimum
Weight 255, 256
Shearing Stress in 250
Solid, Properties of 250-256
Solid, Tables of, Properties
of 256-263
Beams, Solid and Tubular,
Mechanical Properties
of 250
Square Pipe 66
Stiffness of 255
Strength of 254, 255
Stresses in 250
Trolley Poles 197
Tensile and Compressive
Stresses in 250
Tubular, Properties of 250, 256
Tables of, Properties of,
256, 263
Vertical and Horizontal Load-
ing of 256
Vertical Shear of 250
Bearing, Shaft 195
Bedstead Tubing, Weights and
Dimensions of 31
Bell (Definition) 481
Bell and Spigot Joint (Defini-
tion) 481
Bell Mouthed (Definition) 481
Bend (Definition) 481
Close Return (Definition) .... 485
Cross-over (Definition) 486
Double (Definition) 488
Eighth (Definition) 489
Expansion 163, 168
Obstruction to flow of Air . . . 364
Gas 324
Steam 346
Water 283
Open Return (Definition) .... 499
Pipe (Definition) 500
Radius of (Definition) \ 502
Return (Definition) 504
Bending and Flanging, Specifi-
cation for Pipe for 95
Machine, Pipe (Definition) . . . 500
Moment Factor 58-65
Moment of Beams 252, 253
Pipe for 95
Properties of Rectangular
Pipe 67
Square Pipe 66
Wrought Pipe, Radii of 162
Bend, Y (Definition) 516
Bent Specialties, Shelby Seam-
less Steel Tubing 195
Bent Tubes and Pipe 162, 163
Bent Tubes, Seamless > I9S
Bernoulli's Theorem 298
Bessemer Pipe Steel, Chemical
and Physical Analysis 10
Bibb (Definition) 481
520
Index
Bicarbonates of Lime, Magnesia
and Iron in Boiler Water. . . 276
Birmingham Wire Gage 360
Thickness of Pipe 46-49
Tubes 50-56
Birnie's Formula, Applicability
of 222-223
for Strength of Tubes, In-
ternal Pressure,
217, 218, 219, 221, 223
Bituminous Coating 107
Black Pipe, Weights and Dimen-
sions of, Standard (see
Standard Pipe)
Blank Flange (Definition) 481
Blanking Flange (Definition) ... 481
Blast Furnace Fittings 170
Bleeder (Definition) 481
Blind Flange (Definition) 481
Block Joint 481
Boiler Corrosion 275-277
Boiler Flange (Definition) 481
Boiler Flue (Definition) 491
Boiler Flue Joints 164, 165
Boiler Flues (see Boiler Tubes).
Boiler Incrustation and Cor-
rosion , 275-277
Boiler, Remedy for Troublesome
Substances in 276
Boiler Safe Ends, Specifica-
tions IOI-IO2
Boiler Shells 194
Boiler Thimble (Definition) .... 481
Boiler Tube (Definition) 482
Boiler Tubes, Flanging Tests. . . 13
Holding Power 210
Locomotive Lapweld Speci-
fications 99
Test Pressure 72
Weights 40
Locomotive, Seamless,
Shelby Specifications . . 101-102
Test Pressure 102
Weights 38-39
Merchant and Marine Spe-
cifications 100
Test Pressure 72
Weights 41
Slipping Point of 210-211
Standard Specifications 100
Test Pressure 72
Weights 41
Tests . ... 13, 20, 99, 100, 101, 102
Boiler Water, Acid in 276
Animal and Vegetable Oils
in 276
Boiler Water, Bicarbonate of
Lime, Magnesia and Iron
in 276
Carbonate of Soda in 276
Chloride and Sulphate of
Magnesium in 276
Dissolved Carbonic Acid
and Oxygen in 276
Grease in 276
Organic Matter in 276
Sediment in 276
Soluble Salts in 276
Sulphate of Lime in 276
Boiler, Water Tube (Defini-
tion) 515
Boiling Point of Water 272
Bolt and Nut Heads, Screw
Threads, Proportion of. .370-372
Bolts, Dimension of 37i~372
Strength of 371, 372
Bonnet (Definition) 482
Bore, Wine (Definition) 516
Boss on Cylinder Heads 189, 190
Boston Casing, Section of Joint . 78
Test Pressure of •; :*nb3fro
Weights of •SKtfJtG
Pacific Coupling, Section
of Joint 78
Test Pressure of 70
Weights of 28
Standard (see Boston Casing).
Bowl (Definition) ,. 482
Bowls, Cream Separator. 103, 104, 194
Box (Definition) 482
Box Coil (Definition) 482
Box Service (Definition) 505
Boyle's Law 314
Boyle Union (Definition) 482
Bracket Coil (Definition) 482
Bracket Valve (Definition) 482
Branch (Definition) 482
Branch Ell (Definition) 482
Branch Pipe (Definition) 482
Branch Tee (Definition) 482
Branch Y (Definition) 516
Brass Cocks 170
Brass Mounted (Definition) .... 482
Brass Pipe Expansion 347
Brass Unions 169
Brass Valves 170
Brass, Weight 423
Brazed (Definition) 482
Breeches Pipe (Definition) 482
Brick Arch Tube (Definition).. . . 482
Briggs' Standard 21, 208
(Definition) 483
Index
521
Briggs' Standard Gages 21
Pipe Threads 208-209
British Imperial Gallon Equiva-
lents 311-312
Wire Gage 369
Standard Poles 109, 112
Thermal Unit 327
Brown and Sharpe Gage 369
Bucket (Definition) 483
Buckling 244
Building Laws for Columns. . . 244-249
Bulk Measure (see Masses, Vol-
umes and Capacities).. . .460-476
(see Metric Conversion Tables)
Bull Head Tee (Definition) 483
Bump Joints, Riveted 165-166
Bumped (Definition) 483
Bumped Heads, Strength of. ... 190
Joint (Definition) 483
Bursting Strength Formula, Bar-
low 224
of Cylinders. . . 189-192, 212-226
Tubes 212-226
Stress, Formula 224
Tests 223-226
of Commercial Tubes and
Pipes 223-226
Table of 225
Bushels per Acre to Hectoliters
per Hectare 467
to Hectoliters 462, 467
Bushing (Definition) 483
Flush (Definition) 492
Butted and Strapped Joints . . 164, 483
Butterfly (Definition) 483
Butt Sections of Poles 118-157
Butt-weld (Definition) 483
Pipe Sizes 68-69
Process jmb g
BX Casing, California, Dia-
mond (see Cal. Diamond
BX Casing).
Drive Pipe, California Dia-
mond (see Cal. Diam. BX
Drive Pipe).
By-pass (Definition) 483
Valve (Definition) 483
Calculating Table of Water
Horse Power 299
Caliber (Definition) 483
California Diamond BX Casing,
Section of Joint 82
Test Pressure of 71
California Diamond BX Casing.
Weights and Dimen-
sions of 29
Drive Pipe, Section of
Joint 82
Test Pressures of. ... 76
Weights and Dimen-
sions of 31
California Miners' Inch 312
California Special External Up-
set Tubing, Section of
Joint 82
Test Pressure of 76
Weights and Dimen-
sions of 30
Calking (Definition) 483
Calking Recess (Definition) .... 483
Calking Tool (Definition) 483
Calorific Unit 327
Cap (Definition) 483
Caps for Cylinders 194
Capacities, Comparison of Cus-
tomary and Metric
Units 466-467
of Cylindrical Tanks, Table of 302
of Rectangular Tanks, Table
of 305
Capacity, Discharging of
Pipe 306-309
Factors for Tubes 423
Measurements (see Metric
Equivalents) 460-476
of Shelby Tubing, per Lineal
Foot 200-203
Carbon Dioxide, Physical
Properties of 209
Carbonate of Soda in Boiler
Water 276
Carbonic Acid and Oxygen in
Boiler Water 276
Carbonic Acid Cylinders,
15, 188, 209-210
Physical Properties of. . .209-210
Carbon in Bessemer Pipe Steel... 10
Open Hearth Pipe Steel. ... 10
Shelby Seamless Steel
Tubes 16-19
Card Weight Pipe 22, 483
Casing (Definition) 484
Boston (see Boston Casing).
Pacific Couplings (see Bos-
ton Casing Pacific Coup-
ling).
California Diamond BX (see
California Djamond BX
Casing).
522
Index
Casing Coupling (see Casing in
Question) .
Dog (Definition) 484
Elevator (Definition) 484
Expanded Joint 27
Fitting (Definition) 484
Head (Definition) 484
Inserted Joint (see Inserted
Joint Casing).
Nipples, Wrought 174
Shoes (Definition) 484
Size, Trade Practice 21
South Penn (see South Penn
Casing).
Standard, Boston (see Boston
Casing).
Swelled Joint 27
Cast Iron Fittings 168
Flanges Standard 176
Pipe, Expansion 347
Weight 423
Catalogue Pole Number. . . . 118-157
Catcher, Tubing (Definition). . . 512
Cause of Corrosion of Pipe 12
Center Poles 109
Centigrade-Fahrenheit Conver-
sion Tables 473-476
Centimeters to inches.. .461, 463, 476
Central Back Outlet (Defini-
tion). 480
Centrifugal Separator Forgings.. 194
Chain Tongs (Definition) 484
Champfer (Definition) 484
Charles' Law of Gases 314
Chart, Conversion for Lengths,
Weights and Temperatures. 476
Flow of Water 279
Metric Conversion 476
Chasers 10-11
Lead of n
Number in Die for Different
Pipe Sizes n
Threading 10-11
Clearance of 10
Chasing (Definition) 484
Check (Definition) 484
Valves 169, 170, 484
Chemical Analysis Pipe Steel. . . 10
Shelby Seamless Steel
Tubes 15,16,18,19
Chezy Rule for Flow of
Water 281-282
Chicago Building Ordinances,
Formula for Columns . . . 244
Chip Space on Threading
Dies lo-n
Chloride of Magnesium in Boiler
Water 276
Chlorine, Absorption by Water. 316
Christie's Tests on Columns .... 230
C.I.F. (Definition) 484
Circular Flange (Definition) 484
Circular Weld (Definition) 484
Circumference, Table of 419-459
Circumferential Stresses, Inter-
nal Fluid Pressure 220-221
Cisterns, Barrels Contained in. . 304
Clamp (Definition) 484
Leak (Definition) 496
Pipe (Definition) 500
Pouring (Definition) 502
Service (Definition) 505
Water Pipe (Definition) 515
Classification of Pressures,
Valves and Fittings 167
Clavarino's Formula 215
Applicability 223
for Strength of Tubes, In-
ternal Pressure,
215-220, 222-224
Cleaner, Flue (Definition) 492
Cleaner, Tube (Definition) 511
Clean-out Fitting (Definition). . 484
Clearance of Threading Chasers. 10
Clegg's Experiment on Flow of
Gas 317
Close Nipple 171, 174, 485
Return Bend (Definition) 485
Coal Tar (Definition) 485
Coating, Bituminous 107
for Pipe (Definition) 485
for Poles 118
National 94, 107
Protective and Dip. 91, 94, 106, 107
Smith's (Definition) 479, 507
Specification, Dip 91
National 94
with Zinc 92 , 94
Cock (Definition) 485
Cock, Ammonia, Thread (Defi-
nition) 479
Corporation (Definition) .... 485
Four-way (Definition) 492
Gage (Definition) 492
or Faucet, Telegraph (Defi-
nition) 510
Pet (Definition) 500
Plug (Definition) 502
Cocks and Valves 169, 170, 485
Coefficient of Air Discharge .... 358
Expansion of Iron and Steel,
"Bureau of Standards".. 211
Index
523
Coefficient Flow of Steam through
Orifices 341
Roughness, Kutter's For-
mula 281-282
Coil, Box (Definition) 482
Bracket (Definition) 482
(Definition) 485
Expansion (Definition) 489
Cold-drawn, Cold Finished 15
Cold-drawn (Definition) 485
Locomotive Boiler Tubes,
Specifications, Seamless. . 101
Safe Ends, Specification. . . 101
Steel Trolley Poles, Length 198
Weight of 198
Tubes for Cream Separa-
tor Bowls, Shelby
Seamless, Specification 103
Tubes for Diamond Drill
Rods, Shelby Seamless,
Specification for 104
Tubes for Hose Poles and
Hose Molds, Shelby
Seamless, Specification. 105
Tubes 15
Cold Finished Shelby Seamless
Steel Tubes xi&&
Collapse and Column Formulae,
Comparison of 230
Collapsing Pressures 227-243
Lilly's Formula for 231
Marine Law 229
of Pipes and Tubes 227-243
Results of Research 228
Stewart's Formula for 228
Tables 232-243
Tests 227
Collapse related to Strength
Column 230
Research 228
Under External Pressure,
227-243
Collar (Definition) 485
Collar Flange (Definition) 485
Collars, Kimberley 44, 83
Colorado Miner's Inch 294-312
Column and Collapse Formulae. 230
Column Flange, Pump, Rein-
forced (Definition) 503
Column, Pump, Flange (Defi-
nition) 502
Column Sections, Tables of,
Properties of 264-267
Column, Water (Definition). ... 514
Columns, Chicago Building Or-
dinances, Formula for 244
Columns, New York Building
Code, Formula for 244
of Pipe 244-249
Pipe, Double Extra Strong . . . 249
Safe Loads for 249
Extra Strong, Safe Loads
for 247-248
Standard Pipe, Safe Loads
for 245-246
Strength of 244
Relation to Collapse 230
Commercial Pipe, Yield Point
Tests on 222
Tubes and Pipes, Bursting
Tests of 223-226
Pipes and Cylinders to Re-
sist Internal Fluid Pres-
sures, Strength of .... 222-226
and Pipes, Strength of
Weld of 226
Common Formula for Flow of
Gas in Pipes 321
Internal Pressure,
213-214, 218-219, 224
Thread (Definition) 485
Comparative Stiffness of Beams. 255
Strength of Beams 254
Comparison of Collapse and
Column Formulae 230
Customary and Metric
Units from i to 10
Tables 463-469
Formulae for Discharge
of Gas 323
Internal Fluid Pressure For-
mulae for Tubes, Pipes
and Cylinders 218-219
Tons and Pounds 472
Wrought Iron and Pipe
Steel Columns 231
Competition Valve 170
Composition, Angus Smith
(Definition) 479
Chemical of Steel for Seam-
less Pipe 15, 16, 18, 19
Welded Pipe 10
of Air 352
of Pipe Steel,
9, 10, 15, 16, 18, 19, 2ii
of Water 272
Compressed Air, Flow of in
Pipes 360-364
Pressure Losses 360
Transmission, Loss of Pres-
sure of 360
Velocity of Efflux of 357
524
Index
Compressibility of Water 275
Compression, Adiabatic of Natu-
ral Gas 324-325
Work of 356
and Expansion, Adiabatic
Air 355
Isothermal of Air 356
Natural Gas, Adiabatic.. . .324-325
Temperature of Gas 325
Compressive Stresses in
Beams 250
Columns 244
Condensation in Bare Steam
Pipes 348
Conditions of Tests of Poles .... 114
Conduit Pipe (Definition) 485
Cones, Seamless Steel 195
Connection, Flanged 167, 169
Screwed 167, 168
Siamese (Definition) 506
Contents in Gallons, Cylinders,
301, 302
Rectangular Tanks 305
of Cylindrical Vessels, Tanks,
etc., Table of 302, 304
Cylinders and Pipes, Table
of 301
Pipes in Pounds per
Foot .- 303
Contraction and Expansion of
Pipes 168
Lateral, Coefficient 215
Convenient Equivalents 312
Converged End 189, 190, 485
Converse Lock Joint. . . .108, 167, 485
Coating 109
Fittings 93
Hub and Pipe, Section
of 84
Pipe 43, 108
Specifications for 93~95
Test Pressures of 74
Weights and Dimen-
sions of 43
Reinforcement 109
Conversion Chart, Lengths,
Weights and Temperatures. 476
Table 311
Hydraulic 310-312
Volumes 311
Copper Pipe, Expansion of ..... 347
Copper Weight 423
Corporation Cock (Definition).. 485
Correct Sizes of House Pipes for
Gas, Table of 319
Corrosion i2-i3i 106
Corrosion and Incrustation in
Boilers 275-277
Cause of 12
of Boilers 275-277
of Pipes and Tubes 12-13
of Steel Pipe 12
Prevention of (see Dog
Guards) 113
Reference Books on 12
Corrugated Joint (Definition).. . 486
Counterbored (Definition) 486
Countersink (Definition) 486
Countersunk (Definition) 486
Coupling (Definition) 486
Pipe (Definition) 500
Socket (Definition) 507
Steam (Definition) 509
Union (Definition) 513
Couplings (see Product in Ques-
tion, also "Joint")
Covering, Pipe (Definition) 500
Coverings, Steam Pipe 348-350
Cox's Formula for Discharge
of Gas 321
Loss of Head by Friction
in Pipes 289-290
Cream Separator Bowls, Speci-
fications for Shelby Seamless
Cold-drawn Steel Tubes
for 103-104
Specialties 194
Cressed (Definition) : . 486
Artesian Joint (Definition) . . . 486
Crippling of Poles 1 16
Cross (Definition) - 486
Cross-over (Definition) 486
Bend (Definition) 486
Pipe Bend 163
Tee (Definition) 486
Rolls, Effect 105, 8-9
Section of Pipe 58-65
Square Pipe 66
Rectangular Pipe 67
Tube (Definition) 486
Valve (Definition) 487
Crotch (Definition) 487
Crushing Down Test. . 13, 95, 100, 102
Test (Definition) 487
Cubic Centimeters, Capacity
of Pipe 423
Contents, Pipes and Cylin-
ders 301-304, 419-459
Seamless Tubing 200-203
Tubes 419-459
Cubic Feet per Foot of Cylin-
ders, Table 301
Index 525
Cubic Feet per Foot of Pipes . . 301
Second, Gallons per Min-
ute, Table ... .... 300
Dead End of a Pipe (Defini-
tion) 487
Decimal Equivalents of Feet
and Inches 366—368
Foot Equivalents 311
Inch Equivalents 311
Fractions 368
Cup and Ball Joint 487
Vulgar Fractions 366-368
Wire and Sheet Metal
Gages 369
Cup Joint (Definition) 487
Cupped Cylinder Heads 189-190
Cupping (Definition) 487
Fractions of Inch. . . 368
Process 1 5
of a Foot for Each %4 of an
Inch 366
Current Motors, Water 298
Curve Collapsing Pressure. ... 231
Curve Elastic of Beams 251
an Inch for Each %4 368
Definitions (see Particular Defi-
nition).
Definitions of Terms Used in the
Pipe and Fitting Trade. .479-516
Deflection and Set Limits,
Tubular Electric Line Poles,
112-113, 119-157
Due to Load Shelby Seamless
Cold-drawn Steel Trolley
Poles 198
Curved Flange (Definition) 487
Curves, Effect of on Flow of
Water in Pipes 279
Customary Sizes of Poles 109
Cut Length (Definition) 487
Limits of Accuracy, Varia-
tion . 21
Cutter, Pipe (Definition) . . . . 500
Tube Sheet (Definition) 512
Cylinder (Definition) 487
Caps 194
Elastic of Beams 251
Dekaliters to Pecks 462, 467
Delivery, Compressed Air. . . .360-364
Water from Pipes. 278-279
Heads 189—192
Dished, Thickness of 191
Flat, Thickness of 192
Density of Air -352—354
Shapes of 189—190
Water 272
Strength of ... 190-191
Densities of Elementary
Gases . 314
Specialties, Shelby Seamless
Steel. . 194
Depth of Thread, Briggs' Stand-
ard 208—209
Cylinders, Bursting Strength. . . 189
Comparison of Internal Fluid
Pressure, Formulae for . . . 218-219
Contents of Table 301
Development of Pipe Industry. . 7
Diameter, Nominal, Internal
and External 21, 46-56, 58-65
of Pipe Required for Flow
of Known Quantity of
Water 290
for Gasoline Engines *95
Material of 15
Seamless Shelby 188
Strength of, Under Internal
Pressure 212—226
Shelby Seamless Tubing. . . 199
Diamond BX Casing, Califor-
nia (see California Diamond
BX Casing).
Diamond BX Drive Pipe, Cali-
fornia (see California Dia-
mond BX Drive Pipe).
Drill Rods, Shelby Seamless
Cold-drawn Steel Tubes,
Specifications for 104-105
Table of Capacities of 301
to Resist Internal Fluid Pres-
sure Strength of 222—226
Cylindrical Tanks, Table of,
Capacities of, in Barrels. . . . 304
Tanks and Cisterns, Table
of Contents of 302
Walls, Strength of 212-243
D
Dalton's Law of Gaseous Pres-
sures . 315
Diaphragm, Expansion (Defi-
nition) . . 489
Dictionary of Pipe Trade
Terms . . . .477—516
Die (Definition) 487
Darcy's Formula for Flow of
Water in Pipes 282
Master (Definition) . 497
Pipe (Definition) 500
Steam in Pipes 344
DIPS. Threadiner . . . TO— TT
526
Index
Difference in Weight of Pipe
for Difference O. D 379-380
Dimensions, Air Line Pipe 36
Boiler Flues, Lap-welded 41
Boiler Tubes, Locomotive,
Lap-weld, Open Hearth
Steel 40
Seamless, Open
Hearth Steel 38-39
Casing, Boston 26
Pacific Coupling 28
California Diamond BX . . C£_fi 29
Inserted Joint 27
South Penn 35
Converse Lock Joint
Pipe 43
Double Extra Strong Pipe,
Black and Galvanized 25
Drill Pipe Full Weight 36
Drive Pipe 24
Drive Pipe Cal. Dia. BX 31
Dry Kiln Pipe 37
Extra Strong Pipe, Black and
Galvanized 25
Kimberley Joint Pipe 44
Line Pipe 23
Matheson Joint Pipe 42
Pipe, Standard Black and
Galvanized 22
Poles 118-157
Reamed and Drifted Pipe. ... 35
Rectangular Pipe 45
Rotary Pipe, Special 34
Upset 34
Screw Threads, Nuts and
Bolts 37i
Square Pipe 45
Tubing, Allison Vanishing
Thread, Ends Upset 33
Not Upset 33
Bedstead 31
California Special Exter-
nal Upset.. 30
Flush Joint 32
Oil Well 30
Tuyere Pipe 37
Dip Coating (see also Coat-
ing) 91, 106
Specifications 91. 94
Pipe (Definition) 487
Dipping Poles 118
Discharge, Air, Coefficients of. . 358
Capacity of Pipes, Table of,
Relative 306, 309
Chart, Quantity, Diameter,
Velocity 279
Discharge, Coefficient of, Air. . . 358
Steam 341
Water 278
Gas at High Pressure,
Formula for 320-321
Low Pressure, Formula 317
Common Formula for. ... 321
Comparison of Formula 323
Cox's Formula 321
Oliphant's Formula 322
Pittsburgh Formula 321
Rix's Formula 321
Towl's Formula 321
Un win's Formula 323
Pipes Conveying Water. . 278-279
Relative 306-309
Pumping Engines 293
Steam from Pipes, Kent's
Formula 344
Water Through Pipes 278
Discharging Capacity of
Pipe 306-309
Dished (Definition) 487
Dished Cylinder Heads, Thick-
ness of 191
Heads, Strength of 191
Displacement per Lineal Foot
of Shelby Seamless Steel
Tubing 199
Dissolved Carbonic Acid and
Oxygen in Boiler Water. ... 276
Distribution of Gas 317-324
Dog (Definition) 487
Dog, Casing (Definition) 484
Guard (Definition) 487
Guards for Poles, Tubular
113-114
Pipe (Definition) 500
River (Definition) 504
Double Bend (Definition) 488
Branch Elbow (Definition) ... 488
Extra Strong Pipe (Defini-
tion) 488
Bursting Tests 225-226
Columns, Table of Safe
Loads for 249
Hydrostatic Test Pres-
sure of 69
Length per Square Foot
of Surface 57
Process of Manufac-
ture, Lap-weld 8
Butt-weld 9
Weights and Dimen-
sions of 25
Offset U Bend 163
Index
527
Double Riveted Bump Joints, 165-166
Butted and Strapped
Joints 164-165
Double-sweep Tee (Defini-
tion) 488
Drainage Fittings (Definition) . . 488
Drams, Apothecaries, to Mil-
liliters 462, 466
Drawing (see Seamless Pipe
Shelby) 14
Drawn (Definition) 488
Cold (Definition) 485
Hot (Definition) 493
Dresser (Definition) 488
Drifted and Reamed (Defini-
tion) 503
Pipe (see Reamed and
Drifted Pipe).
Drifted (Definition) 488
Drill (Definition) 488
Drill Pipe, Full Weight (see
Full Weight Drill Pipe)
Pole (Definition) 502
Rods, Diamond Shelby Seam-
less Steel Tubes for, Speci-
fication 104-105
Shot (Definition) 506
Drilled (Definition) 488
Drilling Machine (Definition) ... 488
Drive Head (Definition) 488
Pipe, California Diamond BX
(see California Diamond
BX Drive Pipe).
Joint (Definition) 488
Ring (Definition) 488
Section of Joint 77
Test Pressure of 69
Weights and Dimensions of. 24
Drive Shoe (Definition) 488
Drop Elbow (Definition) 489
of Pressure in Steam
Lines 344-346
Tee (Definition) 489
Test 116, 119
Drum (Definition) 489
Dry Joint (Definition) 489
Dry Kiln Pipe, Section of Joint. 83
Test Pressure of 76
Weights and Dimensions. 37
Dry Pipe (Definition) 489
Quarts to Liters 462, 467
Dry Steam 327
E
Eccentric Back Outlet (Defini-
tion) 480
Eccentric Fitting 489
Eckert Joint (Definition) 489
Eduction Pipe (Definition) 489
Eighth Bend (Definition) 489
Effect of Bends and Fittings
on Flow of Air in Pipes .... 364
Gas in Pipes.. 324
Steam in
Pipes 346
Curves and Valves on Flow
of Water in Pipes 283-284
Efficiency of a Fall of Water. . . 297
Efflux of Air 357-358
Gas 316
Steam 341-342
Velocity of 357
Elastic Curve of Beams 251
Deflection of Beams.. .251, 257-263
Elongation 113
Limit of Bessemer Pipe
Steel 10
Open Hearth Pipe
Steel : 10
Shelby Seamless Steel
Tubes 16-17
Elasticity Modulus 112, 255, 257
of Beams 254-255
Elbow (Definition) 489
Back Outlet 489
Double Branch (Definition) . . 488
Drop (Definition) 489
Heel Outlet (Definition) 493
Reducing Taper (Definition).. 503
Resistance to Flow 324
Return (Definition) 504
Service 489
Street (Definition) 509
Taper Reducing (Definition) . . 503
Three-way (Definition) 511
Union 489
Electric Line Poles (see Poles).. 109
Tables, Tubular 120-157
Electrolysis 13
Elementary Gases, Densities of. 314
Elevator Casing (Definition) — 484
Elevator (Definition) 489
Ell Back Outlet (Definition) ... 480
Ell, Branch (Definition) 482
Ell (Definition) 489
Ell, Service (Definition) 505
Ell, Side Outlet (Definition) 506
Ell, Union (Definition) 513
Elongation Bessemer Pipe Steel. 10
Elastic 113
Open Hearth Pipe Steel 10
Pipe Caused by Heat 346-347
528
Index
Elongation Shelby Seamless
Steel Tubes i6-ig
Tubes by Heat 211
End Annealed, Tube (Defini-
tion) 480
Converged (Definition) 485
Cylinder 189-190
Dead, of a Pipe (Definition) . . 487
Expanded, Tube (Definition) . 489
Plain (Definition) 501
Safe (Definition) 505
Energy of Water Flowing in
a Tube 298
Engine Cylinder Forgings 195
Engines, Pumping, Discharge
of .293-294
Sizes of Steam Pipes for 347
Thermal Waste 338
Entrance, Resistance to Flow of
Steam Due to 346
Entropy, Tabular Values,
329-333, 339-340
Entry Head , Flow of Water 277
Equation of Pipes 306-309
Equivalent Heads of Water and
Mercury, Table of Pressure 310
Equivalents, Convenient 312
Cubic Feet, Gallons, Seconds,
Minutes, Hours 300
Decimal 470-471, 476
Foot for Each ^ Inch 366-367
Heat, Mechanical 328
Hydraulic 310, 312
Inch for Each y64 « 368
Masses, Metric, English 468
Mechanical of Heat 328
Metric 460-476
Charts... 476
Pressure to Head 274, 310
Water 310-312
Evaporation Factors 333-336
Exhaust Relief Valve (Defini-
tion) 489
Expanded Upset Tubes 158-161
End Tube (Definition) 489
Joint (Definition) 489
Joint Casing 27
Riveted 165-166
Expander, Tube (Definition) ... 512
Expanding of Boiler Tubes into
Tube Sheets 210
Test Boiler Tubes 102
Expansion and Compression,
Adiabatic of Air 355
Isothermal, of Air 356
Contraction of Pipes 168
Expansion and Compression,
Bend 163, 168
Coefficient 211
Coil 489
Diaphragm (Definition) 489
Gases 314-320
Joint 168,489
Expansion Loop 163, 168, 490
of Air Adiabatic 355
Isothermal 356
Gas, Mariotte's Law 314
Iron and Steel Tubes,
Thermal 211
Pipes by Heat 346-347
Steam 346-347
Tubes by Heat .... 211, 346-347
Water 272
Pipes (Definition) 490
Ring (Definition) 490
Valve (Definition) 490
Experimental Tests or Research,
Bursting 212-226
Carbonic Acid 209
Collapse 227-243
Elasticity 112-113
Holding Power of
Boiler Tubes 210-211
Strength of Pole
Joints 116
Exponential Formula, William's
and Hazen's 283
Extension Piece (Definition).. . . 490
External Diameter of Pipe 58-65
External Pressure to Produce
Collapse 227-243
Surface Length of Pipe per
Square Foot 38-41, 57, 199
per Lineal Foot 38-41, 199,
419-459
External Upset Tubes, Lap-
welded and Seamless 158-161
Tables of 160-161
Tubing, California Special
(see California Special Ex-
ternal Upset Tubing).
External Volume per Lineal
Foot of Pipe 419-459
External Volume per Lineal
Foot of Shelby Seamless
Tubing 190
Extra Heavy (Definition) 4QO
Extra Heavy Fittings 168-169
Pipe Flanges, Threaded.. 169, 175
Pressure 168
Unions 169
Valves 170
Index
529
Extra Long Nipples . . . .171, 172, 174
Strong (Definition) 4QQ
Double (Definition) 488
Pipe 25
Bursting Tests 225-226
Columns, Table of Safe
Loads for 247-248
Hydraulic Test Pres-
sures 69
Length per Square Foot
of Surface 57
Used in Poles. . . .in, 118-157
Weights and Dimen-
sions of 25
Face, Raised (Definition) 503
Faced After (Definition) 490
Spot (Definition) 508
Factors, Area, for Tubes 373~375
Capacity for Tubes 423
Deflection of Poles 119-157
Evaporation of 333~336
Internal Fluid Pressure. . . .220-221
Safety 268-270
for Collapse 228
Strength, for Pipes 58-65
Weight for Different Ma-
terials 423
Steel Tubing 376-378
Fahrenheit Thermometer to Cen-
tigrade 473-476
Fairbairn's, Sir Wm., Tests 227
Fall of Water, Power and Effi-
ciency of 297-299
Faucet (Definition) 490
Faucet or Cock, Telegraph
(Definition) 510
Feed Pipe, Internal (Defini-
tion) 494
Feed Water Impurities 275-277
Regulator Floats 194
Feet, Decimal Equivalent of
Inches and 366-367
Feet to Meters 461 , 463
Female and Male (Definition) . . 497
Fence Railings 177-182
Ferro Steel (Definition) 490
Ferrule (Definition) 490
Tube (Definition) 512
Fiber Stresses, Beams,
250-251, 257-263
Collapse of Tubes 228
Internal Fluid Pres-
sures 212-226
Safe Working 268-270
Field Joint of Poles 115, 490
Field Tube (Definition) 491
Fifth Roots and Powers of
Numbers 365-366
Filling Valve, Receiver (Defini-
tion) 503
Finished Cold, Shelby Seamless
Steel Tubes 15
Finished Hot, Shelby Seamless
Steel Tubes 14
Fire Hydrant (Definition) 491
Plug (Definition) 491
Fitting, Ammonia (Definition).. 479
and Pipe Trade, Glossary of
Terms Used 479
Clean-out (Definition) ..... 484
Eccentric (Definition) 489
Inverted (Definition) 494
Long Turn (Definition) 497
Fittings 167, 491
Blast Furnace 170
Cast Iron 168
Converse Lock Joint . 93
Drainage (Definition) 488
Effect of, on Flow of Air 364
Gases 324
Steam 346
Water 283
Extra Heavy Pipe 175
Flanged 167
Malleable 168
Pipe (Definition) 500
Railing (Definition) 503
Railing 177-182
Screwed (Malleable and
Cast) 168
Their Obstruction to Flow of
Air 364
Gas 324
Steam 346
Water 283
Trade Terms (see Glossary) 477-516
Valves and, General 167-170
Working Pressures of 167-168
Flag Poles 115
Flange Blank (Definition) 481
Blanking (Definition) 481
Blind (Definition) 481
Boiler (Definition) 481
Circular (Definition) 484
Collar (Definition) 485
Curved (Definition) 487
(Definition) 491
Internal (Definition) 494
Joint, Peened (Definition).. . . 499
Welded (Definition) 516
530
Index
Flange Pressed (Definition) .... 502
Pump Column (Definition).. . 502
Reinforced, Pump Column
(Definition) 503
Riveted (Definition) 504
Rolled Steel (Definition) 504
Saddle (Definition) 505
Spun (Definition) 508
Union 169, 491
Flanged (Definition) 491
Connections 167, 169
Fittings 167, 169
Joints '. . . .167, 491
Pipe 167, 491
Valves 167
Flanges, Extra Heavy Pipe,
Threaded 169, 175
Pipe Standard 169, 176
Flanging and Bending, Specifi-
cations of Pipe for 95
Flanging Test 13, 95, 100-102
Flat Cylinder Heads, Thick-
ness of 192
Flat Head (Definition) 491
Flat Heads, Strength of ....... 191
Flattening Test 13, 95, 100, 102
Flexible Joint (Definition) 491
Flexure of Beams, Formulae
for 256-263
Floats, Shelby Seamless Steel. .. 194
Flowing Water, Horse-power
of 297-298
Flowing Water, Measurement
of 291-296
Flow in House Service Pipes. . . . 285
Mean Velocity of 280
Measurement by Maximum
and Mean Velocity 292
Miner's Inch 294-296
Nozzles 293
Piezometer 291
PitotTube 291
Venturi Meter 292
Tubes 293
Obstruction to, Caused by
Bends and Fittings, Air . . . .364
Steam 346
Gas 324
Water 283
Flow of Air 357-364
Through Orifices 357-358
Compressed Air 360-364
Gases 316
Formula for Discharge
at High Pressure... .321-323
Low Pressure. .. 317
Flow of Air, Gill's Formula for 317
Gas in Pipes, High Pres-
sure 320-324
Gas in Pipes, Low Pres-
sure 317-320
Effect of Bends and
Fittings 324
Formulas. . . .317, 321-323
Humphrey Observa-
tions on 319
Flow of Gas in Pipes, Tables
from Molesworth's For-
mula 317-318
Steam 34i~347
in Low Pressure Heat-
ing Lines 345
into the Atmosphere.. .341-342
Resistance Due to En-
trance, Bends and
Valves 346
Water, Approx. Formula. 280
Darcy's Formula 282
Diameter of Pipe Re-
quired 290
Effect of Bends on 283
Curves on 283
Friction 286-288
in House Service Pipes. . . 285
Pipes 277
Air Bound 284
Chart 279
Hydraulic Grade
Line 284
Mean Velocity 280-283
Quantity Discharge
278-279
Water Hammer.. . 168, 284
Kutter's Formula 281
Williams and Hazen's
Formula 283
Flowing Water, Measurement
of 291-296
Flue (Definition) 491
Flue Boiler (Definition) 491
Flue Cleaner (Definition) 492
Joints 164-166
Flues, Boiler (see Boiler Tubes).
Fluid Pressure Factors, In-
ternal 220-221
Formulae, Comparison of
Internal 218-219
Pressures, Strength of Com-
mercial Tubes, Pipes and
Cylinders to Resist In-
ternal 212-226
Flush Bushing (Definition) 492
Index
531
Flush Joint (Definition) 402
Tubing, Section of Joint . . 80
Dimensions of, Weights
of 32
Hydrostatic Test Pres-
sure of 75
Flush, Water (Definition) 515
Follower (Definition) 492
Long Screw (Definition) 497
Foot, Cubic Equivalents. 311, 462, 465
Foot, Inches Reduced to Deci-
mals of 366-367
Forged, Pressed (Definition).. . . 502
Forgings, Various Kinds 193-196
Formula, Approximate 280
Common, Flow of Gas in
Pipes, High Pressure. . . .321-322
Cox's, Loss of Head by
Friction in Pipes 289
Darcy's 282
for Flow of Water in Pipes . . . 280
Kutter's 281
Oliphant's, Flow of Gas in
Pipes, High Pressure 322
(see the Given Problem or Author).
Towl's 321
Unwin's, Flow of Gas in
Pipes, High Pressure 323
Williams and Hazen's 283
Formulae, Comparison of High
Pressure Gas 323
Internal Fluid Pressures, 218-219
Thickness of Pipes and
Tubes under Collapsing
Pressure 228-231
Four-way Cock (Definition) .... 492
Tee (Definition) 492
Fractions, Decimal Equivalent
of 368
Franklin Institute Threads. . .370-372
Free on Rails (Definition) 492
Friction, Cox's Formula for . . . 289
Head of Water 278, 286-290
Loss of Head by, in Pipes . . 286- 288
Full Flow Joints 165
-way Valve (Definition) 492
Weight Drill Pipe, Dimen-
sions and Weights of 36
Coupling and Joint,
Typical Section of. . . 80
Hydrostatic Test Pres-
sure of 76
Pipe (see also Standard
Pipe). 22,492
Furnace Fittings, Blast 170
Melting (Definition) 498
Gage. 369, 492
Briggs' Standard... 21, 168, 208-209
Cock (Definition) 492
Length (Definition) 492
Plug (Definition) 502
Ring (Definition) 492
Thread, Valves and Fitt-
ings 168
Water (Definition) 515
Wire and Sheet Metal in
Decimals of an Inch. ...... 369
Gallon, British Imperial 311
Equivalents 311-312
Gallons, Cubic Feet and
Table 300
per Foot of Cisterns 302
per Foot of Cylinders 301
per Foot of Cylindrical Ves-
sels 302
per Foot of Pipes 301
per Foot of Rectangular
Tanks 305
per Foot of Tanks 302
per Lineal Foot Displaced by
Shelby Seamless Tubing. . . 199
per Minute, Cubic Feet per
Second ...... *°.,. . . . 300
to Liters 462-466
Galvanized and Black Pipe —
Standard 22
Extra and Double-extra
Strong, Pipe, Dimensions
of 25
Nipples, Long Screw, Wrought
Pipe 173
Wrought Pipe 171-172
Pipe 22, 92, 94, 107, 364
Weight 21
Galvanizing. 92, 94, 107, 492
Ganguillet's Formula, Flow of
Water in Pipes 281-282
Gas : 313-325
Absorption of , by Liquids 316
Adiabatic Compression of
Natural 324
Avogadro's Law 314
Charles' Law 314
Cocks 170
Common Formula for Dis-
charge of 321
Comparison of Formula for
Discharge of 323
Compression of 324-325
Cox's Formula 321
Density of 314
532
Index
Gas, Effects of Bends and Fitt-
ings 324
Expansion of, Mariotte's Law
for 314
Flow in Pipes, High Pres-
sure 320-324
Low Pressure. .316, 317-325
Affected by Bends and
Fittings 324
under Pressure, Common
Rule 32
Cox's Rule 32
Oliphant's Rule 32
Pittsburgh Rule 32
Rix's Rule 32
Towl's Rule 32
Unwin's Rule 323
Formula for Discharge at
High Pressure 321
Low Pressure 317
General Index 313
Gill's Formula for Flow of . . 317
Law of Mariotte's 314
Maximum Supply of, Through
Pipes. 317
Mixtures of Gas and Vapors .. 315
Molesworth's Formula for
Flow of 317
Natural, Compression of. . .324-325
Oliphant's Formula for Dis-
charge of 322
Pipe 167
Pipes, Table of Sizes of, for
Different Service 319-320
Pittsburgh Formula for Dis-
charge of 321
Pole's Formula for Flow of ... 317
Properties of 314-316
Rix's Formula for Discharge . 321
Saturation Point of Vapors. . . 315
Sizes of House Pipes 319
Supply of Through Pipes 317
Temperatures Produced by
Compression 325
Thread (Definition) 492
Towl's Formula for Discharge 321
Unwin's Formula for Dis-
charge 323
Gaseous Pressures , D alton 's La w 315
Gasket (Definition) 492
Gasoline Engine Cylinder 195
Gate or Straightway Valve,
169, 170, 492
Gate Valve, Angle (Definition). . 479
Wedge (Definition) 515
General Notes 21
Gill's Formula for Flow of
Gases 317
Globe Valve 169-170, 492
Glossary of Terms Used in the
Pipe and Fittings Trade.. 47 7-51 6
Go Devil (Definition) 492
Goose Neck (Definition) 493
Grade Line, Hydraulic 284
Grains to Grams 462, 468
Gram 460
to Avoirdupois Ounces,
462, 468, 476
to Grains 462, 468
Troy Ounces 462, 468
Grashof's Formula for Flat-
heads 191
Grate, Water (Definition) 515
Grease in Boiler Water, Effect
of 276
Grip of Tubes on Tube Sheets .. 210
Grommet or Grummet (Defi-
nition) 493
Groove and Tongue (Defini-
tion) 511
Ground Joint (Definition) 493
Guards, Dog 113, 487
Gyration, Radius of,
244, 257, 264-267
Pipe 58-65,419-459
Shelby Seamless Tubing
206-207
Tubes and Round
Bars 419-459
H
Half Turn Socket (Definition) . . 493
Hammer Jarring While Under
Pressure Test 69, 76
Hammer, Water 168, 284, 515
Hand Railings 177-182
Hand Tight (Definition) 493
Hanger Pipe (Definition) 501
Hard Solder (Definition) 493
H-Branch (Definition) 493
Hawksley Rule f or Flow of Air . 359
Hazelton Head (Definition) .... 493
Hazen's Exponential Formula. . 283
Head (Definition) 493
Bull, Tee (Definition) 483
Casing (Definition) 484
Drive (Definition) 488
Flat (Definition) 491
Hazelton (Definition) 493
Loss of, by Friction 286-290
Water 277, 286-288, 297-299
Patterson (Definition) 499
Index
533
Head Support, Cylinder,
212-213, 222-223
Heads, Bolt and Nut, Square
and Hexagon 370
Cylinder 189-192
Horse-power of Water. ..... 299
of Water and Mercury, Table
of Pressure in Equivalent. . . 310
Header (Definition) 493
Heat, Latent of Steam 327-333
Loss by Convection 348
from Steam Pipes. . 348
Mechanical Equivalent of 328
of Saturated Steam 327-333
of Vaporization 327-333
Required to Evaporate 328
Specific of Air 355
Ice 274
Saturated Steam 328
Superheated Steam 337
Water 275
Superheated Steam . 339-340
Total of Saturated Steam. .327-333
Treatment (see Seamless Prod-
ucts; also Annealing) 14-20
Unit, British Thermal 327
Water 327~333
Heating Lines, Flow of Steam. . . 345
Surface 38-41, 57
Heavy, Extra (Definition) 490
Hectares to Acres 462, 464
Hectoliters per Hectare to
Bushels per Acre 467
to Bushels 462, 467
Heel Outlet Elbow (Defini-
tion) . . 493
Height of Poles. no
Hexagon and Square Nuts and
Heads 370
High Pressure, Flow of Gas in
Pipes at 320-324
Holding Power of Boiler
Tubes 210
Hook, Threading Dies 10
Horn Socket (Definition) 493
Horse-power of a Running
Stream 297
Flowing Water 297, 298
Water Under Different
Heads 299
Hose Mold and Hose Pole Spe-
cification 105
Hot Drawn (Definition) 493
Hot Finished Seamless Steel
Tubes 14
Tube (Definition) 493
House Pipes, Table of Sizes of,
for Different Lengths and
Number of Outlets 319-320
Service Pipes, Flow in 285
Horizontal Loading of Beams. . . 256
Hub (Definition) 493
Typical Section of Converse
Lock Joint 84
Humphrey Observations on Flow
of Gases in Pipes 319
JIundredths of an Inch to Milli-
meters 469
Hydrant (Definition) 494
Hydrant, Fire (Definition) 491
Hydraulic Conversion Table. .300, 311
Equivalents 311, 312
Fittings 168
Grade Line 284
Joint (Definition) 494
Main (Definition) 494
Pressure 168
Radius 281-282
Unions 169
Valves 170
Hydraulics 271-312
Hydrostatic Test Pressure of
Pipe (see Test Pressures).
Ice and Snow, Properties of 274
Ice on Wire 117-118
Illuminating Gas, Flow of 317
Impact Tests 16-19
Imperial Gage 369
Gallon, British 311
Impurities in Boiler Water 276
Inch, Miner's ... 294-296, 312
Inches and Millimeters 470
Decimals of a Foot 366-367
Decimals of Gages in 369
Decimals of, for Each M$4 .... 368
Increaser (Definition) 494
Incrustation, Boiler 275
Index, Air 351
Gas 313
Steam 326
Water 271
Indicator (Definition) 494
Inertia, Moment of 254
for Pipe 58-65
Rectangular Pipe 67
Shelby Seamless Tubing 204-205
Square Pipe 66
Tubes and Round Bars.4to~459
Ingersoll Rand Rule for Flow
of Compressed Air 360-364
Index
Inserted Joint (Definition) . . . . . 494
Inserted Joint Casing, Test"
Pressure of 71
Section of Joint 78
Weights and Dimensions
of 27
Inside Diameter Pipe, Weight
of 21,46-49
Surface Length of Pipe per
Square Foot 38-41, 57
Surface per Lineal Foot, *
38-41, 206-207, 419-459
Inspection and Tests of Shelby
Seamless Steel Tubes 20
Welded Pipe 13,98
(see also "Specifications.")
of Tubes for Steamboats 229
Internal Feed Pipe (Definition) . 494
Flange (Definition) 494
Fluid Pressure Factors. . . . 220-221
Formulae, Comparison
of 218-219
Strength of Tubes, Pipes
and Cylinders 212-226
Surface 38-41, 206-207, 419-459
Upset Tubes, Lap-welded and
Seamless 158-161
Inverted Fitting (Definition) . . . 494
Iron and Steel Tubes, Thermal
Expansion of 211
Cast, Fittings 168-169
Charcoal Analysis 211
Malleable (Definition) 497
Pipe 7, 12, 106
Bursting Tests 223-226
Corrosion 12, 13, 106
Expansion 211, 347
Strength 223-226
Socket (Definition) 507
Weight 423
Isothermal Expansion and Com-
pression of Air, Work of . . . 356
J
Jarring by Hammer, While
Under Pressure Test 69, 76
Jars (Definition) 494
Joint (Definition) 494
Air Line Pipe 80
Allison Vanishing Thread
Tubing 81
Ammonia (Definition) 479
Armstrong (Definition) 480
Artesian (Definition) 480
Ball (Definition) 480
Ball and Cup (Definition) 487
Joint Bell and Spigot (Defini-
tion) 481
Block (Definition) 481
Boiler Tube, Slipping Point
of 210-211
Boston Casing, Pacific Coup-
ling 78
Standard 78
Briggs' Standard 208
Bumped 165,483
Butted and Strapped 164, 483
California Diamond BX
Casing 82
California Diamond BX Drive
Pipe 82
Special External Upset 82
Converse Lock, Pipe (see also
Converse Lock Joint Pipe),
84, 108-109, 167, 485
Corrugated (Definition) 486
Cressed Artesian (Definition). 486
Cup (Definition) 487
Cup and Ball (Definition) 487
Dresser (Definition) 488
Drive Pipe 77, 488
Dry (Definition) . . \ ^l": '.. . . 489
Dry Kiln Pipe. ;.;.,_, . .; ; .\ . 83
Eckert (Definition) 489
Expanded (Definition) 489
Expansion 168, 489
Field 115,490
Flanged 167,491
Flexible (Definition) 491
Flush (Definition) 492
Tubing 80
Full Weight Drill Pipe ...... 80
Ground (Definition) 493
Hydrostatic (Definition). . .'. . 494
Inserted (Definition) 494
Casing .... 78
Kimberley 83, 495
Knock Off (Definition) 495
Lead 83, 84, 167, 496
Lead and Rubber (Definition) 496
Runner (Definition) 496
Leaded, Valves and Fitt-
ings 167
Line Pipe 77, 496
Matheson, Pipe,
42, 84, 107-108, 497
National (Definition) 498
Normandy (Definition) 498
Oil Well Tubing 81
Peened Flange (Definition).. . 499
Perkins (Definition) 499
Petit's (Definition) 500
Index
535
Joint Pipe « 77-84
Pole in, 115, 116
Pope (Definition) 502
Pressure (Definition) 502
Reamed and Drifted Pipe... . 79
Riedler (Definition) . 504
Riveted Pipe 164-166
Rotary Pipe 79
Rust (Definition) 505
Screwed 167
Shop for Poles. . . .111-115, 116-119
Shrunk (Definition) . . . 506
Siemen's (Definition) 506
Signal Pipe 97
Slip (Definition) 507
Socket (Definition) 507
South Penn Casing 83
Special Rotary Pipe 79
Upset Rotary Pipe 79
Spigot (Definition) 508
Standard Pipe 77
Boston Casing 78
Strength of Poles 115
Swaged in, 115-116
Swing (Definition) 510
Swivel (Definition) 510
Thimble (Definition) 511
Union (Definition) 513
Upset Rotary Pipe 79
Vanishing Thread, Allison 81
Van Stone (Definition) 514
Walker (Definition) 514
Welded Flange (Definition). . 516
Wiped (Definition) . . 516
Joints and Couplings 77-84
Slipping Point of Rolled
Boiler Tube 210-211
Jointer (Definition) 495
Jointing, Special Sizes of Poles. . in
K
Kalameined (Definition) 495
Kent's Formula for Discharge
of Steam from Pipes 344
"Kewanee" (Definition) 495
Union (Definition) 495
Unions 169
Kiln Pipe, Dry (see Dry Kiln
Pipe).
Kilogram 460-462
Equivalents 472
to Avoirdupois Pounds,
462, 468, 472
Troy Pounds 462, 468, 472
Kilometers to Miles 461, 463
Kimberley Joint (Definition) . . . 495
Pipe Section of Joint 83
Test Pressures of . 74
Weights and Dimen-
sions of 44
Knock Off Joint (Definition) .... 495
Kutter's Formula for Flow of
Water in Pipes 281
Ladders, Pipe 183-186
Laid Length (Definition) 495
Lame's Formula for Strength
of Tubes, Internal Pres-
sure 215, 218, 219
Lap-weld (Definition) 496
(Process) 7
Lap-welded Boiler Tubes (see
Boiler Tubes).
Pipe, Bursting Tests 223-226
Expanded 158-161
Tubes, Upset and Expanded,
158-161
Latent Heat of Steam 327-333
Lateral (Definition) 496
Contraction, Coefficient 215
Law, Avogadro's 314
Charles' 314
Chicago Building for
Columns 244-249
Dalton's 315
Marine 229-230
Inspection for Cylinder
Heads 191
Mariotte's 314
New York Building, for
Columns 244-249
Lead (Definition) . 496
Lead and Rubber Joint (Defini-
tion) 496
Joint (Definition) 496
(see Converse, Kimberley
and Matheson Joint.)
Runner (Definition) 496
Lined Pipe (Definition) 496
of Threading Dies 10-11
Weight 423
Wool (Definition) 496
Leaded Joints 167
Leak Clamp (Definition) 496
Length, British Standard Pole . . 109
Columns 244-249
Converse Lock Joint 93, 109
Cut (Definition) 21, 487
Gage (Definition) 492
Laid (Definition) 495
536
Index
Length, Long (Definition) 496
Matheson Joint Pipe. . . .91, 92, 109
Measure (see Metric Equiva-
lents). . . .461, 463, 469-471, 476
Pipe for One Square Foot of
Surface 57
Poles 109, no, 120-157
Shelby Seamless Cold-
drawn Steel Trolley
Poles 198
Signal Pipe 96
Lengths, Comparison of Cus-
tomary and Metric Units. . 463
Conversion Chart for 476
Inches and Millimeters 469-471
of Locomotive Boiler Tubes . . 38-40
of Pipe, Variation in 21
of Threads 208
Random (Definition) 503
Weights and Temperatures,
Chart for Conversion 208, 476
Light Standard Valves 170
Lilly's Formula for Collapsing
Pressures 231
Lime in Feed Water 275-276
Limit of Accuracy of Cut
Length Pipes and Diam-
eters 21, 102
Straight ness, Hose Poles ... 105
Limits Deflection of Poles 112
Set of Poles 112
Linde's Equation 337
Line, Hydraulic Grade 284
Pipe, Dimensions of 23, 496
Section of Joint 77
Test Pressures 68
Air (see Air Line Pipe).
Joint (Definition) 496
Poles Tubular and Electric. 109-1 5 7
Sand (Definition) 505
Lineal Feet per Square Foot of
Shelby Seamless Tubing. . . 199
Linear Expansion of Pipes,
211,346-347
Lined Pipe Lead (Definition) . . . 496
Tin (Definition) 511
Lip of Threading Dies 10
Union 169, 496
Liquid Gallons to Liters 462, 466
Ounces to Milliliters 462, 466
Quarts to Liters 462, 466
Liquids, Absorption of Gases.. . 316
Liquor Marks 91, 93, 98
Liter 460-462
Capacity of Pipe 423
Equivalents 3"
Liter, to Dry Quarts 462, 467
to Liquid Gallons 462, 466
Quarts 462, 466
Pecks 462,467
Live Load on Poles 117
Loading of Beams 258-263
in Any Direction Equally. 256
Vertical and Horizontal 256
Pipe Columns 244-249
Poles 119-157
Safety Factors for Static 268
Variable 268
Seamless Trolley Poles Shelby 1 98
Wind on Poles 116-118
Lock Joint Pipe Converse (see
Converse Lock Joint Pipe).
Nut (Definition) 496
Locomotive Boiler Tubes and
Safe Ends (see Boiler Tubes).
Long Length (Definition) 496
Nipples 171, 172, 174
Screw (Definition) 496
Screw Follower (Definition) . . 497
Nipples 173
Ton Equivalents 462, 472
Turn Fitting (Definition) .... 497
Longitudinal Stresses, Internal
Fluid Pressure 212-220
Loop (Definition) 497
Expansion 163, 168, 490
Loss of Air Pressure in Pipes.35o~36o
Head by Bends 283
Friction in Pipes. . . . 286-290
Cox's Formula 289
Table from For-
mula 289-290
Valves 283
Heat from Engines 338
Heat from Steam Pipes . .348-350
Pressure due to Flow, Air,
359-360
Low Pressure Fittings 167, 169
Flow of Gas in Pipes at. .317-319
Heating Lines, Flow of
Steam in 345-346
Valves 170
Lubrication of Threading Dies . . 1 1
M
Machine, Drilling (Definition).. 488
Pipe Bending (Definition) 500
Tapping (Definition) 510
Machining Allowances, Cream
Separator Bowls 104
Male and Female (Definition) . . . 497
Index
537
Magnesia in Feed Water 275-276
Malleable Iron (Definition) .... 497
Fittings 168
Unions 169
Mandrel Socket (Definition).. . . 497
Manganese in Pipe Steel 10
Shelby Seamless Steel
Tubes 16, 18, 19
Manifold (Definition) 497
Mannesmann (Definition) 497
Manufacture of Ammonia Pipe 98
Converse Lock Joint Pipe . . 93
Double-extra Strong Pipe . . 8,9
M atheson Joint Pipe 91
Pipe for Flanging and
Bending 95
Poles 115
Seamless Cylinders, Shelby 15, 188
Seamless Steel Tubes,
Shelby. , 14-20
Trolley Poles 197-198
Signal Pipe 96
Standard Welded Pipe 89
Tubular Goods 7-20
Working Barrels 187
Manufacturers' Gages 369
Standard Flanges 169, 175
Pipe Thread 209
Margin of Security 268
Marine Boiler Tubes, Specifica-
tions IOO-IOI
Law Formula for Collapse. ... 229
Law Inspection of Cylinder
Heads. 191
Law's Limitation of Pressure
on Tubes 229-230
Mariotte's Law for Expansion
of Gases 314, 320
Marking of Pipe 20
Mass Measures (see Metric
Equivalents) 468
Masses, Comparison of Custom-
ary and Metric Units of. ... 468
Master Die (Definition) 497
Master Steam Fitters Standard
Flanges 169, 176
Master Tap (Definition) 497
Material, Ammonia Pipe 98
Boiler Tubes for Merchant
and Marine Service 100
Converse Lock Joint Pipe .... 93
Cylinder 15
Lap-welded Locomotive Boiler
Tubes 99
Matheson Joint Pipe 91
Pipe 9, 10, 15-19
j Material, Pipe for Flanging and
Bending 95
Poles in
Properties of 9
Seamless Cylinders 188
Seamless Locomotive Boiler
Tubes ioi
Seamless Trolley Poles 198
Steel Tubes 15
Signal Pipe 96
Standard Welded Pipe 89-90
Tubes for Cream Separator
Bowls 103
Tubes for Diamond Drill
Rods 104
Tubes for Hose Poles and
Molds 105
Used in Manufacture of Tubu-
lar Goods 7-20
Weight Factor 423
Working Barrels 187
Matheson and Dresser Joint
(Definition) 497
Joint Pipe 107- 108, 497
Hydrostatic Test Pres-
sure of 73
Length 91, 92, 108
Measurements 92
Protective Coatings 91
Section of Joint 84
Specifications for 91-92
Weights and Dimen-
sions of 42
Maximum Supply of Gas
Through Pipes 317
Mean Velocity of Flow in Pipes . 280
Measurement Equals Weight
(Definition) 498
Converse Lock Joint
Pipe 95
of Discharge of Pumping En-
gines by Means of Nozzles . . 293
Flowing Water by Ven-
turi Tubes 293
Piezometer 291
Pitot Tube 291
the Venturi Meter .... 292
Matheson Joint Pipe 92
Maximum and Mean Veloc-
ity of Flow in Pipes 292
Water by Nozzles 293
Miner's Inch 296
Steamer's (Definition) 509
Measures, Metric 460-472
Mechanical Equivalent of
Heat 328
538
Index
Mechanical Properties of Solid
and Tubular Beams 250-267
Medium Pressure (Definition), 168, 498
Fittings 168, 170
Melting Furnace (Definition). . . 498
Point Influence by Pressure . . 274
Merchant and Marine Boiler
Tubes (See Boiler Tubes).
Mercury, Table of Pressure in
Equivalent Heads of Water 310
Metal Area of Pipe. . . .58-65, 419-459
Metal, Sheet and Wire Gages. . 369
Meter 460-463
to Feet 461, 463
Inches 470-471
Yards 461-463
Venturi 292
Metric and Customary Units . 462-467
Areas 464
Capacities 466-467
Equivalents 461
Lengths 463, 476
Millimeters to Decimals of
an Inch 469
Masses 468
System 460-476
Conversion Chart for
Lengths, Weights and
Temperatures 476
Equivalents of Inches. . .470-471
Ton Equivalents 462, 472
Units 460
Volumes 465
Miles to Kilometers 461, 463
Milliliters to Apothecaries
Drams 462, 466
Scruples 466
Liquid Ounces 462, 466
Millimeters to Inches. . . .463, 469-471
Mill Inspection 13, 14, 20
Tests (see also Hydrostatic
Tests 68-76) 13, 14, 20
Miner's Inch, California. ...... 312
Colorado 312
Flow Measurement 294-296
Minimum Weight of Beams. ... 255
Miscellaneous Specialties 195
Mixtures of Vapors and Gases. . 315
Module 295
Modulus of Elasticity. . .112, 255, 257
Section 253-267
Pipe 58-65
Rectangular Pipe 67
Seamless Tubing Shelby . 204-205
Square Pipe 66
Tubes and Round Bars. .419-459
Molesworth's Formula, Tables
from, for Flow of Gas in
Pipes 317-318
Moment, Bending 252
of Inertia for Shelby Seam-
less Tubing 204-205
of Beams 254
Moment of Inertia of Pipes 58-65
of Rectangular Pipes. ... 67
Square Pipes 66
Tubes and Round
Bars 419-459
Resisting 253
Motors, Water Current 298
Mounted (Definition) 498
Brass (Definition) 482
Mouthed-bell (Definition) 481
Mud in Feed-Water 275, 276
N
Napierfs Formula 342
National Coating (Specification),
94, 107, 108, 109
Joint (Definition) 498
Pole Socket (Definition) 498
Word Rolled on Welded Pipe . 20
Natural Gas, Adiabatic Com-
pression of 324-325
Nature of Stress in Tube Wall . . 212
Neck, Goose 493
Neck of Cylinders 189-190
Needle Valve (Definition) 498
Nested (Definition) 498
Neutral Surface Beams 250
New York Rule for Columns 244
Nickel in Shelby Seamless Steel
Tubes .ri'hc&k
Weight 423
Ninety Degree Pipe Bend 163
Nipple (Definition) 498
Casing 174
Close (Definition) 485
Long Screw 173
Short (Definition) 506
Shoulder (Definition) 506
Space (Definition) 507
Swaged (Definition) 509
Tank 173
Nipples, Wrought Casing 174
Pipe 171-172
Nitric Acid in Boiler Water 276
Nominal Diameter, Internal
and External flj&J 21
Non-return Valve (Definition) . . 498
Normandy Joint (Definition) . . . 498
Notched Test 16-19
Index
539
Notes General, of Pipe Trade. . 21
Nozzle (Definition) 498
Measurement 293
Number of Barrels in Cisterns
and Tanks 304
Chasers Required in Thread-
ing Dies ii
Threads per Inch 208
Nut (Definition) 498
Lock (Definition) 496
Unions 169
Nuts and Bolt Heads, Screw
Threads, Proportions of 370
O
Odd Sizes of Poles in
Offset Pipe (Definition) 499
Bends. 162, 163
Oil for Threading n
Oil Well Tubing, Section of
Joint.' 81
Test Pressure of 69
Weights and Dimensions
of 30
Oils in Boiler Water, Animal
and Vegetable, Effect of 276
Oliphant's Formula for Dis-
charge of Gas 322
Open Hearth Pipe Steel, Chemi-
cal and Physical Analysis
of 10, 211
Open Return Bend (Definition) . 499
Orifices, Flow of Air from . . . .357-358
Steam from 341
Ounces, Avoirdupois to Grams,
462, 468, 476
Liquid to Milliliters 462, 466
per Square Inch in Equiva-
lent Heads 310
Troy to Grams 462, 468
Outflow of Steam into Atmos-
phere 342
Outlet, Back, Central 480
Outlet, Back, Eccentric 480
Outlet Ell, Back (Definition) ... 480
Outlet, Heel Elbow 493
Side (Definition) 506
Tee, Side (Definition) 506
Outside Diameter 21
for Shelby Seamless Tubing 199
Pipe, Weight of 50-56
Surface per Lineal Foot of
Shelby Seamless Tubing. . . 199
Length of Pipe per Square
Foot. . .38-41, 57, 199, 410-459
per Lineal Foot.. .38-41, 419-459
Oval Socket (Definition) 499
Oxidation of Pipes 277
Oxygen Absorption by Water ... 316
Cylinders 188
Pacific Couplings, Boston Casing
(see Boston Casing, Pacific
Couplings).
Packer (Definition) 499
Water (Definition) 515
Packing (Definition) 499
Tube (Definition) 512
Painting Pipe 107
Poles 118
Palliation for Troublesome Sub-
stances in Boilers 276
Patterson Head (Definition) 499
Pecks to Dekaliters .462, 467
Liters... 467
Peened Flange Joint 167, 499
Peening (Definition) 499
Penn Casing, South 35
Penstock (Definition) 499
Perfect Threads 208
Perforated (Definition) 499
Perkins Joint (Definition) 499
Pet Cock (Definition) 500
Petit's Joint (Definition) 500
Phosphorus in Pipe Steel 10
Shelby Seamless Steel
Tubes 16, 18, 19
Physical Properties of Boiler
Tubes 99-102
Carbonic Acid 209
Converse Lock Joint
Pipe 93
Gases 314-316
Matheson Joint Pipe .... 91
of Pipe Steel 10
Shelby Seamless Steel
Tubes 16-19
Tubular Goods 10
Signal Pipe 96
Standard Pipe 90
Piece, Extension (Definition). . . 490
Piercing Process 14
Piezometer 291
Piles, Butted and Strapped 165
Pillars 244
Pilot (Definition) 500
Pipe (Definition) 500
Air Line, Hydrostatic Test
Pressure 73
Section of Coupling and
Joint 80
540
Index
Pipe, Air Line, Weights and
Dimension of 36
Ammonia, Specifications for . . g8
and Fittings Trade, Glossary
of Terms Used in 477-516
Tubes, Application of Table
to 421-423
Tubing, Steel, Weight of
Tables 370-418
Welded Tubes 7-14
Annealing of 10
Area Factors 373~375
Area of 58-65, 419-459
Arranged by Outside Diam-
eter 58-65
Bend (Definition) 500
Bends 162-163
Wrought, Radii of 162
Bending Machine (Definition) 500
Properties of Rectangular. . 67
Square 66
Black 21, 22
Branch (Definition) 482
Breeches (Definition) 482
Bursting Tests 212-226
Butt Welded, How Made 9
California Diamond BX Drive,
Section of Joint . 82
Test Pressures of 76
Weights and Dimensions
of 31
Capacity 301, 303, 4i9~459
Factors 423
Card Weight (Definition) (see
also Standard Pipe) 483
Circumference 419-459
Clamp (Definition) 500
Clamps, Water (Definition). . 515
Coating for,
91, 94, 106-107, 277, 485
Collapsing Pressures of 227-243
Columns, Double Extra
Strong, Safe Loads for 249
Extra Strong, Safe Loads
for 247-248
General 244
Table of Safe Loads for . . 244-249
Tests on 230
Conduit (Definition) 485
Converse Lock Joint 108-109
Section of 84
Specifications for 93~95
Test Pressures of 74
Weights and Dimen-
sions of 43
Corrosion. . , 12, 13, 106
Pipe, Coupling (Definition) (see
also Joints) 500
Coverings, Steam 348-350, 500
Cutter (Definition) 500
Dead End of (Definition). . . . 487
Die (Definition) 500
Dies lo-i i
Dip (Definition) 487
Discharge Capacities of. . . .306-309
Dog (Definition) 500
Double Extra Strong, Dimen-
sions and Weights of 25
(see also Double Extra
Strong Pipe.)
Test Pressures of 69
Drifted and Reamed (see
Reamed and Drifted Pipe.)
Drill Dimensions and Weights 36
Section of Joint 80
Test Pressures of 76
Drive (Definition) 488
California Diamond BX,
Dimensions and Weights 31
Section of Joint 82
Test Pressures 76
Dimensions and Weights. .. 24
Section of Joint 77
Test Pressures of 69
Dry (Definition) 489
Kiln, Dimensions and
Weights of 37
Section of Joint 83
Test Pressures of 76
Eduction (Definition) 489
External Diameter. . . . 50-56, 58-65
Extra Strong, Dimensions
and Weights of 25
Test Pressures 69
Fittings (Definition) 500
Flanged 167, 491
Flanges, Extra Heavy 169, 175
Standard , 169, 176
Flanging and Bending, Speci-
fications for 95
Flow of Air 357-364
Flow of Gas in 317-324
Steam 341-346
Water 277-290
Full Weight (Definition) (see
also Standard Pipe) 492
Full Weight Drill (see Full
Weight Drill Pipe).
Gas 167
Pipe for House Service
319-320
General Notes 21
Index
541
Pipe, Grip (Definition) 501
Hanger (Definition) 501
Hydrostatic Test Pressures. . . 68-76
Industry, Development of ... 7
Inspection and Test 13, 14, 20
Internal Diameter Sizes
(Weight per Foot) 46-49
Internal Feed (Definition).. . . 494
Iron. . . 7, 12, 106, 211, 223-226, 347
Joint Drive (Definition) 488
Line (Definition) 496
Leaded 83, 84, 107-108, 167
Riveted 164-166
Section of 77-84
Kimberley Joint, Dimensions
and Weights of 44
Section of Joint 83
Test Pressures of 74
Ladders 183-186
Lap-welded, How Made 7
Lead Lined (Definition) 496
Length of, for One Square
Foot of Surface 38-41, 57
Line (Definition) 501
Dimensions and Weights. . . 23
Section of Joint 77
Test Pressures of 68
Loss of Head by Friction
\ in 286-290
'Manufacture 7-20
Marking of 20
Matheson Joint 107-108, 167
Dimensions and Weights 42
Section of Joint 84
Specifications for 91
Test Pressures of 73
Moment of Inertia of,
58-65, 119,419-459
Nipples 168, 171-173
Nominal Internal Diameter
Weights per Foot 46-49
Outside Diameter Weights
per Foot 50-56
Offset (Definition) 499
Oxidation 277
Painting 107
Plug (Definition) 502
Plugged and Reamed (see
also Reamed and Drifted
Pipe).
Poles 109-157
Properties of 58-65, 419-459
Materials 9
Radius ot Gyration of,
58-65, 410-459
Railings 177-182
Pipe, Reamed and Drifted,
Dimensions and Weights of 35
Reamed and Drifted, Section
of Coupling and Joint 79
Test Pressure of 73
Rectangular, Bending Proper-
ties of 67
Dimensions and Weights . . 45
Ladders 184-185
Section of 87, 88
Rifled (Definition) 504
Ring, Drive (Definition) 488
Riser (Definition) 504
Roller (Definition) 501
Rotary, Special (see Special
Rotary Pipe).
S (Definition) 508
Screwed 167
Section Modulus 58-65
Service (Definition) 505
Signal (Definition) 506
Assembly of 97
Specifications for 96, 97
Siphon (Definition) 507
Size 21, 208-209
Socket (Definition) 507
Soil (Definition) 507
Special Ammonia Specifica-
tion 98
Special Rotary Section of
Joint 79
Test Pressure 76
Weights' and Dimen-
sions 34
Upset Rotary Section of
Joint 79
Test Pressure 76
Weights and Dimen-
sions 34
Specifications for Converse
Lock Joint 93
Flanging and Bending ... 95
Matheson Joint 91
Signal. 96
Special Ammonia 98
Standard 89
Square Bending Properties of. 66
Dimensions and Weights. . . 45
Ladders 184-186
Section of 85-86
Standard, Definition of 508
Heating Surface 57
Section of Joint 77
Specifications for 89
Test Pressure 68
Weights and Dimensions. . 22
542
Index
Pipe, Stand (Definition) 508
Stay (Definition) 501
Steam Engine 347-348
Steam (see Standard Pipe).
Steel, Annealing 10
Bursting Tests 212-226
Chemical and Physical
Analysis 10
Expansion of Steam 347
Manufacture of 7-20
Protective Coatings for. ... 106
Thermal Expansion of 211
Stock (Definition) 501
Strength Factor of 58-65
Under Internal Pressure,
212-226
Surface of 57
per Foot of Length 419-459
Tail (Definition) 510
Terms Used in Trade 477-516
Test Pressure of 68-76
Thickness of. . .22-45, 46-56, 58-65
Briggs' Standard 208
Thread (Definition) 501
Depth of 209
Threading 10
Threads 21
Briggs' Standard 208-209
Used by National Tube
Company 21
Tin Lined (Definition) 511
Tongs (Definition) 501
Trade Usage 21
Tuyere, Dimensions and
Weights of 37
Test Pressures of 76
Unions (Definition) 501
Vise (Definition) 501
Volume 419-459
Weight 21
Factors 376-378
Weight per Foot,
21-56,58-65,379-459
per Foot of Water in 303
Welded, Manufacture of,
7-14, 89-90
Specification of 89-90
Wrench (Definition) 501
Wrought Nipples 171-172
Yield-point Tests on Commer-
cial 222
Pipes, Air Bound 284
Approximate Formula for Flow
of Water in . . 280
Bursting Tests of Commer-
cial 223-225
Pipes, Comparison of Internal
Fluid Pressure, Formulae for,
218-219
Condensation in 348
Contents of, per Foot Length. . 301
Expansion (Definition),
211, 346-347, 490
Flow in House Service 285
Flow of Air in 357~359
Compressed Air in. . . .360-364
Gas in, at High Pressure,
320-324
Low Pressure.. .317-319
Steam in 341-346
Water in. 277-290
Chart for 279
House Service. . . 285, 317, 319-320
Kent's Formula for Dis-
charge of Steam from 344
Loss of Air Pressure in 359
Head in, by Friction. . . 286-287
Maximum and Mean Veloc-
ity in j . . 292
Mean Velocity of Flow 280-283
Quantity of Water Discharged
Through 278
Relative Discharge Capacity
of, Table of 306-309
Steam, Bare, Condensation
in 348
Coverings 348-350
Expansion of 346-347
Loss of Heat from 348
Sizes of, for Engines 347
Strength of, Under Internal
Pressure 212-226
Weld of Commercial 226
Supply of Gas Through 317
Table of Capacities of 301
Thickness of, Formulas for,
Under Collapsing Pressure,
228-231
Velocities in 292
Water Hammer in. ... 168, 284, 515
Weight of -Water in 303
Piping (Definition) 501
Pitch (Definition) 501
of Threads, Briggs' Stand-
ard 208
Pitot Tube, Flow Measure-
ment 291
Pitting of Boiler Plates 277
Pittsburgh Formula for Dis-
charge of Gas 321
Plain End (Definition) 501
Plain Standard Fittings 168
Index
543
Planting Poles no
Plates, Steel Tubes Made from. . 1 5
Plug (Definition) 501
Cock (Definition) 502
Fire (Definition) 491
Gage (Definition) 502
Pipe (Definition) 502
Signal Pipe 96, 97
Socket (Definition) 507
Tap (Definition) 502
Tube (Definition) 512
Water (Definition). . . . 515
Plugged and Reamed Pipe (see
Reamed and Drifted Pipe).
Plunger Forgings 195
Poisson's Ration 215
Polar Moment of Inertia.257, 420, 422
Pole Drill (Definition) 502
Pole's Formula for Flow of
Gas 317
Poles, Anchor 109
Assembling in, 115
Bending Stresses 117
British Standard 109
Butt Section 118-157 |
Center 109
Coating 118
Column Strength . , 117
Crippling 116
Customary Sizes 109
Deflection Due to Load,
ii2: 113, 119-157, 198
Limit 112
Versus Weight 113
Dimensions of 118-157
Dog Guards for 113-114
Drop Test 116, 119
Elastic Limit in
Extra Strong Pipe for,
in, 118-157
Flag 115
Foundations 110
Height no
Joint in, 115, 116, 119
Length 109, 120-157
of Trolley Poles 198
Loads 117, 110-157, 198
Manufacture in
Modulus of Elasticity 112
Odd Sizes in
Painting 118
Planting no
Seamless Trolley Shelby. . . 197-198
Section Length no, 120-157
Service Conditions 116-118
Set Limits 112, 116, 119
Poles, Size 109, 120-157
Sleeves for 114
Snow Load 1 1 7-118
Span Wire 109
Special Sizes in
Specifications
Standard. .
Stiffnei
Strength. .
.in, i
.110, i
. . .110, i
2, 119
8-157
1-113
if H3
of Joints i 5-116
of Material in
Stresses 117, 197
Tables 118-157
Telegraph 110
Testing 114, 119
Thickness 118-157
Trolley 197-198
Use of Standard Pipe. . in, 118-157
Weight 110,113,120-157,198
Wind Loads 116-118
Yield Point 112
Pop (Definition) 502
Cylinder Heads 189-190
Pope Joint (Definition) 502
Posts 244
Pots, Annealing 190
Pounds and Tons, Comparison
of Various 473
Pounds, Avoirdupois to Kilo-
grams 462, 468, 472
of Water, Equivalents 311
per Square Inch to Heads. .274, 310
Troy to Kilograms. . . 462, 468, 472
Pouring Clamp (Definition) .... 502
Power of a Running Stream. ... 297
Waterfall 297
Water Heads 299
Powers of Numbers, Tables.. 365-366
Pratt and Whitney Gages 21, 209
Pressed Flange (Definition) .... 502
Forged (Definition) 502
Pressure Air 273, 352
Collapsing 227-243
Dalton's Law 315
Drop in Steam Lines 342-346
Equivalents of Water and
Mercury 310
External Fluid 227-243
Extra Heavy 168
Factors, Internal Fluid 220-221
Formulae, Comparison of In-
ternal Fluid 218-219
Gas 3i4,3iS
High, Flow of Gas in Pipes .320-325
Hydraulic 168
Ice and Snow 274
544
Index
Pressure, Internal 212-226
Joint (Definition) 502
Losses, Compressed Air.. . .359-360
Low 167
Flow of Gas in Pipes .... 317-320
Steam in Heating
Lines 345
Marine Law 220-230
Medium 168, 498
of Air Related to Tempera-
ture and Volume 352
Permissible on Tubes Under
Marine Law 229-230
Standard (Definition) 167, 508
Steam 327-333
Strength of Tubes, Pipes and
Cylinders Under Internal
Fluid 212-226
Test, Hydrostatic of Pipe 68-76
(See also Test Pressure).
Volume Air Low 357
Volume, Temperature of Air. . 352
Water 273-274, 277, 310
Working 167-168
Priming, Remedy for 276
Processes Used in Manufacture. 7-20
Stiefel (Definition) 509
Properties of Air 352-356
Beams and Column Sec-
tions 250-267
Bending Rectangular Pipe . 67
Bending Square Pipe 66
Carbonic Acid 209-210
Gas 314-316
Ice 274
Materials Used for Welded
Pipe 9-10
Seamless Pipe (Shel-
by) 15-19
Properties of Pipe 58-65, 419-459
Steel, Physical 10
Saturated Steam 329~333
Screw Threads 370
Shelby Seamless Steel Tub-
ing 16-19, 199-207
Snow 274
Solid Beams 250-267
Steam 327-340
Superheated Steam 339~34O
Tubes and Round Bars,
Table 419-459
Tubular Beams 250-267
Water 272-275
Physical of Carbonic Acid. . . 209
Shelby Seamless Steel
Tubes 16-19
Protecting Caps for Valves 194
Protection of Threads 90, 98
Protective Coatings 106-107
Protector (Definition) 502
Pulling Tests 10
Pump Column Flange (Defini-
tion) 502
Reinforced (Definition). . 503
Pumping Engines, Measure-
ment of Discharge by
Means of Nozzles 293
Pump, Sand (Definition) 505
Quantity of Water Discharged. . 278
Quarts, Dry to Liters 462, 467
Liquid to Liters 462, 466
Radial Stress in Tube Wall. .. 212-213
Radiation from Steam Pipes. . . . 348
Radiator (Definition) 502
Valve (Definition) 502
Radii of Pipe Bends 162
Radius, Hydraulic 281-282
Radius of Bend (Definition) .... 502
Radius of Gyration of Columns 244
Pipe 58-65, 419-459
Seamless Tubes (Shelby),
206-207, 419-459
Pipe Bends 162
Railing Fittings (Definition). ... 503
Railings of Pipe, Hand 177-182
Rails, Free on (Definition) 492
Railway Poles 109
Signal Ass'n. Spec, for Signal
Pipe 96
Raised Face (Definition) 503
Rake, Threading Dies 10
Ram Water 168, 284
Random Lengths (Definition) . . 503
Ratio for Columns, Slenderness . 244
Poisson's 215
Reactions of Supports of Beams. 252
Reamed (Definition) 503
Reamed and Drifted (Defini-
tion) 503
Pipe, Test Pressure 73
Section of Joint 79
Weights and Dimen-
sions of 35
Reamer Under (Definition). ... 513
Reaming Ammonia Pipe 98
Standard Pipe 90
Index
545
Receiver Filling Valve (Defini-
tion) 503
Recess Calking (Definition) .... 483
Recessed (Definition) 503
Rectangular Pipe. Bending
Properties of 67
Ladders 184, 185
Sections of 87-88
Weights and Dimensions 45
Tanks, Table of, Capacities 305
Redrawn Pipes, Bursting
Tests » 225-226
Reducer (Definition) 503
Reducing Taper Elbow (Defi-
nition) 503
Tee (Definition) 503
Valve (Definition) 503
Reference Books on Corrosion . . 12
Reflux Valve (Definition) 503
Reinforced Pump Column
Flange (Definition) 503
Reinforcing Clamp, Converse
Lock Joint Pipe 109
Matheson Joint Pipe 108
Relative Discharge Capacity of
Pipes, Table of 306-309
Relief Valve, Exhaust (Defini-
tion) 489
Remedy for Troublesome Sub-
stances in Boilers 276
Repairing Poles 114
Research Tests of Pole Joints ... 116
Bursting 212-226
Carbonic Acid 209
Collapse 227-243
Elasticity 112, 113
Expansion 211
Reservoir (Definition) 503
Resistance Due to Bends, En-
trance and Valves 169
Air 364
Gas 324
Steam 346
Water 283-284
of Pipe to Internal Pres-
sure 212-226
External Pressure. . . 227-243
to Slipping of Boiler Tubes. . . 210
Resisting Moment of Beams. . . . 253
Return Bend (Definition) 504
Close (Definition) 485
Open (Definition) 499
with Back Outlet (Defini-
tion) 504
Elbow (Definition) 504
Ribbed Tube (Definition) 504
Riedler Joint (Definition) 504
Rifled Pipe (Definition) 504
Ring (Definition) 504
Drive Pipe (Definition) 488
Expansion (Definition) 490
Gage (Definition) 492
Tests 102
Union 169, 594
Riser Pipe (Definition) 504
River Dog (Definition) 504
Sleeve (Definition) 504
Riveted Bump Joints 165-166
Butted and Strapped Joints,
164-165
Flange (Definition) 504
Rivet Spacing, Pipe Joints . . . 165-166
Rivets, Signal Pipe 96, 97
Rix's Formula for Discharge of
Gas 321
Rod (Definition) 504
Sucker (Definition) 509
Rods, Diamond Drill 104-105
Roebling Wire Gage 369
Rolled Boiler Tube Joints,
Slipping Point of 210-211
Steel Flange (Definition) .... 504
Roller, Pipe (Definition) 501
Roots, Fifth, Table of 365-366
Rotary Pipe (see Special and
Special Upset Rotary Pipe).
Round Bars and Tubes, Table
of Properties of 419-459
Cylinder Heads 189-190
Rubber and Lead Joint
(Definition) 496
Run (Definition) 504
Rungs, Ladder 183-186
Runner, Lead Joint (Defini-
tion) 496
Runners, Pipe 183-186
Running Stream, Horse Power 297
Rust Joint (Definition) 505
Saddle (Definition) 505
Flange (Definition) 505
Safe End (Definition) 505
Ends (see Boiler Tubes).
Internal Pressure for Tubes,
220-221
Loads for Extra Strong Pipe
Columns 247-248
Double Extra Strong Pipe
Columns 249
Standard Pipe Columns,
245-246
546
Index
Safety Factors for Static
Loading 268
Variable Loading 268-270
Railings 177-182
Working Fiber Stress 268-270
Salt in Feed Water 277
Sand Line (Definition) 505
Pump (Definition) 505
Saturated Steam (see Steam,
Saturated).
Saturation Point of Vapors 315
Scale in Boilers 276
Sealer, Tube (Definition) 512
Scarf Weld (Definition) 505
Scraper, Tube (Definition) 512
Screw (Definition) 505
Down Valve (Definition) .... 505
Long (Definition) 496
Follower (Definition) 497
Temper (Definition) 511
Threads, Dimensions of 371
Franklin Institute 370-372
Properties of 370
Sellers 370-372
Standard Pipe 208
U. S. Standard 370-372
Screwed (Definition) 505
Fittings, Cast Iron. 168
Malleable Iron 168
Flanges 167
Joints 167
Pipe 167
Scruples, Apothecaries to Milli-
liters 466
Seamless (Definition) 505
Boiler Tubes (see Boiler Tubes
(Shelby).
Bursting Tests (Shelby) . . . 223-225
Cylinders (Shelby) 15, 188
Diamond Drill Rods (Shelby),
104-105
Expanded Tubes (Shelby).. . . 158
Hose Poles 105
Hot Finished Tubes (Shelby) . 14
Locomotive Boiler Tubes (see
Boiler Tubes), Shelby.
Specialties, Angular Section
(Shelby) 196
Automobile (Shelby) 193
Axles (Shelby) 193
Bent (Shelby) 195
Cream Separator Bowl
(Shelby) 194
Cylinders (Shelby) 194
Miscellaneous (Shelby) .... 195
Shelby 192
Seamless Specialties, Tapered
(Shelby) 196
Square Tubing (Shelby) ... 196
Trolley Poles (Shelby). . . 197-198
Deflection Due to Load
(Shelby) 198
Length of (Shelby) 198
Load Carried (Shelby).. . 198
Weight of (Shelby) 198
Tubes (Shelby) 14
Annealing of (Shelby). . 17, 19, 20
Area of Wall (Shelby) . . . 200-201
Capacity per Lineal Foot
of (Shelby) 200-203
Chemical Analysis of
(Shelby) 16-19
Cold Finished (Shelby) 15
Diameter (Shelby) 199
Diamond Drill Rods, Spe-
cifications for (Shelby) . 104-105
Displacement (Shelby) .... 199
Expanded (Shelby) 158-159
Expansion of (Shelby) 211
External Volume (Shel-
by) 199.
for Cream Separator Bowls,
Specifications for (Shelby) ,
103-104
Hose Molds, Specifications
for (Shelby) 105-106
Hot Finished (Shelby) 14
Impact Tests of (Shelby) . . 16
Inside Surface per Lineal
Foot of (Shelby) 206-207
Lineal Feet per Square Foot
of Outside Surface (Shel-
by) 199
Made from Steel Plates
(Shelby) 15
Materials Used in the Manu-
facture of (Shelby) 15
Method of Manufacture
(Shelby) 14
Mill Inspection and Tests
of (Shelby) 20
Moment of Inertia of
(Shelby) 204-205
Nickel Steel (Shelby) 19
Outside Diameter of
(Shelby) 199
Outside Surface per Lineal
Foot of (Shelby) 199
Properties of (Shelby),
16-19, 199-207
Radius of Gyration of
(Shelby) 206-207
Index
547
Seamless Tubes, Section Modulus
of (Shelby) 204-205
Sectional Area of Wall
(Shelby),
200-201, 373-375, 4I9~459
Square (Shelby) 196
Strength of (Shelby)
16-19, 223-225
Surface of (Shelby) 199
Swaged (Shelby) 195
Temper of (Shelby) 16-19
Tensile Strength of
(Shelby)..... 16-19
Tests of (Shelby) 20
Upset and Expanded
(Shelby) 158-161
Volume of (Shelby) 199
Universal Joint Sleeve
(Shelby) 195
Sea Water 273
Seat, Valve (Definition) 514
Second, Foot 312
Sectional Area, Tubes 373~375
Pipe 58-65,419-459
Rectangular Pipe 45, 67
Seamless Tubing (Shelby),
2OO-2OI
Sections 264-267
Square Pipe 45, 66
Tubes and Round Bars . . 419-459
Section Length of Poles, .no, 120-157
Modulus of Beams 254
Pipe 58-65
Rectangular Pipe 67
Shelby Seamless Tubing . 204-205
Square Pipe 66
of Joints (see Joint).
Sections of Beams for Minimum
Weight 255-256
Columns .Tables of, Proper-
ties of 264-267
Rectangular Pipe 87-88
Square Pipe 85, 86
Security, Margin of 268
of Tubes in Tube Sheet 210
Sediment in Boiler Water 276
Seller's Thread 370-372, 505
Semi Steel (Definition) 505
Separator Bowls 103, 194
Service Box (Definition) 505
Clamp (Definition) 505
Conditions, Poles 116
Ell (Definition). . 505
Pipe, Flow of Gas in 319, 505
Flow of Water in House. ... 285
Tee (Definition) 505
Set Limits for Poles 112, 116, 119
Sewage in Boiler Water 276
Shaft Bearing 195
Shapes of Cylinder Heads. . . . 189-190
Shear of Beams, Vertical,
250, 251,254, 257-263
Sheet Cutter Tube (Definition) . 512
Metal Gages in Decimals of
an Inch 369
Stay Tube (Definition) 512
Tube (Definition) 512
Shelby Seamless (see Seamless
Tubes, also Product in
Question).
Shells for Boilers 194
Sherardizing (Definition) 506
Shipment, Converse Lock Joint
Pipe 94, 109
Matheson Joint Pipe 92
Tubes for Cream Separator
Bowls 103
Diamond Drill Rods
Hose Poles and Molds .
105
106
Shoe (Definition) 506
Casing (Definition) 484
Drive (Definition) 488
Shop Joint of Poles 115
Short Nipple 4171-172, 174, 506
Ton Equivalents 462, 472
Shot Drill (Definition) 506
Shoulder Nipple (Definition) . . . 506
Shrunk Joint (Definition) 506
Siamese Connection (Definition) 506
Sickle Rule of Flow of Steam
342-345
Side Outlet Ell (Definition) 506
Tee (Definition) 506
Siemen's Joint (Definition) 506
Signal Pipe (Definition) 506
Specifications .<- : ,g$
Thread (Definition) 506
Single Offset Pipe Bends 163
Riveted Bump Joints 165-166
Butted and Strapped Joints,
164-165
Sinker Bar (Definition) 506"
Siphon (Definition) 506
Pipe (Definition) 507
Size, Casing, Trade Practice .... 21
Sizes of House Pipes for Gas 319
Pipe Arranged in Se-
quence 58-65
Briggs' Standard 208-209
Required for Engines 347
Pipe, Trade Practice 21
Tubing, Trade Practice 21
548
Index
Skelp (Definition) 507
Sleeve (Definition) 507
Butted and Strapped Joint. 164, 165
Pole 114
River (Definition) 504
Universal Joint 195
Slenderness Ratio for Columns. 244
Slip Joint (Definition) 507
Slipping Point of Rolled Boiler
Tube Joints 210-211
Smith's Coating (Definition) 507
Snow and Ice Load of, on
Poles 117-118
Properties of 274
Socket (Definition) 507
Coupling (Definition) 507
Half Turn (Definition) 493
Horn (Definition) 493
Iron (Definition) 507
Joint (Definition) 507
Mandrel (Definition) 497
National Pole (Definition) 498
Oval (Definition) . . .- 499
Pipe (Definition) 507
Plug (Definition) 507
Widemouth (Definition) 516
Wrench Forgings 196
Soft Solder (Definition) 507
Soil Pipe (Definition) 507
Solder (Definition) 507
Hard (Definition) 493
Soft (Definition) 507
Solid Beams, Mechanical
Properties 250-267
South Penn Casing, Section
of Joint ; -\ $-83
Test Pressure of 71
Weights and Dimen-
sions of 35
Space for Chip in Threading
Dies 10-1 1
Nipple (Definition) 507
Spacing of Rivets, Pipe Joints 165, 1 66
Span Wire Poles 109
Special Ammonia Pipe, Speci-
fications for -. 98
External Upset Tubing, Cali-
fornia (see California Spe-
cial External Upset Tubing)
Product (Definition) 507
Rotary Pipe, Section of Joint . 79
Test Pressure of 76
Weights and Dimen-
sions of 34
Upset Rotary Pipe, Section
of Joint 79
Special Rotary Pipe, Test
Pressures of 76
Weights and Dimen-
sions of „ 34
Upsets 158
Specialties (see Seamless Special-
ties).
Specific Heat of Air 355
Ice 274
Saturated Steam 328
Superheated Steam 337
Water 275
Specification for Ammonia
Pipe 98
Boiler Tubes (see Boiler
Tubes).
Converse Lock Joint
Pipe 93-95
Cream Separator Bowl
Tubing 103
Diamond Drill Rod Tub-
ing 104
Hose Poles and Hose Molds
Tubing 105
Matheson Joint Pipe 91-92
Pipe for Flanging and Bend-
ing 95
Poles 119
Signal Pipe 96-97
Standard Welded Pipe. . . . ;. \ 89
Spellerizing (Definition) 507
Spherical Cylinder Heads. . . . 189-190
Spigot and Bell Joint (Defini-
tion) 481
(Definition) 508
Joint (Definition) 508
Spinning (Definition) 508
S-pipe (Definition) 508
Spot Faced (Definition) 508
Spring (Definition) 508
Spud (Definition) 508
Spun Flange (Definition) 508
Square Equivalents, Metric. .462, 464
Foot of Surface,
38-41,57, 199,419-459
Heads and Nuts, Propor-
tions of 370
Pipe, Bending Properties of.. . 66
Dimensions and Weights
of 45
Ladders 183-186
Sections of 85-86
Seamless Forgings (Shelby).. . 196
Squib (Definition) 508
Stair Railings 177-182
Stand Pipe (Definition) 508
Index
549
Standard Boiler Tubes (see
Boiler Tubes).
Boston Casing (see Boston
Casing).
Briggs' 208, 483
Casing (see Boston Casing).
Cylinder Head 189-190
Fittings 167
Flanges for Pipe 176
Franklin Institute Threads
370-372
Gage, Briggs' 168, 208
Pipe (Definition) . 508
Bursting Tests 225-226
Columns 245-246
Coupling 22, 77, 90
Length per Square Foot
Surface 57
Manufacture 7-14, 89
Material. 7-14, 90
Physical Properties 10, 90
Reaming 90
Section of Joint 77
Specification 89
Surface Inspection 89
Test Pressure 68-76
Threading 90, 208-209
Thread Protection 90
Used for Poles in, 118-157
Weights and Dimensions
of 22
Poles in, 118-157
British 109
Pressure 167-508
Process and Materials Used in
the Manufacture of Tubu-
lar Goods 7-20
Specifications (see also Speci-
fications) 89
Threads, Briggs' 208
Unions 169
Upsets 158
Valves 170
Working Barrels 187-188
Static Loading, Safety Factor
for .- 268-270
Load on Poles 117
Stay (Definition) 509
Pipe (Definition) 501
Tube 158,509
Tube Sheet (Definition) 512
Steam 326-350
Absolute Zero 328
Advantages of Superheating. . 338
Boiler Incrustation and Cor-
rosion 275
Steam Boilers, Troublesome Sub-
stances in 276
British Thermal Unit 327
Cocks 170
Condensation in Pipes 348
Coupling (Definition) 509
Dry, Definition of 327
Entropy. 329-333, 339~34O
Expansion of Pipe 346-347
Factors of Evaporation. . . .333-336
Flow of, from Orifices 341
in Low Pressure Heating
Lines 345
Pipes 342-346
into Atmosphere 341
Heat 327-340
Kent's Formula for Discharge
of, from Pipes 344
Latent Heat of 327
Loss of Heat from Pipes 348
Mechanical Equivalent of. ... 328
Pipe Coverings 348-350
Pressure 327-333
Properties of 327-333
Radiation from Pipes 348
Resistance Due to Entrance,
Bends and Valves 346
Saturated, Definition of 327
Properties of, Table 329-333
Specific Heat of 328
Total Heat of 327
Volume of 328
Sizes of Pipes for Engines .... 347
Superheated, Advantages of . . 338
Definition of 327
Properties of 33Q-34O
Specific Heat of 337
Volume of 337
Temperature and Pressure
of 327,329-333
Total Heat of Water. .327, 329-333
Velocity in Pipe 347-348
of Flow into Atmosphere,
341-342
Volume Saturated 328
Superheated 337
Weight 329-333
Wet, Definition of 327
Steamboat Inspection of Tubes . 229
Steamer's Measurement (Defi-
nition) 509
Steel and Iron Tubes, Thermal
Expansion of 211
Steel, Bessemer, Analysis of .. .10, 211
Corrosion 12, 13, 106
Ferro (Definition) 490
550
Index
Steel Flange, Rolled (Definition) 504
Modulus of Elasticity 112, 257
Nickel 19
Open Hearth 10, 211
Pipe and Tubing, Weight of,
Tables 370-418
Plates, Tubes Made from .... 15
Poles (see Poles) 100-157
Semi (Definition) 505
Trolley Poles 197-198
Tubes, Seamless Materials,
(Shelby) 15-19
Tubes, Weight Factor for,
Table 376-378
Stem, Valve (Definition) 514
Stewart's Formula for Collapsing
Pressures 228
Tests 227-229
Stiefel Process (Definition) 509
Stiffness of Beams 255
Poles 110-113
Stock, Pipe (Definition) 501
Storage of Carbonic Acid 209-210
Stove (Definition) 509
Stoved End Tubes (see Upset) . . 158
Straightness, Limit 105
Straight Way (Definition) 509
Straightway Valves 160-170
Strap Joints, Riveted 164-165
Strapped and Butted Joint
(Definition) 483
Stream, Power of Running 297
Street Elbow (Definition) 509
Street Poles 100-157
Strength, Beams 254-255
Bolts 371-372
Bumped Heads 190
Columns 244
Commercial Tubes Internal
Pressure 212-226
Cylinder 212-226
Heads 189-192
Dished Heads 191
Factors for Pipe 58-65
of Pipe Steel 10
to Resist External Fluid
Pressure 227-243
Under Internal Pressure,
212-226
Tubes, Internal Pressure,
Barlow's Formula,
214, 218, 219,223-226
Birnie's Formula,
217-219, 221, 223, 224
Claverino's Formula,
215-220, 222-224
Strength of Tubes, Common
Formula ..... 213-214, 218-219, 224
Lame's Formula. .215, 218, 219
Tests of ....... 68-76, 223, 225
Pole ........ no, in, 115, 120-157
Joints ................. 115, n6
Rectangular Pipe ........... 67
Rolled Tube Joints ........ 210, 211
Seamless Steel Tubes (Shel-
by) .................... 16-19
Trolley Poles (Shelby) . . . 197-198
Square Pipe ............... 66
Steel ...................... 223
Weld ..................... 226
Under Thrust or Compression
Columns (see Collapse
also) .................... 244
Stresses, Beams, Tensile and
Compressive ........... 257-263
Bending ................... 117
Stresses, Collapsing ......... 227-243
Column ................... 244
Combined ................. 117
Internal Fluid Pressure . . . .212-226
Poles (Shelby) ............ 117, 197
Safe Working, in Materials. 268-2 70
Shearing, in Beams ......... 250
Tensile, in Beams ........... 250
Trolley Pole . . ............. 197
Tube Wall, Nature of ....... 212
Wind ..................... 117
Strong, Double-extra (Defini-
tion) (see also, Double-
extra Strong) ............ 488
Extra (Definition) (see also
Extra Strong) ............ 490
Strum (Definition) ............ 509
Struts ....................... 244
Stubb's Gage ................ 369
Sturtevant Rule for Flow of
r ..................... 359
Sub-nipple (Definition) ........ 509
Sucker Rod (Definition) ....... 509
Sulphates in Boiler Water ____ 275-276
Sulphur in Pipe Steel .......... 10
Seamless Tubes (Shelby),
16, 18, 19
Superheated Steam (see Steam
Superheated).
Supervising Inspectors.... 101, 229-230
Supply of Gas Through
Pipes ................... 317
Supports, Beam ........ 252, 257-263
Reactions of ............... 252
Surface Area of Pipe .......... 58-65
Heating ................... 57
Index
551
Surface Area Inside, of Shelby
Tubing 206-207
Length of Pipe for One Square
Foot of 57
of Cylinders, Table of 419-459
Surface Outside, per Lineal
Foot of 199
Square Foot per Foot of
Length 38-41, 419-459
Swaged (Definition) 509
Joints for Poles in, 115, 116
Nipple (Definition) 509
Tube Forgings. . 195
Sweated (Definition) 509
Sweep (Definition) 509
Tee, Double (Definition) 488
Swelled (Definition) 510
Joint Casing 27
Swing Joint (Definition) 510
Switch Valve (Definition) 510
Swivel (Definition) 510
Joint (Definition) 510
Water (Definition) 515
System, Metric, The 460-476
Symbols (see Abbreviations in
Glossary) 477~479
Table (see Article in Question).
Adiabatic Compression or Ex-
pansion of Air 355
of Natural Gas 325
Air Line Pipe 36
Allison Vanishing Thread
Tubing 33
Area Factors for Tubes. . . .373-375
Barrels Contained in Tanks... 304
Bedstead Tubing 31
Bending Properties of Rec-
tangular Pipe 67
Square Pipe 66
Boiler Incrustation and Cor-
rosion 276
Boston Casing, Pacific Coup-
ling 28
Bursting Tests of Commercial
Tubes and Pipes 225
California Diamond BX
Casing 29
Drive Pipe 31
Special External Upset
Tubing 30
Centigrade to Fahrenheit . . 473-474
Coefficients of Air Dis-
charge 358
Collapsing Pressures 232-243
Table Columns 244-249
Comparison Metric Units. .460-476
Various Tons and Pounds. . 472
Converse Lock Joint Pipe 43
Conversion 311
Cylinder Dished Heads 191
Decimals of a Foot 366-367
an Inch 368
Dimensions of Screw Threads,
371-372
Discharge of Air 358
Dog Guards 114
Double-extra Strong Pipe 25
Drive Pipe 24
Dry Kiln Pipe 37
Expansion of Steam Pipes. . . . 347
External Collapsing Pressures,
232-243
Steam Pressure — Marine
Law. 229-230
Extra Strong Pipe 25
Heavy Pipe Flanges 175
Factors of Evaporation . . . .333-336
Fahrenheit to Centigrade... 474-475
Fifth Roots 365-366
Flat Cylinder Heads (Thick-
ness) 192
Flow of Compressed Air — 361-364
Gas in Pipes .317-319
Steam in Atmosphere 342
Low Pressure Heat-
ing Lines 345
Pipes 342-345
Water in House Ser-
vice Pipes 285
Flush Joint Tubing 32
Full Weight Drill Pipe 36
Horse-power of Water Heads. 299
Hydrostatic Test Pressure of
Pipe (see Test Pres-
sure) 68-76
Inserted Joint Casing 27
Internal Fluid Pressure 220-221
Kimberley Joint Pipe 44
Lap-welded Locomotive Boiler
Tubes 40
Length of Pipe for One Square
Foot of Surface 57
Inches and Millimeters. .469-471
Line Pipe 23
Locomotive Seamless Boiler
Tubes 38-39
Long Screw Wrought Pipe
Nipples.. 173
Loss of Air Pressure in Pipes,
359-360
552
Index
Table, Loss of Head by Friction
286-288
Matheson Joint Pipe 42
Miner's Inch Measurements. . 296
Oil Well Tubing 30
Pressure of Atmosphere 352
Properties of Beams 256-263
Column Sections 264-267
Pipe 58-65
Tubes and Round Bars,
419-459
Rectangular Pipe 45
Saturated Steam 329-333
South Penn Casing 35
Special Rotary Pipe 34
Upset Rotary Pipe. 34
Specific Heat of Superheated
Steam 337
Water 275
Square Pipe 45
Standard Boston Casing 26
Lap-welded Boiler Tubes
and Flues 40-41
Pipe 22
Flanges 176
Steam Pipe Coverings 349
Strength of Welds 226
Superheated Steam 339-34°
Trolley Poles (Shelby Seam-
less) 198
Tubular Electric Line Pole. 119-157
Tuyere Pipe 37
Upsets 160-161
Velocity of Air Under Low
Pressures 357
Water Power 299
Pressure 274
Weight and Volume of Water 272
Factors for Steel Tubing. 3 7 7-378
of Air 353-354
Pipe 46-56, 379-4i8
Wire and Sheet Metal Gages. . 369
Working Barrels 188
Wrought Casing Nipples 174
Pipe Nipples 171-173
Tank Nipples 173
Tail Pipe (Definition) 510
Tank (Definition) 510
Capacity 302, 304, 305
Nipple 173
Tap (Definition) 510
Master (Definition) 497
Plug (Definition) 502
Taper Elbow, Reducing (Defi-
nition) 503
Pipe Thread 208
Tapered Specialties, Seamless
Steel (Shelby) 196
Tapped (Definition) 510
Tapping Machine (Definition). . 510
Tar, Coal (Definition) 485
Tee (Definition) 510
Branch (Definition) 482
Bull Head (Definition) 483
Cross Over (Definition) 486
Double Sweep (Definition) ... 488
Drop (Definition) 489
Four Way (Definition) 492
Reducing (Definition) ....... 503
Service (Definition) 505
Side Outlet (Definition) 506
Union (Definition) 513
Telegraph Cock or Faucet
(Definition) 510
Poles. Tubular 109-157
Telescoped (Definition) 510
Temper Screw (Definition) 511
Seamless Steel Tubes (Shel-
by) 16-19
Temperature, Air Weight at
Various 353~354
and Pressure of Steam 327
Centigrade to Fahrenheit,
473-474, 476
Compression of Gas 325
Fahrenheit to Centigrade,
474-475, 476
Pressure Volume of Air . . 352
Steam 327, 32O-333, 339~34O
Weights, Lengths, Conver-
sion Chart 476
Templet (Definition) 511
Tensile Strength, Pipe Steel - . . 10, 223
Seamless Steel Tubes (Shel-
by) 16-19
Stress Beams 250
Terms Used in Pipe and Fittings
Trade 477-516
Test Pressures 13, 14, 20, 68-76
Air Line Pipe 73
Allison Vanishing Thread
Tubing 75
Ammonia Pipe 98
Boiler Tubes (see also,
Boiler Tubes). 72, 100, 101, 102
Boston Casing 70
Pacific Coupling 70
California Diamond BX
Casing 71
Drive Pipe 76
Special External Upset
Tubing 76
Index
553
Test Pressures, Card Weight Pipe
68, 90
Converse Lock Joint Pipe
74, 93
Double-extra Strong Pipe . . 69
Drill Pipe 76
Drive Pipe 69
Dry Kiln Pipe 76
Extra Strong Pipe 69
Flues (see Boiler Tubes).
Flush Joint Tubing 75
Full Weight Drill Pipe 76
Full Weight Pipe 68, 90
Hydrostatic of Pipe 68-76
Inserted Joint Casing 71
Kimberley Joint Pipe 74
Line Pipe 68
Locomotive Boiler Tubes
(see Boiler Tubes) . 72, 100, 102
Matheson Joint Pipe 73, 91
Oil Well Tubing 69
Pacific Casing 70
Reamed and Drifted Pipe . . 73
Seamless Boiler Tubes (see
Boiler Tubes).
Signal Pipe 96
South Penn Casing 71
Special Rotary Pipe 76
Upset Rotary Pipe 76
Standard Boston Casing . . . 70
Standard Pipe 68
Tuyere Pipe 76
Tests, Ammonia Pipe 98
Boiler Tube (see Boiler Tube).
Bursting 212-226
Conditions for Pole 114
Collapsing 227-243
Columns 230-231
Crushing (Definition) 487
Drop 116, 119
Expanding 102
Experimental Bursting. . . .223-226
Collapse 227-243
Flanging 100, 101-102
and Bending Pipe 95
Flattening 100, 102
Holding Power of Boiler
Tubes 210
Impact 16
Lap-welded Locomotive Boiler
Tubes 100
Mill 13-14, 20
Pipe 13-14, 20
Pole 114, 116, 119
Pulling 10
Ring 102
Tests, Seamless Tubes (Shelby)
20, 102
Signal Pipe go
Spellerized Locomotive Boiler
Tubes 99-100
Standard Welded Pipe 90
Tubes Under Internal Pres-
sure 222, 223, 225
Weld, Strength of 226
Theorem Bernouilli, Water
Power.... 298
Thermal Expansion of Iron and
Steel 211
Pipe 346-347
Unit, British 327
Waste of Engines 338
Thermo-Dynamics 327-350
Thermometer Measures 473-476
Thickness of Cylinder Heads,
Dished i9I
Flat 192
Pipe 22-56,58-65
Briggs' Standard 208
for Weight per Foot. . .370-418
Poles 118-157
Tubes 38-41
Thimble (Definition) 511
Boiler (Definition) 481
Joint (Definition) 511
Threads (Definition) 511
Thread, Ammonia Cock (Defi-
nition) 479
Pipe 98
Briggs' Standard 168, 208-209
Common (Definition) 485
Depth 208-209
-Franklin Institute 370-372
Gage Standard 21, 208
Valves and Fittings 168
Gas (Definition) 492
Length 208
Pipe (Definition) 501
Pipe, Briggs' Standard 208-209
Protectors 90
Screw 370-372
Seller's (Definition) . . .370-372, 505
Thread, Signal (Definition) 506
Pipe 96
Standard Welded Pipe 90
Taper 208
U. S. Standard 370-372
V (Definition) 514
Vanishing (Definition) 514
Whitworth (Definition) 516
Working Barrel 187
Threaded Connections 167-168
554
Index
Threaded Flanges for Extra
Heavy Pipe 167, i6g, 175
Standard Pipe.. . .167, 169, 176
Joints 167
Threading 10
Dies, Chasers 1 1
Chip Space on n
Clearance of 10
Lead on u
Lip ,,:-'• '--lie* '
Lubrication of n
Pipe lo-i i
Specifications 90, 96, 98
Three Way Elbow (Definition) . 511
Tight Hand (Definition) 493
Tong (Definition) 511
Tin Weight 423
Lined Pipe (Definition) 511
Ton Equivalents 462, 472
Tong (Definition) 511
Chain (Definition) 484
Pipe (Definition) 501
Tight (Definition) 511
Tongue and Groove (Defini-
tion) 511
Tool, Calking (Definition) 483
Total Heat of Saturated Steam,
327, 320-333
Superheated Steam 339-340
Water 327, 329~333
Towl's Formula for Discharge
of Gas 321
Trade Mark 20
Practice, Casing Size 21
Pipe Size 21
Tubing Size 21
Term Dictionary 477-516
Trailing, Water (Definition). ... 511
Transmission Line Poles no
of Compressed Air 360-364
Trautwine's Formula for Flow
of Water in Pipes 280
Trenton Iron Company's Wire
Gage 369
Trolley Poles (see Poles).
Troublesome Substances in
Boiler 276
Troy Ounces to Grams 462, 468
Pound Equivalents 472
to Kilograms 462, 468, 472
Tube (Definition) 5"
Annealed End (Definition) . . . 480
Area Factors for, Tables. . -373-375
Areas 419-459
Beaded (Definition) 480
Bent 162, 195
Tube, Boiler (Definition) 482
(see Boiler Tubes).
Brick Arch (Definition) 482
Bursting Tests of 223-226
Capacity Factors for 423
Chemical Analysis. . .10, 16-19, 211
Circumference 419-459
Cleaner (Definition) 511
Cold Finished 15
Collapsing Pressures of ... .227-243
Cream Separator Bowl,
103-104, 194
Cross (Definition) /
Diamond Drill Rods 104-105
Expanded 158-159
End (Definition) 489
Holding Power of 210
Expander (Definition) 512
Expansion of 211
Ferrule (Definition) 512
Field (Definition) 491
General Notes 21
Holding Power 210
Hose Molds and Poles 105-106
Hot (Definition) 493
Finished 14
Internal Fluid Pressure for. 2 12-2 2 6
Iron and Steel, Thermal Ex-
pansion Of 211
Joints, Slipping Point of Rolled
Boiler 210
Lap-welded and Seamless, Up-
set and Expanded 158-161
Manufacture of 7
Locomotive Boiler (see Boiler
Tubes).
Merchant and Marine Ser-
vice (see Boiler Tubes).
Mill Inspection and Tests 13, 20
Moment of Inertia 410-459
Packing (Definition) 512
Plug (Definition) 512
Properties of, Table 419-459
Physical Properties of. . . . 10, 16-19
Pitot 291-292
Radius of Gyration 419-459
Ribbed (Definition) 504
. Sealer (Definition) 512
^Scraper (Definition) 512
Seamless (Shelby) (see Seam-
less Tubes).
Sheet (Definition) 512
Sheet Cutter (Definition) 512
Holding Power to Hold
Boiler Tubes 210
Stay (Definition) 512
Index
555
Tube, Size, Trade Practice 21
Specifications (see Specifica-
tions).
Standard Boiler (see Boiler
Tubes).
Stay 158, 509
Steamboat, Inspection of 229
Steel, Impact Test of Seam-
less 16
Surface per Foot Length . . . 410-459
Temper, Seamless 16-19
Test, Pressure (see Test Pres-
sure).
(see Tests) 13, 20
Thermal Expansion of Iron
and Steel 211
Thickness of 38-41
Upset 158-161
Venturi 292-293
Volume 419-459
Wall, Nature of Stress in 212
Weight Factors for Steel. . .376-378
Weight of 46-56, 379-459
Welded, Manufacture of 7-14
Tubing (Definition) 512
Allison Vanishing Thread,
Section of Joint 81
Test Pressure 75
Weights and Dimensions
of 33
Bedstead Weights and Dimen-
sions of 31
California Special External
Upset, Dimensions of and
Weights 30
Section of Joint 82
Test Pressures of ... 76
Capacity of 200-203
Catcher (Definition) 512
Cream Separator Bowl 103
Diamond Drill Rods 104
Displacement 199
Flush Joint, Dimensions and
Weights of 32
Section of 80
Test Pressure of 75
General Notes 21
Hose Poles and Hose Molds . . 105
Inside Surface 206-207
Lineal Feet per Square Foot.. 199
Moment of Inertia 204-205
Oil Well, Dimensions and
Weight of 30
Section of Joint 81
Test Pressures of 69
Outside Diameter 199
Tubing, Outside Surface 199
Properties of 199
Radius of Gyration of 206-207
Tubing, Seamless (Shelby) (see
Seamless Tubes)
Section Modulus 204-205
Sectional Area of Wall 200-201
Steel, Weight Factors for.. .376-378
Test Pressure (see Test Pres-
sure).
Upset, California Special Ex-
ternal (Which see).
Weight of 379-459
Tubular Beams, Properties of,
250-267
Electric Line Poles (see Poles).
Goods, Manufacture of 7
Goods, Weights of,
379-418, 419-459
Swaged Forgings 195
Turn, Half, Socket (Definition) . 493
Long, Fitting (Definition). . . . 497
Tuyere (Definition) 513
Cocks 170
Pipe, Test Pressures of 76
Weights and Dimensions
of 37
Unions 170
U
U-bend 163
Ultimate Strength of Poles in
Tensile Strength,
10, 16-19, 90, 91, 93, 98, 223
Under Reamer (Definition) 513
Uniform Cross Section; Beams
of 256
Union 169, 513
Boyle (Definition) 482
Brass 169
Coupling (Definition) 513
Ell (Definition) 513
Flange 169, 491
Joint (Definition) 513
"Kewanee" (Definition) 495
Lip (Definition) 496
Malleable 169
Nut 169
Pipe (Definition) 501
Ring (Definition) 504
Tee (Definition) 513
Tuyere 170
Universal 170
Unit Heat, British Thermal 327
Metric, Equivalents of 460-472
Weight, Comparisons of 472
556 Index
United States Wire Gage 369
Valves and Fittings, Receiver
Filling (Definition) 503
Gallon Equivalents,
300, 311, 312, 462, 466
Standard Thread 370-372
Universal Joint Sleeves 195
Reducing (Definition) 503
Reflux (Definition) 503
Resistance to Flow (see Val-
ves Effect).
Screw Down (Definition) .... 505
Seat (Definition) 514
Unions 170
Unwin's Formula, Flow of Gas
in Pipes 323
Upset (Definition) . 513
Stem (Definition) 514
Rotary Pipe, Special, Joint
Section of . 79
Straightway 169-170
Switch (Definition) 510
Test Pressure 76
Wedge Gate (Definition) 515
Wheel (Definition) 516
Vanishing Thread (Definition) . . 514
Tubing Allison (see Alli-
son Vanishing Thread
Tubing).
Van Stone Joint (Definition) ... 514
Vapor and Gases, Mixtures of. . . 315
Saturation Point 315
Weights and Dimen-
sions 34
Upset Table of .158-161
Upset Tubes for Diamond Drill
Rods 104
Upset Tubing, Allison Vanish-
ing Thread, Section of
joint 81
Test Pressure 75
Weights and Di-
mensions 33
California Special External,
Section of Joint 82
Vaporization Heat of 327
Variable Loading, Safety Fac-
tor for 268-270
Variation Permissible in Lengths,
21, 91, 99, 102, 103, 105, 106
Diameter,
89, 91, 96, 99, 102, 103, 105, 106
Threading 90, 98
Thickness 99, 100, 102
Weight (see footnote of
Product in Question)
of Signal Pipe 96
Test Pressure 76
Weights and Di-
mensions . 30
Upsetting 158
Uses for Upsets 158
V
Valves and Fittings 167-170, 513
Angle (Definition) 479
Vegetable Oils in Boiler Water,
Effect of 276
Angle 160-170
Velocity Air Flowing into
Atmosphere 3S7-358
Angle Gate (Definition) . . . 479
Back Pressure (Definition) . . . 480
Box (Definition) 514
in Pipes 359~ 360
Flow of Steam into Atmos-
phere. 341—342
Bracket (Definition) 482
By-pass (Definition) 483
Check 169-170, 484
in Pipes 347— 34^
Water in Pipes 277-290
Cross (Definition) . . . .- 487
Wind . H7
Effect of, on Flow of Air 364
Gas 324
Venturi Meter 292
Tube Measurements 293
Vertical and Horizontal Load-
ing of Beams 256
Shear of Beams 250
Steam 346
Water in Pipes. . 283-284
Exhaust Relief (Definition) ... 489
Expansion (Definition) 490
Flanged 167
Vessels, Contents of,
301, 302, 304, 305
Volume, Air 352
Full-way (Definition) 492
Gate (Definition) 160-170, 492
Globe 169-170, 492
Needle (Definition) 498
Comparison of Units 465
Conversion Table 311
Cylinders Table of 419-450
Non-return (Definition) 498
Gas 314
Protecting Caps 194
Metric Equivalents 462, 465
Pressure, Temperature of Air. 352
Radiator (Definition) 502
Index
557
Volume, Saturated Steam 328
Seamless Tubing (Shelby),
199, 419-459
Superheated Steam. . .337, 339-340
Tubes and Round Bars. . . .419-459
Water 272
Volumetric Measures (see Met-
ric Equivalents also) 460-472
V-thread (Definition) 514
Vulgar Fractions and Their
Decimal Equivalents. . . .366-368
V-welding (Definition) 514
W
Walker Joint (Definition) 514
Wall, Area Pipe 58-65, 419-459
Seamless Tubing (Shelby),
2OO-2OI
Tubes and Round Bars. .419-459
Nature of Stress in Tube 212
Washburn and Moen Wire
Gage 369
Water 271-312
Absorption of Gases 316
Air in 277
Arch (Definition) 514
Bar (Definition) 514
Boiling Point 272
Capacity of Pipe 301, 303, 423
Chart for Flow of in Wrought
Pipe 279
Column (Definition) 514
Composition of 272
Compressibility of 275
Contents of Cylinders. 301, 302, 304
Contents of Pipes 303
Rectangular Tanks 305
Density Maximum 272
Discharge 278-279, 285
Discharge Capacities of Pipe
306-309
Energy of 298
Equivalents 310-312
Expansion of 272
Fall, Efficiency of 297
Power of 297
Feed for Boilers 275-277
Flow Affected by Curves and
Valves 283
Flow Diameter Required .... 290
in Pipes 277-290
Flow in House Service Pipes. . 285
Lost Head in Pipes 286-290
Measurement 291-296
Flush (Definition) 515
Water Friction in Pipes 286- 290
Gage (Definition) 515
General Index 271
Grate (Definition) 515
Hammer 168, 284, 515
Head of 273-274, 277, 297-299
Heat of 327-333
Horse-power of Heads 297-299
Hydraulic Conversion Table. . 311
Equivalents 310
Ice and Snow 274
Impurities 275-277
Incrustation and Corrosion. . . 275
Lime in 275-276
Measurement of, by Nozzles. . 293
Flowing 291-296
Packer (Definition) 515
Pipe 167
Clamps (Definition) 515
Plug (Definition) 515
Power 297-299
Bernoulli's Theorem 298
Current Motors 298
Energy of Water Flowing
in a Tube 297
Horse-power of a Running
Stream 297
Calculating Table 299
Table 300-312
Table of Gallons and
Cubic Feet 300
Pressure Equivalents of 310
of Due to Weight 273
per Square Inch, Equiva-
lents of 273
on Vertical Surface 273
Properties 272
Quantity of Discharged 278
Ram 168,284
Relative Discharge of Pipes,
306-309
Specific Heat of 275
Swivel (Definition) 515
Table. of Contents 271
Weight and Volume 272
Total Heat of 327~333
Trailing (Definition) 511
Tube Boiler (Definition) 515
Units of Pressure and Head. . . 273
Velocity of Flow, Darcy 282
Kutter 281
Mean 280
Trautwine 280
Williams and Hazen. . . 283
Volume of, at Different Tem-
peratures 272
558
Index
Water, Weight of, at Different
Temperatures 272
per Foot of Pipe 301 , 303
Wheel 297
Waterfall, Power of 297
Watertown Arsenal Tests,
223, 230-231
Wedge Gate Valve (Definition). 515
Weight (Definition) 516
Air 352-354
Line Pipe 36
Allison Vanishing Thread
Tubing 33
Aluminum 423
Bars, Round 419-459
Bedstead Tubing 31
Black Pipe 22
Boiler Tubes (see Boiler
Tubes).
Boston Casing : . . . . 26
Pacific Couplings 28
Brass 423
California Diamond BX
Casing . 3$ 39
Drive Pipe 31
Special External Upset
Tubing 30
Card, Pipe 22,483
Casing, Boston 26
Pacific Coupling 28
California Diamond BX ... 29
Inserted Joint .1*^*^7
South Penn 35
Cast Iron 423
Converse Lock Joint Pipe. ... 43
Conversion Chart for 476
Copper 423
Difference for Difference in
Outside Diameter 379-380
Double Extra Strong, Pipe,
Black 25
Drill, Full Weight Pipe 36
Drive Pipe 24
California Diamond BX . 31
Dry Kiln Pipe 37
Equals Measurement (Defi-
nition) 498
Extra Strong Pipe, Black 25
Factors for Different Ma-
terials 423
Steel Tubes 376-378
Flues, Boiler (see Boiler
Tubes).
Flush Joint Tubing 32
Full Weight Drill Pipe 36
Galvanized Pipe 21
Weight, Gas 315
Ice 274
Inserted Joint Casing 27
Inside Diameter, Pipe 46-49
Iron 21,423
Kimberley Joint Pipe 44
Lead 423
Lead Converse Lock Joint
Pipe ^ifcti
Kimberley Joint Pipe 44
Matheson Joint Pipe .•/-? 42
Lengths and Temperatures,
Conversion Chart 476
Line Pipe 23
Matheson Joint Pipe 42
Metric Equivalents,
462, 468, 472, 476
Nickel 423
Outside Diameter Pipe 50-56
Oil Well Tubing 30
Pacific Casing 28
Pipe 22-56, 58-65, 370-450
Poles no, 113, 120-157
Reamed and Drifted 35
Rectangular Pipe 45
Rotary Pipe, Special 34
Upset 34
Round Steel Bars 419-459
Saturated Steam 329-333
Seamless Tubes (Shelby) (see
Seamless Tubes).
Trolley Poles 197-198
Sections 264-266
Snow 274
South Penn Casing 35
Special Rotary Pipe 34
Upset Rotary Pipe 34
Square Pipe 45
Standard Boston Casing 26
Standard Pipe, Table of 22
Steel 21, 423
Pipe and Tubing, Tables. 3 70~450
Tin 423
Tubes 419-459
by Outside Diameter 50-56
Tubing, Allison Vanishing
Thread 33
Bedstead 31
California Special External
Upset 30
Flush Joint -iror&a
Oil Well .ni 30
Tubular Goods, Tables,
22-56, 58-65, 370-450
i. Tuyere Pipe 37
Various Materials 423
Index
559
Weight, Water 272
in Pipes, Table of 301, 303
Wrought Iron 423
Working Barrels 188
Weisbach Rule for Water
Flow 289
Air Flow 359
Weld (Definition) 516
Butt 9,483
Circular (Definition) 484
Lap 7,8,496
Scarf (Definition) 505
Strength of, in Pipes 226
Welded Cylinder Heads 190
Flange Joint (Definition) .... 516
Flanges 167
Pipe Bursting Tests 223-226
Manufacturing 7-14
Marking , 20
Standard Specifications. . . .89-90
Welding and Annealing 10
of Pipe Steel 10
V (Definition) 514
Wet Steam 327
Wheel Valve (Definition) 516
Whitworth Thread (Definition) . 516
Widemouth Socket (Definition) . 516
William s and Hazen's Formula. 283
Wind Loads, Poles 116-117
Velocity 117
Wine Bore (Definition) 516
Wiped Joint (Definition) 516
Wire and Sheet Metal Gages 369
Wool Lead (Definition) 496
Work of Adiabatic Compression
of Air 356
Isothermal Compression of
Air 356
Working Barrel (Definition) 516
Working Barrels, Dimensions . . 188
Weights of 188
Fiber Stresses, Safe 268
Pressure, Classification of. ... 167
Valves and Fittings 167
Stresses in Beams 250
Wrench Pipe (Definition) 501
Wrenches, Socket 196
Wrought Casing Nipples 174
Iron Corrosion 12, 13, 106
Weight 21, 423
Iron Pipe 7, 12, 106
Bursting Tests 223-226
Corrosion 12, 13, 106
Expansion 211, 347
Strength 223-226
Pipe Bends 162-163
Radii of. 162
Long Screw Nipples 173
Nipples 168, 171-172
Tank Nipples 173
Wye, Y (Definition) 516
Y (Definition) 516
Yards to Meters 461, 463
Y Base (Definition) 516
Y Bend (Definition) 516
Y Branch (Definition) 516
Yield Point 112, 222
Yoke (Definition) 516
Zero, Absolute 328
Zinc Coating 92-94, 107
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