HATH-STAJ. I A TEBATISE ON THE THEOBY OF SOEEWS, : C. J. CLAY AND SONS, CAMBRIDGE UNIVERSITY PRESS WAREHOUSE, AVE MAKTA LANE. lasgofo: 50, WELLINGTON STREET. ILetpjig : F. A. BBOCKHAUS. gork: THE MACMILLAN COMPANY. Bombnp: E. SEYMOUR HALE. THE CENTRAL PORTION OF THE CYLINDROID. Frontispiece. A TREATISE ON THE THEORY OF SCREWS SIR ROBERT STAWELL BALL, LL.D., F.R.S., LOWNDEAN PEOFESSOE OF ASTEONOMY AND GEOMETEY IN THE TTNIVEESITY OF CAMBEIDGE, FOEMEELY EOYAL ASTEONOMEE OF IEELAND. CAMBRIDGE: AT THE UNIVERSITY PRESS. 1900 [All Rights resented.] Or 4^.. MATH-STAT. PRINTED BY J. AND C. F. CLAY, AT THE UNIVERSITY PRESS. MATtU STAT. UBRARY PEE FACE. A BOUT thirty years ago I commenced to develop the consequences of -*- certain important geometrical and dynamical discoveries properly associated with the illustrious names of Poinsot and Chasles, Hamilton and Klein. The result of rny labours I have ventured to designate as " The Theory of Screws." As the theory became unfolded I communicated the results in a long series of memoirs read chiefly before the Royal Irish Academy. To this learned body I tender my grateful thanks for the continual kind ness with which they have encouraged this work. I published in 1876 a small volume entitled The Theory of Screws: A Study in the Dynamics of a Rigid Body. This contained an account of the subject so far as it was then known. But in a few years great advances were made, the geometrical theories were much extended, and the Theory of Screw-chains opened up a wide field of exploration. The volume just referred to became quite out of date. A comprehensive account of the subject as it stood in 1886 was given in the German work Theoretische Mechanik starrer Systeme : Auf Grund der Methoden und Arbeiten und mit einem Vorworte von Sir Robert S. Ball, herausgegeben von Harry Gravelius, Berlin, 1889. This work was largely a translation of the volume of 1876 supplemented by the sub sequent memoirs, and Dr Gravelius made some further additions. The theory was still advancing, so that in a few years this considerable volume ceased to present an adequate view of the subject. For example, the Theory of Permanent Screws which forms perhaps one of the most B. b M777321 VI PREFACE. instructive developments was not communicated to the Royal Irish Academy until 1890. The twelfth and latest memoir of the series containing the solution of an important problem which had been under consideration for twenty-five years did not appear until 1898. It therefore seemed that the time had now come when an attempt should be made to set forth the Theory of Screws as it stands at present. The present work is the result. I have endeavoured to include in these pages every essential part of the Theory as contained in the twelve memoirs and many other papers. But the whole subject has been revised and rearranged and indeed largely rewritten, many of the earlier parts have been recast with improvements derived from later researches, and I should also add that I have found it necessary to introduce much that has not been previously published. The pleasant duty remains of expressing my thanks for the help that I have received from friends in preparing this book. I have received most useful aid from Prof. W. Burnside, Mr A. Y. G. Campbell, Mr G. Chawner. Mr A. W. Panton, Mr H. W. Richmond, Mr R. Russell, and Dr G. Johnstone Stoney. In the labour of revising the press I have been aided by Mr A. Berry, Mr A. N. Whitehead, and lastly by Professor C. J. Joly, who it will be seen has contributed several valuable notes. Finally, I must express my hearty thanks to the Cambridge Univer sity Press for the liberality with which they undertook the publication of this book and for the willing consent with which they have met all my wishes. ROBERT S. BALL. OBSERVATORY, CAMBRIDGE, 17 May, 1900. CONTENTS. PAGE INTRODUCTION . 1 CHAPTER I. TWISTS AND WRENCHES. 1. Definition of the word Pitch ......... 6 2. Definition of the word Screw 7 3. Definition of the word Twist ......... 7 4. A Geometrical Investigation .......... 8 5. The canonical form of a Small Displacement ...... 9 6. Instantaneous Screws 10 7. Definition of the word Wrench 10 8. Restrictions . . 11 CHAPTER II. THE CYLTNDROID. 9. Introduction 15 10. The Virtual Coefficient 17 11. Symmetry of the Virtual Coefficient ........ 18 12. Composition of Twists and Wrenches 18 13. The Cylindroid . 19 14. General Property of the Cylindroid 21 15. Particular Cases 22 16. Cylindroid with One Screw of Infinite Pitch 22 17. Form of the Cylindroid in general 24 18. The Pitch Conic 24 19. Summary 24 62 Vlll CONTENTS. CHAPTER III. RECIPROCAL SCREWS. PAGE 20. Reciprocal Screws ............ 26 21. Particular Instances 26 22. Screw Reciprocal to Cylindroid ......... 26 23. Reciprocal Cone ............ 27 24. Locus of a Screw Reciprocal to Four Screws ...... 29 25. Screw Reciprocal to Five Screws ......... 30 26. Screw upon a Cylindroid Reciprocal to a Given Screw .... 30 27. Properties of the Cylindroid .......... 30 CHAPTER IV. SCREW CO-ORDINATES. 28. Introduction 31 29. Intensities of the Components ......... 32 30. The Intensity of the Resultant 33 31. Co-reciprocal Screws 33 32. Co-ordinates of a Wrench .......... 34 33. The Work done 34 34. Screw Co-ordinates 34 35 35 36. Calculation of Co-ordinates .......... 35 37. The Virtual Coefficient 36 38 The Pitch 36 39. Screw Reciprocal to Five Screws ......... 36 40. Co-ordinates of a Screw on a Cylindroid ....... 37 41. The Canonical Co- reciprocals 38 42. An Expression for the Virtual Coefficient 38 43. Equations of a Screw ........... 38 44. A Screw of Infinite Pitch 39 45. Indeterminate Screw ........... 40 46. A Screw at Infinity . . , . 41 47. Screws on One Axis . . . . . . . ... 41 48. Transformation of Screw Co-ordinates 42 49. Principal Screws on a Cylindroid 43 CHAPTER V. THE REPRESENTATION OF THE CYLINDROID BY A CIRCLE. 50. A Plane Representation 45 51. The Axis of Pitch 46 52. The Distance between Two Screws . . . 47 CONTENTS. IX PAGE 53. The Angle between Two Screws 48 54. The Triangle of Twists 49 55. Decomposition of Twists and Wrenches ....... 50 56. Composition of Twists and Wrenches 50 57. Screw Co-ordinates 51 58. Reciprocal Screws ....... .... 51 59. Another Representation of the Pitch 52 60. Pitches of Reciprocal Screws ......... 53 61. The Virtual Coefficient 54 62. Another Investigation of the Virtual Coefficient 55 63. Application of Screw Co-ordinates 57 64. Properties of the Virtual Coefficient 59 65. Another Construction for the Pitch 59 66. Screws of Zero Pitch 60 67. A Special Case 60 68. A Tangential Section of the Cylindroid 60 CHAPTER VI. THE EQUILIBRIUM OF A RIGID BODY. 69. A Screw System 62 70. Constraints ............ 63 71. Screw Reciprocal to a System 63 72. The Reciprocal Screw System 63 73. Equilibrium 64 74. Reaction of Constraints 64 75. Parameters of a Screw System 65 76. Applications of Co-ordinates 65 77. Remark on Systems of Linear Equations 67 CHAPTER VII. THE PRINCIPAL SCREWS OF INERTIA. 78. Introduction 69 79. Screws of Reference 70 80. Impulsive Screws and Instantaneous Screws 71 81. Conjugate Screws of Inertia - . . . . 71 82. The Determination of the Impulsive Screw 72 83. System of Conjugate Screws of Inertia 72 84. Principal Screws of Inertia . 73 85. An Algebraical Lemma 75 86. Another Investigation of the Principal Screws of Inertia .... 76 87. Enumeration of Constants 78 88. Kinetic Energy ........ 79 X CONTENTS. PAGE 89. Expression for Kinetic Energy 80 90. Twist Velocity acquired by an Impulsive Wrench 81 91. Kinetic Energy acquired by an Impulsive Wrench 82 92. Formula for a Free Body 82 93. Lemma ........ 83 94. Euler s Theorem . 83 95. Co-ordinates in a Screw System 83 96. The Reduced Wrench 84 97. Co-ordinates of Impulsive and Instantaneous Screws .... 85 CHAPTER VIII. THE POTENTIAL. 98. The Potential . . . . 87 99. The Wrench evoked by Displacement 88 100. Conjugate Screws of the Potential 89 101. Principal Screws of the Potential 90 102. Co-ordinates of the Wrench evoked by a Twist 91 103. Form of the Potential 92 CHAPTER IX. HARMONIC SCREWS. 104. Definition of an Harmonic Screw . 94 105. Equations of Motion ........ 96 106. Discussion of the Results 99 107. Remark on Harmonic Screws 100 CHAPTER X. FREEDOM OF THE FIRST ORDER. 108. Introduction 101 109. Screw System of the First Order . . 101 110. The Reciprocal Screw System 102 111. Equilibrium 103 112. Particular Case ..... 104 113. Impulsive Forces 104 114. Small Oscillations 105 115. Property of Harmonic Screws 106 CONTENTS. XI CHAPTER XI. FREEDOM OF THE SECOND ORDER. H oo 116. The Screw System of the Second Order .... 117. Applications of Screw Co-ordinates ..... 118. Relation between Two Cylindroids 119. Co-ordinates of Three Screws on a Cylindroid . 120. Screws on One Line ........ 121. Displacement of a Point 122. Properties of the Pitch Conic 123. Equilibrium of a Body with Freedom of the Second Order 124. Particular Cases ..... ... 125. The Impulsive Cylindroid and the Instantaneous Cylindroid 126. Reaction of Constraints 127. Principal Screws of Inertia ....... 128. The Ellipse of Inertia . . . . . . 129. The Ellipse of the Potential 130. Harmonic Screws ......... 131. Exceptional Case 132. Reaction of Constraints. ..... CHAPTER XTI. PLANE REPRESENTATION OF DYNAMICAL PROBLEMS CONCERNING A BODY WITH Two DEGREES OF FREEDOM. 133. The Kinetic Energy 120 134. Body with Two Degrees of Freedom 120 135. Conjugate Screws of Inertia 124 136. Impulsive Screws and Instantaneous Screws 125 137. Two Homographic Systems .......... 126 138. The Homographic Axis 127 139. Determination of the Homographic Axis . . . . . . . 128 140. Construction for Instantaneous Screws . . . . . . 128 141. Twist Velocity acquired by an Impulse ....... 129 142. Another Construction for the Twist Velocity 129 143. Twist Velocities on the Principal Screws 131 144. Another Investigation of the Twist Velocity acquired by an Impulse . . 131 145. A Special Case 133 146. Another Construction for the Twist Velocity acquired by an Impulse . 134 147. Constrained Motion 136 148. Energy acquired by an Impulse 137 149. Euler s Theorem 138 150. To determine a Screw that will acquire a given Twist Velocity under a given Impulse 138 151. Principal Screws of the Potential 140 Xll CONTENTS. PAGE 152. Work done by a Twist 141 153. Law of Distribution of v 142 154. Conjugate Screws of Potential 142 155. Determination of the Wrench evoked by a Twist 143 156. Harmonic Screws 143 157. Small Oscillations in general 144 158. Conclusion . 144 CHAPTER XIII. THE GEOMETRY OF THE CYLINDROID. 159. Another Investigation of the Cylindroid . 146 160. Equation to Plane Section of Cylindroid 152 161. Chord joining Two Screws of Equal Pitch 155 162. Parabola . 157 163. Chord joining Two Points 160 164. Reciprocal Screws . . 181 165. Application to the Plane Section 163 166. The Central Section of the Cylindroid 166 167. Section Parallel to the Nodal Line . 167 168. Relation between Two Conjugate Screws of Inertia . . 168 CHAPTER XIV. FREEDOM OF THE THIRD ORDER. 169. Introduction 170 170. Screw System of the Third Order 170 171. The Reciprocal Screw System 171 172. Distribution of the Screws 171 173. The Pitch Quadric 172 174. The Family of Quadrics 173 175. Construction of a Three-system from Three given Screws . . . . 175 176. Screws through a Given Point 176 177. Locus of the feet of perpendiculars on the generators . . . . 178 178. Screws of the Three-System parallel to a Plane 179 179. Determination of a Cylindroid 180 180. Miscellaneous Remarks 182 181. Virtual Coefficients 183 182. Four Screws of the Screw System 184 183. Geometrical Notes 184 184. Cartesian Equation of the Three-System 184 185. Equilibrium of Four Forces applied to a Rigid Body .... 186 186. The Ellipsoid of Inertia 187 187. The Principal Screws of Inertia 188 188. Lemma . . . 189 CONTENTS. Xlll PAGE 189. Relation between the Impulsive Screw and the Instantaneous Screw . 189 190. Kinetic Energy acquired by an Impulse 189 191. Reaction of the Constraints .......... 191 192. Impulsive Screw is Indeterminate 191 193. Quadric of the Potential 192 194. The Principal Screws of the Potential . 192 195. Wrench evoked by Displacement 193 196. Harmonic Screws ............ 193 197. Oscillations of a Rigid Body about a Fixed Point . . . . . . 194 CHAPTER XV. THE PLANE REPRESENTATION OF FREEDOM OF THE THIRD ORDER. 198. A Fundamental Consideration 197 199. The Plane Representation 198 200. The Cylindroid 199 201. The Screws of the Three-System 200 202. Imaginary Screws .......... 201 203. Relation of the Four Planes to the Quadrics 202 204. The Pitch Conies 204 205. The Angle between Two Screws 204 206. Screws at Right Angles 206 207. Reciprocal Screws 206 208. The Principal Screws of the System 207 209. Expression for the Pitch 208 210. Intersecting Screws in a Three-System 212 211. Application to Dynamics 214 CHAPTER XVI. FREEDOM OF THE FOURTH ORDER. 212. Screw System of the Fourth Order 218 213. Equilibrium with Freedom of the Fourth Order 219 214. Screws of Stationary Pitch 221 215. Applications of the Two-System . 224 216. Application to the Three-System 226 217. Principal Pitches of the Reciprocal Cylindroid 227 218. Equations to the Screw in a Four-System 229 219. Impulsive Screws and Instantaneous Screws . . . . . 229 220. Principal Screws of Inertia in the Four-System . . . . . . 230 221. Application of Euler s Theorem 231 222. General Remarks 232 223. Quadratic n-systems 233 224. Properties of a Quadratic Two-System 234 225. The Quadratic Systems of Higher Orders .... 235 XIV CONTENTS. PAGE 226. Polar Screws 238 227. Dynamical Application of Polar Screws ....... 241 228. On the Degrees of certain Surfaces . . . 242 CHAPTER XVII. FREEDOM OF THE FIFTH ORDER. 229. Screw Reciprocal to Five Screws 246 230. Six Screws Reciprocal to One Screw ........ 247 231. Four Screws of a Five-system on every Quadric 250 232. Impulsive Screws and Instantaneous Screws ...... 251 233. Analytical Method. 252 234. Principal Screws of Inertia .......... 252 235. The Limits of the Roots 253 236. The Pectenoid 254 CHAPTER XVIII. FREEDOM OF THE SIXTH ORDER. 237. Introduction 258 238. Impulsive Screws 258 239. Theorem . 259 240. Theorem 260 241. Principal Axis 260 242. Harmonic Screws 261 CHAPTER XIX. HOMOGRAPHIC SCREW SYSTEMS. 243. Introduction 262 244. On Plane Homographic Systems . . . 262 245. Homographic Screw Systems 263 246. Relations among the Co-ordinates 263 247. The Double Screws 264 248. The Seven Pairs 264 249. Homographic Ti-systems ........... 265 250. Analogy to Anharmonic Ratio 266 251. A Physical Correspondence .......... 267 252. Impulsive and Instantaneous Systems 267 253. Special type of Homography 268 254. Reduction to a Canonical Form ......... 269 255. Correspondence of a Screw and a System 270 256. Correspondence of m and n Systems 271 257. Screws common to the Two Systems 271 258. Corresponding Screws denned by Equations 272 259. Generalization of Anharmonic Ratio . . 273 CONTENTS. XV CHAPTER XX. EMANANTS AND PITCH INVARIANTS. PAGE 260. The Dyname 274 261. Emanants 275 262. Angle between Two Screws .......... 276 263. Screws at Right Angles 276 264. Conditions that Three Screws shall be parallel to a Plane . . . 277 265. Screws on the same Axis 277 266. A General Expression for the Virtual Coefficient 278 267. Analogy to Orthogonal Transformation ....... 280 268. Property of the Pitches of Six Co-reciprocals ...... 282 269. Property of the Pitches of n Co-reciprocals ...... 285 270. Theorem as to Signs 285 271. Identical Formulae in a Co-reciprocal System 286 272. Three Pitches Positive and Three Negative 287 273. Linear Pitch Invariant Functions 287 274. A Pitch Invariant 289 275. Geometrical meaning ........... 290 276. Screws at Infinity 291 277. Expression for the Pitch 292 278. A System of Emanants which are Pitch Invariants ... . 294 CHAPTER XXI. DEVELOPMENTS OF THE DYNAMICAL THEORY. 279. Expression for the Kinetic Energy 296 280. Expression for the Twist Velocity 297 281. Conditions to be fulfilled by Two Pairs of Impulsive and Instantaneous Screws 298 282. Conjugate Screws of Inertia ........ 299 283. A Fundamental Theorem ...... 300 284. Case of a Constrained Rigid Body 303 285. Another Proof 304 286. Twist Velocity acquired by an Impulse 305 287. System with Two Degrees of Freedom ...... 306 288. A Geometrical Proof 30g 289. Construction of Chiastic Homography on the Cylindroid . . . 307 290. Homographic Systems on Two Cylindroids 307 291. Case of Normal Cylindroids 30g 292. General Conditions of Chiastic Homography .... 309 293. Origin of the Formulae of 281 310 294. Exception to be noted 312 295. Impulsive and Instantaneous Cylindroids 312 296. An Exceptional Case ...... 314 297. Another Extreme Case 31g 298. Three Pairs of Correspondents 31 7 XVI CONTENTS. PAGE 299. Cylindroid Reduced to a Plane 319 300. A difficulty removed 320 301. Two Geometrical Theorems . 320 CHAPTER XXII. THE GEOMETRICAL THEORY. 302. Preliminary 322 303. One Pair of Impulsive and Instantaneous Screws 323 304. An Important Exception 325 305. Two Pairs of Impulsive and Instantaneous Screws 325 306. A System of _ Rigid Bodies 326 307. The Geometrical Theory of Three Pairs of Screws 330 308. Another Method 332 309. Unconstrained Motion in system of Second Order 332 310. Analogous Problem in a Three-system 334 311. Fundamental Problem with Free Body 336 312. Freedom of the First or Second Order . 338 313. Freedom of the Third Order. . . . 339 314. General Case 339 315. Freedom of the Fifth Order 340 316. Principal Screws of Inertia of Constrained Body 341 317. Third and Higher Systems 342 318. Correlation of Two Systems of the Third Order 344 319. A Property of Reciprocal Screw Systems 347 320. Systems of the Fourth Order 348 321. Systems of the Fifth Order 350 322. Summary 350 323. Two Rigid Bodies 351 CHAPTER XXIII. VARIOUS EXERCISES. 324. The Co-ordinates of a Rigid Body 355 325. A Differential Equation satisfied by the Kinetic Energy .... 356 326. Co-ordinates of Impulsive Screw in terms of the Instantaneous Screw . 356 327. Another Proof of Article 303 357 328. A more general Theorem 357 329. Two Three-Systems 357 330. Construction of Homographic Correspondents 358 331. Geometrical Solution of the same Problem 359 332. Co-reciprocal Correspondents in Two Three-systems 360 333. Impulsive and Instantaneous Cylindroids 361 334. The Double Correspondents on Two Cylindroids 363 335. A Property of Co-reciprocals 364 336. Instantaneous Screw of Zero Pitch 365 337. Calculation of a Pitch Quadric 365 CONTENTS. XVII CHAPTER XXIV. THE THEORY OF SCREW-CHAINS. PAGE 338. 367 339. 368 340. 368 QzLl 369 Orr L. 342. Freedom of the First Order 369 343. Freedom of the Second Order 370 344. 374 345. 375 346. Freedom of the Fourth Order 377 347. Freedom of the Fifth Order 378 348. Application of Parallel Projections ...... 379 349. Properties of this correspondence 383 350. Freedom of the Fifth Order 384 351. Freedom of the Sixth Order 386 352. Freedom of the Seventh Order 386 353. Freedom of the Eighth and Higher Orders ..... 388 354. 388 355. Twists on 6/^ + 1 Screw-chains ....... 390 356. Impulsive Screw-chains and Instantaneous Screw-chains 392 357. The principal Screw-chains of Inertia . .... . . 394 358. Conjugate Screw-chains of Inertia 396 359. Harmonic Screw-chains . 397 CHAPTER XXV. THE THEORY OF PERMANENT SCREWS. 360. Introduction .... 399 361. Different Properties of a Principal Axis ....... 400 362. A Property of the Kinetic Energy of a System 401 363. The Identical Equation in Screw-chain Co-ordinates 403 364. The Converse Theorem 404 365. Transformation of the Vanishing Emanant ....... 405 366. The General Equations of Motion with Screw-chain Co-ordinates . . 405 367. Generalization of the Eulerian Equations ....... 406 368. The Restraining Wrench-chain 407 369. Physical meaning of the Vanishing Emanant 408 370. A Displacement without change of Energy ...... 408 371. The Accelerating Screw-chain . 409 372. Another Proof 409 373. Accelerating Screw-chain and Instantaneous Screw-chain .... 410 374. Permanent Screw-chains 410 375. Conditions of a Permanent Screw-chain . . . . . . . 411 376. Another identical Equation 412 XVlll CONTENTS. PAGE 377. Different Screws on the same Axis 414 378. Co-ordinates of the Restraining Wrench for a Free Rigid Body . . 414 379. Limitation to the position of the Restraining Screw .... 416 380. A Verification 416 381. A Particular Case 417 382. Remark on the General Case 418 383. Two Degrees of Freedom 419 384. Calculation of T 420 385. Another Method 420 386. The Permanent Screw 421 387. Geometrical Investigation 422 388. Another Method 423 389. Three Degrees of Freedom 426 390. Geometrical Construction for the Permanent Screws 427 391. Calculation of Permanent Screws in a Three-system 428 392. Case of Two Degrees of Freedom 430 393. Freedom of the Fourth Order . 431 394. Freedom of the Fifth and Sixth Orders 432 395. Summary ........... 432 CHAPTER XXVI. AN INTRODUCTION TO THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 396. Introduction 433 397. Preliminary notions ........... 433 398. The Intervene 434 399. First Group of Axioms of the Content 435 400. Determination of the Function expressing the Intervene between Two Objects on a Given Range 435 401. Another Process ............ 441 402. On the Infinite Objects in an Extent 442 403. On the Periodic Term in the Complete Expression of the Intervene . 443 404. Intervenes on Different Ranges in a Content ...... 444 405. Another Investigation of the possibility of Equally Graduated Ranges . 446 406. On the Infinite Objects in the Content ....... 447 407. The Departure 448 408. Second Group of Axioms of the Content 448 409. The Form of the Departure Function 449 410. On the Arrangement of the Infinite Ranges 449 411. Relations between Departure and Intervene ...... 450 412. The Eleventh Axiom of the Content 451 413. Representation of Objects by Points in Space ...... 453 414. Poles and Polars 454 415. On the Homographic Transformation of the Content .... 454 416. Deduction of the Equations of Transformation 455 417. On the Character of a Homographic Transformation which Conserves Intervene . . 456 CONTENTS. XIX PAGE 418. The Geometrical Meaning of this Symmetric Function .... 461 419. On the Intervene through which each Object is Conveyed . . . 464 420. The Orthogonal Transformation 465 421. Quadrics unaltered by the Orthogonal Transformation .... 466 422. Proof that U and Q have Four Common Generators .... 467 423. Verification of the Invariance of Intervene 468 424. Application of the Theory of Emanants 469 425. The Vector in Orthogonal Co-ordinates 470 426. Parallel Vectors 472 427. The Composition of Vectors 473 428. Geometrical proof that Two Homonymous Vectors compound into One Homonymous Vector 475 429. Geometrical proof of the Law of Permutability of Heteronymous Vectors 476 430. Determination of the Two Heteronymous Vectors equivalent to any given Motor 476 431. The Pitch of a Motor 478 432. Property of Right and Left Vectors 478 433. The^ Conception of Force in Non-Euclidian Space 480 434. Neutrality of Heteronymous Vectors . . . - 480 APPENDIX I. Notes on various points ....... 483 II. A Dynamical Parable 496 BIBLIOGRAPHICAL NOTES 510 INDEX 540 THE THEOEY OF SCKEWS. INTRODUCTION. THE Theory of Screws is founded upon two celebrated theorems. One relates to the displacement of a rigid body. The other relates to the forces which act on a rigid body. Various proofs of these theorems are well known to the mathematical student. The following method of considering them may be found a suitable introduction to the present volume. ON THE REDUCTION OF THE DISPLACEMENT OF A RIGID BODY TO ITS SIMPLEST FORM. Two positions of a rigid body being given, there is an infinite variety of movements by which the body can be transferred from one of these positions to the other. It has been discovered by Chasles that among these movements there is one of unparalleled simplicity. He has shown that a free rigid body can be moved from any one specified position to any other specified position by a movement consisting of a rotation around a straight line accompanied by a translation parallel to the straight line. Regarding the rigid body as an aggregation of points its change of place amounts to a transference of each point P to a new point Q. The initial and the final positions of the body being given each point P corre sponds to one Q, and each Q to one P. If the coordinates of P be given then those of Q will be determined, and vice versa. If we represent P by its quadriplanar coordinates x l , ae z , x 3 , x 4> then the quadriplanar coordinates 2/i. 2/2> 2/s- 2/4 f Q must be uniquely determined. There must, therefore, be equations connecting these coordinates, and as the correspondence is essentially of the one-to-one type these equations must be linear. We shall, therefore, write them in the form y, = (11) x, + (12) x z + (13) x. + (14) x,, y* = (21) x, + (22) x, + (23) x. A + (24) x t , y 9 = (31) x, + (32) x, + (33) x a + (34) a? 4 , y 4 = (41) ^ + (42) x z + (43) x, + (44) x.. B. 1 2 INTRODUCTION. If we make y l = px 1} y 2 = p# 2 , 2/s = P x a> 2/4 = P x * we can eliminate x l ,x z , x a , \ and obtain the following biquadratic for p, (11) -p, (12) (13) (14) (21) (22) -p, (23) (24) (31) (32) (33) -p, (34) (41) (42) (43) (44) - p = 0. The four roots of this indicate four double points, i.e. points which remain unaltered. But these points are not necessarily distinct or real. What we have written down is of course the general homographic trans formation of the points in space. For the displacement of a rigid system is a homographic transformation of all its points, but it is a very special kind of homographic transformation, as will be made apparent when we consider what has befallen the four double points. In the first place, since the distance between every two points before the transformation is the same as their distance after the transformation it follows that every point in the plane at infinity before any finite trans formation must be in the same plane afterwards. Hence the plane at infinity remains in the same position. Further, a sphere before this transformation is still a sphere after it. But it is well known that all spheres intersect the plane at infinity in the same imaginary circle H. Hence we see not only that the plane at infinity must remain unaltered by the transformation but that a certain imaginary circle in that plane is also unaltered. A system of points P lt P 2 , P 3 , &c. on this circle fl will, therefore, have as their correspondent points Q,, Q.,, Q 3 , <foc. also on fl As all anhar- monic ratios are unaltered by a linear transformation it follows that the systems P lt P 2 , P 3 , &c. and Q l} Q 2 , Q :t , &c. are homographic. There will, therefore, be two double points of this homography, O l and 0, and these will be the same after the transformation as they were before. They are, there fore, two of the four double points of which we were in search. It should be remarked that the points Oj and 0., cannot coincide, for if they coincide in 0, then must be the double point corresponding to a repeated root of the biquadratic for p. But such a root is real. Hence must be real. But every point on fl is imaginary. Hence this case is impossible. As Q is unaltered and Oi and 2 are fixed, the tangents at 0, and 2 are fixed, and so is therefore T, the intersection of these tangents; this is accordingly the third of the four points wanted. It lies in the plane at infinity, but is a real point. The ray O^Og, is also real ; it is the vanishing line of the planes perpendicular to the parallel rays, of which T is the vanishing point. INTRODUCTION. 3 In general in any homographic transformation there cannot be four distinct double points in a plane, unless every point of the plane is a double point. For suppose P 1; P 2 , P 3 , P 4 were four distinct coplanar double points and that any other point R had a correspondent R 1 . Draw the conic through P lt P 2 , P 3 , P 4 , R. Then R must lie on this conic because the anharmonic ratios R(P lt P 2 , P 3 , P 4 ) and R (l\, P 2 , P 3 , P 4 ) are equal. We have also P,(P 2 , P 3 , P 4) R) and P, (P 2 , P 3 , P 4 , R ) equal, but this is impossible if R and R be distinct. R is therefore a double point. In the case of the displaced rigid body suppose there is a fourth distinct double point in the plane at infinity. Each ray connected with the body will then have one double point at infinity, so that after the transformation the ray must again pass through the same point, i.e. the transformed position of each ray must be parallel to its original position. This is a special form of displacement. It is merely a translation of the whole rigid system in which every ray moves parallel to itself. In the more general type of displacement there can therefore be no double point distinct from T, 0], 2 and lying in the plane at infinity. Nor can there be in general another double point at a finite position T . For if so, then the ray TT is unaltered in position, and any finite point T" on the ray TT will be also unaltered, since this homographic transformation does not alter distances. Hence every point on TT is a double point. Here again we must have fallen on a special case where the double points instead of being only four have become infinitely numerous. In this case every point on a particular ray has become a double point. The change of the body from one position to the other could therefore be effected by simple rotation around this ray. There must however be four double points even in the most general case. Not one of these is to be finite, and in the plane at infinity not more than three are to be distinct. The fourth double point must be in the plane at infinity, and there it must coincide with either 0,, 2 or T. Thus we learn that the most general displacement of a rigid system is a homographic trans formation of all its points with the condition that two of its double points are on the imaginary circle fi in the plane at infinity, while the pole of their chord gives a third. Of these three one, we shall presently see which one, is to be regarded as formed of two coincident double points. All rays through T are parallel rays, and hence we learn that in the general displacement of a rigid body there is one real parallel system of rays each of which L is transformed into a parallel ray L . Let A be any plane perpendicular to this parallel system. Let L and L cut A in the points R and R. Then as L and L move, R and R are corresponding points in two plane homographic systems. Any two such systems in a plane will of course 1-2 4 INTRODUCTION. have three double points. The special feature of this homographic trans formation is that every circle is transformed into a circle. Each circle passes through the two circular points at infinity in its plane. These two points in A are therefore two of the double points of the plane homographic trans formation. There remains one real point X in A which is common to the two systems. The normal S to A drawn through X is therefore the one and only ray which the homographic transformation does not alter. This shows that in the most general change of a rigid system from one position to another there is one real ray unaltered Hence every point on S before the transformation is also on S afterwards. There must therefore be two double points distinct or coincident on S. But we have already proved that in the general case there is no finite double point. Hence S must have two coincident double points at T. Thus we learn that in the general transformation of a system which is equivalent to the displacement of a rigid body, there is one real point at infinity which is the result of two coinciding double points, and the polar of this point with respect to the imaginary circle on the plane at infinity cuts that circle in the two other double points. The displacement of the rigid body can thus be produced either by rotating the body around S or by translating the body parallel to 8, or by a combination of such movements. We are therefore led to the funda mental theorem discovered by Chasles. Any given displacement of a rigid body can be effected by a rotation about an axis combined with a translation parallel to that axis. Of much importance is the fact that this method of procedure is in general unique. It is easily seen that there is only one axis by rotation about which, and translation parallel to which, the body can be brought from one given position to another given position. Suppose there were two axes P and Q, which possessed this property, then by the movement about P, all the points of the body originally on the line P continue thereon ; but it cannot be true for any other line that all the points of the body originally on that line continue thereon after the displacement. Yet this would have to be true for Q, if by rotation around Q and translation parallel thereto, the desired change could be effected. We thus see that the displacement of a rigid body can be made to assume an extremely simple form, in which no arbitrary element is involved. ON THE REDUCTION OF A SYSTEM OF FORCES APPLIED TO A RIGID BODY TO ITS SIMPLEST FORM. It has been discovered by Poinsot that any system of forces which act upon a rigid body can be replaced by a single force, and a couple in a plane INTRODUCTION. 5 perpendicular to the force. Thus a force, and a couple in a plane perpen dicular to the force, constitute an adequate representation of any system of forces applied to a rigid body. It is easily seen that all the forces acting upon a rigid body may, by transference to an arbitrary origin, be compounded into a force acting at the origin, and a couple. Wherever the origin be taken, the magnitude and direction of the force are both manifestly invariable ; but this is not the case either with the moment of the couple or the direction of its axis. The origin, however, can always be so selected that the plane of the couple shall be perpendicular to the direction of the force. For at any origin the couple can be resolved into two couples, one in a plane containing the force, and the other in the plane perpendicular to the force. The first com ponent can be compounded with the force, the effect being merely to transfer the force to a parallel position ; thus the entire system is reduced to a force, and a couple in a plane perpendicular to that force. It is very important to observe that there is only one straight line which possesses the property that a force along this line, and a couple in a plane perpendicular to the line, is equivalent to the given system of forces. Sup pose two lines possessed the property, then if the force and couple belonging to one were reversed, they must destroy the force and couple belonging to the other. But the two straight lines must be parallel, since each must be parallel to the resultant of all the forces supposed to act at a point, and the forces acting along these must be equal and opposite. The two forces would there fore form a couple in a plane perpendicular to that of the couple which is found by compounding the two original couples. We should then have two couples in perpendicular planes destroying each other, which is manifestly impossible. We thus see that any system of forces applied to a rigid body can be made to assume an extremely simple form, in which no arbitrary element is involved. These two principles being established we are able to commence the Theory of Screws. CHAPTER I. TWISTS AND WRENCHES. 1. Definition of the word Pitch. The direct problem offered by the Dynamics of a Rigid Body may be thus stated. To determine at any instant the position of a rigid body subjected to certain constraints and acted upon by certain forces. We may first inquire as to the manner in which the solution of this problem ought to be presented. Adopting one position of the body as a standard of reference, a complete solution of the problem ought to provide the means of deriving the position at any epoch from the standard position. We are thus led to inquire into the most convenient method of specifying one position of a body with respect to another. To make our course plain let us consider the case of a mathematical point. To define the position of the point P with reference to a standard point A, there can be no more simple method than to indicate the straight line along which it would be necessary for a particle to travel from A in order to arrive at P, as well as the length of the journey. There is a more general method of defining the position of a rigid body with reference to a certain standard position. We can have a movement prescribed by which the body can be brought from the standard position to the sought position. It was shown in the Introduction that there is one simple movement which will always answer. A certain axis can be found, such that if the body be rotated around this axis through a determinate angle, and translated parallel to the axis for a determinate distance, the desired movement will be effected. It will simplify the conception of the movement to suppose, that at each epoch of the time occupied in the operations producing the change of position, the angle of rotation bears to the final angle of rotation, the same ratio which the corresponding translation bears to the final translation. Under these circumstances the motion of the body is precisely the same as if it were attached to the nut of a uniform screw (in the ordinary sense of the word), 1-3] TWISTS AND WRENCHES. 7 which had an appropriate position in space, and an appropriate number of threads to the inch. In the Theory of Screws the word pitch is employed in a particular sense that must be carefully noted. We define the pitch of a screw to be the rectilinear distance through which the nut is translated parallel to the axis of the screw, while the nut is rotated through the angular unit of circular measure. The pitch is thus a linear magnitude. It follows from this definition that the rectilinear distance parallel to the axis of the screw through which the nut moves when rotated through a given angle is simply the product of the pitch of the screw and the circular measure of the angle. 2. Definition of the word Screw. It is a fundamental principle of the theory developed in these pages that the dynamical significance of screws is precisely analogous to their kinematical significance. It is, therefore, essential that in the formal definition of the particular sense the word screw is to bear in this volume no prominence can be assigned to kinematical terms or conceptions unless it can be equally given to dynamical terms and conceptions. This condition is fulfilled by excluding both Kinematics and Dynamics and constituting the screw as the geometrical entity thus described. A screw is a straight line with which a definite linear magnitude termed the pitch is associated. We shall often denote a screw by a symbol, and then usually by a small Greek letter. With reference to these symbols, a caution may be necessary. If, for example, a screw be denoted by a, then a is not an ordinary algebraic quantity. It is a symbol which denotes all that is included in the conception of a screw, and requires five quantities for its specification ; of these four are required to determine the position of the straight line, and the pitch must be specified by a fifth. It will often be convenient to denote the pitch by a symbol, derived from the symbol employed to denote the screw to which the pitch belongs. The pitch of a screw is accordingly represented by appending to the letter p a suffix denoting the screw. For example, p a denotes the pitch of a and is an ordinary algebraical quantity. 3. Definition of the word Twist. We have next to define the use to be made of the word tiuist. A body is said to receive a twist about a screw when it is rotated uniformly about the screw, while it is translated uniformly parallel to the screw, through a distance equal to the product of the pitch and the circular measure of the angle of rotation. 8 THE THEORY OF SCREWS. [4, 4. A Geometrical Investigation. We can now demonstrate that whenever a body admits of an indefinitely small movement of a continuous nature it must be capable of executing that particular kind of movement denoted by a twist about a screw. Let AI be a standard position of the body, and let P be any marked point of the body initially at P lt As the body is displaced continuously to a neighbouring position, P will generally pursue a certain trajectory which, as the motion is small, may be identified with its tangent on which P n is a point adjacent to P,. In travelling from P, to P n , P passes through the several positions, P 2 , . . . P^. In a similar manner every other point, Q 1} of the rigid body will pass through a series of positions, Q 2 , &c., to Q n . We thus have the points of the body initially at P 1} Q lt R 1} respectively, and each moves along a straight line through the successive systems of positions P*, Qa, RZ, &c., on to the final position P n , Q n , R n . We may thus think of the consecutive positions occupied by the body A 2> A 3 , &c., as defined by the groups of points P lt Q 1} R 1 and P 2 , Q 2 , R 2 , &c. We have now to show that if the body be twisted by a continuous screw motion direct from A 1 to A n , it will pass through the series of positions A 2> A 3 , &c. It must be remembered that this is hardly to be regarded as an obvious consequence. From the initial position A 1 to the final position A n , the number of routes are generally infinitely various, but when these situations are contiguous, it is always possible to pass by a twist about a screw from A 1 to A n via the positions A 2 , A 3 . .. A n _!. Suppose the body be carried direct by a twist about a screw from the position AT, to the position A n . Since this motion is infinitely small, each point of the body will be carried along a straight line, and as Pj is to be conveyed to P B , this straight line can be no other than the line PiP n . In its progress P l will have reached the position P 2 , and when it is there the points Q l} R t will each have advanced to certain positions along the lines QtQ n and R^n, respectively. But the points reached by Q l and R 1 can be no other than the points Q. 2 and R 2 , respectively. To prove this we shall take the case where P 1} Q 1} R 1 are collinear. Suppose that when P! has advanced to P 2 , Q 1 shall not have reached Q.,, but shall be at the intermediate point Q . (Fig. 1.) Then the line P& will have moved to P 2 Q , and as 7^ can only be conveyed along R^.,, while at the same time it must lie along P 2 Q , it follows that the lines P 2 Q and R^ 2 must intersect at the point R , and consequently all the lines in this figure lie in a plane. Further, P 2 Q 2 and P 2 Q are each equal to PjQi, as the body is rigid, and so also P 2 R and P 2 R 2 are equal to P^. Hence it follows that QiQ and R^o are parallel, and consequently all the points on the line P&Ri are displaced in parallel directions. It would hence follow that the motion of every point in the body was in a parallel direction, and that consequently the entire 5] TWISTS AND WRENCHES. 9 movement was simply a translation. But even in this case it would be impossible for the points Q and R to be distinct from Q. 2 and R 2 , because, Fig. l. when a body is translated so that all its points move in parallel lines, it is impossible, if the body be rigid, for the distances traversed by each point not to be all equal. We have thus demonstrated that if a body is free to move from a position A 1 to an adjacent position A n by an infinitely small but continuous movement, it is also free to move through the series of positions A. 2> A 3 , &c., by which it would be conveyed from A^ to A n by a twist. We may also state the matter in a somewhat different manner, as follows : It would be impossible to devise a system of constraints which would permit a body to be moved continuously from A 1 to A n , and would at the same time prohibit the body from twisting about the screw which directly conducts from A l to A n . Of course this would not be true except in the case where the motion is infinitely small. The connexion of this result with the present investigation is now obvious. When A is the standard position of the body, and B an adjacent position into which it can be moved, then the body is free to twist about the screw defined by A and B. 5. The canonical form of a small displacement. In the Theory of Screws we are only concerned with the small displace ments of a system, and hence we can lay down the following fundamental statement. The canonical form to which the displacement of a rigid body can be reduced is a twist about a screw. If a body receive several twists in succession, then the position finally attained could have been reached in a single twist, which is called the resultant tivist. 10 THE THEORY OF SCREWS. [5- Although we have described the twist as a compound movement, yet in the present method of studying mechanics it is essential to consider the twist as one homogeneous quantity. Nor is there anything unnatural in such a supposition. Everyone will admit that the relation between two positions of a point is most simply presented by associating the purely metric element of length with the purely geometrical conception of a directed straight line. In like manner the relation between two positions of a rigid body can be most simply presented by associating a purely metric element with the purely geometrical conception of a screw, which is merely a straight line, with direction, situation, and pitch. It thus appears that a twist bears the same relation to a rigid body which the ordinary vector bears to a point. Each just expresses what is necessary to express the transference of the corresponding object from one given position to another*. 6. Instantaneous Screws. Whatever be the movement of a rigid body, it is at every instant twisting about a screw. For the movement of the body when passing from one position to another position indefinitely adjacent, is indistinguishable from the twist about an appropriately chosen screw by which the same displacement could be effected. The screw about which the body is twisting at any instant is termed the instantaneous screw. 7. Definition of the word Wrench. It has been explained in the Introduction that a system of forces acting upon a rigid body may be generally expressed by a certain force and a couple whose plane is perpendicular to the force. We now employ the word wrench, to denote a force and a couple in a plane perpendicular to the force. The quotient obtained by dividing the moment of the couple by the force is a linear magnitude. Everything, therefore, which could be specified about a wrench is determined (if the force be given in magnitude), when the position of a straight line is assigned as the direction of the force, and a linear magnitude is assigned as the quotient just referred to. Remembering the definition of a screw ( 2), we may use the phrase, ivrench on a screw, meaning thereby, a force directed along the screw and a couple in a plane perpendicular to the screw, the moment of the couple being equal to the product of the force and the pitch of the screw. Hence we may state that The canonical form to which a system of forces acting on a rigid body can be reduced is a wrench on a screw. * Compare M. Rene de Saussure, American Journal of Mathematics, Vol. xvm. No. 4, p. 337. TWISTS AND WRENCHES. 11 If a rigid body be acted upon by several wrenches, then these wrenches could be replaced by one wrench which is called the resultant wrench. A twist about a screw a requires six algebraic quantities for its complete specification, and of these, five are required to specify the screw a. The sixth quantity, which is called the AMPLITUDE OF THE TWIST, and is denoted by a , expresses the angle of that rotation which, when united with a translation, constitutes the entire twist. The distance of the translation is the product of the amplitude of the twist and the pitch of the screw, or in symbols, a p a . The sign of the pitch expresses the sense of the translation corresponding to a given rotation. If the pitch be zero, the twist reduces to a pure rotation around a. If the pitch be infinite, then a finite twist is not possible except the amplitude be zero, in which case the twist reduces to a pure translation parallel to a. A wrench on a screw a requires six algebraic quantities for its complete specification, and of these, five are required to specify the screw a. The sixth quantity, which is called the INTENSITY OF THE WRENCH, and is denoted by a", expresses the magnitude of that force which, when united with a couple, constitutes the entire wrench. The moment of the couple is the product of the intensity of the wrench and the pitch of the screw, or in symbols, a" p a . The sign of the pitch expresses the direction of the moment corresponding to a given force. If the pitch be zero, the wrench reduces to a pure force along a. If the pitch be infinite, then a finite wrench is not possible except the intensity be zero, in which case the wrench reduces to a couple in a plane perpendicular to a. In the case of a twisting motion about a screw a. the rate at which the amplitude of the twist changes is called the TWIST VELOCITY arid is denoted by a. 8. Restrictions. It is first necessary to point out the restrictions which we shall impose upon the forces. The rigid body M, whose motion we are considering, is presumed to be acted upon by the same forces whenever it occupies the same position. The forces which we shall assume are to be such as form what is known as a conservative system. Forces such as those due to a resisting medium are excluded, because such forces do not depend merely on the position of the body, but on the manner in which the body is moving through that position. The same consideration excludes friction which depends on the direction in which the body is moving through the position under considera tion. 12 THE THEORY OF SCREWS. [8 But the condition that the forces shall be defined, when the position is given, is still not sufficiently precise. We might include, in this restricted group, forces which could have no existence in nature. We shall, therefore, add the condition that the system is to be one in which the continual creation of energy is impossible. An important consequence of this restriction is stated as follows : The quantity of energy necessary to compel the body M to move from the position A to the position B, is independent of the route by which the change has been effected. Let L and M be two such routes, and suppose that less energy was required to make the change from A to B via L than via M. Make the change via L, with the expenditure of a certain quantity of energy, and then allow the body to return via M. Now, since at every stage of the route M the forces acting on the body are the same whichever way the body be moving, it follows, that in returning from B to A via M, the forces will give out exactly as much energy as would have been required to compel the body to move from A to B via M ; but by hypothesis this exceeds the energy necessary to make the change via L, and hence, on the return of the body to A, there is a clear gain of a quantity of energy, while the position of the body and the forces are the same as at first. By successive repetitions of the process an indefinite quantity of energy could be created from nothing. This being contrary to experience, compels us to admit that the quantity of energy necessary to force the body from A to B is independent of the route followed. It follows that the amount of work done in a number of twists against a wrench is equal to the work that would be done in the resultant twist. For, the work done in producing a given change of position is independent of the route. We may calculate the work done in a twist against a wrench by deter mining the amount of work done against three forces which are equivalent to the wrench, in consequence of the movements of their points of application which are caused by the twist. We shall assume the two lemmas 1st. The work done in the displace ment of a rigid body against a force is the same at whatever point in its line of application the force acts. 2nd. The work done in the displacement of a point against a number of forces acting at that point, is equal to the work done in the same displacement against the resultant force. The theorem to be proved is as follows : The amount of work done in a given twist against a number of wrenches, is equal to the work done in the same twist against the resultant wrench. 8] TWISTS AND WRENCHES. 13 Let n wrenches, which consist of 3w forces acting at A lt ... A 3n , compound into one wrench, of which the three forces act at P, Q, R. The force at A k may generally be decomposed into three forces along PA^, QA/c, RA^. By the 2nd lemma the amount of work ( W) done against the 3w original forces, equals the amount of work done against the 9w components. It, therefore, appears from the 1st lemma, that W will still be the amount of work done against the 9n components, of which 3/i act at P, 3w at Q, 3n at R. Finally, by the 2nd lemma, W will also be the amount of work done by the original twist against the three resultants formed by compounding each group at P, Q, R. But these resultants constitute the resultant wrench, whence the theorem has been proved. We thus obtain the following theorem, which we shall find of great service throughout this book. If a series of twists A l ,...A m , would compound into one twist A, and a series of wrenches B 1 ,...B n , would compound into one wrench B, then the energy that would be expended or gained when the rigid body per forms the twist A, under the influence of the wrench B, is equal to the algebraic sum of the mn quantities of energy that would be expended or gained when the body performs severally each twist A lt ...A m under the influence of each wrench B l ,...B n . We have now explained the conceptions, and the language in which the solution of any problem in the Dynamics of a rigid body may be pre sented. A complete solution of such a problem must provide us, at each epoch, with a screw, by a twist about which of an amplitude also to be specified, the body can be brought from a standard position to the position occupied at the epoch in question. It will also be of much interest to know the instantaneous screw about which the body is twisting at each epoch, as well as its twist velocity. Nor can we regard the solution as quite complete, unless we also have a clear conception of the screw on which all the forces acting on the body constitute a wrench of which we should also know the intensity. There is one special feature which characterises that portion of Dynamics which is discussed in the present treatise. We shall impose no restrictions on the form of the rigid body, and but little 011 the character of the con straints by which its movements are limited, or on the forces to which the rigid body is submitted. The restriction which we do make is that the body, while the object of examination, remains in, or indefinitely adjacent to, its original position. As a consequence of this restriction, we here make the remark that the amplitude of a twist is henceforth to be regarded as a small quantity. 14 THE THEORY OF SCREWS. [8 If it be objected, that with so great a restriction as that just referred to, only a limited field of inquiry remains, the answer is as follows : A perfectly general investigation could yield but a slender harvest of interesting or valuable results. All the problems of Physical importance are special cases of the general question. Thus, a special character in the constraints has pro duced the celebrated problem of the rotation of a rigid body about a fixed point. To vindicate our particular restriction it seems only necessary to remark, that the restricted inquiry still includes the theory of Equilibrium, of Impulsive Forces, and of Small Oscillations. Whatever novelty may be found in the following pages will, it is believed, be largely due to the circumstance that, with the important exception referred to, all the conditions of each problem are of absolute generality. CHAPTER II. THE CYLINDROID. 9. Introduction. Let a and /3 be any two screws which we shall suppose to be fixed both in position and in pitch. Let a body receive a twist of amplitude of about a, followed by a twist of amplitude /3 about /3. The position attained could have been arrived at by a single twist about some third screw p with an amplitude p. We are always to remember that the amplitudes of the twists are infinitely small quantities. With this assumption the order in which the twists about a and /3 are imparted will be immaterial in so far as the resulting displacements are concerned. The position attained is the same whether a follows /3 or /3 follows a . Any change in a or in /3 will of course generally entail a change both in the pitch and in the position of p. It might thus seem that p depended upon two parameters, and that consequently the different positions of p would form a doubly infinite series, known in linear geometry as a congruence. But this is not the case, for we prove that p depends only upon the ratio of a to /3 and is thus only singly infinite. Take any point P and let h a be the perpendicular distance from P to a, while p a is as usual the pitch of the screw; then the point P is transferred by the twist about a through the distance V^a 2 + / a 2 a . The twist about /3 conveys P to a distance The resultant of these two displacements conveys P in a direction which depends upon the ratio of a to /3 , and not upon their absolute magnitudes. Let P and Q be two points on p, then the resultant displacement will convey P and Q to points P and Q respectively which are also on the axis 16 THE THEORY OF SCREWS. [9, of p. Suppose that a and ft be varied while their ratio is preserved P and Q will then be transferred to P" and Q" while by the property just proved P, P , P" will be collinear and so will Q, Q , Q". It therefore follows that as P, P , Q, Q are collinear so will P, Q, P", Q" be collinear. The line PQ will therefore be displaced upon itself for every pair of values a and $ which retain the same ratio. The position of the resultant screw is thus not altered by any changes of a! and ft , which preserves their ratio. Let f be the angle between a and ft. We take the case of a point P at an infinite distance on the common perpendicular to a and (3. This point is displaced through a distance equal to h \fa!- + ft 2 + 2a /3 cos &&gt;, where h stands for the infinite perpendicular distance from P to a or to ft. This displacement of P is normal to p which itself intersects at right angles the common perpendicular to a and ft. As the perpendicular distance from P to p can only differ by a finite quantity from h hp = h Va 2 + /3 2 + 2a ft cos a>, or p = Va 7 - + ft - 2 +2a ft cos^a. This determines the amplitude of the resulting twist which is, it may be noted, independent of the pitches. Let <j) be the angle between the directions in which a point Q on p is displaced by the twists about a and ft, then the square of the displacement of Q will be (pa 2 + h a a ) a 2 + (pi + hi) ft 2 + 2 Vp a 2 + h* \?pi + hi aft cos cf> ; but this may also be written whence we see that p p depends only on the ratio of a to ft . The pitch and the position of p thus depend on the single numerical parameter expressing the ratio of a and ft . As this parameter varies so will p vary, and it must in successive positions coincide with the several generators of a certain ruled surface. Two of these generators will be the situations of a and of ft corresponding to the extreme values of zero and infinity respectively, which in the progress of its variation the parameter will assume. We shall next ascertain the laws according to which twists (and wrenches) must be compounded together, that is to say, we shall determine the single screw, one twist (or wrench) about which will produce the same effect on the 10] THE CYLINDROID. 17 body as two or more given twists (or wrenches) about two or more given screws. It will be found to be a fundamental point of the present theory that the rules for the composition of twists and of wrenches are identical*. 10. The Virtual Coefficient. Suppose a rigid body be acted upon by a wrench on a screw ft, of which the intensity is ft". Let the body receive a twist of small amplitude a around a screw a. It is proposed to find an expression for the energy required to effect the displacement. Let d be the shortest distance between a and ft, and let 6 be the angle between a and ft. Take a as the axis of x, the common perpendicular to a. and ft as the axis of z, and a line perpendicular to x and z for y. If we resolve the wrench on ft into forces X, Y. Z, parallel to the axes, and couples of moments L, M, N, in planes perpendicular to the axes we shall have X=ft"cosO; Y=ft"smO; Z=0; L = p pfi cos - ft"d sin ; M = ft" Pii sin + ft"d cos ; N = 0. We thus replace the given wrench by four wrenches, viz., two forces and two couples, and we replace the given twist by two twists, viz., one rotation and one translation. The work done by the given twist against the given wrench must equal the sum of the eight quantities of work done by each of the two component twists against each of the four component wrenches. Six of these quantities are zero. In fact a rotation through the angle a around the axis of x can do work only against L, the amount being aft" (p ft cos - d sin 0). The translation p a a parallel to the axis of x can do work only against X, the amount being a ft"p a cos 0. Thus the total quantity of work done is aft" {(pa+pp) cos d sin 0}. The expression i [(P + PP) cos d sin 0] is of great importance in the present theoryf. It is called the virtual * That the analogy between the composition of forces and of rotations can be deduced from the general principle of virtual velocities has been proved by Rodrigues (Liouville s Journal, t. 5, 1840, p. 436). + The theory of screws has many points of connexion with certain geometrical researches on the linear complex, by Pliicker and Klein. Thus the latter has shown (Mathematische Annalen, Band n., p. 368 (1869)), that if p &nd p s be each the "Hauptparameter" of a linear complex, and if (P a +Pft) cos O-d sin = 0, where d and relate to the principal axes of the complexes, then the two complexes possess a special relation and are said to be in " involution." B. 2 18 THE THEORY OF SCREWS. [10- coefficient of the two screws a and ft, and may be denoted by the symbol 11. Symmetry of the Virtual Coefficient. An obvious property of the virtual coefficient is of great importance. If the two screws a and ft be interchanged, the virtual coefficient remains unaltered. The identity of the laws of composition of twists and wrenches can be deduced from this circumstance*, and also the Theory of Reciprocal Screws which will be developed in Chap. III. 12. Composition of Twists and Wrenches. Suppose three twists about three screws a, ft, 7, possess the property that the body after the last twist has the same position which it had before the first : then the amplitudes of the twists, as well as the geometrical rela tions of the screws, must satisfy certain conditions. The particular nature of these conditions does not concern us at present, although it will be fully developed hereafter. We may at all events conceive the following method of ascertaining these conditions : Since the three twists neutralize it follows that the total energy ex pended in making those twists against a wrench, on any screw 77, must be zero, whence a trar, + ft ^ftr, + J^yr, = 0. This equation is one of an indefinite number (of which six can be shown to be independent) obtained by choosing different screws for 77. From each group of three equations the amplitudes can be eliminated, and four of the equations thus obtained will involve all the purely geometrical conditions as to direction, situation, and pitch, which must be fulfilled by the screws when three twists can neutralize each other. But now suppose that three wrenches equilibrate on the three screws a, ft, 7. Then the total energy expended in a twist about any screw 77 against the three wrenches must be zero, whence <*"^a,, + ft ^fr + j ^yr, = 0. An indefinite number of similar equations, one in fact for every screw 77, must be also satisfied. By comparing this system of equations with that previously obtained, it is obvious that the geometrical conditions imposed on the screws a, ft, 7, in * This pregnant remark, or what is equivalent thereto, is due to Klein (Math. Ann., Vol. iv. p. 413 (1871)). 13] THE CYLINDROID. 19 the two cases are identical. The amplitudes of the three twists which neutralise are, therefore, proportional to the intensities of the three wrenches which equilibrate. When three twists (or wrenches) neutralise, then a twist (or wrench) equal and opposite to one of them must be the resultant of the other two. Hence it follows that the laws for the composition of twists and of wrenches must be identical. 13. The Cylindroid. We next proceed to study the composition of twists and wrenches, and we select twists for this purpose, though wrenches would have been equally convenient. A body receives twists about three screws ; under what conditions will the body, after the last twist, resume the same position which it had before the first ? The problem may also be stated thus : It is required to ascertain the single screw, a twist about which would produce the same effect as any two given twists. We shall first examine a special case, and from it we shall deduce the general solution. Take, as axes of x and y, two screws a, /3, intersecting at right angles, whose pitches are p a and pp. Let a body receive twists about these screws of amplitudes & cos I and 6 sin I. The translations parallel to the coordinate axes are p a 6 cos I and p$& sin I. Hence the axis of the resultant twist makes an angle I with the axis of x ; and the two translations may be resolved into two components, of which (p a cos 2 1 + pp sin 2 /) is parallel to the axis of the resultant twist, while 6 sin I cos I (p a - pp) is perpendicular to the same line. The latter component has the effect of transferring the resultant axis of the rotations to a distance sin I cos I (p a pp), the axis moving parallel to itself in a plane perpendicular to that which contains a and /3. The two original twists about a and /3 are therefore compounded into a single twist of amplitude & about a screw 6 whose pitch is The position of the screw 6 is defined by the equations y x tan /, z = (p a pp) sin I cos I. Eliminating I we have the equation 22 20 THE THEORY OF SCREWS. [13, The conoidal cubic surface represented by this equation has been called the cylindroid*. Each generating line of the surface is conceived to be the residence of a screw, the pitch of which is determined by the expression When a cylindroid is said to contain a screw, it is not only meant that the screw is one of the generators of the surface, but that the pitch of the screw is identical with the pitch appropriate to the generator with which the screw coincides. We shall first show that it is impossible for more than one cylindroid to contain a given pair of screws 6 and <f>. For suppose that two cylindroids A and B could be so drawn. Then twists about 6 and <f> will compound into a twist on the cylindroid A and also on the cylindroid B ( 14). There fore the several screws on A would have to be identical with the screws on B, i.e. the two surfaces could not be different. That one cylindroid can always be drawn through a given pair of screws is proved as follows. Let the two given screws be 6 and <, the length of their common perpen dicular be h, and the angle between the two screws be A ; we shall show that by a proper choice of the origin, the axes, and the constants p a and pp, a cylindroid can be found which contains 6 and <. If I, m be the angles which two screws on a cylindroid make with the axis of oc, and if z ly z*, be the values of z, we have the equations of which the last four are deduced from the first six * This surface has been described by Pliicker (Neue Geometric des Eaumes, 1868-9, p. 97) ; he arrives at it as follows : Let ft = 0, and ft = be two linear complexes of the first degree, then all the complexes formed by giving /* different values in the expression O + /ufi = form a system of which the axes lie on the surface z (x^ + y 2 ) - (k - k )xy = Q. The parameter of any complex of which the axis makes an angle w with the axis of x is & = fc cos 2 w + fc sin 2 w. Pliicker also con structed a model of this surface. Pliicker does not appear to have noticed the mechanical and kinematical properties of the cylindroid which make this surface of so much importance in Dynamics ; but it is worthy of remark that the distribution of pitch which is presented by physical considerations is exactly the same as the distribution of parameter upon the generators of the surface, which Pliicker fully discussed. The first application of the cylindroid to Dynamics was made by Battaglini, who showed that this surface was the locus of the wrench resulting from the composition of forces of varying ratio on two given straight lines (Sulla serie dei sistemi di forze, Eendic. Ace. di Napoli, 1869, p. 133). See also the Bibliography at the end of this volume. The name cylindroid was suggested by Professor Cayley in 1871 in reply to a request which I made when, in ignorance of the previous work of both Pliicker and Battaglini, I began to study this surface. The word originated in the following construction, which was then communicated by Professor Cayley. Cut the cylinder x i + y"=(p -p^ in an ellipse by the plane z x, and consider the line x = Q, y=P B ~P a - If any plane z~c cuts the ellipse in the points A, B and the line in C, then CA, CB are two generating lines of the surface. 14] THE CYLINDROID. 21 Pe = Pa cos 2 / + p ft sin 2 1, z 1 = (p a pp) sin I cos I, P<t> = P* C s 2 wi + Pft sin 2 m, z z = (p a pp) sin m cos m, A = I m, k = z l z z , _ Pa JJB A > sin A Pa + pp=pe+p<t,-h cot A, + 5, A with similar values for m and z. 2 . It is therefore obvious that the cylindroid is determined, and that the solution is unique. It will often be convenient to denote by (6, <) the cylindroid drawn through the two screws 6 arid <. On any cylindroid there are in general two but only two screws which like a. and /3 intersect and are at the same time at right angles. These two important screws are often termed the principal screws of the surface. 14. General Property of the Cylindroid. If a body receive twists about three screws on a cylindroid, and if the amplitude of each twist be proportional to the sine of the angle between the two non-corresponding screws, then the body after the last twist will have regained the same position that it held before the first. The proof of this theorem must, according to ( 12), involve the proof of the following: If a body be acted upon by wrenches about three screws on a cylindroid, and if the intensity of each wrench be proportional to the sine of the angle between the two non-corresponding screws, then the three wrenches equilibrate. The former of these properties of the cylindroid is thus proved : Take any three screws 0, </>, i/r, upon the surface which make angles I, m, n, with the axis of x, and let the body receive twists about these screws of amplitudes , </> , -\Jr . Each of these twists can be decomposed into two twists about the screws a and /3 which lie along the axes of x and y. The entire effect of the three twists is, therefore, reduced to two rotations around the axes of x and y, and two translations parallel to these axes. The rotations are through angles equal respectively to cos I 4- <f> cos m + ty cos n and sin I + </> sin m + ty sin n. The translations are through distances equal to p a (0 f cos I + < cos ra + ->/r cos n) and pp (0 sin I + </> sin m + -fy sin n}. 22 THE THEORY OF SCREWS. [14- These four quantities vanish if u <p >lr sin (w - n) sin (n I) ~ sin (I m) and hence the fundamental property of the cylindroid has been proved. The cylindroid affords the means of compounding two twists (or two wrenches) by a rule as simple as that which the parallelogram of force pro vides for the composition of two intersecting forces. Draw the cylindroid which contains the two screws; select the screw on the cylindroid which makes angles with the given screws whose sines are in the inverse ratio of the amplitudes of the twists (or the intensities of the wrenches); a twist (or wrench) about the screw so determined is the required resultant. The amplitude of the resultant twist (or the intensity of the resultant wrench) is proportional to the diagonal of a parallelogram of which the two sides are parallel to the given screws, and of lengths proportional to the given ampli tudes (or intensities). 15. Particular Cases. If p* =P0 the cylindroid reduces to a plane, and the pitches of all the screws are equal. If all the pitches be zero, then the general property of the cylindroid reduces to the well-known construction for the resultant of two intersecting forces, or of rotations about two intersecting axes. If all the pitches be infinite, the general property reduces to the construction for the composition of two translations or of two couples. 16. Cylindroid with one Screw of Infinite pitch. Let OP, Fig. 2, be a screw of pitch p about which a body receives a small twist of amplitude o>. Fig. 2. Let OR be the direction in which all points of the rigid body are trans lated through equal distances p by a twist about a screw of infinite pitch 16] THE CYLINDROID. 23 parallel to OR. It is desired to find the cylindroid determined by these two screws. In the plane FOR draw OS perpendicular to OP and denote Z ROS by X. The translation of length p along OR may be resolved into the components p sin X along OP and p cos X along OS. Erect a normal OT to the plane of POR with a length determined by the condition coOT = p cos X. The joint result of the two motions is therefore a twist of amplitude to about a screw 6 through T and parallel to OP. The pitch p e of the screw is given by the equation (op g = wp + p sin X, whence p e p=QT tan X. Fig. 3. In Fig. 3 we show the plane through OP perpendicular to the plane POR in Fig. 2. The ordinate is the pitch of the screw through any point T. If p 6 = then OT= OH. Thus H is the point through which the one screw of zero pitch on the cylindroid passes, and we have the following theorem : If one screw on a cylindroid have infinite pitch, then the cylindroid reduces to a plane. The screws on the cylindroid become a system of parallel lines, and the pitch of each screw is proportional to the perpendicular distance from the screw of zero pitch. 24 THE THEORY OF SCREWS. [17- 17. Form of the Cylindroid in general. The equation of the surface contains only the single parameter p*pp, consequently all cylindroids are similar surfaces differing only in absolute magnitude. The curved portion of the surface is contained between the two parallel planes z = (papp), but it is to be observed that the nodal line x = 0, y= 0, also lies upon the surface. The intersection of the nodal line of the cylindroid with a plane is a node or a conjugate point upon the curve in which the plane is cut by the cylindroid according as the point does lie or does not lie between the two bounding planes. 18. The Pitch Conic. It is very useful to have a clear view of the distribution of pitch upon the screws contained on the surface. The equation of the surface involves only the difference of the pitches of the two principal screws and one arbitrary element must be further specified. If, however, two screws be given, then both the surface and the distribution are determined. Any constant added to all the pitches of a certain distribution will give another possible distribu tion for the same cylindroid. Let p g be the pitch of a screw 6 on the cylindroid which makes an angle I with the axis of x ; then ( 13) Pe = Pa cos 2 1 +pp sin 2 1. Draw in the plane x, y, the pitch conic where H is any constant ; then if r be the radius vector which makes an angle I with the axis of x, we have H P = -?> whence the pitch of each screw on a cylindroid is proportional to the inverse square of the parallel diameter of the conic. This conic is known as the pitch conic. By its means the pitches of all the screws on the cylindroid are determined. The asymptotes, real or imaginary, are parallel to the two screws of zero pitch. 19. Summary. We shall often have occasion to make use of the fundamental principles demonstrated in this chapter, viz., 19] THE CYLINDROID. That one, but only one, cylindroid can always be drawn so that two of its generators shall coincide with any two given screws a and ft, and that when all the generators of the surface become screws by having pitches assigned to them consistent with the law of distribution characteristic of the cylindroid, the pitches assigned to the generators which coincide with a and /3 shall be equal to the given pitches of a. and /3. Thus the cylindroid must become a familiar conception with the student of the Theory of Screws. A model of this surface is very helpful, and fortu nately there can be hardly any surface which is more easy to construct. In the Frontispiece a photograph of such a model is shown, and a plate repre senting another model of the same surface will be found in Chap. XIII. We shall develop in Chap. V an extremely simple method by which the screws on a cylindroid are represented by the points on a circle, and every property of the cylindroid which is required in the Theory of Screws can be represented by the corresponding property of points on a circle. CHAPTER III. RECIPROCAL SCREWS. 20. Reciprocal Screws. If a body only free to twist about a screw a be in equilibrium, though acted upon by a wrench on the screw ft, then conversely a body only free to twist about the screw ft will be in equilibrium, though acted upon by a wrench on the screw a. The principle of virtual velocities states, that if the body be in equili brium the work done in a small displacement against the external forces must be zero. That the virtual coefficient should vanish is the necessary and the sufficient condition, or ( 10) (p a + pp) cos d sin = 0. The symmetry shows that precisely the same condition is required whether the body be free to twist about a, while the wrench act on ft, or vice versa. A pair of screws are said to be reciprocal when their virtual co efficient is zero. 21. Particular Instances. Parallel or intersecting screws are reciprocal when the sum of their pitches is zero. Screws at right angles are reciprocal either when they intersect, or when one of the pitches is infinite. Two screws of infinite pitch are reciprocal, because a couple could not move a body which was only sus ceptible of translation. A screw whose pitch is zero or infinite is reciprocal to itself*. 22. Screw Reciprocal to Cylindroid. If a screw t] be reciprocal to two given screws 9 and (f>, then 77 is reciprocal to every screw on the cylindroid (6, <). * See also Professor Everett, F.R.S., Messenger of Mathematics, New Series (1874), No. 39. 20-23] RECIPROCAL SCREWS. 27 For a body only free to twist about 77 would be undisturbed by wrenches on 6 and < ; but a wrench on any screw ty of the cylindroid can be resolved into wrenches on 6 and </> ; therefore a wrench on -^r cannot disturb a body only free to twist about 77 ; therefore *fy and rj are reciprocal. We may say for brevity that 77 is reciprocal to the cylindroid. 77 cuts the cylindroid in three points because the surface is of the third degree, and one screw of the cylindroid passes through each of these three points ; these three screws must, of course, be reciprocal to 77. But two intersecting screws can only be reciprocal when they are at right angles, or when the sum of their pitches is zero. The pitch of the screw upon the cylin droid which makes an angle I with the axis of x is p a cos 3 / +pp sin 2 /. This is also the pitch of the screw TT I. There are, therefore, two screws of any given pitch ; but there cannot be more than two. It follows that 77 can at most intersect two screws upon the cylindroid of pitch equal and opposite to its own ; and, therefore, 77 must be perpendicular to the third screw. Hence any screw reciprocal to a cylindroid must intersect one of the generators at right angles. We easily infer, also, that a line intersecting one screw of a cyliudroid at right angles must cut the surface again in two points, and the screws passing through these points have equal pitch. These important results can be otherwise proved as follows. A wrench can always be expressed by a force at any point 0, and a couple in a plane L through that point but not of course in general normal to the force. For wrenches on the several screws of a cylindroid, the forces at any point all lie on a plane and the couples all intersect in a ray. The first part of this statement is obvious since all the screws on the cylindroid are parallel to a plane. To prove the second it is only necessary to note that any wrench on the cylindroid can be decomposed into forces along the two screws of zero pitch. Their moments will be in the planes drawn through arid the two screws of zero pitch. The transversal across the two screws of zero pitch drawn from must therefore lie in every plane L. We hence see that the third screw on the cylindroid which is crossed by such a transversal must be perpendicular to that transversal. 23. Reciprocal Cone. From any point P perpendiculars can be let fall upon the generators of the cylindroid, and if to these perpendiculars pitches are assigned which are equal in magnitude and opposite in sign to the pitches of the two remaining 28 THE THEORY OF SCREWS. [23, screws on the cylindroid intersected by the perpendicular, then the perpen diculars form a cone of reciprocal screws. We shall now prove that this cone is of the second order, and we shall show how it can be constructed. Let be the point from which the cone is to be drawn, and through let a line OT be drawn which is parallel to the nodal line, and, therefore, perpen dicular to all the generators. This line will cut the cylindroid in one real point T (Fig. 4), the two other points of intersection coalescing into the in finitely distant point in which OT intersects the nodal line. Draw a plane through T and through the screw LM which, lying on the cylindroid, has the same pitch as the screw through T. This plane can cut the cylindroid in a conic section only, for the line LM and the conic will then Fig. 4. make up the curve of the third degree, in which the plane must intersect the surface. Also since the entire cylindroid (or at least its curved portion) is included between two parallel planes ( 17), it follows that this conic must be an ellipse. We shall now prove that this ellipse is the locus of the feet of the per pendiculars let fall from on the generators of the cylindroid. Draw in the plane of the ellipse any line TUV through T ; then, since this line intersects two screws of equal pitch in T and U, it must be perpendicular to that generator of the cylindroid which it meets at V. This generator is, therefore, perpendicular to the plane of OT and VT, and, therefore, to the line 0V. It follows that V must be the foot of the perpendicular from on the 24] RECIPROCAL SCREWS. 29 generator through V, and that, therefore, the cone drawn from to the ellipse TL VM is the cone required. We hence deduce the following construction for the cone of reciprocal screws which can be drawn to a cylindroid from any point 0. Draw through a line parallel to the nodal line of the cylindroid, and let T be the one real point in which this line cuts the surface. Find the second screw LM on the cylindroid which has a pitch equal to the pitch of the screw which passes through T. A plane drawn through the point T and the straight line LM will cut the cylindroid in an ellipse, the various points of which joined to give the cone required*. We may further remark that as the plane TLM passes through a gene rator it must be a tangent plane to the cylindroid at one of the intersections, suppose L, while at the point M the line LM must intersect another generator. It follows (22) that L must be the foot of the perpendicular from T upon LM, and that M must be a point upon the nodal line. 24. Locus of a Screw Reciprocal to Four Screws. Since a screw is determined by five quantities, it is clear that when the four conditions of reciprocity are fulfilled the screw must generally be confined to one ruled surface. But this surface can be no other than a cylindroid. For, suppose three screws X, //., v, which were reciprocal to the four given screws did not lie on the same cylindroid, then any screw <f> on the cylindroid (X, fi), and any screw -^r on the cylindroid (X, v) must also fulfil the conditions, and so must also every screw on the cylindroid (<, ^) (22). We should thus have the screws reciprocal to four given screws, limited not to one surface, as above shown, but to any member of a family of surfaces. The construction of the cylindroid which is the locus of all the screws reciprocal to four given screws, may be effected in the following manner : Let a, /3, 7, 8 be the four screws, of which the pitches are in descending order of magnitude. Draw the cylindroids (a, 7) and (13, 8). If <r be a linear magnitude intermediate between pp and p y , it will be possible to choose two screws of pitch or on (a, 7), and also two screws of pitch <r on (/3, 8). Draw the two transversals which intersect the four screws thus selected ; attribute to each of these transversals the pitch a, and denote the screws thus pro duced by 6, <j>. Since intersecting screws are reciprocal when the sum of their pitches is zero, it follows that 6 and </> must be reciprocal to the cylindroids (a, 7) and (13, 8). Hence all the screws on the cylindroid (6, </>) must be re ciprocal to a, /3, 7, 8, and thus the problem has been solved. * M. Appell has proved conversely that the cylindroid is the only conoidal surface for which the feet of the perpendiculars from any point on the generators form a plane curve. Revue de Mathematiques Speciales, v. 129 30 (1895). More generally we can prove that this property cannot belong to any ruled surface whatever except a cylindroid and of course a cylinder. 30 THE THEORY OF SCREWS. [25-27 25. Screw Reciprocal to Five Screws. The determination of a screw reciprocal to five given screws must in general admit of only a finite number of solutions, because the number of conditions to be fulfilled is the same as the number of disposable constants. It is very important to observe that this number must be unity. For if two screws could be found which fulfilled the necessary conditions, then these conditions would be equally fulfilled by every screw on the cylindroid determined by those screws ( 22), and therefore the number of solutions of the problem would not be finite. The construction of the screw whose existence is thus demonstrated, can be effected by the results of the last article. Take any four of the five screws, and draw the reciprocal cylindroid which must contain the required screw. Any other set of four will give a different cylindroid, which also contains the required screw. These cylindroids must therefore intersect in the single screw, which is reciprocal to the five given screws. 26. Screw upon a Cylindroid Reciprocal to a Given Screw. Let e be the given screw, and let X, p, v, p be any four screws reciprocal to the cylindroid ; then the single screw 77, which is reciprocal to the five screws e, X, //., v, p, must lie on the cylindroid because it is reciprocal to X, /A, v, p, and therefore 77 is the screw required. The solution must generally be unique, for if a second screw were reciprocal to e, then the whole cylindroid would be reciprocal to e ; but this is not the case unless e fulfil certain conditions ( 22). 27. Properties of the Cylindroid*. We enunciate here a few properties of the cylindroid for which the writer is principally indebted to that accomplished geometer the late Dr Casey. The ellipse in which a tangent plane cuts the cylindroid has a circle for its projection on a plane perpendicular to the nodal line, and the radius of the circle is the minor axis of the ellipse. The difference of the squares of the axes of the ellipse is constant wherever the tangent plane be situated. The minor axes of all the ellipses lie in the same plane. The line joining the points in which the ellipse is cut by two screws of equal pitch on the cylindroid is parallel to the major axis. The line joining the points in which the ellipse is cut by two intersecting screws on the cylindroid is parallel to the minor axis. * For some remarkable quaternion investigations into " the close connexion between the theory of linear vector functions and the theory of screws " see Professor C. J. Jolj , Trans. Royal Irish Acad., Vol. xxx. Part xvi. (1895), and also Proc. Royal Irish Acad., Third Series, Vol. v. No. 1, p. 73(1897). CHAPTER IV. SCREW CO-ORDINATES. 28. Introduction. We are accustomed, in ordinary statics, to resolve the forces acting on a rigid body into three forces acting along given directions at a point and three couples in three given planes. In the present theory we are, however, led to regard a force as a wrench on a screw of which the pitch is zero, and a couple as a wrench on a screw of which the pitch is infinite. The ordinary process just referred to is, therefore, only a special case of the more general method of resolution by which the intensities of the six wrenches on six given screws can be determined, so that, when these wrenches are com pounded together, they shall constitute a wrench of given intensity on a given screw*. The problem which has to be solved may be stated in a more symmetrical manner as follows: To determine the intensities of the seven wrenches on seven given screws, such that, when these wrenches are applied to a rigid body, which is entirely free to move in every way, they shall equilibrate. The solution of this problem is identical (12) with that of the problem which may be enunciated as follows : To determine the amplitudes of seven small twists about seven given screws, such that, if these twists be applied to a rigid body in succession, the body after the last twist shall have resumed the same position which it occupied before the first. The problem we have last stated has been limited as usual to the case where the amplitudes of the twists are small quantities, so that the motion of a point by each twist may be regarded as rectilinear. Were it * If all the pitches be zero, the problem stated above reduces to the determination of the six forces along six given lines which shall be equivalent to a given force. If further, the six lines of reference form the edges of a tetrahedron, we have a problem which has been solved by Mobius, Grelle s Journal, t. xvm. p. 207 (1838). 32 THE THEORY OF SCREWS. [28- not for this condition a distinct solution would be required for every variation of the order in which the successive twists were imparted. If the number of screws were greater than seven, then both problems would be indeterminate ; if the number were less than seven, then both problems would be impossible (unless the screws were specially related) ; the number of screws being seven, the problem of the determination of the ratios of the seven intensities (or amplitudes) has, in general, one solution. We shall solve this for the case of wrenches. Let the seven screws be a, ft, 7, B, e, 77. Find the screw ty which is reciprocal to 7, 8, e, , 77. Let the seven wrenches act upon a body only free to twist about ty. The reaction of the constraints which limit the motion of the body will neutralize every wrench on a screw reciprocal to i/r (20). We may, therefore, so far as a body thus circumstanced is con cerned, discard all the wrenches except those on a and ft. Draw the cylindroid (a, ft), and determine thereon the screw p which is reciprocal to -^r. The body will not be in equilibrium unless the wrenches about a and ft constitute a wrench on p, and hence the ratio of the intensities a" and ft" is determined. By a similar process the ratio of the intensities of the wrenches on any other pair of the seven screws may be determined, and thus the problem has been solved. (See Appendix, note 1.) 29. Intensities of the Components. Let the six screws of reference be w l , &c. &&gt; 6 , and let p be a given screw on which is a wrench of given intensity p". Let the intensities of the components be p/ , &c. p 6 ", and let 77 be any screw. A twist about 77 must do the same quantity of work acting directly against the wrench on p as the sum of the six quantities of work which would be done by the same twist against each of the six components of the wrench on p. If TS^ be the virtual coefficient of 7; and the nth screw of reference, we have P"^r,p = P"^ + &C. p G "^rfl- By taking five other screws in place of 77, five more equations are obtained, and from the six equations thus found p/ , &c. p 6 " can be de termined. This process will be greatly simplified by judicious choice of the six screws of which 77 is the type. Let 77 be reciprocal to G> 2 , &c. &&gt; 6 , then oj-,,2 = 0, &c. -or^ = 0, and we have P"^r,p ^ Pl ^rft- From this equation p" is at once determined, and by five similar equations the intensities of the five remaining components may be likewise found. Precisely similar is the investigation which determines the amplitudes of the six twists about the six screws of reference into which any given twist may be decomposed. 31 J SCREW CO-ORDINATES. 33 30. The Intensity of the Resultant may be expressed in terms of the intensities of its components on the six screws of reference. Let a be any screw of pitch p a , let p lt p. 2 , &c. p e be the pitches of the six screws of reference w l} o> 2 , ... &&gt; 6 ; then taking each of the screws of refer ence in succession, for 77 in 29, and remembering that the virtual coefficient of two coincident screws is simply equal to the pitch, we have the following equations : ar 6 = ai + + cr-BT,,, + ap s . But taking the screw p in place of 77 we have <*"pa = l"r ttl + tt/ ^ae. Substituting for ^ al ... -5r o6 from the former equations, we deduce pj 1 * = $ OW) + 22 (/ V^ 12 ). This result may recall the well-known expression for the square of a force acting at a point in terms of its components along three axes passing through the point. This expression is of course greatly simplified when the three axes are rectangular, and we shall now show how by a special disposition of the screws of reference, a corresponding simplification can be made in the formula just written. 31. Co-Reciprocal Screws. We have hitherto chosen the six screws of reference quite arbitrarily ; we now proceed in a different manner. Take for &) 1? any screw; for co 2 , any screw reciprocal to a^; for o> 3 , any screw reciprocal to both &&gt;! and &&gt; 2 ; f r &&gt; 4 , any screw reciprocal to o) 1} &&gt;.,, &&gt; 3 ; for &&gt; 5 , any screw reciprocal to a> l , <o 2 > MS, &&gt; 4 ; for &&gt; 6 , the screw reciprocal to Wj, &&gt;.,, &&gt; 3 , &&gt; 4 , o> 5 . A set constructed in this way possesses the property that each pair of screws is reciprocal. Any set of screws not exceeding six, of which each pair is reciprocal, may be called for brevity a set of co-reciprocals*. Thirty constants determine a set of six screws. If the set be co- reciprocal, fifteen conditions must be fulfilled ; we have, therefore, fifteen elements still disposable, so that we are always enabled to select a co- reciprocal set with special appropriateness to the problem under con sideration. * Klein Las discussed (Math. Ann. Band n. p. 204 (1869)) six linear complexes, of which each pair is in involution. If the axes of these complexes be regarded as screws, of which the " Hauptparameter " are the pitches, then these six screws will be co-reciprocal. B. 3 34 THE THEORY OF SCREWS. [31- The facilities presented by rectangular axes for questions connected with the dynamics of a particle have perhaps their analogues in the conveniences which arise from the use of co-reciprocal sets of screws in the present theory. If the six screws of reference be co-reciprocal, then the formula of the last section assumes the very simple form 32. Co-ordinates of a Wrench. We shall henceforth usually suppose that the screws of reference are co-reciprocal. We may also speak of the co-ordinates of a wrench*, meaning thereby the intensities of its six components on the six screws of reference. So also we may speak of the co-ordinates of a twist, meaning thereby the amplitudes of its six components about the six scretvs of reference. The co-ordinates of a wrench of intensity a" on the screw a are denoted by / , ... fi ". The co-ordinates of a twist of amplitude a about a are denoted by a/, . . . a B . The co-ordinates of a twist-velocity a about a are denoted by a 1? cL, ... d ti . The actual motion of the body is in this case a translation with velocity ap a parallel to a and a rotation around p with the angular velocity d. 33. The Work done in a twist of amplitude a about a screw a, by a wrench of intensity ft" on the screw ft, can be expressed in terms of the co-ordinates. Replace the twist and the wrench by their respective components about the co-reciprocals. Then the total work done will be equal to the sum of the thirty-six quantities of work done in each component twist by each component wrench. Since the screws are co-reciprocal, thirty of these quantities disappear, and the remainder have for their sumf 34. Screw Co-ordinates. A wrench on the screw a, of which the intensity is one unit, has for its components, on six co-reciprocal screws, wrenches of which the intensities may be said to constitute the co-ordinates of the screw a. These co-ordinates may be denoted by a lt ... a 6 . * Pliicker introduced the conception of the six co-ordinates of a system of forces Phil. Trans., Vol. CLVI. p. 362 (1866). See also Battaglini, " Sulle dinami in involuzione," Atti di Nnpoli iv., (1869); Zeuthen, Math. Ann., Band i. p. 432 (1869). t That the work done can be represented by an expression of this type was announced by Klein, Math. Ann. Band iv. p. 413 (1871). 30] SCREW CO-ORDINATES. 35 When the co-ordinates of a screw are given, the screw itself may be thus determined. Let e be any small quantity. Take a body in the position A, and impart to it successively twists about each of the screws of reference of amplitudes ea ly <z. 2 , ... e 6 . Let the position thus attained be B\ then the twist which would bring the body directly from A to B is about the required screw a. 35. Identical Relation. The six co-ordinates of a screw are not independent quantities, but fulfil one relation, the nature of which is suggested by the relation between three direction cosines. When two twists are compounded by the cylindroid ( 14), it will be observed that the amplitude of the resultant twist, as well as the direction of its screw, depend solely on the amplitudes of the given twists, and the directions of the given screws, and not at all upon either their pitches or their absolute situations. So also when any number of twists are compounded, the amplitude and direction of the resultant depend only on the amplitudes and directions of the components. We may, therefore, state the following general principle. If n twists neutralize (or n wrenches equilibrate) then a closed polygon of n sides can be drawn, each of the sides of which is proportional to the amplitude of one of the twists (or intensity of one of the wrenches), and parallel to the corresponding screw. Let a n , b n , c n , be the direction cosines of a line parallel to any screw of reference &&gt;, and drawn through a point through which pass three rect angular axes. Then since a unit wrench on a has components of intensities a,,... a 6 , we must have (!! 4 . . . + tt (i a fi ) 2 + (&ii + . + &) 2 + (Cjfli 4- . . . + c (i a (i ) 2 = 1, whence ^X 2 -f 2Sai<x,cos (12) = 1, if we denote by cos (12) the cosine of the angle between two straight lines parallel to m 1 and &&gt; 2 . 36. Calculation of Co-ordinates. We may conceive the formation of a table of triple entry from which the virtual coefficient of any pair of screws may be ascertained. The three argu ments will be the angle between the two screws, the perpendicular distance, and the sum of the pitches. These arguments having been ascertained by ordinary measurement of lines and angles, the virtual coefficient can be extracted from the tables. Let a be a screw, of which the co-ordinates are to be determined. The 32 36 THE THEORY OF SCREWS. [36- work done by the unit wrench on a in a twist of amplitude &&gt;/ about the screw &&gt;! is 2&)j VTal, but this must be equal to the work done in the same twist by a wrench of intensity j on the screw &&gt; 1} whence or j = - . Pi Thus, to compute each co-ordinate a n , it is only necessary to ascertain from the tables the virtual coefficient of e*i and w n and to divide this quantity 37. The Virtual Coefficient of two screws may be expressed with great simplicity by the aid of screw co-ordinates. The components of a twist of amplitude are of amplitudes a a lt ... a a B . The components of a wrench of intensity ft" are of intensities @" j3 lt ... /3"#, Comparing these expressions with 32, we see that and we find that the expression for the work done in the twist about a, by the wrench on ft, is a. ft" [2 The quantity inside the bracket is twice the virtual coefficient, whence we deduce the important expression l&aft = S/)j !/?]. Since a and ft enter symmetrically into this expression, we are again reminded of the reciprocal character of the virtual coefficient. 38. The Pitch of a screw is at once expressed in terms of its co ordinates, for the virtual coefficient of two coincident screws being equal to the pitch, we have p a = 2^ 1 a 1 2 . 39. Screw Reciprocal to five Screws. We can determine the co-ordinates of the single screw p, which is reciprocal to five given screws, a, ft, y, 8, e. ( 25.) The quantities p l} ... p ti , must satisfy the condition , = 0, 40J SCREW CO-ORDINATES. 37 and four similar equations ; hence p n p n is proportional to the determinant obtained by omitting the /t th column from the matrix or : i> 72. 7a. 74. 75> 7 ,, 0,, &,, S 4 , 8 3 , 8 8 I i, e,, e 3 , 6 4 , 6 5 , e 6 , | and affixing a proper sign. The ratios of p 1} ... p s , being thus found, the actual values are given by 35. If there were a sixth screw f the evanescence of the determinant which written in the usual notation is (a 1; /3 2 , 73, S 4 , e 5 , f 6 ) would express that the six screws had a common reciprocal. This is an important case in view of future developments. 40. Co-ordinates of a Screw on a Cylindroid. We may define the screw 8 on the cylindroid by the angle I, which it makes with a, one of the two principal screws a and /3. Since a Avrcnch of unit intensity on 6 has components of intensities cos I and sin I on a and j3 ( 14), and since each of these components may be resolved into six wrenches on any six co-reciprocal screws, we must have ( 34) 6 n = On cos I + fin sin I. From this expression we can find the pitch of : for we have p e = Spj (: cos I 4- & sin If, whence expanding and observing that as a and /3 are reciprocal p 1 a. 1 @ 1 0, and also that S,p 1 a l ~ = p a and f!h& >a *Pjh we have the expression already given ( 18), viz. pe = p* cos 2 I+PP sin 2 1. If two screws, and <, upon the cylindroid, are reciprocal, then (m being the defining angle of <), 2p t (! cos I + Pi sin 1) (! cos m + {3 l sin m) = 0, or p a cos I cos m+pft sin I sin m = 0. Comparing this with 20, we have the following useful theorem : Any two reciprocal screws on a cylindroid are parallel to conjugate diameters of the pitch conic. Since the sum of the squares of two conjugate diameters in an ellipse is constant, we obtain the important result that the sum of the reciprocals of the pitches of two reciprocal screws on a cylindroid is constant *. * Compare Octonions, p. 190, by Alex. M u Aulay, 1898. 38 THE THEORY OF SCREWS. [41- 41. The Canonical Co-Reciprocals. If all the six screws of a co-reciprocal system are to pass through the same point, they must in general constitute a pair of screws of pitches 4- a and a on an axis OX, a pair of screws of pitches -1- b and 6 on an axis Y which intersects OX at right angles, and a pair of screws of pitches + c and c on an axis OZ perpendicular to both OX and OF. It is convenient to speak of a co-reciprocal system thus arranged as a set of canonical co-reciprocals. The three rectangular axes OX, OY, OZ we may refer to as the associated Cartesian axes. If a, , 2 2 , ... a 6 be the six co-ordinates of a screw referred to the canonical co-reciprocals, then the pitch is given in general by the equation p a = a Or - 2 2 ) + b (ot s 2 - a 4 2 ) + c ( 5 2 - 6 2 ). It must be remembered that in this formula we assume that the co-ordi nates satisfy the condition | 35 1 = (! + a a ) 2 + (a, + 4 ) 2 + ( 5 + a*) 2 - Of course this condition is not necessarily complied with when a.^ ,, ... or some of them are infinite, as they are in the case of a screw of infinite pitch 44. In general the direction cosines of the screw a are 42. An Expression for the Virtual Coefficient. Let X , fjf, v be the direction cosines of the screw B (of pitch p e ) which passes through the point x, y , z . Let X", p", v" be the direction cosines of the screw a (of pitch p a ) which passes through the point x" , y", z". Then it can easily be shown that the virtual coefficient of 6 and a is half the expression j x - x", y - y\ z - z" (l } 9 + P<t>) (X X" + p fJi" + v v") X , fJL , v X" , /*" , "" 43. Equations of a Screw. Given the six co-ordinates a l , 2 , . . . 6 of a screw, with reference to a set of six canonical co-reciprocals, it is required to find the equations of that screw with reference to the associated Cartesian axes. If we take for 6 in the expression just written the screw of pitch a in the canonical system, thus making X = 1 ; pf = ; v = ; x = ; y = ; z = 0, 44] SCREW CO-ORDINATES. 39 we have 2aa l = ( a+p a )\"- (p"z - v"y ), similarly 2aa 2 = (- a + p a ) A." (fjif z v"y ), we thus find \" = a, + a., ; v"y pf z = a (i a,) p a (a, -f a,). In like manner we obtain two similar pairs of equations for the required equations of the screw a, (a.-, + ?) y - (a, f 04) z = a (j - ou) - p a (^ + o 2 ), (a, -f a,) z - ( 6 4- ) a; = 6 (a, - a 4 ) - > (a s + 4 ), (i). (a s + 4 ) # - (i + ,) y=c(a s - a 6 ) - ^ a ( 5 + a 6 The expressions on the right-hand side of these equations are the co ordinates of the extremity of a vector from the origin of length equal to the perpendicular distance of a from the centre, and normal to the plane containing both a and the origin. The co-ordinates of the foot of the perpendicular from the origin on the screw a are easily shown to be x - ( 5 - 6 ) ( + a 4 ) c - (a 5 + a,) ( 3 - a 4 ) b, i/ = (di- a,) ( 3 + O a - (! 4- a ) ( 5 - ) c, ^ = (a s - a,) (a, -1- a,) b - (a 3 + 4 ) (otj - a 2 ) a, 44. A Screw of Infinite Pitch. The conception of the screw co-ordinates as defined in 41 require special consideration in the case of a screw of infinite pitch. Consider a wrench on such a screw. If the intensity of the wrench be one unit, then the moment of the couple which forms part of the wrench is infinite. As the pitches of the screws of reference or any of those pitches are not in general to be infinite, it follows that the wrench of unit intensity on a screw of infinite pitch must have for its components on one or more of the screws of reference wrenches of infinite intensity. If therefore a u 2 , ... a 6 be the co-ordinates of a wrench of infinite pitch, it is essential that one or more of the quantities ci l} a.,, ... a s shall be infinite. In the case where the screws of reference form a canonical system we can obtain the co-ordinates as follows : (p a + a) cos (al) - d Al sin (al) _ (/> a - a) cos (al) - rf al sin (rl) ~~ ; " 2 ~ - 40 THE THEORY OF SCREWS. [44- It p a be indefinitely great with respect to a and d a i, then p a cosf(ai ) pa cos (oci) -- 2a "2a _ ;j a cos (as) " 26 " " 4 ~ 26 _ Pa cos (as) _ Pa cos (as) a 5 ~ 2c 2c If the co-ordinates of a screw not itself at infinity satisfy ai + a, = 0; a :j + a 4 = 0; 5 + a 6 = 0; then we must have for the equations (Pa + ) cos (ai) - dai sin (ai) ttj = & > _ (p a a) cos (ai) - d al sin (ai) and two similar pairs could not be otherwise satisfied. We are not however entitled to assume the converse, i.e. that if the pitch is infinite then the three equations a 1 + a. 2 = 0, &c. must be satisfied. It will however be true that but some at least of the co-ordinates being infinite, we are in general prevented from replacing these equations by the ordinary linear form. 45. Indeterminate Screw. It may however be instructive to investigate otherwise the circumstances of a screw a possessing the property that its six co-ordinates a 1( a, ... a^ are submitted to the three conditions ! + a, = ; a s + a 4 = ; a 5 + 6 = 0. Two distinct cases must be considered. Either the screw a must have some finite points, or it must lie altogether at infinity. The first alternative is now supposed. The second will be discussed in the next article. If there be any finite points on a then for such points the three left- hand members of the equations in 43 are all zero. The three right-hand members must also reduce to zero. The only way in which this can be accomplished (for we need not consider the case in which all the co-ordinates are zero) is by making p a infinite. 47] SCREW CO-ORDINATES. 41 The direction of the screw of infinite pitch is indicated by the fact that as a twist about it is a translation with components a (i - 2 ), b (a 3 a 4 ), c ( g 6 ), the screw must be parallel to a ray of which these three quantities are proportional to the direction cosines. As the three equations to the screw have disappeared, the situation of the screw is indeterminate. This is of course what might be expected, because a couple is equally efficacious in any position in its plane. 46. A Screw at infinity. If we have <*! + 2 = ; 3 + a 4 = ; 5 + = : then the three equations (i), of (43) will be satisfied for a screw entirely at infinity, no matter what its pitch may be. From this and the last article we see that the three equations j + , = ; a 3 + a 4 = ; a, + % = may mean either a screw of infinite pitch and indefinite position, or a screw of indefinite pitch lying in the plane at infinity. 47. Screws on one axis. The co-ordinates being referred to six canonical co-reciprocals, it is required to determine the co-ordinates of the screws of various pitches which lie on the same axis as a given screw a. We have from 36 _ (a + j?.)(i + . 2 ) - < sin (al) ~ _ (i + a ) - d ai sin (ai) ~ ~~ whence ^ w 1 = (^ + tt,). 2Q We thus have the useful results 6)5 = a& ~ These formulae may be verified by observing that one of the equations ( 43) defining o> is (&&gt; 5 + a> 9 ) y (w 3 + w 4 ) s = a (a^ o> 2 ) p m (coj -f o) a ). 42 THE THEORY OF SCREWS. [47 Introducing the values just given for eo this equation becomes - (a a + a 4 ) z = a fa - o 2 ) - p a fa + a,), as of course it ought to do, for the pitch is immaterial when the question is only as to the situation of the screw. 48. Transformation of Screw-co-ordinates. Let i...a 6 be the co-ordinates of a screw which we shall call to, with reference to a canonical system of screws of reference with pitches + a and a on an axis X ; + b and b on an intersecting perpendicular axis Y, and + c and c on the intersecting axis OZ which is perpendicular to both OX and Y. Let x , 7/0, z be the co-ordinates of any point with reference to the associated system of Cartesians. Draw through a system of rectangular axes O X , O Y , O Z parallel to the original system OX, OF, OZ. Let a new system of canonical screws of reference be arranged with pitches + a and a on O X , + b and b on O Y , and + c and c on O Z . Let 1} 0., ... # 6 be the co-ordinates of the screw o with regard to these new screws of reference. It is required to find these quantities in terms of !, ... 6 . Let x, y , z be the current co-ordinates of a point on w referred to the new axes, the co-ordinates of this point with respect to the old axes being x, y, z, then x=x + x ; y = y + y - z = z + z< ) . The equations of &&gt; with respect to the new axes are ( 43), (0, + 0) </ - (&, + OJ z = " (0i - 0.) - JP. (0i + 0,)) (0 1 + 0JS-(0 s + 0Jaf = b(0 > -0 4 )-p..(0 t + 0^ ......... (i). (0, + 4 ) x - (0, + 0,) y = c(0 5 - 6 ) - p M (0, + 6 }) We have also ( 5 + 8 ) y ~ fa + 4> z = a (tfj - a,) - p u fa + 2 )j (! + ,) .2 -fa + a 6 )x = b(a 3 -a,)-p ta (a 3 +a 4 )[ ......... (ii). ( 3 + ce 4 ) x - fa + a.,) y = c (a g - a fi ) - _p u (a 5 + or 6 )J Remembering that the new axes are parallel to the original axes we have 1 + 3 = a, + a a ; 3 + 4 = a 3 + a 4 ; 5 + 0, = a, + a ti ......... (iii). 49] SCREW CO-ORDINATES. 43 Hence by subtracting the several formulae (i) from the formulae (ii) we obtain // ( 5 + ) - z (flf g + 4 ) = a (a, - a,) - a (0, - 0,)j z n (! -I- a,) - a? (a 5 + a fi ) = 6 (a, - a 4 ) - b (0 3 - 4 ) L ........ (iiii). # ( 3 + 4> - 2/o (i + 2 ) = c ( s -- a 6 ) - c (0 5 - 6 ) ) The six e( {nations (iii) and (iiii) determine 6 l) ... # in terms of ,,.... 49. Principal Screws on a Cylindroid. If two screws are given we determine as follows the pitches of the two principal screws on the cylindroid which the two given screws define. Let a and /3 be the two given screws. Then the co-ordinates of these screws referred to six canonical co-reciprocals are !,... and fr,...fr. The co-ordinates of any other screw on the same cylindroid are propor tional to pa, + fr, py 2 + /3,, . . . pa, + & ; when p is a variable parameter. The pitch p of the screw so indicated is given by the equation ( 41) a (pa, + J3J* - a (pa, + /3,) 2 + b (pa 3 + &)* - b (pa, + &) 3 = p [{p ( ttl + a,) + fr + fr}* + p {(a, + a 4 ) + & + /3 4 j 2 + p {(a s + a) + fr + ft,]- 2 ], or p*p a + 2pvr ali + p ft = p {p 2 + 2p cos (a/3) +1], or p- (p a -p) + 2p {CT a/3 - p cos (a/9)] + pp p = 0. For the principal screws p is to be determined so that p shall be a maxi mum or a minimum ( 18), whence the equation for p is Ka0 - p cos (a/3)] 2 = (p a - p) (p ft - p), or I? sin 2 (a/3) + p (2OT a/3 cos (a/8) - p a - pp) + p a p ft - vr^ = 0. The roots of this quadratic are the required values of p. The quadratic may also receive the form = (P ~ Pa) (p ~ Pft) sin 2 () + d a/5 -sin (a/3) cos (a/9) (/j a - i (Pa -p p y cos 2 (a/S) - i #. sin 2 (a/3), where d a p is the shortest distance of a and /3. 44 THE THEORY OF SCREWS, [49, 50 In this form it i.s obvious that to increase each of the three quantities Pa> pp> P by in does not affect the equation. This is of course the well-known property of the cylindroid. ( 20.) If the quadratic have two equal roots, then all the screws of the cylindroid form a plane pencil, and all have equal pitches. The discriminant of the quadratic is ^ a +^) 2 -4w 0(j; a +p0)cos(a/S)-4^ a p0 sin 2 (a/S)+4OT^ 2 si - (p a + p ft ) cos (a/3)} 3 + (p a + ppf sin 2 (a/3) - 4>p a p ft sin 2 (a/ (^a-^) 2 )sin 2 (a/3). Hence discarding the case when (a/3) = we have d.fi=0, p*-p ft = 0, as was to be expected. CHAPTEK V. THE REPRESENTATION OF THE CYLINDROID BY A CIRCLE*. 50. A Plane Representation. The essence of the present chapter lies in the geometrical representation of a screw by a point. The series of screws which constitute the cylindroid correspond to, or are represented by, a series of points in a plane. By choosing a particular type of correspondence we can represent the screws of the cylindroid by the points of a circle "f. Various problems on the cylindroid can then be studied by the aid of the corresponding circle. We commence with a very simple process for the discovery of the circle. It will in due course appear how this circular representation is suggested by the geometry of the cylindroid itself ( 68). It has been shown ( 13) that the positions of the several screws on the cylindroid may be concisely defined by the intersections of the pairs of planes, y = x tan 0, z = in sin 26. In these equations, 9 varies in correspondence with the several screws, while in is a parameter expressing the size of the cylindroid. In fact, the whole surface, except parts of the nodal line, is contained between two parallel planes, the distance between which is 2m. The pitch of the screw corresponding to 9 is expressed by P=pn + cos 20, where p is a constant. * See papers in Proceedings of the lioyal Irish Academy, Ser. n. Vol. iv. p. 29 (1883), and the Cunningham Memoirs of the lioyal Irish Academy, No. 4 (1886). t I may refer to a paper by Professor Mannheim, in the Comptes rendits for 2nd February, 1885, entitled "Representation plane relative aux deplacements d une figure de forme invariable assujettie a quatre conditions." Professor Mannheim here shows how the above plane repre sentation might also have been deduced from the instructive geometrical theory which he had brought before the Academy of Sciences on several occasions. 46 THE THEORY OF SCREWS. Eliminating 6 between the equations for z and p, we obtain [50- Let p and z be regarded as the current co-ordinates of a point. Then the locus of this point is the circle which forms the foundation of the plane representation*. 7?i is, of course, the radius, and p is the distance of the centre from a certain axis. Any point on this circle being given, then its co-ordinates p and z are completely determined. Thus sin 20 and cos 20, and, consequently, tan 0, are known. We therefore see that the position of a screw and its pitch are completely determined when the corresponding point on the circle is known. To each point of the circle corresponds one screw on the cylin- droid. To each screw on the cylindroid corresponds one point on the circle. This may be termed the representative circle of the cylindroid. 51. The Axis of Pitch. Let T (fig. ">) be the origin. Then p Q is the perpendicular ST from the centre 8 of the circle to the axis PT. The ordinate AP is the pitch of the P T Fig. 5. * The following elegant construction for the cylindroid is given by Mr T. C. Lewis, Messenger of Mathematics, Vol. ix. pp. 15, 1879. " Suppose that a point P moves with uniform velocity around a circle while the circle itself rotates uniformly about an axis in its plane with half the angular velocity that P has around the centre. Then the perpendiculars from P on the axis of rotation trace out the cylindroid, while the lengths of those perpendiculars are the pitches of the corresponding screws." This construction is of special interest in connexion with the represen tation of the cylindroid by a circle discussed in this chapter. The construction of Mr Lewis shows that if the circle rotate around the axis of pitch with half the angular velocity of the point P around the circle, then not only does P represent the screw in this circle but the perpendicular from P on the axis of pitch is the position of the screw itself. 52] THE REPRESENTATION OF THE CYLINDROID BY A CIRCLE. 47 screw, and the line PT may be called the axis of pitch. We have, accord ingly, the following theorem : The pitch of any screw on the cylindroid is equal to the perpendicular let fall on the axis of pitch from the corresponding point on the circle. A parallel A A to the axis of pitch cuts the circle in two points, A and A , which have equal pitch. The diameter perpendicular to the pitch axis intersects the circle in the points U, V of maximum and minimum pitch. These points, of course, correspond to the two principal screws on the cylin droid. The two screws of zero pitch are defined by the two real or imaginary points in which the axis of pitch cuts the circle. A fundamental law of the pitch distribution on the several screws of a cylindroid is simply illustrated by this geometrical representation. The law states that if all the pitches be augmented by a constant addition, the pitches so modified will still be a possible distribution. So far as the cylindroid is concerned, such a change would only mean a transference of the axis of pitch to some other parallel position. The diameter 2m merely expresses the size of the cylindroid, and is, of course, independent of the constant part in the expression of the pitch. 52. The Distance between two Screws. We shall often find it convenient to refer to a screw as simply equivalent to its corresponding point on the circle. Thus, in fig. 6, the two points, A and B, may conveniently be called the screws A and B. The propriety of this language will be admitted when it is found that everything about a 48 THE THEORY OF SCREWS. [52- screw can be ascertained from the position of its corresponding point on the circle. Let us, for instance, seek the shortest distance between the two screws A and J5. Since all screws intersect the nodal axis of the cylindroid at right angles, the required shortest distance is simply the difference between the values of m sin 20 for the two screws : this is, of course, the difference of their abscissae, i.e. the length PQ. Hence we have the following theorem : The shortest distance between two screws, A and B, is equal to the pro jection of the chord AB on the axis of pitch. We thus see that every screw A on the cylindroid must be intersected by another screw A, and the chord A A is, of course, perpendicular to the axis of pitch. The ray through S, parallel to the axis of pitch, will give two screws, L and M. These are the bounding screws of the cylindroid, and in each a pair of intersecting screws have become coincident. The two principal screws, U and V, lying on a diameter perpendicular to the axis of pitch, must also intersect. If all the pitches be reduced by p , then the pitch axis passes through the centre of the circle, and the case assumes a simple type. The extremities of a chord perpendicular to the axis of pitch define screws of equal and opposite pitches, and every pair of such screws must intersect. The screws of zero pitch will then be the bounding screws, while the two principal screws will have pitches +m and m, respectively. 53. The Angle between two Screws. This important function also admits of simple representation by the corresponding circle. Let A, B (fig. 7) denote the two screws; then, if 6 and 6 be the angles corresponding to A and B, AST =26; B8T=28 , whence ASB = 2(8- 6 }. If IT be any point on the circle, then AHB = 0-8 , and we deduce the following theorem : The angle between two screws is equal to the angle subtended in the circle by their chord. The extremities of a diameter denote a pair of screws at right angles: thus, A , in fig. 7, is the one screw on the cylindroid which is at right angles to A. The principal screws, f/"aud V, are also seen to be at right angles. 54] THE REPRESENTATION OF THE CYLINDROID BY A CIRCLE. 49 The circular representation of the cylindroid is now complete. We see how the pitch of each screw is given, and how the perpendicular distance and the angle between every pair of screws can be concisely represented. We may therefore study the dynamical and kinematical properties of the cylindroid by its representative circle. We commence by proving a funda mental principle very analogous to an elementary theorem in Statics. 54. The Triangle of Twists. It has been already shown ( 14) that any three screws on the cylindroid possess the following property : If a body receive twists about three screws, so that the amplitude of each twist is proportional to the sine of the angle between the two non- corresponding screws, the body, after the last twist, will be restored to where it was before the first. With the circular representation of the cylindroid we transform this theorem into the following: If any three screws, A, B, C (Fig. 8), be taken on the circle, and if twists be applied to a body in succession, so that the amplitude of each twist is proportional to the opposite side of the triangle ABC, then the body will be restored by the last twist to the place it had before the first. From the analogy of wrenches, and of twist velocities to twists, we are also able to enunciate the following theorems : If wrenches upon the three screws A, B, C be applied to any rigid body, then these wrenches will equilibrate, provided that the intensity of each is proportional to the opposite side of the triangle. 50 THE THEORY OF SCREWS. [54- If twist velocities about the three screws A, B, C animate a rigid body, then these twist velocities will neutralize if they are respectively proportional to the opposite sides of the triangle. 55. Decomposition of Twists and Wrenches. The theorems we have just enunciated lead to simple rules for effecting the composition, or the decomposition of twists or of wrenches. Let a twist on a screw X be given, and let it be required to find the components of this twist on any two given screws A, B, all three, of course, lying on the same cylindroid. Let o be the amplitude of the twist on X. Then, by the last article, the following triad of twists on the screws X, A, B, respectively, will neutralize : BX AX w > "AB "AB whence the components on A a,nd B of the twist about X are, so far as magnitudes are concerned, AX and "AS A similar proposition holds of course for wrenches. 56. Composition of Twists and Wrenches. Let two twists, of amplitudes a and /3, about the screws A and B, respec tively, be applied to a rigid body. It is required to find the single resultant screw X, and the amplitude CD of the resulting twist. Divide AB (Fig. 9) in the point /, so that the segments AI and BI shall be in the inverse ratio of a to /3. Bisect the arc AB at H, and draw HI, which will cut the circle in the required point X. The value of &&gt; is obtained from the equations 58] THE REPRESENTATION OF THE CYLINDROID BY A CIRCLE. 51 If the amplitudes a and /3 had opposite signs, then the point / should have divided AB externally in the given ratio. 57. Screw Co-ordinates. We have developed in the last chapter the general conception of Screw Co-ordinates. In the case of the cylindroid, the co-ordinates of any screw X, with respect to two standard scresvs A and B, are found by resolving a wrench of unit intensity on X into its two components on A and B. These components are said to be the co-ordinates of the screw. If we denote the co-ordinates of X by X l and X 2 , we have ^BX = AX l ~AB ~~ AB The co ordinates satisfy the identical relation, where e denotes the angle between the two screws of reference, that is, the angle subtended by the chord AB. 58. Reciprocal Screws. Every screw A on the cylindroid has one other reciprocal screw B tying also on the cylindroid ( 26). Denoting as usual A and B by their corre sponding points on the circle, we may enunciate the following theorem : The chord joining a pair of reciprocal screws passes through the pole of the axis of pitch. The condition that two screws shall be reciprocal is (p a -I- pft) cos 6 d af } sin = 0, where p a and p^ are the pitches, 6 is the angle between the two screws, and d^ their shortest distance. It is easy to show that this condition is fulfilled for any two screws A and B (Fig. 10), whose chord passes through 0, the pole of the axis of pitch PQ. 42 52 THE THEORY OF SCREWS. [58- Since SO . ST = >SM 2 = SB 2 , we have Z STA = Z SAB, and z whence Z A TB is bisected by ST, and therefore Z A TP = \ Z 4 SB = 6 = Z B TQ. = z It follows that .4Pcos0 = PTs mO, since each is equal to the perpen dicular from P on A T. Similarly, BQ cos = QT sin ; whence ( A P + BQ) cos0-(PT + QT) sin = 0, which reduces to (p a + pi) cos 6 daft sin 6 = 0. The theorem has thus been proved. We have, therefore, a simple construction for finding the screw B reci procal to a given screw A. It is only necessary to join A to 0, the pole of the axis of pitch, and the point in which this cuts the circle again gives B the required reciprocal screw. We also notice that the two principal screws of the cylindroid are reci procal, inasmuch as their chord passes through 0. 59. Another Representation of the Pitch. We can obtain another geometrical expression for the pitch, which will be often more convenient than the perpendicular distance from the point to the axis of pitch. Let A (Fig. 11) be the point of which the pitch is required. Join AOB, draw AP perpendicular to the axis of pitch PT, and produce AP to 60] THE REPRESENTATION OF THE CYL1NDROID BY A CIRCLE. 53 intersect BT at E. Then, since is the pole of PT, the line PT bisects the angle ATE ( 58), and therefore AE must be bisected at P. From similar triangles, OB:AB:: OT : AE; whence, if p a be the pitch of A, arid, of course, equal to AP, or \AE, _AB.OT IP*- QB . But since the quadrilateral ASBT is inscribable in a circle, OT.OS = OA.OB; whence, eliminating OT, we have, finally, _ AO.AB Pa m<r : as OS is constant, we see that p a varies as AO . AB, whence the following theorem : If AB be any chord passing through 0, the pole of the axis of pitch, then the pitch of the screw A is proportional to the product AO . AB. 60. Pitches of Reciprocal Screws. It is known that the sum of the reciprocals of the pitches of a pair of reciprocal screws on the cylindroid is constant ( 40). This is also plain from the geometrical representation. For, since the triangles APT and BQT (Fig. 10) are similar, we have AP-.BQ:: TP : TQ :: OA :OB; 54 THE THEORY OF SCREWS. [60- whence is the centre of gravity of particles of masses and placed at A and B, respectively. From the known property of the centre of gravity, .1 1 /I Pa Pft \Pa but each of the terms on the left-hand side is unity, whence, as required, I 1- _?_ The second mode of representing the pitch also verifies this theorem. For since ( 59) AO.AB _BO.BA Pft ~ ~20S~ ; we have _AB> AB 2 .AO.BO p+pft- from which but OA . OB is constant for every chord through ; and, as OS is constant, it follows that the sum of the reciprocals of the pitches of two reciprocal screws on any cylindroid must be constant. 61. The Virtual Coefficient. Let A and B (Fig. 12) be the two screws. Let, as usual, be the pole of the axis of pitch PT. Let be the point in which the chord AB intersects OT the perpendicular drawn from to the axis of pitch, and let FT be the polar of , which is easily shown to be perpendicular to SO. From T let fall the perpendicular TF upon AT , and from let fall the perpendicular OG upon AB. As before ( 58), we have AT F = tT TF=e\ also, since ^SAO =^AT , and ^SAO = ^ATO, we must have ^SAO -^SAO = /.AT O 1 -^ATO, or Z OAG = z TAF- whence the triangles OA G and TAF are similar, and, consequently, (52] THE REPRESENTATION OF THE CYLINDROID BY A CIRCLE. 55 but, as in 58, we have (p a -TT + pp- TT ) cos - d aft sin = ; Fig. 12. whence the virtual coefficient is simply, AS OS and we have the following theorem : The virtual coefficient of any pair of screws varies as the perpendicular distance of their chord from the pole of the axis of pitch. We also notice that the line TF expresses the actual value of the virtual coefficient. The theorem of course includes, as a particular case, that property of reciprocal screws, which states that their chord passes through the pole of the axis of pitch ( 58). 62. Another Investigation of the Virtual Coefficient. It will be instructive to investigate the theorem of the last article by a different part of the theory. We shall commence with a proposition in ele mentary geometry. Let ABC (Fig. 13) be a triangle circumscribed by a circle, the lengths of the sides being, as usual, a, b, c. Draw tangents at A, B, C, and thus form the triangle XYZ. It can be readily shown that if masses a 2 , b", c" be placed 56 THE THEORY OF SCREWS. [62, at A, H, C, their centre of gravity must lie on the three lines AX, BY, GZ. These lines must therefore be concurrent at /, which is the centre of gravity of the three masses. Fig. 13. Let B Y intersect the circle again at H. Then, since AC is the polar of Y, the arc AC is divided harmonically at H and B: consequently the four points A, C, B, H subtend a harmonic pencil at any point on the circle. Let that point be B, then BC, BI, BA, BZ form a harmonic pencil ; hence CZ is cut harmonically, and consequently Z must be the centre of gravity of particles, + a? at A, + b 2 at B, and - c 2 at C. Suppose the axis of pitch to be drawn (it is not shown in the figure), and let h be the perpendicular let fall from Z on this axis, also let p lt p 2 , p 3 be the pitches of the screws A, B, C. Then, by a familiar property of the centre of gravity, we must have Pitf + p^ - p.? = (a? + b 3 - c 2 ) k = 2abh cos C. We shall take A, B as the two screws of reference, and if p, and p,, be the co ordinates of C with respect to A and B ; then, from the principles of screw co-ordinates ( 30), we have where W|3 is the virtual coefficient of A and B. In the present case we have _ a _b pl ~c p *~c whence and, finally, Pi 2 12 = h cos C. 63] THE REPRESENTATION OF THE CYLINDROID BY A CIRCLE. 57 The negative sign has no significance for our present purpose, and hence we have the following theorem : The virtual coefficient of two screws is equal to the cosine of the angle subtended by their chord, multiplied into the perpendicular from the pole of the chord on the axis of pitch. This is, perhaps, the most concise geometrical expression for the virtual coefficient. It vanishes if the perpendicular becomes zero, for then the chord must pass through the pole of the pitch axis, and the two screws be reciprocal. The cosine enters the expression in order that its evanescence, when 0= 90, may provide for the circumstance that the perpendicular is then infinite. This result is easily shown to be equivalent to that of the last article by the well-know ti theorem : If any two chords be drawn in a circle, then the cosine of the angle sub tended by the first chord, multiplied into the perpendicular distance from its pole to the second chord, is equal to the cosine of the angle subtended by the second chord, multiplied into the perpendicular from its pole to the first chord. It follows that the virtual coefficient must be equal to the perpendicular from the pole of the axis of pitch upon the chord joining the two screws, multiplied into the cosine of the augle in the arc cut off by the axis of pitch. This is the expression of 61, namely, nr AS OG 08 63. Application of Screw Co-ordinates. It will be useful to show how the geometrical form for the virtual coefficient is derived from the theory of screw co-ordinates. Let a }> 2 > and ft l} #> be the co-ordinates of two screws on the cylindroid ; then, if the screws of reference be reciprocal, the virtual coefficient is ( 37) Let A, B (Fig. 14) be the screws of reference, and let C and C be the two screws of which the virtual coefficient is required. Let PQ be the axis of pitch of which is the pole, then lies on AB, as the two screws of reference are reciprocal ( 58). As AB is divided harmonically at and H, we have AO : OB :: HA : HE :: AP : BQ :: p, : p 2 ; whence is the centre of gravity of masses , at A and B, respectively. 58 THE THEORY OF SCREWS. [63- If, therefore, AX, BY, OG be perpendiculars on CO , we have, from the principle of the centre of gravity, Fig. 14. or, p 2 AX + PI BY = ( Pl +PJ OG ; but, by a well-known property of the circle, if ra be the radius, 2mAX = AC . AC -, 2mBY = BC.BC - whence or P1 BC.BC + p.,AC.AG = 2m ( Pi + P ,) OG = m ~ ( 60), Ob BC_ BW_ AC_ pl +P - OG _ _ _ AB AB - AB AB~ m OS But, from the expressions for screw co-ordinates ( 57), this reduces to * The required expression has thus been demonstrated. We can give another proof of this theorem as follows : If the two screws of reference be reciprocal, and if p l and p 2 be the co ordinates of another screw, then it is known, from the theory of the co ordinates, that the virtual coefficients of this screw, with respect to the screws of reference, are p 1 p l and p.,p, respectively ( 37). Thus (Fig. 15) the virtual coefficient of X and A must be ( 57), BX 65] THE REPRESENTATION OF THE CVLINDRO1D BY A CIRCLE. 59 AO.AB but we know ( 59) p l whence the virtual coefficient is 280 AO.BX 2m sin A . AO OG = in 280 2SO OS as already determined. This is an instructive proof, besides being much shorter than the other methods. Fig. 15. Fig. 16. 64. Properties of the Virtual Coefficient. If the virtual coefficient be given then the chord envelopes a circle with its centre at the pole of the axis of pitch. Two screws can generally be found which have a given virtual coefficient with a given screw. Let A (Fig. lo) be a given screw, and X a variable screw ; then their virtual coefficient is proportional to OG, and therefore to the sine of A, that is, to the length BX. Thus, as X varies, its virtual coefficient with A varies proportionally to the distance of X from the fixed point B. 65. Another Construction for the Pitch. As the virtual coefficient of two coincident screws is equal to their pitch, we shall obtain another geometrical construction for the pitch by supposing two screws to coalesce. For (in Fig. 1C), let AG be the chord joining the two coincident screws, that is the tangent, then, from 61, we have for the pitch, OG m OS whence the following theorem : The pitch of any screw is proportional to the perpendicular on the tangent at the point let fall from the pole of the axis of pitch. 60 THE THEORY OF SCREWS. [66- 66. Screws of Zero Pitch. A screw of zero pitch is reciprocal to itself. The tangent at a point corresponding to a screw of zero pitch, being the chord joining two reciprocal screws, must pass through the pole of the axis of pitch. This is, of course, the same thing as to say that the axis of pitch intersects the circle in two screws, each of which has zero pitch. 67. A Special Case. We have supposed that the axis of pitch occupies any arbitrary position. Let us now assume that it is a tangent to the representative circle. This specialization of the general case could be produced by augmenting the pitches of all the screws on the cylindroid, by such a constant as shall make one of the two principal screws have zero pitch. The following properties of the screws on the cylindroid are then obvious : 1. There is only one screw of zero pitch, 0. 2. The pitches of all the other screws have the same sign. 3. The maximum pitch is double the radius. 4. The screw is reciprocal to every screw on the surface, arid this is the only case in which a screw on the cylindroid is reciprocal to every other screw thereon. 68. A Tangential Section of the Cylindroid*. Let the plane of section be the plane of the paper in Fig. 17, and let the plane contain one of the screws of zero pitch OA. Let OH be the projection of the nodal axis on the plane of the paper. Then OA being perpendicular to the nodal axis must be perpendicular to OH, Let P be the point where the second screw of zero pitch cuts the curve. Then since any ray through P and across AO, meets two screws of equal pitch, it must be perpendicular to the third screw which it also meets on the cylindroid ( 22). Hence PH is perpendicular to the screw through H, and as the latter lies in the normal plane through OH it follows that the angle at H is a right angle. Any chord perpendicular to AO must for the same reason intersect two screws of equal pitch, and therefore APHO must be a rectangle. If tangents be drawn at A and P intersecting at T, then it can be shown that any chord TLM through T cuts the ellipse in points L and M on two reciprocal screws. * For proofs of theorems in this article see a paper in the Transactions of the Royal Irish Academy, Vol. xxix. pp. 132 (1887). 68] THE REPRESENTATION OF THE CYLINDROID BY A CIRCLE. 61 If from any point X a perpendicular XR be let fall on AP, then the pitch of the screw through X is XR tan 6, where sin 6 is the eccentricity of the ellipse. Also 6 is the angle between the normal to the plane and the nodal axis. Fig. 17. Let two circles be described, one with the major axis of the ellipse as diameter and the other with the line joining the two foci as a diameter. Let ^i be the point in which the ordinate through X meets the first circle and X., be the point in which a ray drawn from X^ to the centre meets the second circle. Then this point X 2 on this inner circle will be exactly the circular representation of the screws on the cylindroid with which this chapter com menced. There is only one such circle, for the distance between the foci is the same for every tangential section, and so is the distance from the centre to the axis of pitch. CHAPTER VI. THE EQUILIBRIUM OF A RIGID BODY. 69. A Screw System. To specify with precision the nature of the freedom enjoyed by a rigid body, it is necessary to ascertain all the screws about which the constraints will permit the body to be twisted. When the attempt has been made for every screw in space, the results will give us all the information conceivable with reference to the freedom of the body, and also with reference to the constraints by which the movement may be hampered. Suppose that by these trials, n screws A 1} ... A n have been found about each of which the body can receive a twist. It is evident, without further trial, that twisting about an infinite number of other screws must also be possible (w>l): for suppose the body receive any n twists about A^, ... A n the position attained could have been reached by a twist about some single screw A. The body can therefore twist about A. Since the amplitudes of the n twists may have any magnitude (each not exceeding an infinitely small quantity), A is merely one of an infinite number of screws, about which twisting must be possible. All these screws, together with A,, ... A n , will in general form what we call a screw system of the nth, order. If it be found that the body cannot be twisted about any screw which does not belong to the screw system of the nth order, then the body is said to have freedom of the nth order. It is assumed that A lf ... A n are independent screws, i.e. not themselves members of a screw system of order lower than n. If this were the case, the screws about which the body could be twisted would only consist of the members of that lower screw system. Since the amplitudes of the n twists about AI, ... A n are arbitrary, it might be thought that there are n disposable quantities in the selection of a screw S from a screw system of the ?ith order. It is, however, obvious from 14 that the determination of the position and pitch of S depends only upon 69-72] THE EQUILIBRIUM OF A RIGID BODY. 63 the ratios of the amplitudes of the twists about A 1} ... A n and hence in the selection of a screw from the screw system of the nth order, we have n 1 disposable quantities. 70. Constraints. An essential feature of a system of constraints consists in the number of independent quantities which are necessary to specify the position of the body when displaced in conformity with the requirements of the constraints. That number which cannot be less than one, nor greater than six, is the order of the freedom. To each of the six orders of freedom a certain type of screw system is appropriate. The study of the six types of screw system as here defined is a problem of kinematics, but the statical and kinematical properties of screws are so interwoven that we derive great advantages by not attempting to relegate the statics and kinematics to different chapters. We shall not require any detailed examination of the constraints. Every conceivable condition of constraints must have been included when the six screw systems have been discussed in their most general form. Nor does it come within our scope, except on rare occasions, to specialize the enunciation of any problem, further than by mentioning the order of the freedom permitted to the body. 71. Screw Reciprocal to a System. If a screw X be reciprocal to n independent screws, A l} ... A n , of a screw system of order n, then X is reciprocal to every other screw A which belongs to the same screw system. For, by the property of the screw system, it appears that twists of appropriate amplitudes about A 1} ... A n , would compound into a twist about A. It follows ( 69) that wrenches on A l , ... A n , of appropriate intensities ( 30) compound into a wrench on A. Suppose these wrenches on A 1} ... A n> were applied to a body only free to twist about X, then since X is reciprocal to A lt ... A H , the equilibrium of the body would be undisturbed. The resultant wrench on A must therefore be incapable of moving the body, therefore A and X must be reciprocal. 72. The Reciprocal Screw System. All the screws which are reciprocal to a screw system P of order n constitute a screw system Q of order 6 n. This important theorem is thus proved : Since only one condition is necessary for a pair of screws to be reciprocal, it follows, from the last section, that if a screw X be reciprocal to P it will fulfil n conditions. The screw X has, therefore, 5 n elements still dis posable, and consequently (n < f>) an infinite number of screws Q can be 64 THE THEORY OF SCREWS. [72- found which are reciprocal to the screw system P. The theory of reciprocal screws will now prove that Q must really be a screw system of order 6 n. In the first place it is manifest that Q must be a screw system of some order, for if a body be capable of twisting about even six independent screws, it must be perfectly free. Here, however, if a body were able to twist about the infinite number of screws embodied in Q, it would still not be free, because it would remain in equilibrium, though acted upon by a wrench about any screw of P. It follows that Q can only denote the collection of screws about which a body can twist which has some definite order of freedom. It is easily seen that that number must be 6 n, for the number of constants disposable in the selection of a screw belonging to a screw system is one less than the order of the system ( 36). But we have seen that the constants disposable in the selection of X are 5 n, and, therefore, Q must be a screw system of order G - n. We thus see, that to any screw system P of order n corresponds a reciprocal screw system Q of order 6 n. Every screw of P is reciprocal to all the screws of Q, and vice versa. This theorem provides us with a definite test as to whether any given screw a is a member of the screw system P. Construct 6?i screws of the reciprocal system. If then a be reciprocal to these 6 n screws, a must in general belong to P. We thus have 6 n conditions to be satisfied by any screw when a member of a screw system of order n. 73. Equilibrium. If the screw system P expresses the freedom of a rigid body, then the body will remain in equilibrium though acted upon by a wrench on any screw of the reciprocal screw system Q. This is, perhaps, the most general theorem which can be enunciated with respect to the equilibrium of a rigid body. This theorem is thus proved : Suppose a wrench to act on a screw 77 belonging to Q. If the body does not continue at rest, let it commence to twist about a. We would thus have a wrench about rj disturbing a body which twists about a, but this is impossible, because a and ?; are reciprocal. In the same manner it may be shown that a body which is free to twist about all the screws of Q will not be disturbed by a wrench about any screw of P. Thus, of two reciprocal screw systems, each expresses the locus of a wrench which is unable to disturb a body free to twist about any screw of the other. 74. Reaction of Constraints. It also follows that the reactions of the constraints by which the move ments of a body are confined to twists about the screws of a system P can only be wrenches on the reciprocal screw system Q, for the reactions of the 76] THE EQUILIBRIUM OF A RIGID BODY. 65 constraints are only manifested by the success with which they resist the efforts of certain wrenches to disturb the equilibrium of the body. 75. Parameters of a Screw System. We next consider the number of parameters required to specify a screw system of the ?ith order often called for brevity an ?i-system. Since the system is defined when n screws are given, and since five data are required for each screw, it might be thought that on parameters would be necessary. It must be observed, however, that the given 5n data suffice not only for the purpose of defining the screw system but also for pointing out n special screws upon the screw system, and as the pointing out of each screw on the system requires n - 1 quantities ( 69), it follows that the number of parameters actually required to define the system is only 5n n (n 1) = n (6 n). This result has a very significant meaning in connexion with the theory of reciprocal screw systems P and Q. Assuming that the order of P is n, the order of Q is 6 n ; but the expression n (6 n) is unaltered by changing n into 6 n. It follows that the number of parameters necessary to specify a screw system is identical with the number necessary to specify its reciprocal screw system. This remark is chiefly of importance in connexion with the systems of the fourth and fifth orders, which are respectively the reciprocal systems of a cylindroid and a single screw. We are now assured that a collection of all the screws which are reciprocal to an arbitrary cylindroid can be nothing less than a screw system of the fourth order in its most general type, and also, that all the screws in space which are reciprocal to a single screw must form the most general type of a screw system of the fifth order. 76. Applications of Co-ordinates. If the co-ordinates of a screw satisfy n linear equations, the screw must belong to a screw system of the order 6 n. Let 77 be the screw, and let one of the equations be whence 77 must be reciprocal to the screw whose co-ordinates are pro portional to ^, . ~ 6 ,(37). Pi P* It follows that 77 must be reciprocal to n screws, and therefore belong to a screw system of order 6 n. Let a, /3, 7, B be for example four screws about which a body receives twists of amplitudes a , # , 7 , & . It is required to determine the screw p and B. 5 66 THE THEORY OF SCREWS. [76, the amplitude p of a twist about p which will produce the same effect as the four given twists. We have seen ( 37) that the twist about any screw a may be resolved in one way into six twists of amplitudes a a,, ... a 6 , on the six screws of reference ; we must therefore have p pe = a a,, + /3 @ + 77 fi + 8 8 6 , whence p and p l} ... p K can be found ( 35). A similar process will determine the co-ordinates of the resultant of any number of twists, and it follows from 12 that the resultant of any number of wrenches is to be found by equations of the same form. In ordinary mechanics, the conditions of equilibrium of any number of forces are six, viz. that each of the three forces, and each of the three couples, to which the system is equivalent shall vanish. In the present theory the conditions are likewise six, viz. that the intensity of each of the six wrenches on the screws of reference to which the given system is equivalent shall be zero. Any screw will belong to a system of the ?ith order if it be reciprocal to 6 n independent screws ; it follows that 6 n conditions must be fulfilled when n + 1 screws belong to a screw system of the nib. order. To determine these conditions we take the case of n 3, though the process is obviously general. Let a, /3, 7, & be the four screws, then since twists of amplitudes a, (3 , 7 , & neutralise, we must have p zero and hence the six equations a a, + /3 A + 77, + S S, = 0, &c. from any four of these equations the quantities a , /3 , 7 , S can be eliminated, and the result will be one of the three required conditions. It is noticeable that the 6 n conditions are often presented in the evanescence of a single function, just as the evanescence of the sine of an angle between a pair of straight lines embodies the two conditions necessary that the direction cosines of the lines coincide. The function is suggested by the following considerations : If n + 2 screws belong to a screw system of the (n + l)th order, twists of appropriate amplitudes about the screws neutralise. The amplitude of the twist about any one screw must be pro portional to a function of the co-ordinates of all the other screws. We thus see that the evanescence of one function must afford all that is necessary for n + 1 screws to belong to a screw system of the nth order.* * Philosophical Transactions, 1874, p. 23. 77] THE EQUILIBRIUM OF A RIGID BODY. 67 77. Remark on systems of Linear Equations. Let a right line be, as usual, represented by the two equations Ax + By + Cz + D = 0, There are here six independent constants involved, while a right line is completely defined by four constants. The fact of course is that these two equations not only determine the right line on which our attention is fixed, but they also determine two planes through that line. Four constants are needed for the straight line and one more for each of the planes, so that there are six constants in all. If we are concerned with the straight line only the intrusion of two superfluous constants is often inconvenient. We can remove them by first eliminating y and then x, thus giving the two equations the form We have here no more than the four constants P, Q, P , Q , which are indis pensable for the specification of the straight line. Of course it may be urged that these equations also represent two planes. No doubt they do, but the equation z = Px + Q is a plane parallel to the axis of y, which is absolutely determined when the straight line is known. The plane Aac+By+Cz + D = Q may represent any one of the pencil of planes which can be drawn through the straight line. Analogous considerations arise when the screws of an n-system are represented by a series of linear equations. We commence with the case of the two-system, in which of course the screws are limited to the generators of a cylindroid. Let 0j, 2 , ... 6 be the co-ordinates of a screw referred to any six screws of reference. Let these co-ordinates satisfy the four linear equations A,e, +A&+ +4 6 = 0, B& + B,0 2 + ... +B,0 B = 0, 0,6,+ <7 a 2 + ... + c\e c> = o, A0i + A& + ... + A0 8 = o, where AI, A, ..., B l , B 2 , ... G ly (7, and D 1} D.,, ... are constants. Then it is a fundamental part of the present Theory that the locus so defined is a cylindroid (| 76). 52 68 THE THEORY OF SCREWS. [77, 78 But it will be observed that there is here a mass of not fewer than 20 independent constants, while the cylindroid is itself completely defined by eight constants ( 75). The reason is that these four equations really each specify one screw, i.e. four screws in all, and as each screw needs five constants the presence of 20 constants is accounted for. But when it is the cylindroid alone that we desire to specify there is no occasion to know these four particular screws. All we want is the system of the fourth order which contains those screws. For the specification of the position of a screw in a four-system three constants are required. Thus the selection of four screws in a given four-system requires 12 constants. These subtracted from 20 leave just so many as are required for the cylindroid. This is of course the interpretation of the process of solving for 3 ,0 4 , r> , 6 in terms of 9 and 2 . We get 3 = P0, + Q0 2 6 4 = P 6, + Q 2 5 = P"0, + Q"0 2 ; 8 6 = P" 0, + Q "0 2 . Thus we find that the constants are now reduced to eight, which just serve to specify the cylindroid. An instructive case is presented in the case of the three-system. The three linear equations of the most general type contain 15 constants. But a three-system is defined by 9 constants ( 75). This is illustrated by solving the equations for 0. 2 , 4 , K in terms of 1; 3 , r ,, when we have 0, = P0, + Q0 3 + RB S , 4 = P B, + Q S + R0 5 , 6 = P"0, + Q"d, + R"0 5 . This symmetrical process is specially convenient when the screws of reference are six canonical co-reciprocals. The general theory may also be set down. An ?i-system of screws is defined by 6 n linear equations. These contain 5(6 n) = 30 5n constants. We can, however, solve for 6 n of the variables in terms of the remaining n. Thus we get 6 n equations, each of which has n constants, i.e. n (6 n) in all. This is just the number of constants necessary to specify an ?i-system. The original number in the equation 30 - 5n may be written n (6 - n) + (6 - n) (5 - n). The redundancy of (6 n) (5 n) expresses the number of constants necessary for specifying 6 n screws in a system of the (6 n)th order. CHAPTER VII. THE PRINCIPAL SCREWS OF INERTIA*. 78. Introduction. If a rigid body be free to rotate about a fixed point, then it is well known that an impulsive couple about an axis parallel to one of the principal axes which can be drawn through the point will make the body commence to rotate about that axis. Suppose that there was on one of the principal axes a screw ij with a very small pitch, then a twisting motion about 77 would closely resemble a simple rotation about the corresponding axis. An impul sive wrench on 77 (i.e. a wrench of great intensity acting for a small time) will reduce to a couple when compounded with the necessary reaction of the fixed point. If we now suppose the pitch of 77 to be evanescent, we may still assert that an impulsive wrench on it] of very great intensity will cause the body, if previously quiescent, to commence to twist about ?;. We have stated a familiar property of the principal axes in this indirect manner, for the purpose of showing that it is merely an extreme case for a body with freedom of the third order of the following general theorem : If a quiescent rigid body have freedom of the nth order, then n screws can always be found (but not generally more than n), such that if the body receive an impulsive wrench on any one of these screws, the body will commence to tiuist about the same screw. These n screws are of great significance in the present method of studying Dynamics, and they may be termed the principal screws of inertia. In the present chapter we shall prove the general theorem just stated, while in the chapters on the special orders of freedom we shall show how the principal screws of inertia are to be determined for each case. * Philosophical Transactions, 1874, p. 27. 70 THE THEORY OF SCREWS. [79- 79. Screws of Reference. We have now to define the group of six co-reciprocal screws ( 31) which are peculiarly adapted to serve as the screws of reference in Kinetic investi gations. Let be the centre of inertia of the rigid body, and let OA, OB, OC be the three principal axes through 0, while a, b, c are the corresponding radii of gyration. Then two screws along OA, viz. w l , &&gt; 2 , with pitches + a, a; two screws along OB, viz. o> 3 , &&gt; 4 , with pitches + b, b, and two along OC, viz. <y D , w 6) with pitches + c, c, are the co-reciprocal group which we shall employ. The group thus indicated form of course a set of canonical co-reciprocals ( 41). For convenience in writing the formulae, we shall often use p ly ... p 6 , to denote the pitches as before. We shall first prove that the six screws thus defined are the principal screws of inertia of the rigid body when perfectly free. Let the mass of the body be M, and let a great constant wrench on w, act for a short time e. The intensity of this wrench is &&gt;/ , and the moment of the couple is aw". We now consider the effect of the two portions of the wrench separately. The effect of the force &&gt;/ is to give the body a velocity of translation parallel to OA and equal to /? -rj / . The effect of the couple is to impart an angular velocity d^ about the axis OA. This angular velocity is easily determined. The effective force which must have acted upon a particle dm at a perpendicular distance r from OA is - dm. The sum of the moments of all these forces is e Mo? -~ . This quantity is equal to the moment of the given couple so that 60 Ma 2 - 1 = aw,", e &&gt; x The total effect of the wrench on w l is, therefore, to give the body a velocity of translation parallel to OA, and equal to T^WI", and also a velocity ff of rotation about OA equal to ^ &&gt;/ . These movements unite to form a twisting motion about a screw on OA, of which the pitch, found by dividing the velocity of translation by the velocity of rotation, is equal to a. This same quantity is however the pitch of eoj, and thus it is proved that an impulsive wrench on ^ will make the body commence to twist about w^. We shall in future represent ew" by the symbol &&gt;/", which is accordingly to express the intensity of the impulsive wrench. 81] THE PRINCIPAL SCREWS OF INERTIA. 7i 80. Impulsive Screws and Instantaneous Screws. If a free quiescent rigid body receive an impulsive wrench on a screw 77, the body will immediately commence to twist about an instantaneous screw a. The co-ordinates of a being given for the six screws of reference just denned, we now seek the coordinates of 77. The impulsive wrench on 77 of intensity 77 " is to be decomposed into com ponents of intensities tj "r} 1 , ... i} "rj 6 on ( l , ... w s . The component on co n will generate a twist velocity about o> H amounting to jL W M Pn but if a be the twist velocity about a which is finally produced, the expression just written must be equal to aa n , and hence we have the following useful result : If the co-ordinates of the instantaneous screw be proportional to a l} ... a fi> then the co-ordinates of the corresponding impulsive screw are proportional to 81. Conjugate Screws of Inertia. Let a be the instantaneous screw about which a quiescent body either free or constrained in any way will commence to twist in consequence of receiving an impulsive wrench on any screw whatever 77. Let ft be the instantaneous screw in like manner related to another impulsive screw We have to prove that if be reciprocal to a then shall 77 be reciprocal to j3. When the body receives an impulsive wrench on of intensity "" there is generally a simultaneous reaction of the constraints, which takes the form of an impulsive wrench of intensity ///" on a screw /*. The effect on the body is therefore the same as if the body had been free, but had received an impulsive wrench of which the component wrench on the first screw of reference had the intensity ^ "^ + p, "^ . This and the similar quantities will be proportional to the co-ordinates of the impulsive screw which had the body been perfectly free would have /3 as an instantaneous screw. These latter, as we have shown in 80, are proportional to p l /3 1 ,p.,@. i ...p 6 /3 6 . Hence it follows that, h being some quantity differing from zero, we have Multiplying the first of these equations by p^, the second by^oa^, &c. adding 72 THE THEORY OF SCREWS. [81 the six products and remembering that a and are reciprocal by hypothesis while a. and /* are reciprocal by the nature of the reactions of the constraints, we have The symmetry of this equation shows that in this case 77 must be reciprocal to ft. Hence we have the following theorem which is of fundamental import ance in the subject of the present volume. If a. be the instantaneous screw about which a quiescent rigid body either perfectly free or constrained in any manner whatever commences to twist in consequence of an impulsive wrench on some screw tj, and if ft be another instantaneous screw, similarly related to an impulsive screw , then whenever % is reciprocal to a we shall find that 77 is reciprocal to ft. When this relation is fulfilled the screws a and ft are said to be conjugate screws of inertia. 82. The Determination of the Impulsive Screw, corresponding to a given instantaneous screw, is a definite problem when the body is perfectly free. If, however, the body be constrained, we shall show that any screw selected from a certain screw system will, in general, fulfil the required condition. Let B lf ... B n _ n be 6 n screws selected from the screw system which is reciprocal to that corresponding to the freedom of the nth order possessed by the rigid body. Let S be the screw about which the body is to twist. Let X be any one of the screws, an impulsive wrench about which would make the body twist about S ; then any screw Y belonging to the screw system of the (7 - n)th order, specified by the screws, X, B 1} ... B 6 _ n is an impulsive screw, corresponding to S as an instantaneous screw. For the wrench on Y may be resolved into 7 n wrenches on X, B 1} ... B 6 _ n ; of these, all but the first are instantly destroyed by the reaction of the constraints, so that the wrench on Y is practically equivalent to the wrench on X, which, by hypo thesis, will make the body twist about S. As an example : if the body had freedom of the fifth order, then an impulsive wrench on any screw on a certain cylindroid will make the body commence to twist about a given screw. As another example : if a body have freedom of the third order, then the "locus" of an impulsive wrench which would make the body twist about a given screw consists of all the screws in space which are reciprocal to a certain cylindroid. 83. System of Conjugate Screws of Inertia. We shall now show that from the screw system of the nth order P, which expresses the freedom of the rigid body, generally n screws can be selected 84] THE PRINCIPAL SCREWS OF INERTIA. 73 so that every pair of them are conjugate screws of inertia (81). Let B l , &c. B 6 _ n be (6 n) screws defining the reciprocal screw system. Let A l be any screw belonging to P. Then in the choice of A l we have n 1 arbitrary quantities. Let 7 X be any impulsive screw corresponding to A l as an instan taneous screw. Choose A 2 reciprocal to 7 1( B 1} ... B s ^ n , then A l and A 2 are conjugate screws, and in the choice of the latter we have n 2 arbitrary quantities. Let /., be any impulsive screw corresponding to A 2 as an instan taneous screw. Choose A 3 reciprocal to I I , I 2 , B l} ... B 6 _ n , and proceed thus until A n has been attained, then each pair of the group A l} &c. A n are conjugate screws of inertia. The number of quantities which remain arbitrary in the choice of such a group amount to or exactly half the total number of arbitrary constants disposable in the selection of any n screws from a system of the nth order. 84. Principal Screws of Inertia. We have now to prove the important theorem in Dynamics which affirms the existence of n principal Screws of Inertia in a rigid body with n degrees of freedom. The proof that we shall give is, for the sake of convenience, enunciated with respect to the freedom of the third order, but the same method applies to each of the other degrees of freedom. Let 6 be one of the principal screws of inertia, then an impulsive wrench on must make the body commence to twist about 0. In the most general case when the body is submitted to constraint, the impulsive wrench on will of course be compounded with the reaction on some screw A, of the reciprocal system. The result will be to produce the impulsive wrench which would, if the body had been free, have generated an instantaneous twist velocity about 6. We thus have the following equations ( 80) where x and y are unknown : pA = uQi + yXi, Let a be one of the screws of the three-system in question. Then since X must be reciprocal to a we have by multiplying these equations respectively by pii, . .. p s ct 6 and adding, K = xp^e, + xp.a.,6, + . . . + xp ( &$. 74 THE THEORY OF SCREWS. In like manner if ft, 7 be two other screws of the three-system, A = xpijrfi -f But as 6 belongs to the three-system its co-ordinates must satisfy three linear equations. These we may take to be We have thus six linear equations in the co-ordinates of 0. We can therefore eliminate those co-ordinates, thus obtaining a determinantal equation which gives a cubic for x. The three roots of this cubic will give accordingly three screws in the three -system which possess the required property. Thus we demonstrate that in any three-system there are three principal screws of inertia, and a precisely similar proof for each of the six values of n establishes by induction the important theorem that there are n principal screws of inertia in the screw system of the ?ith order. It is shown in 86 that all the roots are real. We shall now prove that the Principal Screws of Inertia are co-reciprocal. Let and </> be two such screws, corresponding to different roots x, x" of the equation in x. Then we have , , , , , pi-x p-2 -m p t x Let /* be the screw of the reciprocal system on which the impulsive wrench is generated by the impulse given on 0. Then , y/*i , y^ , yn* <Pl = // , 0-J = - 7, , 06 = - 7, PI X p., x p 6 x As fi is reciprocal to and X is reciprocal to <f>, we have . , / T n Pi - % P* X ps-% , , // T ~77 "T ~r pi - as p. 2 -x p 6 - x Subtracting these equations and discarding the factor x x", we get __ "\ i i / f\ / i- x") ( ^ 2 - x )( p 2 - x") ( p 6 - x } ( p s - x"} 85] THE PRINCIPAL SCREWS OF INERTIA. 75 which is of course 2M4>i = ; whence 6 and </> are reciprocal, and the same being true for each pair of principal screws of inertia we thus learn that they form a co-reciprocal system. We can also show that each pair of the Principal Screws of Inertia are Conjugate Screws of Inertia. It is easy to see that x ^ Pi^-if^i x v Pi^iA 1 ! \ ~~i // ** i + 77 j2t - ~ = i , ^ & 1 ~- x PI x x x PI -~ x y p^ x \ As each of the terms on the left-hand side of this equation is zero, the expression on the right-hand is also zero, but this is equivalent to whence we show that 6 and </> are conjugate screws of inertia and the required theorem has been proved. 85. An algebraical Lemma. Let U and V be two homogeneous functions of the second degree in n variables. If either U or V be of such a character that it could be expressed by linear transformation as the sum of n squares, then the discriminant of U + \V when equated to zero gives an equation of the nth degree in \ of which all the roots are real *. Suppose that V can by linear transformation assume the form x 2 _j_ x 2 -\- x and adopt x ly x.,, ... x n as new variables, so that TT ,- /vi 2 i ft /-.i 2 i 9/f ** U Ct jjwj |~ Lv nJi *2 i~ ^i(rj2 l * / i t * 2 The discriminant of U+\V will, when equated to zero, give the equation for \, a n + X, a 12 , . . . a m j = 0, ; ft 2 i , $2-2 "I" * ^2i and the discriminant being an invariant the roots of this equation will be * A discussion is found in Zanchevsky, Theory of Screws and its application to Mechanics, Odessa, 1889. Mr G. Chawner has most kindly translated the Russian for me. 76 THE THEORY OF SCREWS. [85, the same as those of the original equation. The required theorem will therefore be proved if it can be shown that all the roots of this equation are real. That this is so is shown in Salmon s Modern Higher Algebra, Lesson VI.* 86. Another investigation of the Principal Screws of Inertia. The n Principal Screws of Inertia can also be investigated in the following fundamental manner by the help of Lagrange s equations of motion in generalized co-ordinates. Let . . . be the co-ordinates ( 95) of the impulsive screw. Let </>!,... < n be the co-ordinates of the body, then <j>i, ... <f> n will be the co-ordinates of the instantaneous screw, and from Lagrange s equations, _^ = dtdfj d$r where T is the kinetic energy and where P-$$i denotes the work done in a twist S< t against the wrench. If the screws of reference be co-reciprocal and if " be the intensity of a wrench on , then p, - 2^r&. As we are considering the action of only an impulsive wrench the effect of which is to generate a finite velocity in an infinitely small time we must have the acceleration infinitely great while the wrench is in action. The term , - is therefore negligible in comparison with - ( r ) and hence for the dfa dt \d<j)J impulsive motion -f d (dT\ *Wr?S We may regard i and " as both constant during the indefinitely small time e of operation of the impulsive wrench, whence ( 79) 2f 1 f" = ^. Pi cty, Hence replacing <fa l} ... (j> n by 6 lt ... B n we deduce the following ( 95, 96). If T be the kinetic energy of a body ivith freedom of the nth order, twisting about a screw 6 whose co-ordinates referred to any n co-reciprocals belonging to the system expressing the freedom are B l} ... n , then the co-ordinates * See also Williamson and Tarleton s Dynamics, 2nd edition, p. 457 (1889), and Kouth s Rigid Dynamics, Part II, p. 49 (1892). t Niven, Messenger of Math., May 1867, quoted by Bouth, Rigid Dynamics, Part I, pp. 327-8. 86] THE PRINCIPAL SCREWS OF INERTIA. 77 of an impulsive wrench by which the actual motion of the body could be produced are proportional to dT ^dT_ p l d0 1 " p n dd n The existence of n Principal Screws of Inertia can now be readily deduced, for suppose that l dT l dT where X is an unknown factor. If then we make T = a u 0!~ + a<v>Q>? + 2,a K 0i0<> . . . we have an equation of the nth degree for X as follows : tt-ia , . . . a^n =: " Ct n i , Gt n2 > &nn It is essential to note that T is A function of such a character that by linear transformation it can be expressed as the sum of n squares, for suppose it could be expressed as it would be possible to find a real screw which made H 1} H 2 , ... II n -i each zero, and then the kinetic energy of the body twisting about that screw would be negative. Of course this is impossible. Hence we deduce from 85 the important principle that all the Principal Screws of Inertia are real. If the equation had a repeated root the number of Principal Screws of Inertia is infinite. We take n = 4f, but the argument applies to 3 and 2 also. (There can be no repeated root when n is either 5 or 6. See chaps. XVII. and XVIII.) We can choose variables such that T becomes and the pitch X becomes simultaneously If therefore the discriminant of T + \p, equated to zero, has a pair of equal values for X, we must have a condition like Take any screw of the system for which ;i = 0, # 4 = 0, then T = M 6* (1*1*0!* + ii*0.?), P= p , or T= p. Pl 78 THE THEORY OF SCREWS. [86- Hence we find that for all screws on the cylindroid represented by 6 l} 2 , 0, the energy will vary as the pitch when the twist velocity remains the same. It appears from the representation of the Dynamical problem in chap. XII. that in this case all the screws of the cylindroid O lt 2 , 0, must be principal screws of Inertia. The number of principal screws of inertia is therefore infinite in this case. (See Routh s Theorem, Appendix, Note 2.) 87. Enumeration of Constants. It is the object of this article to show that there are sufficient constants available to permit us to select from the screw system of the ?ith order expressing the freedom of a rigid body, one group of n screws, of which every pair are both conjugate and reciprocal, and that these constitute the principal screws of inertia ( 78). To prove this, it is sufficient to show that when half the available con stants have been disposed of in making the n screws conjugate (81) the other half admit of adjustment so as to make the screws also co-reciprocal. Choose A! reciprocal to B lt ... B 6 _ n , with n - 1 arbitrary quantities; A z reciprocal to A ly B^, ... B K _ n> with n 2 arbitrary quantities, and so on, then the total number of arbitrary quantities in the choice of n co-reciprocal screws from a system of the ?ith order is n(n 1) n-l + w-2... +1= -y . Hence, by suitable disposition of the n(n 1) constants it might be anticipated that we can find at least one group of n screws which are both conjugate and co-reciprocal. We have now to show that these screws would be the principal screws of inertia ( 78). We shall state the argument for the freedom of the third order, the argument for any other order being precisely similar. Let AI, A 2 , A 3 be the three conjugate and co-reciprocal screws which can be selected from a system of the third order. Let B lt B. 2 , B 3 be any three screws belonging to the reciprocal screw system. Let R lt R y , R. } be any three impulsive screws corresponding respectively to A l} A z , A 2 as instantaneous screws. An impulsive wrench on any screw belonging to the screw system of the 4th order defined by R lt B l} B z , B 3 will make the body twist about A, ( 82), but the screws of such a system are reciprocal to A 2 and A a ; for since A l and A z are conjugate, R l must be reciprocal to A z ( 81), and also to A 3 , since A^ and A 3 are conjugate. It follows from this that an impulsive wrench on any screw reciprocal to A 2 and A 3 will make the body commence to twist about A lt but A l is itself reciprocal to A 3 and A a , and hence an impulsive wrench THE PRINCIPAL SCREWS OF INERTIA. 79 on A 1 will make the body commence to twist about 4,. Hence A l and also A. 2 and A 3 are principal screws of inertia. We shall now show that with the exception of the ?? screws here deter mined, generally no other screw possesses the property. Suppose another screw S were to possess this property. Decompose the wrench on S into n wrenches of intensities S", ... S n " on A lt ... A n ; this must be possible, because if the body is to be capable of twisting about S this screw must belong to the system specified by A lt ... A n . The n impulsive wrenches on A lt ... A n will produce twisting motions about the same screws, but these twisting motions are to compound into a twisting motion on S. It follows that the component twist velocities $ ... <S n must be proportional to the intensities $/ , ... S n ". But if this were the case, then every screw of the system would be a principal screw of inertia ; for let X be any impulsive screw of the system, and suppose that Y is the corresponding instantaneous screw, the components of X on A lt ... A nt have intensities X", ... X n ", these will generate twist velocities equal to c* C Q! y n *-*M -y II -~-jj A. i , . . . // -A- n > Of and these quantities must equal the components of the twist velocity about Y. But the ratios are all equal, and hence the twist velocities of the components on the screws of reference of the twisting motion about Y must be proportional to the intensities of the components on the same screws of reference of the wrench on X. Remembering that twisting motions and wrenches are compounded by the same rules, it follows that Y and X must be identical. As it is not generally true that all the screws of the system defining the freedom possess the property enjoyed by a principal screw of inertia, it follows that the number of principal screws of inertia must be generally equal to the order of the freedom. 88. Kinetic Energy. The twisting motion of a rigid body with freedom of the nth order may be completely specified by the twist velocities of the components of the twisting motion on any n screws of the system defining the freedom. If the screws of reference be a set of conjugate screws of inertia, the expression for the kinetic energy of the body consists of n square terms. This will now be proved. If a free or constrained rigid body be at rest in a position L, and if the 80 THE THEORY OF SCREWS. [88- body receive an impulsive wrench, the body will commence to twist about a screw a with a kinetic energy E a . Let us now suppose that a second impulsive wrench acts upon the body on a screw /*, and that if the body had been at rest in the position L, it would have commenced to twist about a screw /?, with a kinetic energy E$. We are to consider how the amount of energy acquired by the second impulse is affected by the circumstance that the body is then not at rest in L, but is moving through L in consequence of the former impulse. The amount will in general differ from Ep, for the movement of the body may cause it to do work against the wrench on JJL during the short time that it acts, so that not only will the body thus expend some of the kinetic energy which it previously possessed, but the efficiency of the impulsive wrench on /A will be diminished. Under other circumstances the motion through A might be of such a character that the impulsive wrench on p acting for a given time would impart to the body a larger amount of kinetic energy than if the body were at rest. Between these two cases must lie the intermediate one in which the kinetic energy imparted is precisely the same as if the body had been at rest. It is obvious that this will happen if each point of the body at which the forces of the impulsive wrench are applied be moving in a direction perpendicular to the corresponding force, or more generally if the screw a. about which the body is twisting be reciprocal to /A. When this is the case a and ft must be conjugate screws of inertia ( 81), and hence we infer the following theorem : If the kinetic energy of a body twisting about a screw a with a certain twist velocity be E a , and if the kinetic energy of the same body twisting about a screw /3 with a certain twist velocity be Ep, then when the body has a motion compounded of the two twisting movements, its kinetic energy will amount to E a + Ep provided that a and /3 are conjugate screws of inertia. Since this result may be extended to any number of conjugate screws of inertia, and since the terms E a , &c., are essentially positive, the required theorem has been proved. 89. Expression for Kinetic Energy. If a rigid body have a twisting motion about a screw a, with a twist velocity a, what is the expression of its kinetic energy in terms of the co-ordinates of a ? We adopt as the unit of force that force which acting upon the unit of mass for the unit of time will give the body a velocity which would carry it over the unit of distance in the unit of time. The unit of energy is the work done by the unit force in moving over the unit distance. If, therefore, 90] THE PRINCIPAL SCREWS OF INERTIA. 81 a body of mass M have a movement of translation with a velocity v its kinetic energy expressed in these units is The movement is to be decomposed into twisting motions about the screws of reference ta l , &c. <o 6 , the twist velocity of the component on w n being do,,. One constituent of the twisting motion about <a m consists of a velocity of translation equal to dp n a n , and on this account the body has a kinetic energy equal to ^Ma 2 p n 2 a n -. On account of the rotation around the axis with an angular velocity aa n the body has a kinetic energy equal to 1/J2/V 2 j r2fj m 2 Lin I / (C///6 where r denotes the perpendicular from the element dM on co m . Remembering that p m is the radius of gyration this expression also reduces to ^Ma?p m *a m 2 , and hence the total kinetic energy of the twisting motion about w m is Ma?p n *Qi n ~. We see, therefore ( 88), that the kinetic energy due to the twisting motion about a is The quantity inside the bracket is the square of a certain linear mag nitude which is determined by the distribution of the material of the body with respect to the screw a. It will facilitate the kinetic applications of the present theory to employ the symbol u a to denote this quantity. It is then to be understood that the kinetic energy of a body of mass M, animated by a twisting motion about the screw a with a twist velocity a, is represented by 90. Twist Velocity acquired by an Impulsive Wrench. A body of mass M, which is only free to twist about a screw a, is acted upon by an impulsive wrench of intensity ij" on a screw 77. It is required to find the twist velocity d which is acquired. The initial reaction of the constraints is an impulsive wrench of intensity X" on a screw X. Then the body moves as if it were free, but had been acted upon by an impulsive wrench of which the component on &&gt; m had the intensity This component would generate a velocity of translation parallel to <a n and equal to ^ W^n + X^X,,). The twist velocity about &&gt; produced by this component is found by dividing the velocity of translation by p n . On the B. 82 THE THEORY OF SCREWS. [90- other hand, since the co-ordinates of the screw a are a 1; ... 6 , the twist velocity about <u n may also be represented by ay n ( 34), whence Iiii r\ If we multiply this equation by p n 2 w , add the six equations found by giving n all values from 1 to 6, and remember that a and X are reciprocal, we have ( 39) ftua z = M -n"^a\ whence a is determined. This expression shows that the twist velocity produced by an impulsive wrench on a given rigid body constrained to twist about a given screw, varies directly as the virtual coefficient and the intensity of the impulsive wrench, and inversely as the square of u a . (See Appendix, Note 3.) 91. The Kinetic Energy acquired by an Impulsive Wrench can be easily found by 89 ; for, from the last equation, 1///0 fj ^ Mr/I ll 2 - __ - _ 7TT - (Ua ~ M ?C "" hence the kinetic energy produced by the action of an impulsive wrench on a body constrained to twist about a given screw varies directly as the product of the square of the virtual coefficient of the two screws and the square of the intensity of the impulsive wrench, and inversely as the square of u a . 92. Formula for a free body. We shall now express the kinetic energy communicated by the impulsive wrench on TJ to the body when perfectly free. The component on eo n of intensity r!"t] n imparts a kinetic energy equal to ///o whence the total kinetic energy is found by adding these six terms. The difference between the kinetic energy acquired when the body is perfectly free, and when the body is constrained to twist about a, is equal to The quantity inside the bracket reduces to the sum of 15 square terms, of which (>!! 770 j9 2 02?7i) 2 is a specimen. The entire expression being therefore essentially positive shows that a given impulsive wrench imparts greater energy to a quiescent body when free than to the same quiescent body when constrained to twist about a certain screw. 95j THE PRINCIPAL SCREWS OF INERTIA. 83 93. Lemma. If a group of instantaneous screws belong to a system of the rath order, then the body being quite free the corresponding group of impulsive screws also belong to a system of the nth order ; for, suppose that n + 1 twisting motions about n + 1 screws neutralise, then the corresponding n + 1 im pulsive wrenches must equilibrate, but this would not be possible unless all the impulsive screws belonged to a screw system of the ?ith order. 94. Euler s Theorem. If a free or constrained rigid body is acted upon by an impulsive wrench, the body will commence to move with a larger kinetic energy when it is permitted to select its own instantaneous screw from the screw system P defining the freedom, than it would have acquired, had it been arbitrarily restricted to any other screw of the system. Let Q be the reciprocal system of the (6 w)th order, and let P be the screw system of the nth order, consisting of those impulsive screws which, if the body were free, would correspond to the screws of P as instantaneous screws. Let i) be any screw on which the body receives an impulsive wrench. De compose this wrench into components on a system of six screws consisting of any n screws from P , and any 6 n screws from Q. The latter are neutralised by the reactions of the constraints, and may be omitted, while the former com pound into one wrench on a screw belonging to P ; we may therefore replace the given wrench by a wrench on , If the body were perfectly free, an impulsive wrench on must make the body twist about some screw a on P. In the present case, although the body is not perfectly free, yet it is free so far as twisting about a is concerned, and we may therefore, with reference to this particular impulse about ", consider the body as being perfectly free. It follows from 92 that there would be a loss of energy if the body were compelled to twist about any screw other than a, which is the one it naturally chooses. 95. Co-ordinates in a Screw System. The co-ordinates of a screw belonging to a specified screw-system can be greatly simplified by taking n co-reciprocal screws belonging to the given screw system as a portion of the six screws of reference. The remaining 6 n screws of reference must then belong to the reciprocal screw system. It follows that out of the six co-ordinates a l} ... a tt of a screw a, which belongs to the system, 6 n are actually zero. Thus we are enabled to give the more general definition of screw co-ordinates which is now enunciated. If a wrench, of which the intensity is one unit on a screw a, which belongs to 62 84 THE THEORY OF SCREWS. [95- a certain screw system of the nth order, be decomposed into n wrenches of intensities a 1} ... a n on n co-reciprocal screws belonging to the same screw system, then the n quantities a 1} . . . ^ are said to be the co-ordinates of the screw a. Thus the pitch of a will be represented by p^ + . . . + p n a n *. The virtual coefficient of a and /3 will be (p&fa + ... +p n <*n@n)- We may here remark that in general one screw can be found upon a screw system of the wth order reciprocal to n 1 given screws of the same system. For, take 6 n screws of the reciprocal screw system, then the required screw is reciprocal to 6 n + n 1 = 5 known screws, and is therefore determined ( 25). 96. The Reduced Wrench. A wrench which acts upon a constrained rigid body may in general be replaced by a wrench on a screiu belonging to the screw system, which defines the freedom of the body. Take n screws from the screw system of the ?ith order which defines the freedom, and 6 n screws from the reciprocal system. Decompose the given wrench into components on these six screws. The component wrenches on the reciprocal system are neutralized by the reactions of the constraints, and may be discarded, while the remainder must compound into a wrench on the given screw system. Whenever a given external wrench is replaced by an equivalent wrench upon a screw of the system which defines the freedom of the body, the latter may be termed, for convenience, the reduced wrench. It will be observed, that although the reduced wrench can be determined from the given wrench, that the converse problem is indeterminate (n < 6). We may state this result in a somewhat different manner. A given wrench can in general be resolved into two wrenches one on a screw of any given system, and the other on a screw of the reciprocal screw system. The former of these is what we denote by the reduced wrench. This theorem of the reduced wrench ceases to be true in the case when the screw system and the reciprocal screw system have one screw in common. As such a screw must be reciprocal to both systems it follows that all the screws of both systems must be comprised in a single five-system. This is obviously a very special case, but whenever the condition indicated is satisfied it will not be possible to resolve an impulsive wrench into components on the two reciprocal systems, unless it should also happen that the impulsive wrench itself belongs to the five-system*. * I am indebted to Mr Alex. M c Aulay for having pointed out in his book on Octonions, p. 251, that I had overlooked this exception when enunciating the Theorem of the reduced wrench in the Theory of Screws (1876). 97] THE PRINCIPAL SCREWS OF INERTIA. 85 97. Co-ordinates of Impulsive and Instantaneous Screws. Taking as screws of reference the n principal screws of inertia ( 84), we re quire to ascertain the relation between the co-ordinates of a reduced impulsive wrench and the co-ordinates of the corresponding instantaneous screw. If the co-ordinates of the reduced impulsive wrench are v\" , ...r} n ", and those of the twist velocity are a l} d 2> ... a n , then, remembering the property of a principal screw of inertia ( 78), and denoting by u l} ... u n , the values of the magnitude u ( 89) for the principal screws of inertia, we have, from 90, ^ = M^" whence observing that d l = dot 1 ; ... a n = da n we deduce the following theorem, which is the generalization of 80. If a quiescent rigid body, which has freedom of the nth order, commence to twist about a screw a, of which the co-ordinates, with respect to the principal screws of inertia, are a lt ... a n and if p 1} ... p n be the pitches, and iii, ... u n the constants defined, in 89, of the principal screws of inertia, then the co-ordinates of the reduced impulsive wrench are proportional to U,* U n * !, ... a n . PI Pn Let T denote the kinetic energy of the body of mass M when animated by a twisting motion about the screw a, with a twist velocity a. Let the twist velocities of the components on any n conjugate screws of inertia be denoted by a,, a 2 , ... d n . [These screws will not be co-reciprocal unless in the special case where they are the principal screws of inertia.] It follows ( 88) that the kinetic energy will be the sum of the n several kinetic energies due to each component twisting motion. Hence we have ( 89) T = Mufa? + . . . + and also u a * = u? a, 3 + . . . + u n 2 a 2 . Let i, ... a n and /3 1( ... /3 7i , be the co-ordinates of any two screws belong ing to a screw system of the ?ith order, referred to any n conjugate screws of inertia, whether co-reciprocal or not, belonging to the same screw system, then the condition that a and /3 should be conjugate screws of inertia is Mi a a x ft + . . . + ujttnpn = 0. To prove this, take the case of n = 4, and let A, B, C, D be the four screws of reference, and let A l} ... A s be the co-ordinates of A with respect to the six principal screws of inertia of the body when free ( 79). The unit wrench on a is to be resolved into four wrenches of intensities cti, ... a 4 on A, B, C, D: each of these components is again to be resolved into six wrenches on the 86 THE THEORY OF SCREWS. [97, 98 screws of reference. The six co-ordinates of a, with respect to the same screws, are therefore A^j, + B 1 a 2 + Ojttg + D^t, A^ + B 6 a, + C We can now express the condition that a and /3 are conjugate screws of inertia. This condition is ( 81) Sp! 2 (A lttl + B^, + 0,0, + A4> (A& + B& + C& + A/3 4 ) - 0. Denoting pfAf + ... +p 6 A/ by uf y and observing that S l p 1 2 A l B 1 and similar expressions are zero, we deduce A similar proof may be written down for each of the remaining degrees of freedom. CHAPTER VIII. THE POTENTIAL. 98. The Potential. Suppose a rigid body which possesses freedom of the ?tth order be sub mitted to a system of forces. Let the symbol define a position of the body from which the forces would be unable to disturb it. By a twist of amplitude & about a screw belonging to the screw system, the body may be displaced from to an adjacent position P, the energy consumed in making the twist being denoted by the Potential V, and no kinetic energy being supposed to be acquired. The same energy would be required, whatever be the route by which the movement is made from to P. So far as we are at present concerned V varies only with the changes of the position of P with respect to 0. The most natural co-ordinates by which the position P can be specified with respect to are the co-ordinates of the twist ( 32) by which the movement from to P could be effected. In general these co-ordinates will be six in number; but if n of the screws of reference be selected from the screw system defining the freedom of the body, then ( 95) there will be only n co-ordinates required, and these may be denoted by 0i, ... &n. The Potential V must therefore depend only upon certain quantities independent of the position and upon the n co-ordinates #/, . . . n ; and since these are small, it will be assumed that V must be capable of development in a series of ascending powers and products of the co-ordinates, whence we may write + terms of the second and higher orders, where H, H 1} ... H n are constants, in so far as different displacements are concerned. In the first place, it is manifest that H = ; because if no displacement be made, no energy is consumed. In the second place, H l , ... H n must also be each zero, because the position is one of equilibrium ; and therefore, 88 THE THEORY OF SCREWS. [98- by the principle of virtual velocities, the work done by small twists about the screws of reference must be zero, as far as the first power of small quantities is concerned. Finally, neglecting all terms above the second order, on account of their minuteness, we see that the function V, which expresses the potential energy of a small displacement from a position of equilibrium, is generally a homogeneous function of the second degree of the n co-ordinates, by which the displacement is defined. 99. The Wrench evoked by Displacement. When the body has been displaced to P, the forces no longer equilibrate. They have now a certain resultant wrench. We propose to determine, by the aid of the function V, the co-ordinates of this wrench, or, more strictly, the co-ordinates of the equivalent reduced wrench ( 96) upon a screw of the system, by which the freedom of the body is defined. If, in making the displacement, work has been done by the agent which moved the body, then the equilibrium of the body was stable when in the position 0, so far as this displacement was concerned. Let the displacement screw be 0, and let a reduced wrench be evoked on a screw rj of the system, while the intensities of the components on the screws of reference are *7i"j W- Suppose that the body be displaced from P to an excessively close position P , the co-ordinates of P , with respect to 0, being ( 95) 0i + 861, . . . n + 80 n . The potential V of the position P is it being understood that 861, ... 80 n are infinitely small magnitudes of a higher order than #/, . . . n . The work done in forcing the body to move from P to P is V V. This must be equal to the work done in the twists about the screws of reference whose amplitudes are S0/, . . . 80 n , by the wrenches on the screws of reference whose intensities are T?/ , ... rj n ". As the screws of reference are co-reciprocal, this work will be equal to ( 33) + 2r h "p 1 80 1 +... + 2r Jn "pn80 n - Since the expression just written must be equal to V V for every position P in the immediate vicinity of P, we must have the coefficients of 80i, ... 80 n equal in the two expressions, whence we have n equations, of which the first is "_ JL d l 7/1 : + 2 PI d0\ Hence, we deduce the following useful theorem : 100] THE POTENTIAL. 89 If a free or constrained rigid body be displaced from a position of equi librium by twists of small amplitudes, #, , ... # , about n co-reciprocal screws of reference, and if V denote the work done in producing this movement, then the reduced wrench has, for components on the screws of reference, wrenches of which the intensities are found by dividing twice the pitch of the corresponding reference screw into the differential coefficient of V with respect to the corresponding amplitude, and changing the sign of the quotient. It is here interesting to notice that the co-ordinates of the reduced impulsive wrench referred to the principal screws of inertia, which would give the body a kinetic energy T on the screw 0, are proportional to ^dT 1 dT 2 Pl de, "2p n d0 n vs 100. Conjugate Screws of the Potential. Suppose that a twist about a screw 6 evokes a wrench on a screw ?/, while a twist about a screw <f> evokes a wrench on a screw . If 6 be reci procal to , then must <f> be reciprocal to ij. This will now be proved. The condition that 6 and are reciprocal is pAti + + p n 6 n n = ; but the intensities (or amplitudes) of the components of a wrench (or twist) are proportional to the co-ordinates of the screw on which the wrench (or twist) acts, whence the last equation may be written but we have seen ( 99) that _ 1^ t _ *%V<*fc" nn whence the condition that 9 and f are reciprocal is 0/jEj^p9W&** d(f)i d<f) n Now, as V$ is an homogeneous function of the second order of the quantities <J>i, ... (j> n } we may write V* = A u ft* + . . . + A nn $n> + 2^ 12 <k> s + 2^/0; + . . . , in which A hk = A ai . Hence we obtain: 90 THE THEORY OF SCREWS. [100- Introducing these expressions we find, for the condition that and should be reciprocal, This may be written in the form : .. /) i i i . A a > i i i f Q I i f) i >\ I A "-ll* ! Y I i " L nn"n 0n T "1J \"l 0-2 T t Qi ) i = " But this equation is symmetrical with respect to and <, and therefore we should have been led to the same result by expressing the condition that was reciprocal to 77. When and </> possess this property, they are said to be conjugate screws of the potential, and the condition that they should be so related, expressed in terms of their co-ordinates, is obtained by omitting the accents from the last equation. If a screw be reciprocal to 77, then is a conjugate screw of the potential to 0. If we consider the screw to be given, we may regard the screw system of the fifth order, which embraces all the screws reciprocal to 77, as in a certain sense the locus of <. All the screws conjugate to 0, and which, at the same time, belong to the screw system C by which the freedom of the body is defined, must constitute in themselves a screw system of the (n l)th order. For, besides fulfilling the 6 n conditions which define the screw system C, they must also fulfil the condition of being reciprocal to 77 ; but all the screws reciprocal to 7 n screws constitute a screw system of the (ra-l)th order ( 72). The reader will be careful to observe the distinction between two conju gate screws of inertia ( 81 ), and two conj ugate screws of the potential. Though these pairs possess some useful analogies, yet it should be borne in mind that the former are purely intrinsic to the rigid body, inasmuch as they only depend on the distribution of its material, while the latter involve extrinsic considerations, arising from the forces to which the body is submitted. 101. Principal Screws of the Potential. We now prove that in general n screws can be found such that when the body is displaced by a twist about any one of these screws, a reduced wrench is evoked on the same screw. The screws which possess this property are called the principal screws of the potential. Let a be a principal screw of the potential, then we must have, 99: dV a i = + , , 2wj dflj and ( /i 1) similar equations. 102] THE POTENTIAL. 91 Introducing the value of V a , and remembering (34) that a/ = <*"! and a/ = a ci, we have the following n equations: (ft \ AH rpi) + a 2 A 12 + ... + a n A ln =0, a / &c., &c. aiA m + a. 2 A n2 + ... +a n (A nn T p n j = 0. \ ^* / From these linear equations a n ... a n can be eliminated, and we obtain // " an equation of the nth degree in . The values of substituted suc cessively in the linear equations just written will determine the co-ordinates of the n principal screws of the potential. If the position of equilibrium be one which is stable for all displacements then V a must under all circumstances be positive. As it can be reduced to the sum of n squares all the roots of this equation will be real ( 86) and consequently all the n principal screws of the potential will be real. We can now show that these n screws are co-reciprocal. It is evident, in the first place, that if S be a principal screw of the potential, and if be a displacement screw which evokes a wrench on 77, the principle of 100 asserts that, when 6 is reciprocal to S, then must also y be reciprocal to S. Let the n principal screws of the potential be denoted by Si, ... S n , and let T n be that screw of the screw system which is reciprocal to Si, ... S n -i ( 95), then if the body be displaced by a twist about T n , the wrench evoked must be on a screw reciprocal to Si,... S n -i , but T n is the only screw of the screw system possessing this property; therefore a twist about T n must evoke a wrench on T n , and therefore T n must be a principal screw of the potential. But there are only n principal screws of the potential, therefore T n must coincide with S n , and therefore S n must be reciprocal to Si, ... S n ^. 102. Co-ordinates of the Wrench evoked by a Twist. The work done in giving the body a twist of small amplitude a! about a screw a, may be denoted by fttfta*. In fact, remembering that a a 1 = 1 , ... , and substituting these values for 0.1 in I 7 " ( 100), we deduce the expression: Fv a - = A n a,- + ...+ A nn a n - + 24 18 * 1 a + 24 13 a, + . . . where F is independent of a and has for its dimensions a mass divided by the square of a time, and where v a is a linear magnitude specially appropriate to each screw a, and depending upon the co-ordinates of a, and the constants in the function 92 THE THEORY OF SCREWS. [102, The parameter v a may be contrasted with the parameter u a considered in 89. Each is a linear magnitude, but the latter depends only upon the co-ordinates of a, and the distribution of the material of the rigid body. Both quantities may be contrasted with the pitch p a , which is also a linear magnitude, but depends on the screw, and neither on the rigid body nor the forces. If a body receive a twist of small amplitude a? about one of the principal screws of the potential, then the intensity of the wrench evoked on the same screw is (99) : 1 dV a + 2p a da but we have just seen that V=Fv a -a 2 , whence we have the following theorem : If a body which has freedom of the nth order be displaced from a position of equilibrium by a twist about a screw a, of which the co-ordinates with respect to the principal screws of the potential arc i, ... a n , then a reduced wrench ( 96) is evoked on a screw with co-ordinates proportional to /tj 2 rt 2 1 -!,... a n , where v l} ... , p l} ... , are the values of the quantity v, and PI Pn the pitch p, for the principal screws of the potential. We can now express with great simplicity the condition that two screws and (f> shall be conjugate screws of the potential. For, if 6 be reciprocal to the screw whose co-ordinates are proportional to we have : Vi*0i<l> l +...+v n *0 n <f> n = 0. The expression for the potential assumes the simple form Fv 1 *a 1 3 +... + Fv n *a n s . If the function V be proportional to the product of the pitch of the displacement screw and the square of the amplitude, then every displacement screw will coincide with the screw about which the wrench is evoked. 103. Form of the Potential. The n principal screws of the potential form a unique group, inasmuch as they are co-reciprocal, as well as being conjugate screws of the potential. They therefore fulfil n (n 1) conditions, being the total number available in the selection of n screws in an n system. 103] THE POTENTIAL. 93 We now show that the expression of the potential will consist of the sum of n square terms, when referred to any set of n conjugate screws of the potential. The energy consumed in giving a body a twist of amplitude 6 from the position of equilibrium to a new position P, is equal to Fv e *0 z ( 102), and 77 is the screw on which the wrench is evoked. Suppose that from the position P the body receive a twist of amplitude <j> about a screw <, it would generally riot be correct to assert that the energy consumed in the second twist was proportional to the square of its amplitude. For, during the second twist, either a portion of the energy will be consumed in doing work against the wrench on rj, or the energy expended in the second twist will be rendered less, in consequence of the assistance afforded by the wrench on t]. If, however, 77 be reciprocal to (f>, then the quantity of energy con sumed in the twist about </> will be unaffected by the presence of a wrench on 77. Hence if 6 and <f> be two conjugate screws of the potential, the energy expended in giving the body first a twist of amplitude 6 about 6, and then a twist of amplitude </> about <f>, is to be represented by By taking a third screw, conjugate to both 6 and <, and then a fourth screw conjugate to the remaining three, and so on, we see finally that the potential reduces to the sum of n square terms, where each pair of the screws of reference are conjugate screws of the potential. CHAPTER IX. HARMONIC SCREWS. 104. Definition of an Harmonic Screw. We have seen in 97 that to each screw 6 of a screw system of the nth order corresponds a screw X, belonging to the same screw system. The relation between 6 and X is determined when the rigid body, and also the screw system which defines its freedom, are completely known. The physical connection between the two screws 6 and \ may be thus stated. If an impulsive wrench act on the screw \, the body, if previously quiescent, will commence to move by twisting about 6. We have also seen ( 102) that to each screw 6 of a screw system of the nth order corresponds a certain screw 77 belonging to the same screw system. The relation between 6 and 77 is determined when the rigid body, the forces, and the screw system which defines the freedom, is known. The physical connexion between the two screws 6 and 77 may be thus stated. If the body be displaced from a position of equilibrium by a twist about 6, the evoked wrench, when reduced ( 96) to the screw system, acts on 17. The rigid body being given in a position of equilibrium, and the forces which act on the body being known, and also the screw system by which the freedom of the body is prescribed, we then have corresponding to each screw of the given screw system, two other screws X and 77, which also belong to the same screw system. Considering the very different physical character of the two systems of correspondence, it will of course usually happen that the two screws X and 77 are not identical. But a little reflection will enable us to foresee what we shall afterwards prove, viz., that when 6 has been appropriately chosen, then \ and 77 may coincide. For since n 1 arbitrary quantities are disposable in the selection of a screw from a screw system of the nth order ( 69), it follows that for any two screws (for example X and 77) to coincide, n1 conditions 104] HARMONIC SCREWS. 95 must be fulfilled ; but this is precisely the number of arbitrary elements available in the selection of 6. We can thus conceive that for one or more particular screws 6, the two corresponding screws \ and 17 are identical ; and we shall now prove the following important theorem : If a rigid body be displaced from a position of equilibrium by a twist about a screw 6, and if the evoked wrench tend to make the body commence to twist about the same screw 6, then if we call 9 an harmonic screw ( 106), we assert that the number of harmonic screws is generally the same as the order of the screw system which defines the freedom of the rigid body. We shall adopt as the screws of reference the n principal screws of inertia. The impulsive screw, which corresponds to 6 as an instantaneous screw, will have for co-ordinates , Pi Pn where A is a certain constant which is determined by making the co-ordinates satisfy the condition ( 35). If 6 be an harmonic screw, then, remembering that the screws of reference are co-reciprocal ( 87), we must have n equations, of which the first is ( 102) : 1 L U *0>- J ^1 %/ *2 Pl de>- j nm Assuming -p = Ms", where M is the mass of the body, and .9 an unknown quantity, and developing F, we deduce the n equations : 6, (A n + Ms*u*} + z A K +...+ n A ln = 0, t A m + 0*A m +... + n (A nn + Ms 2 u n 2 ) = 0. Eliminating 0^, ... n , we have an equation of the nth degree for s". The n roots of this equation are all real ( 85), and each one substituted in the set of n equations will determine, by a system of n linear equations, the ratios of the n co-ordinates of one of the harmonic screws. It is a remarkable property of the n harmonic screws that each pair of them are conjugate screws of inertia, and also conjugate screws of the potential. Let H l , . . . H n _ t , be n 1 of the harmonic screws, to which correspond the impulsive screws S lt ... S n ^. Also suppose T to be that one screw of the given screw system which is reciprocal to S lt ...$_! ( 95), then T must form with each one of the screws H lt ... 7/ n _! a pair of con jugate screws of inertia (81). But, since S lt ... /S M _, are the screws on which wrenches are evoked by twists about //,,... #_! respectively, it is 96 THE THEORY OF SCREWS. [104, evident that T must form with each one of these screws H lt ... H n ^ a pair of conjugate screws of the potential ( 100). It follows that the impulsive screw, corresponding to T as the instantaneous screw, must be reciprocal to 7/i , ... ff n -i , and also that a twist about T must evoke a wrench on a screw reciprocal to H lt ... H n ^. As in general only one screw of the system can be reciprocal to H l ,...H n ^, it follows that the impulsive screw, which corresponds to T as an instantaneous screw, must also be the screw on which a wrench is evoked by a twist about T. Hence, T must be a harmonic screw, and as there are only n harmonic screws, it is plain that T must coincide with H n , and that therefore H n is a conjugate screw of inertia, as well as a conjugate screw of the potential, to each one of the remaining n 1 harmonic screws. Similar reasoning will, of course, apply to each of the harmonic screws taken in succession. 105. Equations of Motion. We now consider the kinetical problem, which may be thus stated. A free or constrained rigid body, which is acted upon by a system of forces, is displaced by an initial twist of small amplitude, from a position of equi librium. The body also receives an initial twisting motion, with a small twist velocity, and is then abandoned to the influence of the forces. It is required to ascertain the nature of its subsequent movements. Let T represent the kinetic energy of the body, in the position of which the co-ordinates, referred to the principal screws of inertia, are #/, . . . n . Then we have ( 97) : while the potential energy which, as before, we denote by V, is an homo geneous function of the second order of the quantities #/, . . . # . By the use of Lagrange s method of generalized co-ordinates we are enabled to write down at once the n equations of motion in the form : Substituting for T we have : with (n 1) similar equations. Finally, introducing the expression for V ( 100), we obtain n linear differential equations of the second order. The equations which we require can be otherwise demonstrated as follows. 105] HARMONIC SCREWS. 97 Suppose the body to be in motion under the influence of the forces, and that at any epoch t the co-ordinates of the twisting motion are dt " dt~ " when referred to the principal screws of inertia. Let / , ... " be the co-ordinates of a wrench which, had it acted upon the body at rest for the small time e, would have communicated to the body a twisting motion identical with that which the body actually has at the epoch t. The co-ordinates of the impulsive wrench which would, in the time e, have pro duced from rest the motion which the body actually has at the epoch t + e, are : - 1 dt "" n dt On the other hand, the motion at the epoch t + e may be considered to arise from the influence of the wrench / , . . . f M " for the time e, followed by the influence of the evoked wrench for the time e. The final effect of the two wrenches must, by the second law of motion, be the same as if they acted simultaneously for the time e upon the body initially at rest. The co-ordinates of the evoked wrench being : I dV + J^ 2p l ddi 2p n ddn we therefore have the equation : dt 2/>i or dt 1 dV dt ~ 2 Pl d6J and w1 similar equations ; but we see from 97 that ef -M^W e ^- ^^ ~dt Differentiating this equation with respect to the time, and regarding e as constant, we have dt Pl dt* whence 2 <9/ dV the same equation as that already found by Lagrange s method. B. 98 THE THEORY OF SCREWS. [105, To integrate the equations we assume tf^/n, ...#,/=/ n ; where f lt ...f n are certain constants, which will be determined, and where H is an unknown function of the time : introducing also the value of V, given in 100, we find for the equations of motion : - MI*/I fj + (4,1/1 + 4 M / + + 4i/) n = o, &c. c? 2 n - Mu n % ^ + (A m f, + An.fi + ...+ Annfn) 11 = 0. If the quantity s, and the ratios of the n quantities f 1} .../, be deter mined by the n equations : (A u + Mu*s-) +f*A lz + ... +f n A m = 0, &c., &c. +f,A nn _ +... +f n (A nn + Mu^ff) = J then the n equations of motion will reduce to the single equation : By eliminating /j, ... f n from the n equations, we obtain precisely the same equation for s 2 as that which arose ( 104) in the determination of the n harmonic screws. The values of fj, ... f n , which correspond to any value of s 2 , are therefore proportional to the co-ordinates of a harmonic screw. The equation for Q gives : H = H sin (st + c). Let H l} ... H n , Cj , ... c n be 2n arbitrary constants. Let f pq denote the value of/ 9 , when the root s p z has been substituted in the linear equations. Then by the known theory of linear differential equations*, ff n sin (s n t + c n ), 0n =fmffi Si" (*i* + C,) + . +fnnH n Sin (s n t + C M ). In proof of this solution it is sufficient to observe, that the values of #/,... n satisfy the given differential equations of motion, while they also contain the requisite number of arbitrary constants. * Lagrange s Method, Routh, Rigid Dynamics, Vol. i., p. 369. 106] HARMONIC SCREWS. 99 106. Discussion of the Results. For the position of the body before its displacement to have been one of stable equilibrium, it is manifest that the co-ordinates must not increase indefinitely with the time, and therefore all the values of s 2 must be essen tially positive, since otherwise the values of #/, .. n would contain expo nential terms. The 2n arbitrary constants are to be determined by the initial circum stances. The initial displacement is to be resolved into n twists about the n screws of reference ( 95). This will provide n equations, by making t = 0, and substituting for Oi,...0 n , in the equations just mentioned, the amplitudes of the initial twists. The initial twisting motion is also to be resolved into twisting motions about the n screws of reference. The twist velocities of JQ I JQ > these components will be the values of ; , . . . , ~, , when t = ; whence we have n more equations to complete the determination of the arbitrary constants. If the initial circumstances be such that the constants H.,, ..., H n are all zero, then the equations assume a simple form : 0i =f u #! sin (s^ + c), O n =/!?! sin (sj + c). The interpretation of this result is very remarkable. We see that the co-ordinates of the body are always proportional to f u , ...,f ln , hence the body can always be brought from the initial position to the position at any time by twisting it about that screw, whose co-ordinates are proportional to fu> >f-m\ but, as we have already pointed out, the screw thus defined is a harmonic screw, and hence we have the following theorem : If a rigid body occupy a position of stable equilibrium under the influence of a conservative system of forces, then n harmonic screws can be selected from the screw system of the nth order, which defines the freedom of the body, and if the body be displaced from its position of equilibrium by a twist about a harmonic screw, and if it also receive any small initial twist velocity about the same screw, then the body will continue to perform twist oscillations about that harmonic screw, and the amplitude of the twist will be always equal to the arc of a certain circular pendulum, which has an appropriate length, and was appropriately started. The integrals in their general form prove the following theorem : A rigid body is slightly displaced by a twist from a position of stable equilibrium under the influence of a system of forces, and the body receives 7-2 100 THE THEORY OF SCREWS. [106-109 a small initial twisting motion. The twist, and the twisting motion, may each be resolved into their components on the n harmonic screws : n circular pendulums are to be constructed, each of which is isochronous with one of the harmonic screws. All these pendulums are to be started at the same instant as the rigid body, each with an arc, and an angular velocity equal respectively to the initial amplitude of the twist, and to the twist velocity, which have been assigned to the corresponding harmonic screw. To ascertain where the body would be at any future epoch, it will only be necessary to calculate the arcs of the n pendulums for that epoch, and then give the body twists from its position of equilibrium about the harmonic screws, whose amplitudes are equal to these arcs. 107. Remark on Harmonic Screws. We may to a certain extent see the actual reason why the body, when once oscillating upon a harmonic screw, will never depart therefrom. The body, when displaced from the position of equilibrium by a twist upon a harmonic screw 0, and then released, is acted upon by the wrench upon a certain screw rj, which is evoked by the twist. But the actual effect of an impulsive wrench on 77 would be to make the body twist about the harmonic screw ( 104), and as the continued action of the wrench on 77 is indis tinguishable from an infinite succession of infinitely small impulses, we can find in the influence of the forces no cause adequate to change the motion of the body from twisting about the harmonic screw 0. CHAPTER X. FREEDOM OF THE FIRST ORDER. 108. Introduction. In the present chapter we shall apply the principles developed in the preceding chapters to study the Statics and Dynamics of a rigid body which has freedom of the first order. Ensuing chapters will be similarly devoted to the other orders of freedom. We shall in each chapter first ascertain what can be learned as to the kinematics of a rigid body, so far as small displacements are concerned, from merely knowing the order of the freedom which is permitted by the constraints. This will conduct us to a knowledge of the special screw system which defines the freedom enjoyed by the body. We shall then be enabled to determine the reciprocal screw system, which involves the theory of equilibrium. The next group of questions will be those which relate to the effect of an impulse upon a quiescent rigid body, free to twist about any screw of the screw system. Finally, we shall discuss the small oscillations of a rigid body in the vicinity of a position of stable equilibrium, under the influence of a given system of forces, the movements of the body being limited as before to the screws of the screw system. 109. Screw System of the First Order. A body which has freedom of the first order can execute no movement which is not a twist about one definite screw. The position of a body so circumstanced is to be specified by a single datum, viz., the amplitude of the twist about the given screw, by which the body can be brought from a standard position to any other position which it is capable of attaining. As examples of a body which has freedom of the first order, we may refer to the case of a body free to rotate about a fixed axis, but not to slide along it, or of a body free to slide along a fixed axis, but not to rotate around it. In the former case the screw system consists of one screw, whose pitch is zero ; in the latter case the screw system consists of one screw, whose pitch is infinite. 102 THE THEORY OF SCREWS. [HO, 110. The Reciprocal Screw System. The integer which denotes the order of a screw system, and the integer which denotes the order of the reciprocal screw system, will, in all cases, have the number six for their sum ( 72). Hence a screw system of the first order will have as its reciprocal a screw system of the fifth order. For a screw 6 to belong to a screw system of the fifth order, the necessary and sufficient condition is, that 6 be reciprocal to one given screw a. This condition is expressed in the usual form : (p a + Pe) cos d ag sin = 0, where is the angle, and d ae the perpendicular distance between the screws 9 and a. We can now show that every straight line in space, when it receives an appropriate pitch, constitutes a screw of a given screw system of the fifth order. For the straight line and a being given, d a6 and are determined, and hence the pitch p e can be determined by the linear equation just written. Consider next a point A, and the screw a. Every straight line through A, when furnished with the proper pitch, will be reciprocal to a. Since the number of lines through A is doubly infinite, it follows that a singly infinite number of screws of given pitch can be drawn through A, so as to be reciprocal to a. We shall now prove that all the screws of the same pitch which pass through A, and are reciprocal to a, lie in a plane. This we shall first show to be the case for all the screws of zero pitch*, arid then we shall deduce the more general theorem. By a twist of small amplitude about a the point A is moved to an adja cent point B. To effect this movement against a force at A which is per pendicular to AB, no work will be required; hence every line through A, perpendicular to AB, may be regarded as a screw of zero pitch, reciprocal to a. We must now enunciate a principle which applies to a screw system of any order. We have already referred to it with respect to the cylindroid ( 18). If all the screws of a screw system be modified by the addition of the same linear magnitude (positive or negative) to the pitch of every screw, then the collection of screws thus modified still form a screw system of the same order. The proof is obvious, for since the virtual co-efficient depends on the sum of the pitches, it follows that, if all the pitches of a system be * This theorem is due to Mdbius, who has shown, that, if small rotations about six axes can neutralise, and if five of the axes be given, and a point on the sixth axis, then the sixth axis is limited to a plane. (" Ueber die Zusammensetzung unendlich kleiner Drehungen," Crelle s Journal, t. xviii., pp. 189212.) (Berlin, 1838.) HI] FREEDOM OF THE FIRST ORDER. 103 increased by a certain quantity, and all the pitches of the reciprocal system be diminished by the same quantity, then all the first set of screws thus modified are reciprocal to all the second group as modified. Hence, since a screw-system of the nth order consists of all the screws reciprocal to 6 n screws, it follows that the modified set must still be a screw system. We shall now apply this principle to prove that all the screws X of any given pitch k, which can be drawn through A, to be reciprocal to a, lie in a plane. Take a screw ij, of pitch p a + k, on the same line as or, then we have just shown that all the screws p, of zero pitch, Avhich can be drawn through the point A, so as to be reciprocal to ?;, lie in a plane. Since fj, and 77 are reciprocal, the screws on the same straight lines as /u, and 77 will be reciprocal, provided the sum of their pitches is the pitch of r) ; therefore, a screw X, of pitch k, on the same straight line as p, will be reciprocal to the screw a, of pitch p a ; but all the lines //. lie in a plane, therefore all the screws X lie in the same plane. Conversely, given a plane and a pitch k, a point A can be determined in that plane, such that all the screws drawn through A in the plane, and possessing the pitch k, are reciprocal to a. To each pitch k 1} & 3 , ..., will correspond a point A 1} A. ... ; and it is worthy of remark, that all the points A l} A. 2 must lie on a right line which intersects a at right angles; for join A l} A, then a screw on the line A^.^, which has for pitch either k : or k., must be reciprocal to a; but this is impossible unless A^A^ intersect a at a right angle. 111. Equilibrium. If a body which has freedom of the first order be in equilibrium, then the necessary and sufficient condition is, that the forces which act upon the body shall constitute a wrench on a screw of the screw system of the fifth order, which is reciprocal to the screw which defines the freedom. We thus see that every straight line in space may be the residence of a screw, a wrench on which is consistent with the equilibrium of the body. If two wrenches act upon the body, then the condition of equilibrium is, that, when the two wrenches are compounded by the aid of a cylindroid, the single wrench which replaces them shall lie upon that one screw of the cylindroid, which is reciprocal to a ( 2G). We can express with great facility, by the aid of screw co-ordinates, the condition that wrenches of intensities 6", <", on two screws 6, <f>, shall equilibrate, when applied to a body only free to twist about a. Adopting any six co-reciprocals as screws of reference, and resolving each of the wrenches on 9 and </> into its six components on the six screws of 104 THE THEORY OF SCREWS. [ill- reference, we shall have for the intensity of the component of the resultant wrench on &&gt; n 6" 6 n + 4>"<j> n - Hence the co-ordinates of the resultant wrench are proportional to For equilibrium this screw must be reciprocal to a, whence we have Pl a, (ff 0, + f >0 +...+P*. (ff Ot + f &) = 0, Or, 0"^a6 + $"1*04 = 0. This equation merely expresses that the sum of the works done in a small twist about a against the wrenches on and <f> is zero. We also perceive that a given wrench may be always replaced by a wrench of appropriate intensity on any other screw, in so far as the effect on a body only free to twist about a is concerned. It may not be out of place to notice the analogy which the equation just written bears to the simple problem of the determination of the condition that two forces should be unable to disturb the equilibrium of a particle only free to move on a straight line. If P, Q be the two forces, and if I, m be the angles which the forces make with the direction in which the particle can move, then the condition is P cos I + Q cos in = 0. This suggests an analogy between the virtual co-efficient of two screws, and the cosine of the angle between two lines. 112. Particular Case. If a body having freedom of the first order be in equilibrium under the action of gravity, then the vertical through the centre of inertia must lie in the plane of reciprocal screws of zero pitch, drawn through the centre of inertia. 113. Impulsive Forces. If an impulsive wrench of intensity 77 " act on the screw >/, while the body is only permitted to twist about a, then we have seen in 90 how the twist velocity produced can be found. We shall now determine the impulsive reaction of the constraints. This reaction must be an impulsive wrench of intensity X " on a screw X, which is reciprocal to a. The determination of X may be effected geometrically in the following manner : Let /* be the screw, an impulsive wrench on which would, if the body were perfectly free, cause an instantaneous twisting motion about a ( 80). Draw the cylindroid (77, fi). 114] FREEDOM OF THE FIRST ORDER. 105 Then A, must be that screw on the cylindroid which is reciprocal to a, for a wrench on X, and the given wrench on 77, must compound into a wrench on p, whence the three screws must be co-cylindroidal * ; also X must be reciprocal to a, so that its position on the cylindroid is known ( 20). Finally, as the impulsive intensity 17 " is given, and as the three screws 77, X, /* are all known, the impulsive intensity X " becomes determined ( 14). 114. Small Oscillations. We shall now suppose that a rigid body which has freedom of the first order occupies a position of stable equilibrium under the influence of a system of forces. If the body be displaced by a small twist about the screw a which prescribes the freedom, and if it further receive a small initial twist velocity about the same screw, the body will continue to perform small twist oscillations about the screw a. We propose to determine the time of an oscillation. The kinetic energy of the body, when animated by a twist velocity 7 / , CLt> is Mu a ~ (~ J ( 89). The potential energy due to the position attained by giving the body a twist of amplitude a away from its position of equili brium, is Fv a 2 af 2 ( 102). But the sum of the potential and kinetic energies must be constant, whence Mu a -?-) dt I Fv a -a- = const. Differentiating we have Integrating this equation we have a = A sin A/ - Mu a t + B cos / Fv a V Mu where A and B are arbitrary constants. The time of one oscillation is therefore IM F" Regarding the rigid body and the forces as given, and comparing inter se the periods about different screws a, on which the body might have been constrained to twist, we see from the result just arrived at that the time for each screw a is proportional to -- . We shall often for convenience speak of three screws on the same cylindroid as co-cylindroidal. 106 THE THEORY OF SCREWS. [115-117 115. Property of Harmonic Screws. As the time of vibration is affected by the position of the screw to which the motion is limited, it becomes of interest to consider how a screw is to be chosen so that the time of vibration shall be a maximum or minimum. With slightly increased generality we may state the problem as follows : Given the potential for every position in the neighbourhood of a position of stable equilibrium, it is required to select from a given screw system the screw or screws on which, if the body be constrained to twist, the time of vibration will be a maximum or minimum, relatively to the time of vibration on the neighbouring screws of the same screw system. Take the n principal screws of inertia belonging to the screw system, as screws of reference, then we have to determine the n co-ordinates of a screw a by the condition that the function shall be a maximum or a V a minimum. Introducing the value of u a ( 97), and of v a ( 102), in terms of the co-ordinates, we have to determine the maximum and minimum of the function Multiplying this equation by the denominator of the left-hand side, differentiating with respect to each co-ordinate successively, and observing that the differential coefficients of a; must be zero, we have the n equations : (^ n - U^X) j + A 12 dz ... + A ln n = 0, &c., &c. AM&! + A H .,a., ... -I- (A nn ~ Unty H = 0. We hence see that there are n screws belonging to each screw of the nth order on which the time of vibration is a maximum or minimum, and by comparison with 104 we deduce the interesting result that these n screws are also the harmonic screws. Taking the screw system of the sixth order, which of course includes every screw in space, we see that if the body be permitted to twist about one of the six harmonic screws the time of vibration will be a maximum or minimum, as compared with the time of vibration on any adjacent screw. If the six harmonic screws were taken as the screws of reference, then u a 2 and w a 2 would each consist of the sum of six square terms ( 89, 102). If the coefficients in these two expressions were proportional, so that u a " only differed from v^ by a numerical factor, we should then find that every screw in space was an harmonic screw, and that the times of vibrations about all these screws were equal. CHAPTER XL FREEDOM OF THE SECOND ORDER. 116. The Screw System of the Second Order. When a rigid body is capable of being twisted about two screws and (j), it is capable of being twisted about every screw on the cylindroid (6, <) ( 14). If it also appear that the body cannot be twisted about any screw which does not lie on the cylindroid, then as we know the body has freedom of the second order, and the cylindroid is the screw system of the second order by which the freedom is defined ( 219). Eight numerical data are required for determination of a cylindroid (75). We must have four for the specification of the nodal line, two more are required to define the extreme points in which the surface cuts the nodal line, one to assign the direction of one generator, and one to give the pitch of one screw, or the eccentricity of the pitch conic. Although only eight constants are required to define the cylindroid, yet ten constants must be used in defining two screws 6, (f>, from which the cylindroid could be constructed. The ten constants not only define tne cylindroid, but also point out two special screws upon the surface ( 77). 117. Applications of Screw Co-ordinates. We have shown ( 40) that if a, /3 be the two screws of a cylindroid, which intersect at right angles, then the co-ordinates of any screw 9, which makes an angle I with the screw a, are : ttj cos I + & sin I, . . . a s cos I + /9 (j sin I, reference being made as usual to any set of six co-reciprocals. In addition to the examples of the use of these co-ordinates already given ( 40), we may apply them to the determination of that single screw 6 upon the cylindroid (a, /8), which is reciprocal to a given screw rj. 108 THE THEORY OF SCREWS. [117- From the condition of reciprocity we must have : P\n\ (i cos I + & sin /)+...+ p ti rj 6 ( cos I + /3 6 sin I) = 0, or, OT ar| cos I + zap,, sin I = 0. From this tan I is deduced, and therefore the screw becomes known ( 26). In general if tn^ be the virtual coefficient of any screw 77 and a screw on the cylindroid, we have V*r,0 = ^ar, COS I + CT^, SU1 I \ whence if on each screw a distance be set off from the nodal line equal to the virtual coefficient between 77 and 6, the points thus found will lie on a right circular cylinder, of which the equation is ; X? + y* = TS^X + TX^y. Thus the screw which has the greatest virtual coefficient with 77 is at right angles to the screw reciprocal to 77, and in general two screws can be found upon the cylindroid which have a given virtual coefficient with any given external screw. 118. Relation between Two Cylindroids. We may here notice a curious reciprocal relation between two cylindroids, which is manifested when one condition is satisfied. If a screw can be found on one cylindroid, which is reciprocal to a second cylindroid, then conversely a screw can be found on the latter, which is reciprocal to the former. Let the cylindroids be (a, /3), and ( X, fi). If a screw can be found on the former, which is reciprocal to the latter, then we have : pAi (i cos I + /3j sin 1) -f . . . + p n ^n (oi cos I + /3 n sin I) = 0, Pif^i (i cos I + ft sin 1) + . . . 4- pn^n ( a n cos I + ft n sin I) = 0. Whence eliminating I, we find : As this relation is symmetrical with regard to the two cylindroids, the theorem has been proved. 119. Co-ordinates of Three Screws on a Cylindroid. The co-ordinates of three screws upon a cylindroid are connected by four independent relations. In fact, two screws define the cylindroid, and the third screw must then satisfy four equations of the form ( 20). These relations can be expressed most symmetrically in the form of six equations, which also involve three other quantities. 120] FREEDOM OF THE SECOND ORDER. 109 Let X, JJL, v be three screws upon a cylindroid, and let A, B, C denote the angles between /LI v, between v X, and between X //., respectively. If wrenches of intensities X", // , v", on \, /*, v, respectively, are in equilibrium, we must have ( 14): _X" p" v" sin A sin B ~~ sin C But we have also as a necessary condition that if each wrench be resolved into six component wrenches on six screws of reference, the sum of the intensities of the three components on each screw of reference is zero ; whence Xj sin A + /ij sin B + v l sin (7 = 0, X sin A + p, 6 sin B + v 6 sin G = 0. From these equations we deduce the following corollaries : The screw of which the co-ordinates are proportional to aXj + bfa , ... X 6 + bfj, G , lies on the cylindroid (X, //.), and makes angles with the screws X, IJL, of which the sines are inversely proportional to a and 6. The two screws, of which the co-ordinates are proportional to aXj 6/ij, ... aX 6 + &/A G , and the two screws X, /* are respectively parallel to the four rays of a plane harmonic pencil. 120. Screws on One Line. There is one case in which a body has freedom of the second order that demands special attention. Suppose the two given screws 9, <f>, about which the body can be twisted, happen to lie on the same straight line, then the cylindroid becomes illusory. If the amplitudes of the two twists be 6 , $> , then the body will have received a rotation 6 + <f> , accompanied by a trans lation p e + <f> p<t>. This movement is really identical with a twist on a screw of which the pitch is : O pe + & + <!> Since , </> may have any ratio, we see that, under these circumstances, the screw system which defines the freedom consists of all the screws with pitches ranging from -co to +00, which lie along the given line. It follows ( 47), that the co-ordinates of all the screws about which the body can be twisted are to be found by giving x all the values from QO to + GO in the expressions : a x dR * x dR l + ~ " K + in which L10 THE THEORY OF SCREWS. [121- 121. Displacement of a Point. Let P be a point, and let a, /3 be any two screws upon a cylindroid. If a body to which P is attached receive a small twist about a, the point P will be moved to P . If the body receive a small twist about /3, the point P would be moved to P". Then whatever be the screw 7 on the cylindroid about which the body be twisted, the point P will still be displaced in the plane PP P". For the twist about 7 can be resolved into two twists about a and /3, and therefore every displacement of P must be capable of being resolved along PP and PP". Thus through every point P in space a plane can be drawn to which the small movements of P, arising from twists about the screws on a given cylindroid are confined. The simplest construction for this plane is as follows: Draw through the point P two planes, each containing one of the screws of zero pitch; the intersection of these planes is normal to the required plane through P. The construction just given would fail if P lay upon one of the screws of zero pitch. The movements of P must then be limited, not to a plane, but to a line. The line is found by drawing a normal to the plane passing through P, and through the other screw of zero pitch. We thus have the following curious property due to M. Mannheim*, viz., that a point in the rigid body on the line of zero pitch will commence to move in the same direction whatever be the screw on the cylindroid about which the twist is imparted. This easily appears otherwise. Appropriate twists about any two screws, a and /3, can compound into a twist about the screw of zero pitch X, but the twist about X cannot disturb a point on X. Therefore a twist about ft must be capable of moving a point originally on X back to its position before it was disturbed by a. Therefore the twists about /3 and a. must move the point in the same direction. 122. Properties of the Pitch Conic. Since the pitch of a screw on a cylindroid is proportional to the inverse square of the parallel diameter of the pitch conic ( 18), the asymptotes must be parallel to the screws of zero pitch ; also since a pair of reciprocal screws are parallel to a pair of conjugate diameters ( 40), it follows that the two screws of zero pitch, and any pair of reciprocal screws, are parallel to the rays of an harmonic pencil. If the pitch conic be an ellipse, there * Journal de I ecole Polytechnique, T. xx. cah. 43, pp. 57122 (1870). 123] FREEDOM OF THE SECOND ORDER. Ill are no real screws of zero pitch. If the pitch conic be a parabola, there is but one screw of zero pitch, and this must be one of the two screws which intersect at right angles. 123. Equilibrium of a Body with Freedom of the Second Order. We shall now consider more fully the conditions under which a body which has freedom of the second order is in equilibrium. The necessary and sufficient condition is, that the forces which act upon the body shall constitute a wrench upon a screw which is reciprocal to the cylindroid which defines the freedom of the body. It has been shown ( 23), that the screws which are reciprocal to a cylin droid exist in such profusion, that through every point in space a cone of the second order can be drawn, of which the entire superficies is made up of such screws. We shall now examine the distribution of pitch upon such a cone. The pitch of each reciprocal screw is equal in magnitude, and opposite in sign, to the pitches of the two screws of equal pitch, in which it intersects the cylindroid ( 22). Now, the greatest and least pitches of the screws on the cylindroid are p a and p$ ( 18). For the quantity p a cos 2 1 + p ft sin 2 1 is always intermediate between p a cos 2 1 + p a sin 2 1 and pp cos 2 1 + pp sin 2 1. Hence it follows that the generators of the cone which meet the cylindroid in three real points must have pitches intermediate between p a and pp. It is also to be observed that, as only one line can be drawn through the vertex of the cone to intersect any two given screws on the cylindroid, so only one screw of any given pitch can be found on the reciprocal cone. One screw can be found upon the reciprocal cone of every pitch from oo to + oo . The line drawn through the vertex parallel to the nodal line is a generator of the cone to which infinite pitch must be assigned. Setting out from this line around the cone the pitch gradually decreases to zero, then becomes negative, and increases to negative infinity, when we reach the line from which we started. We may here notice that when a screw has infinite pitch, we may regard the infinity as either + or indifferently. If we conceive distances marked upon each generator of the cone from the vertex, equal to the pitch of that generator, then the parallel to the nodal line drawn from the vertex forms an asymptote to the curve so traced upon the cone. It is manifest that we must admit the cylindroid to possess imaginary screws, whose pitch is nevertheless real. The reciprocal cone drawn from a point to a cylindroid, is decomposed into two planes, when the point lies upon the cylindroid. The first plane is normal to the generator passing through the point. Every line in this plane must, when it receives the proper pitch, be a reciprocal screw. The 112 THE THEORY OF SCREWS. [123- second plane is that drawn through the point, and through the other screw on the cylindroid, of equal pitch to that which passes through the point. We have, therefore, solved in the most general manner the problem of the equilibrium of a rigid body with two degrees of freedom. We have shown that the necessary and sufficient condition is, that the resultant wrench be about a screw reciprocal to the cylindroid expressing the freedom, and we have seen the manner in which the reciprocal screws are distributed through space. We now add a few particular cases. 124. Particular Cases. A body which has two degrees of freedom is in equilibrium under the action of a force, whenever the line of action of the force intersects both the screws of zero pitch upon the cylindroid. If a body acted upon by gravity have freedom of the second order, the necessary and sufficient condition of equilibrium is, that the vertical through the centre of inertia shall intersect both of the screws of zero pitch. A body which has freedom of the second order will be in equilibrium, notwithstanding the action of a couple, provided the axis of the couple be parallel to the nodal line of the cylindroid. A body which has freedom of the second order will remain in equilibrium, notwithstanding the action of a wrench about a screw of any pitch on the nodal line of the cylindroid. 125. The Impulsive Cylindroid and the Instantaneous Cylin droid. A rigid body M is at rest in a position P, from which it is either partially or entirely free to move. If M receive an impulsive wrench about a screw X lt it will commence to twist about an instantaneous screw A 1} if, however, the impulsive wrench had been about X 2 or X 3 (M being in either case at rest in the position P) the instantaneous screw would have been A 2 , or A 3 . Then we have the following theorem: If Xi, X z , X 3 lie upon a cylindroid S (which we may call the impulsive cylindroid), then A 1} A.,, A 3 lie on a cylindroid S (which we may call the instantaneous cylindroid). For if the three wrenches have suitable intensities they may equilibrate, since they are co-cylindroidal ; when this is the case the three instantaneous twist velocities must, of course, neutralise; but this is only possible if the instantaneous screws be co-cylindroidal ( 93). 12 5] FREEDOM OF THE SECOND ORDER. 113 If we draw a pencil of four lines through a point parallel to four gene rators of a cylindroid, the lines forming the pencil will lie in a plane. We may define the (inharmonic ratio of four generators on a cylindroid to be the anharmonic ratio of the parallel pencil. We shall now prove the follow ing theorem : The anharmonic ratio of four screws on the impulsive cylindroid is equal to the anharmonic ratio of the four corresponding screws on the instantaneous cylindroid. Before commencing the proof we remark that, If an impulsive wrench of intensity F acting on the screw X be capable of producing the unit of twist velocity about A, then an impulsive wrench of intensity Fta on X will produce a twist velocity w about A. Let X 1} X 2 , X 3) X^ be four screws on the impulsive cylindroid, the intensities of the wrenches appropriate to which are F^, F 2 a) 2 , F 3 to 3t Fw. Let the four corresponding instantaneous screws be A 1} A 2 , A s , A^ and the twist velocities be a> 1; &&gt; 2 , a> 3 , a> 4 . Let <j) m be the angle on the impulsive cylindroid defining X m , and let 6 m be the angle on the instantaneous cylindroid defining A m . If three impulsive wrenches equilibrate, the corresponding twist velocities neutralize by the second law of motion : hence ( 14) certain values of &&gt;!, <B.;,, 6) :! , ft) 4 must satisfy the following equations: to, sin (0 2 - 3 ) sin (0 3 - 0,) sin (0, - a ) sin (fa (j> 3 ) sin (</> 3 fa) sin (fa too sin (0 3 - 4 ) sin (0 4 - 2 ) sin (0 2 - :! ) _ sin (0 :j - fa) ~ sin (fa - fa) sin (fa - fa*) whence sin (0j 0) sin (0 3 4 ) _ sin (fa fa) sin (<ft :i fa) sin (0 3 0!> sin (0 4 - 2 ) ~ sin (fa fa) sin (fa fa,) which proves the theorem. If we are given three screws on the impulsive cylindroid, and the corresponding three screws on the instantaneous cylindroid, the connexion between every other corresponding pair is, therefore, geometrically deter mined. B. $ 114 THE THEORY OF SCREWS. [126- 126. Reaction of Constraints. Whatever the constraints may be, their reaction produces an impulsive wrench R l upon the body at the moment of action of the impulsive wrench X^. The two wrenches X l and 7^ compound into a third wrench F,. If the body were free, Y l is the impulsive wrench to which the instantaneous screw A-i would correspond. Since X lt X 2 , X 3 are co-cylindroidal, A lt A z , A 3 must be co-cylindroidal, and therefore also must be Y lt F 2 , Y 3 . The nine wrenches X ly X. 2 , X 3 , R lt E, R i} - F,, F 2 , Y 3 must equilibrate; but if Xi, X 2 , X 3 equilibrate, then the twist velocities about A lt A 2 , A a must neutralize, and therefore the wrenches about F, , F 2 , F 3 must equilibrate. Hence RI, R. 2 , R 3 equilibrate, and are therefore co-cylindroidal. Following the same line of proof used in the last section, we can show that If impulsive wrenches on any four co-cylindroidal screws act upon a partially free rigid body, the four corresponding initial reactions of the constraints also constitute wrenches about four co-cylindroidal screws; and, further, the anharmonic ratios of the two groups of four screws are equal. 127. Principal Screws of Inertia. If a quiescent body with freedom of the second order receive impulsive wrenches on three screws X l} X. 2 , X 3 on the cylindroid which expresses the freedom, and if the corresponding instantaneous screws on the same cylin droid be A lt A%, A s , then the relation between any other impulsive screw X on the cylindroid and the corresponding instantaneous screw A is completely defined by the condition that the anharmonic ratio of X, X lt X 2 , X 3 is equal to the anharmonic ratio of A, A^, A.,, A 3 . If three rays parallel to X lt X 2 , X 3 be drawn from a point, and from the same point three rays parallel to A^, A.,, A 3 , then, all six rays being in the same plane, it is well known that the problem to determine a ray Z such that the anharmonic ratio of Z, A l , A 2 , A 3 is equal to that of Z, X^, X 2 , X 3) admits of two solutions. There are, therefore, two screws on a cylindroid such that an impulsive wrench on one of these screws will cause the body to commence to twist about the same screw. We have thus arrived by a special process at the two principal screws of inertia possessed by a body which has freedom of the second order. This is, of course, a particular case of the general theorem of 78. We shall show in the next section how these screws can be determined in another manner. 128. The Ellipse of Inertia. We have seen ( 89) that a linear parameter u a may be conceived appro priate to any screw a of a system, so that when the body is twisting about 128] FREEDOM OF THE SECOND ORDER. 115 the screw a. with the unit of twist velocity, the kinetic energy is found by multiplying the mass of the body into the square of the line u a . We are now going to consider the distribution of this magnitude u a on the screws of a cylindroid. If we denote by u lt u^ the values of ti a for any pair of conjugate screws of inertia on the cylindroid (81), and if by a l , a, we denote the intensities of the components on the two conjugate screws of a wrench of unit intensity on a, we have ( 97) From the centre of the cylindroid draw two straight lines parallel to the pair of conjugate screws of inertia, and with these lines as axes of as and y construct the ellipse of which the equation is U-fX* + M 2 2 7/ 2 = H, where H is any constant. If r be the radius vector in this ellipse, we have ( 35) x y - = ! and - = a,, ; r r whence by substitution we deduce which proves the following theorem: The linear parameter u a on any screw of the cylindroid is inversely proportional to the parallel diameter of a certain ellipse, and a pair of conjugate screws of inertia on the cylindroid are parallel to a pair of conjugate diameters of the same ellipse. This ellipse may be called the ellipse of inertia. The major and minor axes of the ellipse of inertia are parallel to screws upon the cylindroid, which for a given twist velocity correspond respectively to a maximum and minimum kinetic energy. An impulsive wrench on a screw 77 acts upon a quiescent rigid body which has freedom of the second order. It is required to determine the screw 6 on the cylindroid expressing the freedom about which the body will commence to twist. The ellipse of inertia enables us to solve this problem with great facility. Determine that one screw <f> on the cylindroid which is reciprocal to ?? ( 26). Draw a diameter D of the ellipse of inertia parallel to <. Then the required screw 6 is simply that screw on the cylindroid which is parallel to the diameter conjugate to D in the ellipse of inertia. The converse problem, viz., to determine the screw 77, an impulsive wrench 82 116 THE THEORY OF SCREWS. [128, on which would make the body commence to twist about 6, is indeterminate. Any screw in space which is reciprocal to </> would fulfil the required condition (136). We have seen in 96 that an impulsive wrench on any screw in space may generally be replaced by a precisely equivalent wrench upon the cylindroid which expresses the freedom. We are now going to determine the screw 77, on the cylindroid of freedom, an impulsive wrench on which would make the body twist about a given screw 6 on the same cylindroid. This can be easily determined with the help of the pitch conic ; for we have seen ( 40) that a pair of reciprocal screws on the cylindroid of freedom are parallel to a pair of conjugate diameters of the pitch conic. The construction is therefore as follows: Find the diameter A which is conjugate, with respect to the ellipse of inertia, to the diameter parallel to the given screw 6. Next find the diameter B which is conjugate to the diameter A with respect to the pitcfi conic. The screw on the cylindroid parallel to the line B thus determined is the required screw 77. Two concentric ellipses have one pair of common conjugate diameters. In fact, the four points of intersection form a parallelogram, to the sides of which the pair of common conjugate diameters are parallel. We can now interpret physically the common conjugate diameters of the pitch conic, and the ellipse of inertia. The two screws on the cylindroid parallel to these diameters are conjugate screws of inertia, and they are also reciprocal; they are, therefore, the principal screws of inertia, to which we have been already conducted (127). If the distribution of the material of the body bear certain relations to the arrangement of the constraints, we can easily conceive that the pitch conic and the ellipse of inertia might be both similar and similarly situated. Under these exceptional circumstances it appears that every screw of the cylindroid would possess the property of a principal screw of inertia. 129. The Ellipse of the Potential. We are now to consider another ellipse, which, though possessing many useful mathematical analogies to the ellipse of inertia, is yet widely different from a physical point of view. We have introduced ( 102) the conception of the linear magnitude w , the square of which is proportional to the work done in effecting a twist of given amplitude about a screw a. from a position of stable equilibrium under the influence of a system of forces. We now propose to consider the distribution of the parameter v a upon the screws of a cylindroid. It appears from 102 that if v l} v denote the values of the quantity v a for each of two conjugate screws of the potential, and if a,, 2 denote the intensities of the components on the two conjugate screws of a 129] FREEDOM OF THE SECOND ORDER. 117 wrench of unit intensity on a screw a, which also lies upon the cylindroid, then * = From the centre of the cylindroid draw two straight lines parallel to the pair of conjugate screws of the potential, and with these lines as axes of x and y construct the ellipse, of which the equation is vi*a? + v./y* = H, where H is any constant. If r be the radius vector in this ellipse, we have x y = a, and - = a., ; r r whence by substitution we deduce -- i ^;* a :; which proves the following theorem : The linear parameter v a on any screw of the cylindroid is inversely pro portional to the parallel diameter of a certain ellipse, and a pair of conjugate screws of the potential are parallel to a pair of conjugate diameters of the same ellipse. This ellipse may be called the ellipse of the potential. The major and minor axes of the ellipse of the potential are parallel to screws upon the cylindroid, which, for a twist of given amplitude, correspond to a maximum and minimum potential energy. When the body has to relinquish its original position of equilibrium by the addition of a wrench on a screw 77 to the forces previously in operation, the twist by which the body may proceed to its new position of equilibrium is about a screw 0, which can be constructed by the ellipse of the potential. Determine the screw </> (on the cylindroid of freedom) which is reciprocal to 77 ( 26), then </>, and the required screw 0, are parallel to a pair of conjugate diameters of the ellipse of the potential. The common conjugate diameters of the pitch conic, and the ellipse of the potential, are parallel to the two screws on the cylindroid, which we have designated the principal screws of the potential ( 101). When a body is disturbed from its position of equilibrium by a small wrench upon a principal screw of the potential, then the body could be moved to the new position of equilibrium required in its altered circumstances by a small twist about the same screw. 118 THE THEORY OF SCREWS. [130- 130. Harmonic Screws. The common conjugate diameters of the ellipse of inertia, and the ellipse of the potential, are parallel to the two harmonic screws on the cyliudroid ( 104). This is evident, because the pair of screws thus determined are conjugate screws both of inertia and of the potential. If the body be displaced by a twist about one of the harmonic screws, and be then abandoned to the influence of the forces, the body will continue to perform twist oscillations about that screw. If the ellipse of inertia, and the ellipse of the potential, be similar, and similarly situated, it follows that every screw on the cylindroid will be a harmonic screw. 131. Exceptional Case. We have now to consider the modifications which the results we have arrived at undergo when the cylindroid becomes illusory in the case con sidered ( 120). Suppose that and were a pair of conjugate screws of inertia on the straight line about which the body was free to rotate and slide independently. Then taking the six absolute principal screws of inertia as screws of reference, we must have (97) ps dR\ / pf dR\ + f j- hi + -:- , - = o, % drjj \ 4^j drjj where 77 denotes the screw of zero pitch on the same straight line. Expanding this equation, and reducing, we find This result can be much simplified. By introducing the condition that as in 120 R = (77! + 77,)- + (7/3 + 1J 4 )- + (rj, + 77 6 ) 2 , we obtain Hence we can prove ( 133) that in this case the product of the pitches of two conjugate screws of inertia is equal to minus the square of the radius of gyration about the common axis of the screws. 132] FREEDOM OF THE SECOND ORDER. 119 132. Reaction of Constraints. We shall now consider the following problem : A body which is free to twist about all the screws of a cylindroid C receives an impulsive wrench on a certain screw 77. It is required to find the screw X, a wrench on which constitutes the impulsive reaction of the constraints. Let C represent the cylindroid which, if the body were perfectly free, would form the locus of those screws, impulsive wrenches on which correspond to all the screws of C as instantaneous screws. Since a wrench on 77, and one on \, make the body twist about some screw on C, it follows that the cylindroid (77, X) must have a screw p in common with C . The wrench on X might be resolved into two, one on 77, and the other on p, and the latter might be again resolved into two wrenches on any two screws of C . It therefore follows that X must belong to the screw system of the third order, which may be defined by 77, and by any two screws from C . Take any three screws reciprocal to this system, and any two screws on C. We have then five screws to which X is reciprocal, arid it is therefore geometrically determined ( 26). When X is found, the cylindroid (77, X) can be drawn, and thus p is deter mined. The position of p on C will point out the screw on C, about which the body will commence to twist, while the position of p on (77, X), and the known intensity of the wrench on 77, will determine the intensity of the wrench on X. CHAPTER XII. PLANE REPRESENTATION OF DYNAMICAL PROBLEMS CONCERNING A BODY WITH TWO DEGREES OF FREEDOM*. 133. The Kinetic Energy. If a rigid body of mass M twist about a screw 0, with the twist velocity 0, then the kinetic energy of the body may be written in the form Mufffi, where u e is a linear magnitude appropriate to the screw 6 ( 89). The function uf is the arithmetic mean between the square of the radius of gyration and the square of the pitch, for the kinetic energy of the body when twisting about 9 is the sum of two parts : one, the kinetic energy of the rotation ; the other, of the translation. The energy of the rotation is simply this being in accordance with the definition of the radius of gyration p e . The kinetic energy due to the translation is, of course, whence the total kinetic energy is and therefore 134. Body with two Degrees of Freedom. The movements are under these circumstances restricted to twists about the screws of a cylindroid, and we shall now examine the law of distribution * Royal Irish Academy, Cunningham Memoirs, No. 4, p. 19 (1886) ; see also Proceedings of the Royal Irish Academy, 2nd Series, Vol. iv. p. 29 (1883). 133, 134] PLANE REPRESENTATION OF DYNAMICAL PROBLEMS. 121 of u e upon the several screws of the cylindroid ( 128). The representative circle ( 50) will give a convenient geometrical construction. Let 6 l and 0. 2 be the two co-ordinates of 6 relatively to any two screws of reference on the cylindroid. Then the components of the twist velocity will be 00i and 00.,. The actual velocity of any point of the body will necessarily be a linear function of these components. The square of the velocity will contain terms in which 3 is multiplied into 0f, 0^0.,, #./, respec tively. If, then, by integration we obtain the total kinetic energy, it must assume the form whence, from the definition of u g The three constants, X, /m, v, are the same for all screws on the cylindroid. They are determined by the material disposition of the body relatively to the cylindroid. We have taken the two screws of reference arbitrarily, but this equation can receive a remarkable simplification when the two screws of reference have been chosen with special appropriateness. Fig. 18. Let the lengths AX and BX (fig. 18) be denoted by p l and p 2 , and if e be the angle subtended by AB, we have from 57, X/?! 2 + 2/zp^ + vpJ - u e ~ (ps - Zptfz cos e + p./) = 0. Let us now transform this equation from the screws of reference A, B to another pair of screws A , B . Let p^, p., be the distances of X from A , B , respectively ; then, from Ptolemy s theorem, we have the following equations : pl .A B = p.;.AA - pl .AB , p,.A B = p 2 .A B-p, .BB . 122 THE THEORY OF SCREWS. [134 We thus see that p^ and p., are linear functions of /?/ and p. 2 } the several coefficients A B , A B, &c., in these two equations being constant. The equation for u is thus to be transformed by a linear substitution for p 1 and p.,. Of course ti e , being dependent only upon the position of X, is quite unaffected by the change of the screws of reference. We can therefore apply the well-known principle that the invariant of this binary quantic can only differ by a constant factor from the transformed value. The invariant is (\ - u e -) (v - u e 2 ) - (yu, + / cos e) 2 . This must be true for every point X, and therefore for all values of u g -. It is necessary that the coefficients of the terms in the expression itg 4 sin 2 e UQ" (X + v -f 2/t cos e) + \v p? shall be severally proportional to those in the transformed expression u e 4 sin 2 e u g - (X + v -f 2// cos e ) + XV // 2 . We thus obtain the two equations of condition, sin 2 e _ X + v + 2// cos e _ X i/- // 2 sin 2 e X + v + 2/it cos e Xp /A 2 The four quantities, X , /A , v , e , may now be chosen arbitrarily, subject to these two equations, which are the necessary as well as the sufficient conditions. Indeed it is obvious that there must be but two independent quantities corresponding to the two positions of A and B . We may impose two conditions on the four quantities, and for our present purpose we shall make X = v ; /u/ = 0. The equations of X and e are then sin 2 e _ 2X _V* sin 2 e X -4- 2/A cos e + v \v fi 2 and we obtain x/= 2 (^-A^ X + 2/A cos e + v 4 (\v - /u 2 ) sin - e = sin 1 e - s r, (X + 2/LA COS 6 + V) 2 X is thus uniquely determined, and the expression for sin 2 e gives for e four values of the type e , + (TT e ). The negative values are meaningless, and the two others are coincident, because the arc which subtends e on one side subtends IT e on the other. There is thus a single pair of screws of reference which permit the expression for u e - to be exhibited in the canonical form 134] PLANE REPRESENTATION OF DYNAMICAL PROBLEMS. 123 We are now led to a simple geometrical representation for u e 2 . Let A, B (fig. 19) be the two canonical screws of reference. Bisect AB in , then = -2AO -+2XO -, = 2XY.XO . It is obvious that the point must have a critical importance in the kinetic theory, and its fundamental property, which has just been proved, is expressed in the following theorem : If a rigid body be twisting with the unit of twist velocity about any screw X on the cylindroid, then its kinetic energy is proportional to the rectangle X . X Y, where is a fixed point. We are at once reminded of the theorem of 59, in which a similar law is found for the distribution of pitch, only in this case another point, 0, is used instead of the point . Both points, and , are of much significance in the representative circle. We can easily prove the following theorem, in which we call the polar of the axis of inertia : If a rigid body be twisting with the unit of twist velocity about X, then its kinetic energy is proportional to the perpendicular distance from X to the axis of inertia. The geometrical construction for the pitch given in 51 can also be applied to determine w fl 2 . This quantity is therefore proportional to the perpendicular from on the tangent at X. It thus appears that the representative circle gives a graphic illustration of the law of distribu tion of u e - around the screws on a cylindroid. The axis of inertia cannot cut the representative circle in real points, for 124 THE THEORY OF SCREWS. [134- otherwise we should have at either intersection a twist velocity without any kinetic energy. There is no similar restriction to the axis of pitch. We thus see that must always lie inside the circle, but that may be in any part of the plane. 135. Conjugate Screws of Inertia. We have already made much use of the conception of Conjugate Screws of Inertia. We shall here approach the subject in a manner different from that previously employed. Let a be a screw about which a rigid body is twisting with a twist velocity d ; let the body be simultaneously animated by a twist velocity /? about a screw /3. These two will compound into a twist velocity about some screw 6. If the body only had the first twist velocity, its kinetic energy would be Mv-ffi. If it only had the second, the energy would be Muf fP. When it has both twist velocities together, the kinetic energy is Mufti*. Generally it will not be true that the resulting kinetic energy is equal to the sum of the components ; but, under a special relation between a and /8, we can have this equality ; and as shown in 88 under these cir cumstances a and /3 are conjugate screws of inertia. The necessary condition is thus expressed : ufu* = u a 2 d* + M/j 2 /3 2 . We have now to prove the following important theorem : Any chord through the pole of the axis of inertia intersects the representa tive circle in a pair of conjugate screws of inertia. For we have 0- tct 2 :^ 2 :: AR- : BX* : AX 2 ; but if AB passes through the pole of the axis of inertia, then the centre of gravity of masses AIF at X, + BX" at A, and + AX- at B, will lie on the axis of inertia ; and, accordingly, uf = BX-u a 2 + whence which proves the theorem. Or we might have proceeded thus: From Ptolemy s theorem (fig. 19), AB.XY = AX .BY+AY.BX: multiplying by AB . XO , 136] PLANE REPRESENTATION OF DYNAMICAL PROBLEMS. but, from the property of the circle, B Y. XO = AX . BO ; A Y . XO = EX . A ; whence AB .XY. XO =AX\ AB. BO + BX>.AB.AO , from which we obtain, as before, 125 136. Impulsive Screws and Instantaneous Screws. A rigid body having two degrees of freedom lies initially at rest. It is suddenly acted upon by an impulsive wrench of large intensity acting for a short time. The body will, in general, commence to move by twisting about some screw on the cylindroid, and the kinetic problem now to be studied is the following : Given the impulsive screw, and the intensity of the impul sive wrench, find the instantaneous screw and the acquired twist velocity. The problem will be rendered more concise by the conception of the reduced wrench ( 96). It is to be remembered, that as the body is only partially free, there are an infinite number of screws on which wrenches would make the body commence to twist about a given screw on the cylin droid. For, let 6 be an impulsive screw situated anywhere, and let an impulsive wrench on cause the body to commence to move by twisting about some screw, a, on the cylindroid. Let \, /u-, v, p be any four screws reciprocal to the cylindroid. Then any wrench on a screw belonging to the system defined by these five screws will make the body commence to move by twisting about a. Let e be that one screw on the cylindroid which is reciprocal to 6, then e is reciprocal to the whole system defined by A,, /*, v, p, 0, and, conversely, each screw of this system will be reciprocal to e. We thus see that any screw, wherever situated, provided only that it is reciprocal to e, will be an impulsive screw corresponding to a as an instan taneous screw. Any one of this system may, with perfect generality, be chosen as the impulsive screw. Among them there is one which has a special feature. It is that screw, </>, on the cylindroid which is reciprocal to 77 ; and hence we have the following theorem ( 128): Given any screw, a, on the cylindroid, then there is in general another screw, </>, also on the cylindroid, such that an impulsive wrench administered on <f) will make the body twist about a. This correspondence of the two systems of screws must be of the one-to- one type ; for, suppose that two impulsive screws on the cylindroid had the same instantaneous screw, it would then be possible for two impulsive wrenches, of properly chosen intensities on two different screws, to produce 126 THE THEORY OF SCREWS. [136- equal and opposite twist velocities on the common instantaneous screw. The body would then not move, and therefore the two impulsive wrenches must equilibrate. But this is impossible, if they are on two different screws. 137. Two Homographic Systems. From what has been shown it might be expected that the points corre sponding to the instantaneous screws and those corresponding to the impulsive screws should, on the representative circle, form two homographic systems. That this is so we shall now prove. Let A, B (fig. 20) be a pair of impulsive screws, and let A , B be respec tively the corresponding pair of instantaneous screws, i.e. an impulsive wrench on A will make the body commence to twist about A , and similarly for B and B . Let an impulsive wrench on A, of unit intensity, generate a twist velocity, a, about A , and let /3 be the similar quantity for B and B . Let X be any other screw on which an impulsive wrench is to be applied to the body supposed quiescent. The body will commence to twist about some other screw, X , with a certain twist velocity fa. We can determine <Z> in the following manner: The unit impulsive wrench on X can be replaced by two component wrenches on A and B, the intensities of these being BX A;X ~AB AB respectively. These impulsive wrenches will generate about A , B twist velocities respectively equal to BX 138] PLANE REPRESENTATION OF DYNAMICAL PROBLEMS. 127 those components must, when compounded, produce the twist velocity &&gt; about X , and, accordingly, we have . BX . B X AX . A X Retaining A, B, A , B , as before, let us now introduce a second pair of points, Y and F , instead of X and X , and writing &&gt; instead of o>, we have .BY .,FT _ a AB ~ * A B AB ~ A B whence, eliminating a, /3, &&gt;, o> , we have 5Z BY B X FT AX : AY :: A X : A Y" As the length of a chord is proportional to the sine of the subtended angle, we see that the anharmonic ratio of the pencil, subtended by the four points A, B, X, Fat a point on the circumference, is equal to that subtended by their four correspondents, A , B , X , Y . We thus learn the following important theorem : A system of points on the representative circle, regarded as impulsive screws, and the corresponding system of instantaneous screws, form two homo- graphic systems. 138. The Homographic Axis. Let A, B, C, D (fig. 21) represent four impulsive screws, and let A , B , C , D be the four corresponding instantaneous screws. Then, by the well- Fig. 21. known homographic properties of the circle, the three points, L, M, N, will be collinear, and we have the following theorem : 128 THE THEORY OF SCREWS. [138- If A and B be any two impulsive screws, and if A and B be the corre sponding instantaneous screws, then the chords AR and BA will always intersect upon the fixed right line XY. This right line is called the homographic axis. It intersects the circle in two points, X and Y, which are the double points of the homographic systems. These points enjoy a special dynamical significance. They are the two Principal Screws of Inertia, and hence The homographic axis intersects the circle in two points, each of which possesses the property, that an impulsive wrench administered on that screw will make the body commence to move by twisting about the same screw. The method by which we have been conducted to the Principal Screws of Inertia shows how there are in general two, and only two, of these screws on the cylindroid. The homographic axis is the Pascal line, for the Hexagon AA BB CC , and thus we have a dynamical significance for Pascal s theorem. 139. Determination of the Homographic Axis. The two principal screws of inertia must be reciprocal, and must also be conjugate screws of inertia ( 84). The homographic axis must therefore comply with the conditions thus prescribed. We have already shown ( 58) the condition that two screws be reciprocal, and ( 135) the condition that two screws be conjugate screws of inertia, and, accordingly, we see 1. That the homographic axis must pass through 0, the pole of the axis of pitch. 2. That the homographic axis must pass through , the pole of the axis of inertia. The points and having been already determined we have accordingly, as the simplest construction for the homographic axis, the chord joining and . 140. Construction for Instantaneous Screws. The points and afford a simple construction for the instantaneous screw, corresponding to a given impulsive screw. The construction depends upon the following theorem ( 81): If two conjugate screws of inertia be regarded as instantaneous screws, then the impulsive screw corresponding to either is reciprocal to the other. Let A be an impulsive screw (fig. 22); if we join AO we obtain H, the screw reciprocal to A ; and if we join HO we obtain A , the conjugate screw 142] PLANE REPRESENTATION OF DYNAMICAL PROBLEMS. 129 of inertia to H. But, as A is the only screw reciprocal to H, it is necessary, by the theorem just given, that an impulsive wrench on A must make the body commence to move by twisting about A . Fig. 22. As and are fixed, it follows from a well-known theorem, that as otherwise proved in 137, A and A form two homographic systems. 141. Twist Velocity acquired by an Impulse. We can obtain a geometrical expression for the twist velocity acquired about A by a unit impulsive wrench on A (Fig. 22). It appears, from 90 (see also 147), that the twist velocity acquired on cc by an impulsive wrench on 77, is proportional to 2 The numerator being the virtual coefficient is proportional to AO.A H ( 68), and as u^ is proportional to A O .A H ( 134), we see that the required ratio varies as AO -f- A O which itself varies as HO HO hence we obtain the following theorem : The impulsive wrench on A, of intensity proportional to HO, generates a twist motion about A , with velocity proportional to HO . The geometrical representation of the effect of impulsive forces is thus completely determined both as regards the instantaneous screw, and the instantaneous twist velocity acquired. 142. Another Construction for the Twist Velocity. A still more concise method of determining the instantaneous screw can be obtained if we discard the points and , and introduce a new fixed point, ft, also on the homographic axis. B. 9 130 THE THEORY OF SCREWS. [142- Let X, Y (Fig. 23) be the two principal screws of inertia. Let A be an impulsive screw, and A the corresponding instantaneous screw. Draw Fig. 23. through -A the line AH parallel to XY. Join HA , and produce it to meet the homographic axis at fl. Let a be the twist velocity generated by an impulsive wrench of unit intensity at X, and let /3 be the corresponding quantity for F. It may be easily shown that the triangle AA X is similar to YA Cl, and that the triangle AA Y is similar to XA l ; whence we obtain A YflA __ AX~~ OF AY The unit wrench on A can be decomposed into components on X and F of respective intensities AY AX XY XY AX These will generate twist velocities AT a ~XY Let <w be the resulting twist velocity on A , then the components on X and F must be equal to the quantities just written ; whence A Y AY XY A X XY = a. and we obtain or, XY ZF CIA "OF 5 a : /3 :: OF: we thus see that O is a fixed point wherever A and A may be. 144J PLANE REPRESENTATION OF DYNAMICAL PROBLEMS. 131 It also follows that is constant ; whence we have the following theorem : Draw through the impulsive screw A a ray AH parallel to the homographic axis, then the ray from H to a fixed point fl on the homographic axis will cut the circle in the instantaneous screw A , and the acquired twist velocity will be inversely proportional to CIA . If the twist velocity to be acquired by A from a unit impulsive wrench on A be assigned, then CIA is determined : there will be two screws A , and two corresponding impulsive screws, either of which will solve the problem. The diameter through Cl indicates the two screws about which the body will acquire the greatest and the least velocities respectively with a given intensity for the impulsive wrench. 143. Twist Velocities on the Principal Screws. The quantities a and ft, which are the twist velocities acquired by unit impulsive wrenches on the principal screws, can be expressed geometrically as follows (Fig. 22) : Let to be the twist velocity acquired on A by the wrench on A, then, by the last article, aAY = (oA Y, /3AX=a,A X; A Y AY whence : ft :: ^ : ^ . This ratio is the anharmonic ratio of the four points X, Y, A, A , that is, of X, Y, 0, ; whence, finally, O Y OY * : P O X OX 144. Another Investigation of the Twist Velocity acquired by an Impulse. We have just seen that <*AY=a>A Y, whence aft AX . AY= tfA X . A Y. Let fall perpendiculars AP, A P , HQ on the homographic axis (Fig. 24). Then, by the properties of the circle,. AX. AY : A X. A Y :: AP : A P ; so that a/3 A P = a>-A P . 92 132 THE THEORY OF SCREWS. By similar triangles, [144, whence or, as before ( 141), Fig. 24. OA . O H O H* CO X OH OH It will be noticed that, for this investigation, H may have been chosen arbitrarily on the circle. We thus see that, besides the two points and , there will be a system of pairs of points of which any one may be employed for finding the instantaneous screw, and for determining the instantaneous twist velocity. If we choose any two points (Fig. 25), fl and H , so that Fig. 25. then A being given, Al determines H, and Hfl determines A , while the twist velocity is proportional to O T/ -=- IH. We can suppose fl at infinity, 145] PLANE REPRESENTATION OF DYNAMICAL PROBLEMS. 133 and thus obtain the construction used in 142. A similar construction is obtained when fl is at infinity. The two points, A and A , will divide the arc cut off by XY in a constant anharmonic ratio, for the pencil H (XQQ Y) always preserves the same anharmonic ratio as H moves round the circle. 145. A Special Case. If 77 be an impulsive screw, arid if a be the corresponding instantaneous screw, it will not usually happen that when a. is the impulsive screw ij is the corresponding instantaneous screw. If, however, in even a single case, it be true that the impulsive screw and the instantaneous screw are interchange able, then the relation will be universally true. Let fl and 1 (Fig. 26) be a pair of points belonging to the system described in 144. Then A being given, A is found. If A is similarly to Fig. 26. determine A, then the figure shows that fl must lie on the polar of fl , and, consequently, fl and fl are conjugate points with respect to the circle; or, what comes to the same thing, they divide XY harmonically. The same must be true of each pair of points H and fl , and therefore of and , and we have the following theorem : If the points and be harmonic conjugates of the points where the homo- graphic axis intersects the circle, then every pair of instantaneous and impulsive screws on the cylindroid are interchangeable. We might, perhaps, speak of this condition of the system as one of dynamical involution. In this remarkable case an impulsive wrench of unit intensity applied to one of the principal screws of inertia will generate a velocity equal and opposite to that which would have been produced if the wrench had been applied to the other principal screw. The construction 134 THE THEORY OF SCREWS. [145, for the pairs of related screws becomes still more simplified by the theorem, that When the system is one of dynamical involution, the chord joining an impulsive screw with its instantaneous screw passes through the pole of the homograpldc axis. We may take the opportunity of remarking, that dynamical involution is not confined to the system of the second order. It may be extended to a rigid body with any number of degrees of freedom, or even to any system of rigid bodies. Whenever it happens that the relation of impulsive screw and instantaneous screw is interchangeable in one case, it is interchangeable in every case. For, let O l , ... 6 n be the co-ordinates of an instantaneous screw, then ( 97) the corresponding impulsive screw has for co-ordinates, MI n u n a v ly ... v n ; PI Pn and if this latter were regarded as an instantaneous screw, then its impulsive screw would be 3 * Pn but as this is to be only we must have which shows that if the theorem be true for one pair, it is true for all. The conditions, of course, are, that any one of the following systems of equations be satisfied : 1/2 ,.2 ,,. 2 , "i _ i III _ i U n ~ Pi ~ P 2 ~ ~ Pn 146. Another Construction for the Twist Velocity acquired by an Impulse. Reverting to the general case, we find that the chord A A (Fig. 27) is cut by the homographic axis at T, so that the square of the acquired twist velocity is proportional to the ratio of TA to TA . For, with the construction in 142, draw HQ parallel to AT; then, AT 146] PLANE REPRESENTATION OF DYNAMICAL PROBLEMS. 135 but we showed, in the article referred to, that A l varies inversely as the acquired twist velocity, whence the theorem is proved. Fig. 27. This is, in one respect, the simplest construction, for it only involves the chord A A and the homographic axis. The chord A A must envelop a conic having double contact with the circle (Fig. 28), for this is a general property of the chord uniting two corre sponding points, A and A , of two homographic systems. Let / be the Fig. 28. point of contact of the chord and conic (Fig. 28). Then A A is divided harmonically in 7 and T ; for, if ZFbe projected to infinity, the two conies become concentric circles, and the tangent to one meets it at the middle point of the chord in the other ; the ratio is therefore harmonic, and must be so in every projection ; whence, AI _^AT A I A T but the last varies as the square of the twist velocity acquired, and hence we see that 136 THE THEORY OF SCREWS. [146- The chord joining any impulsive screw A to the corresponding instantaneous screw A envelops a conic, and the point of contact, I, divides the chord into segments, so that the ratio of A I to A I is proportional to the square of the twist velocity acquired about A by the unit impulsive wrench on A. 147. Constrained Motion. We can now give another demonstration of the theorem in 90, which is thus stated : If a body, constrained to twist about the screw a, be acted upon by an impulsive wrench on the screw 77, then the twist velocity acquired varies as W 2 The numerator in this expression is the virtual coefficient of the two screws, and the denominator is the function of 134, which is proportional to the kinetic energy of the body when twisting about a with the unit of twist velocity. Let a and t] be represented by A and I respectively (Fig. 29), and let A Fig. 29. be the impulsive screw which would correspond to A if the body had been free to twist about any screw whatever on the cylindroid defined by A and A . Let K be reciprocal to A . The impulsive wrench on / is decomposed into components on K and A. The former is neutralized by the constraints ; the latter has the intensity KI KA whence the twist velocity &&gt;, acquired by A , is ( 141) proportional to KI HO KA HO 148] PLANE REPRESENTATION OF DYNAMICAL PROBLEMS. 137 but, by geometry, whence, 63, ft) GC x OA KI.HO .OA HO.HA .OA A .HA 3C ~i> j which is the required result. 148. Energy acquired by an Impulse. The kinetic energy acquired by a given impulse, using the same notation as before, is ( 91) proportional to Let A be the impulsive screw, and A the screw about which the body is constrained to twist. Draw the chord AOH (Fig. 30), then, as A varies, Fig. 30. while A is fixed, the virtual coefficient of A and A varies as A H (63). The square of this is proportional to AT, the length of the perpendicular from A on the tangent at H. If PQ be the axis of inertia, the value of u* is proportional to the perpendicular A Q, and, accordingly, the kinetic energy acquired is proportional to AT 138 THE THEORY OF SCREWS. [148- Any ray through P, the intersection of the axis of inertia with the tangent at H, cuts the circle in two points, A and A", either of which will receive the same kinetic energy from the given impulse. 149. Euler s Theorem. If the body be permitted to select the screw about which it will commence to twist, then, as already mentioned, 94, Euler s theorem states that the body will commence to move with a greater kinetic energy than if it be restricted to some other screw. By drawing the tangent from P (not, however, shown in the figure) we obtain the point of contact B, where it is obvious that the ratio of the perpendiculars on PH and PQ is a maximum, and, consequently, the kinetic energy is greatest. It follows from Euler s theorem that B will be the instantaneous screw corresponding to A as the impulsive screw. The line BH is the .polar of P, and, consequently, BH must contain , the pole of the axis of inertia. We are thus again led to the construction ( 140) for the instantaneous screw 5; that is, draw AOH, and then HO B. 150. To determine a Screw that will acquire a given Twist Velocity under a given Impulse. The impulsive screw being given, and the intensity of the impulsive wrench being one unit, the acquired twist velocity ( 147) will vary as (Fig. 30), AfH A Q If, therefore, the twist velocity be given, this ratio is given. A must then lie on a given ellipse, with H as the focus and the axis of inertia as the directrix. This ellipse will intersect the circle in four points, any one of which gives a screw which fulfils the condition proposed in the problem. The relation between the intensity of the impulsive wrench and the twist velocity generated can be also investigated as follows : Let P, Q, R, S be points on the circle (Fig. 31) corresponding to four im pulsive screws, and let P , Q , R , S be the four corresponding instantaneous screws deduced by the construction already given. Let p, q, r, s denote the intensities of the impulsive wrenches on P, Q, R, S, which will give the units of twist velocity on P , Q , R, S . Supposing that impulsive wrenches on P, Q, R neutralize, then the corresponding twist velocities generated on P , Q , R must neutralize also. In the former case, the intensities must be proportional to the sides of the triangle PQR ; in the latter, the twist 150] PLANE REPRESENTATION OF DYNAMICAL PROBLEMS. 139 velocities must be proportional to the sides of the triangle P Q R . Introducing another quantity d, we have rP Q = dPQ, qP R = dPR, The three other groups of equations are similarly obtained rQ S = aQS, qP S = cPS, rP S = bPS, sR Q = aRQ, sQ P = cQP, sR P = bRP. Whence we easily deduce ap = bq = cr = ds = hpqrs, where h is a new quantity. We hence obtain from the first equation P Q = hPQpq. As this is absolutely independent of R and S, it follows that h must be inde pendent of the special points chosen, and that consequently for any two points on the circle P and Q, with their corresponding points P and Q , we must have P Q PI 140 THE THEORY OF SCREWS. [150- In the limit we allow P and Q to coalesce, in which case, of course, P and Q coalesce, and p and q become coincident ; but obviously we have then PQ : ML :: PX : LX, P Q : ML :: P Y : LY- P Q P Y LX whence PQ = PX = LY> and as P Foc -L and PX oc , we have finally p oc - T v . Li The result is, of course, the same as that of 141. Being given the impulsive screw corresponding to P, we find P by drawing PXL and LYP ; and then to produce a unit twist velocity on P , the intensity of the impul sive wrench on P must be proportional to LX -r- LY. It is obvious that by a proper adjustment of the units of length, force and twist velocity, LX may be the intensity of the impulsive wrench, and LY the acquired twist velocity. 151. Principal Screws of the Potential. Let us suppose that a body having two degrees of freedom is in a position of stable equilibrium under the influence of a conservative system of forces. If the body be displaced by a small twist, it will no longer be in a position of equilibrium, and a wrench has commenced to act upon it. This wrench can always, by suitable composition with the reactions of the constraints, be replaced by an equivalent wrench on a screw of the cylindroid (see 96). For every point H, corresponding to a displacement screw, we have a related point, H , corresponding to the screw about which the wrench is evoked. The relation is of the one-to-one type, and it will now be proved that the system of screws H is homographic with the corresponding system H . The proof is obtained in the same manner as that already given in 137, for impulsive and instantaneous screws. Let E be a displacement screw about which a twist of unit magnitude evokes a wrench of intensity e on E ; let f be the similar quantity for another pair of screws, F and F . A twist of unit amplitude about H may be decomposed into components, HF HE EF EF about E and F, respectively. 152] PLANE REPRESENTATION OF DYNAMICAL PROBLEMS. 141 These will evoke wrenches on E and F of the intensities HF HE EF EF respectively. But this pair of wrenches are to compound into a wrench of intensity h on H , and consequently we have H F HF H E _ S EF HF H F , whence ~ : , :: J : e. If we take another pair of points, K and K , we have KF H F K F ^ HE : KE :: H E K E whence (HKFE) = (H K F E ). Thus, the anharmonic ratio of any four points in one system is equal to that of their correspondents, and the two systems are homographic. The homographic axis intersects the circle in two points, which are the principal screws of the potential, i.e. a twist about either evokes a wrench on the same screw. Of course this homographic axis is distinct from that in 139. But this homographic axis, like the former one, passes through the pole of the axis of pitch because the principal screws of the potential are reciprocal. 152. Work done by a Twist. Suppose that the body, when in equilibrium under the system of forces, receives a twist of small amplitude of about any screw a, a quantity of work is expended, which we shall denote by Fv a -a 2 . In this, F is a constant, whose dimensions are a mass divided by the square of a time, and v* is a linear magnitude specially appropriate to the screw a, and depending also upon the system of forces ( 102). We may compare and contrast the three quantities,^, u a , v a : each is a linear magnitude specially correlated to the screw a. The first and simplest, p a , is the pitch of the screw, and depends on the geometrical nature of the constraints ; u a involves also the mass of the body, and the distribution of the mass relatively to a ; v a , still more complicated, depends also on the system of forces. 142 THE THEORY OF SCREWS. [153- 153. Law of Distribution of v a . As we follow the screw a around the circle, it becomes of interest to study the corresponding variations of the linear magnitude v a . We have already found a very concise representation of p a and u a by the axis of pitch and the axis of inertia, respectively. We shall now obtain a similar representation of v a by the aid of the axis of potential. It is shown ( 102) that v a 2 must be a quadratic function of the co ordinates; we may therefore apply to this function the same reasoning as we applied to u a 2 ( 134). We learn that v a 2 is at each point proportional to the perpendicular on a ray, which is the axis of potential. Thus, if A (Fig. 32) be the screw, the value of v a 2 is proportional to AP, the perpendicular on PT\ if 0" be the pole of the axis of potential, then, as in 59, we can also represent the value of v a ~ by the product AO". A A . 154. Conjugate Screws of Potential. In general the energy expended by a small twist from a position of equilibrium can be represented by a quadratic function of the co-ordinates of the screw. If, moreover, the two screws of reference form what are called conjugate screws of potential ( 100), then the energy is simply the sum of two square terms. The necessary and sufficient condition that the two screws shall be so related is, that their chord shall pass through 0". Another property of two conjugate screws of potential is also analogous to that of two conjugate screws of inertia. If A and A be two conjugate screws of potential, then the wrench evoked by a twist round A is reciprocal to A , and the wrench evoked by a twist around A is reciprocal to A. 156] PLANE REPRESENTATION OF DYNAMICAL PROBLEMS. 143 155. Determination of the Wrench evoked by a Twist. The theorem just enunciated provides a simple means of discovering the wrench which would be evoked by a small twist which removes the body from a position of equilibrium. Let A (Fig. 33) be the given screw; join AO", and find H; then the required screw A must be reciprocal to H, and is, accordingly, found by drawing the chord HA through 0. Fig. 33. The axis 00" is of course the homographic axis of 151. We need not here repeat the demonstration of 141, which will apply, mutatis mutandis, to the present problem. We see that the ratio of the intensity of the wrench to the amplitude of the twist is proportional to HO HO" The other constructions of a like character can also be applied to this case. 156. Harmonic Screws. If after displacement the rigid body be released, and small oscillations result, the present geometrical method permits us to study the resulting movements. It has been shown ( 130) that there are two special screws on the surface, each of which possesses the property of being a harmonic screw. If a body be displaced from rest by a small twist about a harmonic screw, and if it also receive any small initial twist velocity about the same screw, then the body will continue for ever to perform harmonic twist oscillations about the same screw. The two harmonic screws are X and T, where the circle is intersected by the axis passing through the pole of the axis of inertia , and the pole of the axis of potential 0" (Fig. 34). 144 THE THEORY OF SCREWS. [156- For, suppose the body receives a small initial displacement about X, this will evoke a wrench on H, found by drawing XO"Y and YOH ( 155). But the Fig. 34. effect of a wrench on H will be to produce twist velocity about a screw found by drawing HOY and YO X, i.e. X itself ( 140). Hence the wrench evoked can only make the body still continue to twist about X, and harmonic vibration on X will be the result. Similar reasoning, of course, applies to Y. 157. Small Oscillations in general. The initial displacement, and the initial twist velocity of the body, can always be decomposed into their respective components on X and Y. The resulting small oscillations can thus be produced by compounding simple harmonic twist oscillations about X and Y. If it should happen that and 0" become coincident, then every screw would be a harmonic screw. If and coincided, then every screw would be a principal screw of inertia ( 86). If and 0" coincided, then every screw would be a principal screw of potential. 158. Conclusion. The object proposed in this Chapter has now been completed. It has been demonstrated that the representative circle affords a concise method of exhibiting many problems in the Dynamics of a Rigid System with two degrees of freedom, so long as the body remains near its initial position. The geometrical interest of the enquiry is found mainly to depend on the completely general nature of the constraints. If the constraints be specialized to those with which mechanical problems have made us familiar, it will 158] PLANE REPRESENTATION OF DYNAMICAL PROBLEMS. 145 frequently be found that the geometrical theory assumes some extreme and uninteresting type. For instance, a case often quoted as an illustration of two degrees of freedom, is that of a body free to rotate around an axis, and to slide along it. The representative circle has then an infinite radius, and the finite portion thereof is merely a ray perpendicular to the axis of pitch. The geometrical theory then retains merely a vestige of its interest. B. 10 CHAPTER XIII. THE GEOMETRY OF THE CYLINDROID. 159. Another investigation of the Cylindroid. The laws of the composition of twists and wrenches are of such funda mental importance in the present subject that the following method* of investigating the cylindroid seems worthy of attention. This method is not, however, presented as a substitute for that already given (Chap. II.) which is certainly both more simple and more direct. Let a and /3 be any two screws, then if a body receives a twist about a, followed by another twist about /3, the position arrived at could have been reached by a single twist about a third screw 7. If the amplitudes of the twists about a and ft are given, then the position of 7, as well as the ampli tude of the resultant twist thereon, are, of course, both determined. If, however, the amplitudes of the twists on a and ft are made to vary while the screws a and ft themselves remain fixed, then the position of 7, no less than the amplitude of the resultant twist, must both vary. It has however been shown in 9 that the position and pitch of 7 remain constant so long as the ratio of the amplitudes of the twists about a and ft remains unchanged. As this ratio varies, the position of 7 will vary, so that this position is a function of a single parameter ; and, accordingly, 7 must be restricted to be one of the generators of a certain ruled surface S, which includes a and ft as extreme cases in which the ratio is zero and infinity respectively. Let 6 l be a screw which is reciprocal both to a and ft, then 6 l must also be reciprocal to every screw 7 on S. Let 2 , 3> # 4 be three other screws also reciprocal to S. Since a screw is defined by five conditions, it is plain that a screw which fulfils the four conditions of being reciprocal to lf # 2 > 0s> $4 will have one disposable parameter, and must, therefore, be generally confined to a certain ruled surface. This surface must include S, inasmuch as all the screws on S are reciprocal to l} 2 , 3 , 4 ; but further, it cannot include any * Proceedings of the Royal Irish Academy, 2nd Ser., Vol. iv. p. 518 (1885). 159] THE GEOMETRY OF THE CYLINDROID. 147 screw e not on S ; for as e and any screw 7 on S are reciprocal to lt # a , 3 ,0 4 , it will follow that any screw on the surface made from e and 7, just as S is made from a and ft, must also be reciprocal to 6 l) 2 , 3 , 4 . As 7 may be selected arbitrarily on S, we should thus find that the screws reciprocal to &i, &2, $s> #4 were not limited to one surface, but constituted a whole group of surfaces, which is contrary to what has been already shown. It is therefore the same thing to say that a screw lies on S, as to say that it is reciprocal to 0i, 6* d. ( 24). Since the condition of reciprocity involves the pitches of the two screws in an expression containing only their sum, it follows that if all the pitches on 1} 2 , 3 , # 4 be diminished by any constant in, and all those on S be increased by m, the reciprocity will be undisturbed. Hence, if the pitches of all the screws on S be increased by + m, the surface so modified will still retain the property, that twists about any three screws will neutralize each other if the amplitudes be properly chosen. We can now show that there cannot be more than two screws of equal pitch on 8 ; for suppose there were three screws of pitch m, apply the constant m to all, thus producing on S three screws of zero pitch. It must therefore follow that three forces on 8 can be made to neutralize ; but this is obviously impossible, unless these forces intersect in a point and lie on a plane. In this case the whole surface degrades to a plane, and the case is a special one devoid of interest for our present purpose. It will, however, be seen that in general S does possess two screws of any given pitch. We can easily show that a wrench can always be decomposed into two forces in such a way that the line of action of one of these forces is arbitrary. Suppose that 8 only possessed one screw A, of pitch m. Reduce this pitch to zero ; then any other wrench must be capable of decomposition into a force on X (i.e. a wrench of pitch zero), and a force on some other line which must lie on S; therefore in its transformed character there must be a second screw of zero pitch on S, and, therefore, in its original form there must have been two screws of the given pitch m. Intersecting screws are reciprocal if they are rectangular, or if their pitches be equal and opposite ; hence it follows that a screw 6 reciprocal to S must intersect 8 in certain points, the screws through which are either at right angles to or have an equal and opposite pitch thereto. From this we can readily show that S must be of a higher degree than the second ; for suppose it were a hyperboloid and that the screws lay on the generators of one species A, a screw which intersected two screws of equal pitch m must, when it receives the pitch m, be reciprocal to the entire system A. We can take for one of the generators on the hyper boloid belonging to the species B ; will then intersect every screw of the 10-2 148 THE THEORY OF SCREWS. [159 surface ; it must also be reciprocal to all these ; and, as there are only two screws of the given pitch, it will follow that 6 must cut at right angles every generator of the species A. The same would have to be true for any other reciprocal screw < similarly chosen ; but it is obvious that two lines 6 and < cannot be found which will cut all the generators at right angles, unless, indeed, in the extreme case when all these are coplanar and parallel. In the general case it would require two common perpendiculars to two rays, which is, of course, impossible. We hence see that S cannot be a surface of the second degree. We have thus demonstrated that 8 must be at least of the third degree in other words, that a line which pierces the surface in two points will pierce it in at least one more. Let a and ft be two screws on 8 of equal pitch in, and let 6 be a screw of pitch m which intersects a and ft. It follows that 6 is reciprocal both to a and ft, and therefore it must be reciprocal to every screw of 8. Let 6 cut 8 in a third point through which the screw 7 is to be drawn, then 6 and 7 are reciprocal ; but they cannot have equal and opposite pitches, because then the pitch of 7 should be equal to that of a and ft. We should thus have three screws on the surface of the same pitch, which is impossible. It is therefore necessary that 6 shall always intersect 7 at right angles. From this it will be easily seen that 8 must be of the third degree ; for suppose that 6 intersected 8 in a fourth point, through which a screw 8 passed, then 6 would have to be reciprocal to 8, because it is reciprocal to all the screws of $; and it would thus be necessary for 9 to be at right angles to 8. Take then the four rays a, ft, 7, 8, and draw across them the two common transversals 6 and <. We can show, in like manner, that (j) is at right angles to 7 and 8. We should thus have 6 and </> as two common perpendiculars to the two rays 7 and 8. This is impossible, unless 7 and 8 were in the same plane, and were parallel. If, however, 7 and 8 be so circumstanced, then twists about them can only produce a resultant twist also parallel to 7 and 8, and in the same plane. The entire surface 8 would thus degenerate into a plane. We are thus conducted to the result that 8 must be a ruled surface of the third degree, and we can ascertain its complete character. Since any transversal 6 across a, ft, and 7 must be a reciprocal screw, if its pitch be equal and opposite to those of a and ft, it will follow that each such trans versal must be at right angles to 7. This will restrict the situation of 7, for unless it be specially placed with respect to a and ft, the transversal 6 will not always fulfil this condition. Imagine a plane perpendicular to 7, then this plane contains a line / at infinity, and the ray 6 must intersect / as the necessary condition that it cuts 7 at right angles. As 6 changes its position, it traces out a quadric surface, and as I is one of the generators of that quadric, it must be a hyperbolic paraboloid. The three rays a, ft, 7, 159] THE GEOMETRY OF THE CYLINDROID. 149 belonging to the other system on the paraboloid must also be parallel to a plane, being that denned by the other generator / , in which the plane at infinity cuts the quadric. Let PQ be a common perpendicular to a and 7, then since it intersects 7 at right angles, it must also intersect / ; and since PQ cuts the three generators of the paraboloid a, 7 and /, it must be itself a generator, and therefore intersects ft. But a, ft, 7 are all parallel to the same plane, and hence the common perpendicular to a and 7 must be also perpendicular to ft. We hence deduce the important result, that all the screws on the surface S must intersect the common perpendicular to a and ft, and be at right angles thereto. The geometrical construction of S is then as follows: Draw two rays a and ft, and also their common perpendicular X. Draw any third ray 6, subject only to the condition that it shall intersect both a and ft. Then the common perpendicular p to both and X will be one of the required generators, and as 6 varies this perpendicular will trace out the surface. It might at first appear that there should be a doubly infinite series of common perpendiculars p to X and to 6. Were this so, of course S would not be a surface. The difficulty is removed by the consideration that every trans versal across p, a, ft is perpendicular to p. Each p thus corresponds to a singly infinite number of screws 9, and all the rays p form only a singly infinite series, i.e. a surface. A simple geometrical relation can now be proved. Let the perpendicular distance between p and a be d lt and the angle between p and a be A l ; let d z and A 2 be the similar quantities for p and ft, then it will be obvious that rfj : d z : : tan A l : tan A 2 ; or rfj + d 2 : d 1 d. 2 : : sin (A^ + A 2 ) : sin (A l A 2 ), if z be the distance of p from the central point of the perpendicular h between a and ft ; and if e be the angle between a and ft, and 6 be the angle made by p with a parallel to the bisector of the angle e, then we have from the above z : h : : sin 2< : sin 2e. The equation of the surface 8 is now deduced for oc tan 6 = - ; y whence we obtain the equation of the cylindroid in the well-known form z (# 2 + */*) = xy. sm 2e * The law of the distribution of pitch upon the cylindroid can also be deduced 150 THE THEORY OF SCREWS. [159 from the same principles. If a and yS are screws of zero pitch, then any reciprocal transversal 6 will be also of zero pitch ; and as p must be reciprocal to 6, it will follow that the pitch of p must be equal to the product of the shortest perpendicular distance between p and 6, and the tangent of the angle between the two lines. In short, the pitch of p must simply be equal to what is sometimes called the moment between p and 6. We are also led to the following construction for the cylindroid. Draw a plane pencil of rays and another ray L, situated anyivhere. Then the common perpendiculars to L and the several rays of the pencil trace out the cylindroid. I have already mentioned (p. 20) that the first model of the cylindroid was made by Plucker in illustration of his Neue Geometric des Raumes. The model of the surface which is represented in the Frontispiece was made from my design by Sir Howard Grubb, the cost being defrayed by a grant from the Scientific Fund of the Royal Irish Academy. A hollow cylinder was mounted on a dividing engine and holes were drilled at the calculated points. Silver wires were then stretched across in the positions of the generators and a beautiful model is the result. The equation to the tangent cone drawn from the point x, y , z to the surface, z (x 2 4- y 2 ) - 2mxy = 0, is of the fourth degree and is given by equating to zero the discriminant of the following function in &&gt;, to 3 (xz- zx) - <u 2 [yz -zy + 2m (x - x }} + o> {xz - zx + 2m (y - y )} + zy - yz. This cone has three cuspidal edges, and accordingly the model exhibits in every aspect a remarkable tricuspid arrangement. I here give the details of the construction of the much simpler model of the cylindroid figured in Plate II.* A boxwood cylinder, O m lo long and O m> 05 in diameter, is chucked to the mandril of a lathe furnished with a dividing plate. A drill is mounted on the slide rest, and driven by overhead gear. The parameter p a -p ft (in the present case O ^OGG) is divided into one hundred parts. By the screw, which moves the slide rest parallel to the bed of the lathe, the drill can be moved to any number z of these parts from its original position at the centre of the length of the cylinder. Four holes are to be drilled for each value of z. These consist of two pairs of diametrically opposite holes. The directions of the holes intersect the * See Transactions of Royal Irish Academy, Vol. xxv. p. 216 (1871) ; and also Phil. Mag. Vol. XLII. p. 181 (1871); also B. A. Report, Edinburgh, 1871. THE CYLINDROID. To face IL 150 159] THE GEOMETRY OF THE CYLINDROID. 151 axis of the cylinder at right angles. The following table will enable the work to be executed with facility. I is the angle of 13 : z I 90-1 180 + 1 270 -I o-o 90 180 270 17-4 5 85 185 265 34-2 10 80 190 260 50-0 15 75 195 255 64-3 20 70 200 250 76-5 25 65 205 245 86-6 30 60 210 240 94-0 35 55 215 235 98-5 40 50 220 230 100-0 45 45 225 225 For example, when the slide has been moved 34 2 parts from the centre of the cylinder, the dividing plate is to be set successively to 10, 80, 190, 260, and a hole is to be drilled in at each of these positions. The slide rest is then to be moved on to 50 parts, and holes are to be drilled in at 15, 75, 195, 255. Steel wires, each about O m- 3 long, are to be forced into the holes thus made, and half the surface is formed. The remaining half can be similarly constructed : a length of n 066 cos 21 is to be coloured upon each wire to show the pitch. The sign of the pitch is indicated by using one colour for positive, and another colour for negative pitches. Among the various other representations of the cylindroid I can now do no more than refer to an ingenious plan described by Goebel in his Neueren Statik, by which a model of this surface in card-board can be made with facility. There is also a model in the collection of the Cavendish Laboratory at Cambridge, and another belonging to the Mathematical Society of London, which, like that figured in Plate II., was made by myself. Sir Howard Grubb has also made a second model with the same dimensions as that figured in the frontispiece but mounted in a different manner. This exquisite exhibition of a ruled surface is the property of Mr G. L. Cathcart, Fellow of Trinity College, Dublin. A suggestive construction for the cylindroid has been also given by Professor G. Minchin in his well-known book on Statics, and we have already mentioned (note to 50) the construction given by Mr Lewis. 152 THE THEORY OF SCREWS. [160 160. Equation to plane section of Cylindroid. Each generator of the cylindroid is the abode of a certain screw, and accordingly each point in a plane section will lie on one screw, and generally on only one. We may, accordingly, regard the several points of the cubic as in correspondence with the several screws on the cylindroid. It will often be convenient to speak of the points on the section as synonymous with the screws themselves which pass through those points. We must first investigate the equation* to the cubic curve produced by cutting the cylindroid by a plane situated in any arbitrary position. Fig. 35. Let OX and OF (Fig. 35) be the two principal screws of the cylindroid of which OH is the nodal line. Let XYl be the arbitrary plane of section. The position of this plane is defined by the magnitudes h, a, (3, whereof h is the length of the perpendicular from on XY, a. is the angle between OR and OX, and ft is the angle ORl, or the inclination of the plane of section to the principal plane of the cylindroid. Draw through H the line 1$ parallel to XY; then we shall adopt IN as the new axis of x and SIR as the new axis of y, so that if P be any point on the surface, we have PN = y and IN = x. The dotted letters, x , y , z refer to the original axes of the cylindroid. Let fall PT perpendicular on the plane of OXY, and TM perpendicular to XY. Then we have MN= whence y + z cosec ft = h sec /3 (i), * Transactions of the Eoyal Irish Academy, Vol. xxix. p. 1 (1887). 160] THE GEOMETRY OF THE CYLINDRO1D. 153 while, if 6 be the angle XOT, and OT be denoted by r, we have x = r sin(0 - a), or x = y cos a x sin a (ii) ; but, obviously, OR = r cos (0 - a) + M T ; whence h = x cos a 4- y sin a + z cot /3 (iii). Solving the equations (i), (ii), (iii), we obtain x e = x sin a + y cos /3 cos a, y = + x cos a + y cos /3 sin a, z = h tan /3 y sin /3. It appears from these that # 2 + y z = x* + ifcos 2 ft, a; ?/ = #?/ cos /3 cos 2 a + (y 2 cos 2 /3 # 2 ) sin a cos a. The equation of the cylindroid gives z (x z + y 2 ) = Zmx y ; whence we deduce, as the required equation of the section, (h tan ft - y sin /3) (# 2 + y z cos 2 /3) = 2m3ry cos ft cos 2a + 2m sin a cos a (y 2 cos 2 ft a?); or, arranging the terms, sin /3 cos 3 fty 3 + sin yS?/a; 2 (m sin 2a + h tan /3) # 2 + Zmxy cos /3 cos 2 + (m sin 2a cos 2 ft h sin /3 cos /3) y J = 0. It is often convenient to use the expressions x = h tan (6 0) m sin 20 cot ft tan (0 a), y = hsecft msin 20cosec/3, from which, if be eliminated, the same equation for the cubic is obtained ; or, still more concisely, we may write x = y cos ft tan (0 a), y = h sec ft m sin 20 cosec ft. This cubic has one real asymptote, the equation of which is ysinft = m sin 2a + h tan ft, and the asymptote cuts the curve in the finite point for which x = tan 2a (h + m sin 2a cot ft). The value of at this point is a. 154 [160, Fig. 36. EXPLANATION OF FIG. 36. General Section of the Cylindroid, showing (1) Cubic with the double point 0. (2) Asymptote of the cubic. (3) The parabola, which is the envelope of the chords joining screws of equal pitch. (4) Hyperbola having triple contact with the cubic, being envelope of reciprocal chords. (5) Section of the principal plane. It is a tangent to the hyperbola. (6) A tangent to the parabola, showing two screws, P and Q, of equal pitch. (7) Common tangents to the parabola and the cubic, touching the latter at the two principal screws. (8) Any tangent to the hyperbola intersects the cubic in three points, two of which belong to reciprocal screws (not shown). Equations of Cubic. Equation of Parabola. Equations of Hyperbola. a; = -9f/tan(0-25 ), /_ x \ 2 a; = 1-6 21-6 sec047 5 tan 0, y = 20 -66 sin 20. V ~ \ + 15J y = - 12-8 + 32 8 sec <f>. 161] THE GEOMETRY OF THE CYLINDROID. 155 In Fig. 36 will be found a drawing of this curve. The following are the values of the constants adopted : a = 25; /3 = 26; h = lS; wi = 28 9; with which the equations become = % tan (0-25), y = 20 - 66 sin 20. The curve was plotted down on " papier millimetrique," and has been copied in reduced size in the figure. The constants were selected after several trials, in order to give a curve that should be at once characteristic, and of manageable dimensions. The distribution of pitch upon the screws of the cylindroid is of fundamental importance in the theory, so that we must express the pitches appropriate to the several points on the cubic. Let p denote the pitch ; then, from the known property of the cylindroid, p=p + mcos 26, where p Q is a constant. Transforming this result into the co-ordinates of the point on the cubic, we have (x 2 if cos 2 ft) cos 2a + 2xy cos 8 sin 2a /\1 /i /vvi v_ * P ~ P ^ + 2/ 2 cos 2 /3 161. Chord joining Two Screws of Equal Pitch. As the pitches of the two screws, defined by + and 6, are equal, the chord in question is found by drawing the line through the points x , y and x", y", respectively, where x = y cos ft tan (9 a), y = h sec ft m cosec ft sin 20, x" = y" cos ft tan ( a), y" = h sec ft + m cosec ft sin 20. After a few reductions, the required equation is found to be xm (cos 20 + cos 2a) + y (h sin ft + m cos ft sin 2a) - h- tan ft + m 2 cot ft sin 2 20 - 0. If this chord passes through the origin, then - h* tan- ft + ??i 2 sin 2 20 = ; or, h tan m sin 20 = 0. But this is obviously necessary ; for from the geometry of the cylindroid it is plain that must then fulfil the required condition. 156 THE THEORY OF SCREWS. [161, We can also determine the chord in a somewhat different manner, which has the advantage of giving certain other expressions that may be of service. Let U = be the cubic curve. Let V= be the equation of the two straight lines from the origin to the points of intersection with the two equal pitch screws + 6. Let L = be the chord joining the two intersections of U and V, distinct from the origin : this is, of course, the chord now sought for. Then we must have an identity of the type cU=VX where c is some constant. For the conditions L = and V= imply U=0, and L cuts U in three points, two of which lie on V, and the third point, called /, must lie on X. The line X is otherwise arbitrary, and we may, for con venience, take it to be the line 11 from the origin to /. The product VX thus contains only terms of the third degree, and accordingly the terms of the second degree in U must be sought in LY. Let U=u 3 +u 2 where u 3 and u 2 are of the third and second degrees respectively, then cu. 2 must be the quadratic part of the product L Y. As L does not pass through the origin, it must have an absolute term, conse quently Y must not contain either an absolute term or a term of the first degree. If, therefore, c be the absolute term in L, it is plain that Y must be simply u 2 , and we have accordingly, c (u s + MS) = VX + (L + c) u 2 , where L denotes the value of L without the absolute term : we have con sequently the identity cu 3 = VX + L u 2 . In this equation we know u z , u 3 , V, and the other quantities have to be found. If we substitute x = y cos /3 tan (a + 6), we make V vanish, and representing L by \x + py, we find X cos ft tan (a 6) p = c T~ 5 - ^ > h tan /9 + ra sin 20 and after a few steps \ m cos 2a + tn cos 20 c - h* tan /3 + ?/i 2 cot /3 sin 2 2 p _ h sin /3 + m cos ft sin 2a c ~~ h 2 tan /3 + ??i 2 cot ft sin 2 2 162J THE GEOMETRY OF THE CYLINDROID. 157 We can also obtain X ; for let it be Px+ Qy, then severally identifying the coefficients of a? and y 3 , we have, P = m sin 2a 4- h tan ft, Q = m cos ft (cos 2a + cos 20) ; finally, resuming the various results, we obtain the identity wherein, c = - h 2 tan ft + m 2 cot /3 sin 2 20, U = sin/3 cos 2 /3?/ 3 + sin Pyx?, (m sin 2a + A tan /3) a? 2 + 2mxy cos /3 cos 2a + (m sin 2a cos 2 ft h sin ft cos /3) t/ 2 . F= wz# 2 (cos 2a + cos 2$) + 2//m/ sin 2a cos ft + my 2 cos 2 ft (cos 20 cos 2a), X = oc(m sin 2a + A tan /3) my cos ft (cos 2a + cos 20), i = TO# (cos 2a + cos 20) + y (h sin /3 + m cos /3 sin 2a) - A 2 tan /3 + m 2 cot sin 2 20, F= a? ( m sin 2a A tan /3) -f 2?n#y cos ^ cos 2a + 2/ 2 (m sin 2a cos 2 /3 h sin y3 cos y3). 162. Parabola. The screws reciprocal to a cylindroid intersect two screws of equal pitch on the surface. Any chord in the section which cuts the cubic in two points of equal pitch must thus be the residence of a screw reciprocal to the surface; accordingly the chord mx (cos 2a + cos 20) + y (h sin ft + m cos ft sin 2a) - h- tan ft + m? cot ft sin 2 20 = 0, when it receives a pitch equal to p Q m cos 20, forms a screw reciprocal to the cylindroid. It is easily shown that the envelope of this chord is a parabola; differ entiating with respect to we have x = 2m cot ft cos 20. Eliminating we obtain x z + 4<mx cot ft cos 2<z + 4y (h cos ft + m cos ft cot ft sin 2a) - 4h? + 4m 2 cot 2 ft = 0. The vertex of the parabola is at the point x = - 2m cot ft cos 2a ; y = h sec ft m cosec ft sin 2a. 158 THE THEORY OF SCREWS. [162 The latus rectum is 4 cos /3 (h + m cot /3 sin 2a). The values of the two equal pitches (p) on the pair of screws are thus expressed in terms of the abscissa x of the point in which the chord touches the envelope by means of the equation From any point P, on the cubic, two tangents can be drawn to the parabola. Each of these tangents must intersect the cubic in a pair of screws of equal pitch. One tangent will contain the other screw whose pitch is equal to that of P. The second tangent passes through two screws of equal pitch in the two other points which, with P, make up the three intersections with the cubic. As the principal screws of the cylindroid are those of maximum and minimum pitch respectively, it follows that the tangents at these points will also touch the parabola. These common tangents are shown in the figure. This parabola is drawn to scale in Fig. 36. The equation employed was 2 5 + When the figure was complete, it was obvious that the parabola touched the cubic, and thus the following theorem was suggested : The parabola, which is the envelope of chords joining screws of equal pitch, touches the cubic in three points. The demonstration is as follows : To seek the intersections of the parabola with the cubic, we substitute, in the equation of the parabola, the values x = h tan (6 a) m cot /3 sin 20 tan (9 a), y = h sec /3 m cosec /3 sin 20, This would, in general, give an equation of the sixth degree for tan 9. It will, however, be found in this case that the expression reduces to a perfect square. The six points in which the parabola meets the cubic must thus coalesce into three, of which two are imaginary. The values of 9 for these three points are given by the equation h tan (9 - a) - m cot (sin 26 tan (9 - a) + 2 cos 20} = 0. We can also prove geometrically that the parabola touches the cubic at three points. In general, a cone of screws reciprocal to the cylindroid can be drawn from any external point. If the point happen to lie on the cylindroid, 162] THE GEOMETRY OF THE CYLINDROID. 159 the cone breaks up into two planes. The nature of these planes is easily seen. One of them, A, must be the plane perpendicular to the generator through ; the other, B, is the plane containing 0, and the screw of equal pitch to that of the screw through 0. These planes intersect in a ray, L, and it must first be shown that L is a tangent to the cyliridroid. Any ray intersecting one screw on a cylindroid at right angles must cut the surface again in two screws of equal pitch ; consequently L can only meet the surface in two distinct points, each of which has the pitch of the generator through 0. It follows that L must intersect the surface at two coincident points 0, i.e. that it is a tangent to the cylindroid at 0. Let any plane of section be drawn through 0. This plane will, in general, intersect A and B in two distinct rays : these are the two screws reciprocal to the cylindroid, and they are accordingly the two tangents from to the parabola we have been discussing. The only case in which these two rays could coalesce would occur when the plane of section was drawn through L ; but the two tangents to a parabola from a point only coalesce when that point lies on the parabola. At a point where the parabola meets the cubic, L must needs be a tangent both to the parabola and to the cubic, which can only be the case if the two curves are touching. We have thus proved that the parabola must have triple contact with the cubic. There are thus three points on the cubic which have the property that the tangent intersects the curve again in a point of equal pitch to that of the point of contact. We thus learn that all the screws of a four-system which lie in a plane touch a parabola having triple contact with the reciprocal cylindroid. From any point P, on the cubic, two tangents can be drawn to the parabola. Each of these tangents must intersect the cubic in a pair of screws of equal pitch. One tangent will contain the two screws whose pitch is equal to that of P. The other tangent passes through two screws of equal pitch in the two other points, which, with P, make up the three intersections with the cubic. As the principal screws of the cylindroid are those of maximum and minimum pitch, respectively, it follows that the tangents at these points will also touch the parabola. These common tangents are shown in Fig. 36. From the equation of the cylindroid, z (a? + 2/ 2 ) = 2ma?y, it follows that the plane at infinity cuts the surface in three straight lines on the planes, * = 0, x iy = 0. 160 THE THEORY OF SCREWS. [162- The line at infinity 011 the plane of z is of course intersected by all the real generators of the cylindroid, inasmuch as they are parallel to z. The points at infinity on the planes x iy = are each the residence of an imaginary screw, also belonging to the surface. The pitches of both these screws are infinite. We may deduce the two screws of infinite pitch on the surface in another way. The equations of a screw are y = x tan 6, z = m sin 20, while the pitch is p + m cos 20. If tan 6 be either + i, we find both z infinite and the pitch infinite. We thus see that through the infinitely distant point /, on the nodal line of the cylindroid, two screws belonging to the surface can be drawn, just as at any finite point. The peculiarity of the two screws through / is, that their pitches are equal, i.e. both infinite, and this is not the case with any other pair of intersecting screws. It is now obvious why the envelope just considered turned out to be a parabola rather than any other conic section. Every plane section will have the line at infinity for a transversal cutting two screws of equal pitch ; the envelope of such transversals must thus have the line at infinity for a tangent, i.e. must be a parabola. 163. Chord joining Two Points. If 6 and 6" be the angles by which two points on the cubic are defined, then the equation to the chord joining those points is where A = 2m cos (0 - a) cos (9" - a) cos (0 + 0"), B = hsm/3+m cos j3 cos (6 r + 0") sin (2a - & - & } - m cos sin (0 + 0") cos (ff - 0"), C = - tan /3 (h - m cot /3 sin 20 ) (h-m cot j3 sin 2(9"). If in these expressions we make + 6" = 0, we obtain the equation for the chord joining screws of equal pitch, as already obtained. We shall find that, in particular sections, these expressions become con siderably simplified. Suppose, for example, that the plane of section be a tangent plane to the cylindroid. The cubic then degenerates to a straight line and a conic. The condition for this will be obvious from the equation 164] THE GEOMETRY OF THE CYLINDROID. 161 of the cubic. If the coefficient of a? become zero, the required decomposition takes place, for y is then a factor. The necessary and sufficient condition for the plane of section being a tangent, is therefore ra sin 2a + h tan /3 = 0. When this is the case, the three expressions of A, B, C may be divided by a common factor, 2m cos (6 a) cos (6" a). and we have A = cos (& + 0"), B = - cos /3 sin (& + 0"), G = - 2m cot 13 sin (a + ) sin (a + 0"). If the screws be of equal pitch, 9 + 0" = 0, the coefficient of y disappears, and we see that all the chords are merely lines parallel to the axis of y, which is parallel to one of the axes of the ellipse. The equation to the chord then becomes (cos 2a + cos 20) [x + m cot ft (cos 2a cos 20)} = 0. For a given value of x there are two values of corresponding to the two chords that can be drawn through the point. One of these chords is parallel to y, and has a obtained from the equation cc + m cot /3 (cos 2a cos 20) = 0. 7T The other value of is -- a, from the equation 2 cos 2a+ cos 20 = 0. This is independent of x, as might have been foreseen from the fact that the two screws of equal pitch are in this case the line in the section and the other screw of equal pitch. The latter cuts the section in a certain point, and, of course, all chords through this point meet the curve in two screws of equal pitch. 164. Reciprocal Screws. Another branch of the subject must now be considered. We shall first investigate the following general problem : From any point, P, a series of transversals is drawn across each pair of reciprocal screws on the cyliiidroid. It is required to determine the cone which is the locus of these transversals. We shall show that this is a cone of the second degree. B. 11 162 THE THEORY OF SCREWS. [164, Let a, /3, 7 be the co-ordinates of the point. Then the plane through this point, and the generator of the cylindroid defined by the equations y = x tan 0, z = in sin 20, is (y x tan 6) (7 m sin 20) = (/3 a tan 6) (z m sin 20) ; or, if we arrange in powers of tan 0, we obtain A tan 3 + B tan 2 + Otan + D = 0, in which A = VLZ yx ; D = <yy (3z, B = yy /3z + 2mx 2ma ; C = a.z yx + 2m/3 2my. If the same transversal also crosses the generator defined by , then, A tan 3 + B tan 2 & + G tan & + D = 0. When the two screws defined by and are reciprocal, tan tan = H, when H is a constant. By eliminating and rejecting the factor tan - tan & we obtain - A*H 3 + A CH* - BDH + D n - = 0. And as this is of the second degree in x, y, z, the required theorem has been proved. All these cones must pass through the centre of the cylindroid, inasmuch as the two principal screws of the cylindroid are reciprocal. If a constant be added to the pitches of all the screws on the cylindroid, then the pairs of reciprocals alter, inasmuch as H alters. The cone changes accordingly, and thus there would be through each point a family of cones, all of which, however, agree in having, as a generator, the ray from the vertex to the centre of the cylindroid. Thus, even when the cylindroid is given, we must further have the pitch of a stated screw given before the cone becomes definite. This state of things may be contrasted with that presented by the cone of reciprocal screws which may be drawn through a point. The latter depends only upon the cylindroid itself, and is not altered if all the pitches be modified by a constant increment. 165] THE GEOMETRY OF THE CYLINDROID. 163 The discriminant of the cubic - A n -H 3 + A CH* - SDH + D* = is A -D* (A 2 D* + B 3 D + -fa AC 3 - &C* - f ABCD). Omitting the factor A~D 2 , we have, for the envelope of the system of cones, the cone of the fourth order, found by equating the expression in the bracket to zero. It may be noted that the same cone is the envelope of the planes 165. Application to the Plane Section. We next study the chord joining a pair of reciprocal points on the cubic of 160. Take any point in the plane of the section ; then, as we have just seen, a cone of screws can be drawn through this point, each ray of which crosses two reciprocal screws. This cone is cut by the plane of section in two lines, and, accordingly, we see that through any point in the plane of section two chords can be drawn through a pair of reciprocal points. The actual situation of these chords is found by drawing a pair of tangents to a certain hyperbola. This will now be proved. The values of 6 and 6 , which correspond to a pair of reciprocal points, fulfil the condition tan0tan0 =#; whence, cos (6 -0 ) = \ cos (0 + ) ; where, for brevity, we write X instead of l+H l-H If, further, we make + 6 = ty, we shall find, for the equation of the chord, Px + Qy + Rz = 0; in which, ra ,, . m . m P = -^ (X + cos 2a) -f sin 2a sin 2i/r + -- (\ + cos 2a) cos 2^, 22 ^ Q = /t sin y3 + cos ft sin 2a ( (\ + cos 2a) sin 2\fr A & -~ cos 8 sin 2a cos 7)1- = -h" tan 8 - (\ 2 - 1 ) cot B + \hm sin 2-f - ~ (\ - 1) cot B cos 11-2 164 THE THEORY OF SCREWS. [165 The envelope of this chord is found to be = +# 2 ra 2 sin 2 2a, + y 2 | ra 2 cos 2 & cos 2 2a - hm sin cos sin 2a - A 2 sin 2 /3 + |m 2 X cos 2a cos 2 /3 + |ra 2 X 2 cos 2 /3, w 2 + x y \ a s i n 2 cos 2 cos ~ m ^ cos ^ a s ^ n & | m 2 X sin 2a cos /3 ra&X sin /3, + ac + m/t 2 cos 2a tan fS + hm 2 X sin 2a + mA 2 X tan /3, + y | - w 2 A cos /3 + w/i 2 sin y3 sin 2a + 2/i 3 sin tan /3 - w 2 AX cos cos 2a, + | m 2 A 2 - A 4 tan 2 0. Using the data already assumed in 160, and, with the addition now made of taking X to be , the equation reduces to 122a; 2 - 2(% 2 - 16 Ley - 2417^ - 5003y + 245436 = ; which, for convenience of calculation, I change into x = 1-6 + 21 6 sec <J> 47 5 tan </>, y = - 12-8 + 32-8 sec </>. This hyperbola has been plotted down in Fig. 36. It obviously touches the cubic at three points. I had not anticipated this until the curves were care fully drawn ; but, when the theorem was suggested in this manner, it was easy to provide the following demonstration : The cone of reciprocal chords drawn through any point P breaks up into a pair of planes when P lies on the cylindroid. (I use the expression, reciprocal chord, to signify the transversal drawn across a pair of reciprocal screws on the cylindroid. This is very different from a screw reciprocal to the cylindroid.) For, take the screw reciprocal to that which passes through P. Then the plane X, through P and this screw, is obviously one part of the locus. Draw through P any transversal across a pair of reci procals on the cylindroid, then the plane Y, through the centre and this transversal, will be the other part of the locus. This pair of planes, X and Y, intersect in a ray which we shall call 8. A plane of section through P will, of course, usually cut the two planes in two rays, and these will be the two reciprocal chords through P. But suppose the plane of section happened to pass through 8, then there will be only one reciprocal chord through P, and this will, of course, be 8. Now, 8 must be a tangent to the cylindroid at P. Every chord through P, in the plane of Y, must cut the surface again in a pair of reciprocal points. To this 8 must be no exception, and as it lies in X, it intersects the screw 165] THE GEOMETRY OF THE CYLINDROID. 165 reciprocal to that through P ; therefore the third intersection of S with the surface must coalesce with P, or, in other words, S must be a tangent to the surface at P. We have thus shown that in the case where two reciprocal chords through a point on the cubic coalesce into one, that one must be the tangent to the cubic at P. But the two reciprocal chords through a point will only coalesce when the point lies on the hyperbola, in which case the two chords unite into the tangent to the hyperbola. Consider, then, the case where the hyperbola meets the cubic at a point P, inasmuch as P lies on the hyperbola, the two chords coalesce into a tangent thereto, but because they do coalesce, this line must needs be also a tangent to the cubic ; hence, whenever the hyperbola meets the cubic the two curves must have a common tangent. Altogether the curves meet in six points, which unite into three pairs, thus giving the required triple contact between the hyperbola and the cubic. If a constant h be added to all the pitches of the screws on a cylindroid, then, as is well known, the screws so altered still represent a possible cylin droid ( 18). The variations of h produce no alteration in the cubic section of the cylindroid ; but, of course, the hyperbola just considered varies with each change of h. In every case, however, it has the triple contact, and there is also a fixed tangent which must touch every hyperbola. This is the chord joining the two principal screws on the cylindroid ; for, as these are reciprocal, notwithstanding any augmentation to the pitches, their chord must always touch the hyperbola. The system of hyperbolae, corresponding to the variations of h, is thus concisely represented ; they must all touch this fixed line, and have triple contact with a fixed curve : that is, they must each fulfil four conditions, leaving one more disposable quantity for the complete definition of a conic. See Appendix, note 4. We write the tangent to the hyperbola or the reciprocal chord in the form L cos 2i/r + M sin 2-f + N = 0. If a pair of values can be found for x and y, which will simultaneously satisfy L = 0, M = 0, N = 0, then every chord of the type L cos 2ir must pass through this point. The condition for this is, that the discriminant of the hyperbola is zero, and we find the discriminant to be {m*h sin (X, 2 - 1) (h tan ft + m sin 2a). 166 THE THEORY OF SCREWS. [165- There are two critical cases in which this expression vanishes. It does so if h tan ft + m sin 2a = ; where the plane of section is tangential to the cylindroid. But we also note that the discriminant will vanish if h = 0, i.e. if the plane of section passes through the centre of the cylindroid. We might have foreseen this from the results of the last article ; for the plane of Y is a central section, and the hyperbola has evidently degenerated, for all the reciprocal chords, instead of touching an hyperbola, merely pass through the common apex P. The case of the central section is therefore of special interest. 166. The Central Section of the Cylindroid. By this we mean a section of the surface, special in no other sense, save that it passes through the centre of the surface. The equation to the central section is ( 160) y 3 sin ft cos 2 /3 + yx z sin (3 mx z sin 2a + 2mxy cos ft cos 2a + my- sin 2a cos 2 /3 = 0. The chord joining points of equal pitch + 6 is x (cos 20 + cos 2a) + y cos ft sin 2a + m cot ft sin 2 20 = 0. The apex P through which all reciprocal chords pass is _ m (\ 2 - 1) cot ft (\ + cos 2) 1 + 2X cos 2a 4- A, 2 _ m (A 2 1) cosec ft . sin 2a V ~ 1 + 2X cos 2a + X 2 and in general the co-ordinates of a point on the cubic are x = y cos ft tan (6 a), y = m cosec ft sin 26. One of these curves may be conveniently drawn to scale, from the equations as = % tan (0 - 25), y = - 66 sin 20. The parabola, which is the envelope of equal pitch-chords, would in this case have as its equation THE CENTRAL SECTION OF THE CYLINDROID. To fncf p. 166 167] THE GEOMETRY OF THE CYLINDROID. 167 The principal screws on the cylindroid both pass through the double point ; the two tangents to the curve at this point must therefore both touch the parabola. The leading feature of the central section is expressed by the important property possessed by the chords joining reciprocal screws. If we add any constant to the pitches, then we alter X, and, accordingly, the point P, through which all reciprocal chords pass, moves along the curve. The tangent to the cubic at P meets the cubic again in the point reciprocal to P. Two tangents, real or imaginary, can be drawn from P to the cubic touching it in the points 1\, T 2 , respectively: as these must each correspond to a screw reciprocal to itself, it follows that T l and T 2 are the screws of zero pitch. We hence see that the two tangents from any point on the cubic touch the cubic in points of equal pitch. Let a and ft be two screws, and 7 and 8 another pair of screws, and let the two chords, a/9 and 78, intersect again on the cubic. If d and 6 be the perpendicular distance and angle between the first pair, and d and the corresponding quantities for the second pair, then there must be some quantity ay, which, if added to all the pitches on the cyliridroid, will make a. and /3 reciprocal, and also 7 and 8 reciprocal. We thus have (p a + pp + 2&&gt;) cos d sin 6 = 0, (Py + Ps + 2w) cos - d sin 6 = ; whence, p a + pp d tan = p y + p& d tan 6 ; in other words, for every pair of screws, a and /8, whose chords belong to a pencil diverging from a common point on the surface, the expression Pa + p? d tan 6 is a constant. The value of this constant is double the pitch of the screw of either of the points of contact of the two tangents from P to the curve. 167. Section Parallel to the Nodal Line. If the node on the cubic be at infinity, the form of equation to the cubic hitherto employed will be illusory. The nature of this section must therefore be studied in another way, as follows : Let the plane cut the two perpendicular screws in A and B. Let I be the perpendicular OC from upon G, and let rj be the inclination of this perpendicular to the axis of x. Then, taking OA as the new axis of x, in which case z will be the new y, we have x = I tan (t) 0\ y = m sin 20. 168 THE THEORY OF SCREWS. [167, Eliminating 6, and omitting the accents, we have, as the equation of the cubic, yx 1 + mx 2 sin 2ij + l-y + 2lmx cos 2^ ml 2 sin 2?; = 0. The chord joining the two points and & has, as its equation, mac cos (0 + ) [cos (2rj - - ) + cos (0 - )] + ly - ml sin (2vi-0- ) cos (0 + ) - ml cos (0 - ) sin (0 + ) = 0. If this be the chord joining the screws of equal pitch, then + = 0, and the equation reduces to mas (cos 2?7 + cos 20) + ly ml sin 2^ = 0. We thus see that this chord, which in the general section envelops a parabola, now passes constantly through the fixed point x = 0, y = + m sin 2?;. This result could have been foreseen ; for, consider that screw on the cylin- droid (and there must always be one) normal to the plane which it intersects at a point P, any ray in the plane through P is perpendicular to this screw, and, therefore, by a well-known property of the cylindroid, must intersect the curve again in two points of equal pitch. This point P is, of course, the point whose existence we have demonstrated above. 168. Relation between Two Conjugate Screws of Inertia. We have found the relation between a pair of conjugate screws of inertia so important in the dynamical part of the theory, that it is worth while to investigate the properties of the chord joining two such points in the central section. It can readily be shown that this chord must envelop a conic. This conic and the point P on the cubic through which all reciprocal chords will pass, will enable the impulsive screw, corresponding to any instantaneous screw, to be immediately determined. For, draw through any point S that tangent to the conic which gives S as one of the two conjugate screws of inertia which must lie upon it ; let S be the other conjugate screw ; then the chord PS will cut the cubic again in the required impulsive screw. The two principal screws of inertia are found by drawing from P that tangent to the conic which has not P as one of the two conjugate screws of inertia. The two intersections of this tangent, with the cubic, are the required principal screws of inertia. We can also determine the relation between the impulsive screw and the instantaneous screw with regard to any section whatever. We have here 168] THE GEOMETRY OF THE CYLINDROID. 169 to consider two conies connected with the cubic, viz. the reciprocal conic, which is the envelope of reciprocal chords, and the inertia conic, which is the envelope of chords of conjugate screws of inertia. We must provide a means of discriminating the two tangents from a point P on the cubic to either conic ; any ray, of course, cuts the cubic in three points, of which two possess the characteristic relation. If P be one of these two, we may call this tangent the odd tangent. The other tangent will have, as its significant points, the two remaining intersections ; leaving out P, we can then proceed, as follows, to determine the impulsive screw corresponding to P as the instantaneous screw : Draw the odd tangent from P to the inertia conic, and from the con jugate point thus found draw the odd tangent to the reciprocal conic. The reciprocal point Q thus found is the impulsive screw corresponding to P as the instantaneous screw. In general there are four common tangents to the two conies. Of these tangents there is only one possessing the property, that the same two of its three intersections with the cubic are the correlative points with respect to each of the conies. These two intersections are the principal screws of inertia. To determine the small oscillations we find the potential conic, the tangents to which are chords joining two conjugate screws of the potential ( 100). The two harmonic screws are then to be found on one of the two common tangents to the two conies. It can be shown that both the inertia conic and the potential conic will, like the reciprocal conic, have triple contact with the cubic. CHAPTER XIV. FREEDOM OF THE THIRD ORDER*. 169. Introduction. The dynamics of a rigid body which has freedom of the third order, possesses a special claim to attention, for, included as a particular case, we have the celebrated problem of the rotation of a rigid body about a fixed point. In the theory of screws the screw system of the third order is characterised by the feature that the reciprocal screw system is also of the third order, and this is a fertile source of interesting theorems. We shall first study the screw system of the third order, and its reciprocal. We shall then show how the instantaneous screw, corresponding to a given impulsive screw, can be determined for a rigid body whose movements are prescribed by any screw system of the third order. We shall also point out the three principal screws of inertia, of which the three principal axes are only special cases, and we shall determine the kinetic energy acquired by a given impulse. Finally, we shall determine the three harmonic screws, and we shall apply these principles to the discussion of the small oscillations of a rigid body about a fixed point under the influence of gravity. A screw system of the first order consists of course of one screw. A screw system of the second order consists of all the screws on a certain ruled surface (the cylindroid). Ascending one step higher, we find that in a screw system of the third order the screws are so numerous that a finite number (three) can be drawn through every point in space. In the screw system of the fourth order a cone of screws can be drawn through every point, while to a screw system of the fifth order belongs a screw of suitable pitch on every straight line in space. 170. Screw System of the Third Order. We shall now consider the collocation of the screws in space which constitute a screw system of the third order. A free rigid body can receive * Transactions of the Royal Irish Academy, Vol. xxv. p. 191 (1871). 169-172] FREEDOM OF THE THIRD ORDER. 171 six independent displacements. Its position is, therefore, to be specified by six co-ordinates. If, however, the body be so constrained that its six co ordinates must always satisfy three equations of condition, there are then only three really independent co-ordinates, and any position possible for a body so circumstanced may be attained by twists about three fixed screws, provided that twists about these screws are permitted by the constraints. Let A be an initial position of a rigid body M. Let M be moved from A to a closely adjacent position, and let x be the screw by twisting about which this movement has been effected ; similarly let y and z be the two screws, twists about which would have brought the body from A to two other independent positions. We thus have three screws, x, y, z, which com pletely specify the circumstances of the body so far as its capacity for movement is considered. Since M can be twisted about each and all of x, y, z, it must be capable of twisting about a doubly infinite number of other screws. For suppose that by twists of amplitude x , y , z , the final position V is attained. This position could have been reached by twisting about some screw v, so as to come from A to V by a single twist. As the ratios of x to y , and z , are arbitrary, and as a change in either of these ratios changes v, the number of v screws is doubly infinite. All the screws of which v is a type form what we call a screw system of the third order. We may denote this screw system by the symbol S. 171. The Reciprocal Screw System. A wrench which acts on a screw 77 will not be able to disturb the equili brium of M, provided t] be reciprocal to x, y, z. If rj be reciprocal to three independent screws of the system S, it will be reciprocal to every screw of S. Since rj has thus only three conditions to satisfy in order that it may be reciprocal to S, and since five quantities determine a screw, it follows that tj may be any one of a doubly infinite number of screws which we may term the reciprocal screw system S . Remembering the property of reciprocal screws ( 20) we have the following theorem ( 73). A body only free to twist about all the screws of S cannot be disturbed by a wrench on any screw of S ; and, conversely, a body only free to tAvist about the screws of S cannot be disturbed by a wrench on any screw of S. The reaction of the constraints by which the freedom is prescribed constitutes a wrench on a screw of S . 172. Distribution of the Screws. To present a clear picture of all the movements which the body is 172 THE THEORY OF SCREWS. [172- competent to execute, it will be necessary to examine the mutual connexion of the doubly infinite number of screws which form the screw system. It will be most convenient in the first place to classify the screws in the system according to their pitches ; the first theorem to be proved is as follows : A II the screws of given pitch + k in a three-system lie upon a hyperboloid of which they form one system of generators, while the other system of gene rators with the pitch k belong to the reciprocal screw system. This is proved as follows : Draw three screws, p, q, r, of pitch + k belonging to S. Draw three screws, I, m, n, each of which intersects the three screws p, q, r, and attribute to each of I, m, n, a pitch k. Since two intersecting screws of equal and opposite pitches are reciprocal, it follows that p, q, r, must all be reciprocal to I, m, n. Hence, since the former belong to S, the latter must belong to 8 . Every other screw of pitch + k intersecting I, m, n, must be reciprocal to S , and must therefore belong to S. But the locus of a straight line which intersects three given straight lines is a hyperboloid of one sheet, and hence the required theorem has been proved. 173. The Pitch Quadric. One member of the family of hyperboloids obtained by varying k presents exceptional interest. It is the locus of the screws of zero pitch belonging to the screw complex. As this quadric has an important property ( 176) besides that of being the locus of the screws of zero pitch, it is desirable to denote it by the special phrase pitch quadric. We shall now determine the equation of the pitch quadric. Let one of the principal axes of the pitch quadric be denoted by x, this will intersect the surface in two points through each of which a pair of generators can be drawn. One generator of each pair will belong to S, and the other to S . Each pair of generators will be parallel to the asymptotes of the section of the pitch quadric by the plane containing the remaining principal axes y and z. Let /*, v be the two generators belonging to S, then lines bisecting internally and externally the angle between two lines in the plane of y and z, parallel to /i, v will be two of the principal axes of the pitch quadric. Draw the cylindroid (pit). The two screws of zero pitch on the cylindroid are equidistant from the centre of the cylindroid, and the two rectangular screws of the cylindroid bisect internally and externally the angle between the lines parallel to the screws of zero pitch. Hence it follows that the two rectangular screws of the cylindroid (pv) must be on the axes of y and z of the pitch quadric. We shall denote these screws by ft and 7, and their 174] FREEDOM OF THE THIRD ORDER. 173 pitches by p$ and p y . From the properties of the cylindroid it appears that a, the semiaxis of the pitch quadric, must be determined from the equations a = (pp py) sin I cos I, P cos 2 1 + p y sin 2 1 = ; whence eliminating I, we deduce with of course similar values of b and c. Substituting these values in the equation of the quadric we deduce the important result which may be thus stated : The three principal axes of the pitch quadric, when furnished with suitable pitches p a ,pii, p-f, constitute screws belonging to the screw system of the third order, and the equation of the pitch quadric has the form PO.CO" + ppf + p y z 2 + p a pppy = 0. We can also show conversely that every screw 6 of zero pitch, which belongs to the screw system of the third order, must be one of the generators of the pitch quadric. For must be reciprocal to all the screws of zero pitch on the reciprocal system of generators of the pitch quadric ; and since two screws of zero pitch cannot be reciprocal unless they intersect either at a finite or infinite distance, it follows that 9 must intersect the pitch quadric in an infinite number of points, and must therefore be entirely contained thereon. 174. The Family of Quadrics. It has been shown that all the screws of given pitch belonging to a system of the third order are the generators of a certain hyperboloid. There is of course a different hyperboloid for each pitch. We have now to show that all these hyperboloids are concentric. Take any two screws whatever belonging to the system and draw the cylindroid which passes through those screws. This cylindroid contains two screws of every pitch. It must therefore have two generators in common with every hyperboloid of the family. But from the known sym metrical arrangement of the screws of equal pitch on a cylindroid, it follows that the centre of that surface must lie at the middle point of the shortest distance between each two screws of equal pitch. The centres of the hyper boloids for all possible pitches must therefore lie in the principal plane of any cylindroid of the system. Take any three cylindroids of the system. 174 THE THEORY OF SCREWS. [174, The centres of all the hyperboloids coincide with the intersection of the three principal planes of the cylindroids. It will be convenient to call this point the centre of the three-system. We hence see that whenever three screws of a three-system are given, the centre of the system is determined as the intersection of the principal planes of the three cylindroids denned by each pair of screws taken suc cessively. We may also show that not only are the family of hyperboloids concentric, but that they have also their three principal axes coincident in direction and situation with the principal axes of the pitch quadric. Draw any principal axis z of the pitch quadric. Two screws of zero pitch belonging to the system will be intersected by z and we draw the cylindroid through these two screws. Let L l and L.> be the two screws of equal pitch p on this cylindroid. Let be the centre of the cylindroid, this same point being also the centre of the pitch quadric, and therefore as shown above of every p-pitch hyperboloid S p . As the centre bisects every diameter, it follows that the plane OL 2 cuts the hyperboloid S p again in a ray LI which is perpendicular to z and crosses L l at its intersection with z. The plane containing L l and Z/ is therefore a tangent to 8 P at the point where the plane is cut by z. As z is perpendicular to this plane it follows that the diameter is perpendicular to its conjugate plane. Hence z is a principal axis of S p , and the required theorem is proved. Let now S denote a screw system of the third order, where a, /3, y are the three screws of the system on the principal axes of the pitch quadric. Dimmish the pitches of all the screws of S by any magnitude k. Then the quadric must be the locus of screws of zero pitch in the altered system, and therefore of pitch + k in the original system ( 110). Regarding & as a variable parameter, the equation just written represents tlie family of quadrics which constitute the screw system S and the reciprocal screw system 8 . Thus all the generators of one system on each quadric, with pitch + k, constitute screws about which the body, with three degrees of freedom, can be twisted ; while all the generators of the other system, with pitch k, constitute screws, wrenches about which would be neutralized by the reaction of the constraints. For the quadric to be a real surface it is plain that k must be greater than the least, and less than the greatest of the three quantities p a ,pp, p y - 175] FREEDOM OF THE THIRD ORDER. 175 Hence the pitches of all the real screws of the screw system S are inter mediate between the greatest and least of the three quantities p a> pp, p y . 175. Construction of a three-system from three given Screws. If a family of quadric surfaces have one pair of generators (which do not intersect) in common, then the centre of the surface will be limited to a certain locus. We may investigate this conveniently by generalizing the question into the search for the locus of the pole of a fixed plane with respect to the several quadrics. Let A be the given plane, / be the ray which joins the two points in which the given pair of generators intersect A, X be the plane through / and the first generator, Y the plane through / and the second generator, B the plane through / which is the harmonic conjugate of A with respect to X and Y. Then B is the required locus. For, draw any quadric through the two given generators, and let be the pole of A with respect to that quadric. Draw a transversal through cutting the plane A in the point A l and the first and second generators in X l and Y t respectively. Since A 1 is on the polar of it follows that OZ^Fj is an harmonic section. But the transversal must be cut harmonically by the pencil of planes I(BXAY) and hence must lie in B, which proves the theorem. In the particular case when A is the plane at infinity, then is the centre of the quadric. A plane parallel to the two generators cuts the plane at infinity in the line /, and the planes X, Y and B must also contain 7. Then A, B, X, Y are parallel planes. Any transversal across X and Y is cut harmonically by B and A, and as A is at infinity, the transversal must be bisected at B. It thus appears that when a family of quadrics have one pair of non-intersecting generators in common, then the plane which bisects at right angles the shortest distance between these generators is the locus of the centres of the quadrics. If therefore three generators of a quadric are given, the three planes determined by each pair of the quadrics determine the centre by their intersection. The construction of the axes of the quadric may be effected geometrically in the following manner. Draw three transversals Q l} Q 2 , Q 3 across the three given generators R 1} R 2 , R 3 . Draw also two other trans versals Hi, R 5 across Q 1} Q 2 , Q 3 . Construct the conic which passes through the five points in which R 1} R 2 , R 3> R it R s intersect the plane at infinity. Find the common conjugate triangle to this conic and to the circle which is the intersection of every sphere with the plane at infinity. Then the three 176 THE THEORY OF SCREWS. [175- rays from the centre of the quadric to the vertices of this triangle are the three principal axes of the quadric. We thus prove again that if a and /3 be any two screws of a three-system, the centre of the pitch-quadric must lie in the principal plane of the cylindroid through a and /?. For the common perpendicular to any two screws of equal pitch on the cylindroid will be bisected by the principal plane and therefore any hyperboloid through these two screws of equal pitch must have its centre in that plane. 176. Screws through a Given Point. We shall now show that three screws belonging to S, and also three screws belonging to 8 , can be drawn through any point x , y , z . Substitute x, y , z , in the equation of 17 5 and we find a cubic for k. This shows that three quadrics of the system can be drawn through each point of space. The three tangent planes at the point each contain two generators, one belonging to S, and the other to S . It may be noticed that these three tangent planes intersect in a straight line. From the form of the equation it appears that the sum of the pitches of three screws through a point is constant and equal to p a +pp + p y - Two intersecting screws can only be reciprocal if they be at right angles, or if the sum of their pitches be zero. It is hence easy to see that, if a sphere be described around any point as centre, the three screws belonging to S, which pass through the point, intersect the sphere in the vertices of a spherical triangle which is the polar of the triangle similarly formed by the lines belonging to S . We shall now show that one screw belonging to S can be found parallel to any given direction. All the generators of the quadric are parallel to the cone (p a - k) x* + (p ft - k) f + (p y - k) z* = 0, and k can be determined so that this cone shall have one generator parallel to the given direction ; the quadric can then be drawn, on which two gene rators will be found parallel to the given direction ; one of these belongs to S, while the other belongs to S . It remains to be proved that each screw of 8 has a pitch which is propor tional to the inverse square of the parallel diameter of the pitch quadric*. * This theorem is connected with the linear geometry ol Plucker, who has shown (Neue Geometric des Ratlines, p. 130) that k l x- + L 2 y- + k, t z 2 + k 1 kJ{ 3 ) is the locus of lines common to three linear complexes of the first degree. The axes of the three complexes are directed along the co-ordinate axes, and the parameters of the complexes are fcj, ._,, k 3 ; the same author has also proved that the parameter of any complex belonging to the " dreigliedrige Gruppe" is propor tional to the inverse square of the parallel diameter of the hyperboloid. 176] FREEDOM OF THE THIRD ORDER. 177 Let r be the intercept on a generator of the cone (p a - k) tf + (pp -k)f + (p y -k)z* = 0; by the pitch quadric p a x" + ptf + W> + paptpy = ; then k = -PP^- r- but k is the pitch of the screw of S, which is parallel to the line r. Nine constants ( 75) are required for the determination of a screw system of the third order. This is the same number as that required for the specification of a quadric surface. We hence infer, what is indeed otherwise manifest, viz., that when the pitch quadric is known the entire screw system of the third order is determined. Another interesting property of the pitch quadric is thus enunciated. Any three co-reciprocal screws of a given screw system of the third order are parallel to a triad of conjugate diameters of its pitch quadric. Take any three co-reciprocal screws of the system as screws of reference, and let p lt p^, p 3 be their pitches. If then the co-ordinates of any screw p belonging to the system be denoted by p l} p 2 , p 3 , we shall have for the pitch ofp(95) Pp = PlP* + P*P* If a parallelepiped be constructed, of which the three lines parallel to the reciprocal screws, drawn through the centre of the pitch quadric, are conterminous edges, and of which the line parallel to p is the diagonal, and if x, y, z be the lengths of the edges, and r the length of the diagonal, then we have ( 35) x y z ~ = Pi> - = P* -=P*- It follows that p p must be proportional to the inverse square of the parallel diameter of the quadric surface P& 2 + p 2 y n - + p 3 z = H. But p ft must be proportional to the inverse square of the parallel diameter of the pitch quadric, and hence the equation last written must actually be the equation of the pitch quadric, when H is properly chosen. But the equation is obviously referred to three conjugate diameters, and hence three conjugate diameters of the pitch quadric are parallel to three co-reciprocal screws of the screw system. B. 12 178 THE THEORY OF SCREWS. [176- We see from this that the sum of the reciprocals of the pitches of three co-reciprocal screws is constant. This theorem will be subsequently generalised. 177. Locus of the feet of perpendiculars on the generators*. If p be the pitch of the screw of the three-system which makes angles a, ft, 7 with the three principal screws, it is then easy to show that the equation of the screw is (p a) cos a + z cos /3 y cos 7 = 0, z cos a + (p b) cos ft + a; cos 7 = 0, + y cos a x cos ft + (p c) cos 7 = 0. If perpendiculars be let fall from the origin on the several screws of the system, then if x, y, z be the foot of one of the perpendiculars sc cos a + y cos ft + z cos 7 = 0. Eliminating cos a, cos /3, cos 7 from this equation and the two last of those above, we have a; y z = 0, z p b x + y x p c or (pV)(p-c)x + x (# 2 + y- + z 2 ) + yz (b - c) = ; from this and the two similar equations we have, by elimination of p 2 and p and denoting x 2 + y z + z* by r 2 , x, (b + c) x, bcx + (b c) yz + xr* = ; y, (c + a) y, cay + (c a) zx + yr n - z, (a+b)z, abz + (a b) xy + zr 3 multiplying the first column by r- and subtracting it from the last, we have x, (b + c) x, bcx + (b c) yz = 0, y, (c + a) y, cay + (c a) zx z, (a + b) z, abz + (a b) xy which may be written (a - b) 2 #y + (b - cf y*z- + (c - a) 2 z-ac" = (a -b)(b- c) (c - a) vyz. * This Article is due to Professor C. Joly, On the theory of linear vector functions," Transac tions of the Royal Irish Academy, Vol. xxx. pp. 601 and 617 (1895), where a profound discussion of Steiner s surface is given. See also by the same author Bishop Law s Mathematical Prize Examination, Dublin University Examination Papers, 1898. 178] FREEDOM OF THE THIRD ORDER. 179 This equation denotes a form of Steiner s surface : v a + V/3 + V7 + VS = 0, where ----- __ b c c a a o Q_ ^ 2y 2z r-* 7 7 "T" - j 6 c c a a b 2x 2y 2z 7 = - 7 --- + ^ ------ -, + 1, o c c a a o .__ -- . 6 c c a a 6 From the form of its equation it appears that this surface has three double lines, which meet in a point, viz. the three axes OX, OY, OZ. This being so any plane will cut the surface in a quartic curve with three double points, being those in which the plane cuts the axes. If the plane touch the surface, the point of contact is an additional double point on the section, that is, the section will be a quartic curve with four double points, i.e. a pair of conies. The projections of the origin on the generators of any cylindroid belonging to the system lie on a plane ellipse ( 23). This ellipse must lie on the Steiner quartic. Hence the plane of the ellipse must cut the quartic in two conies and must be a tangent plane. See note on p. 182. 178. Screws of the Three-System parallel to a Plane. Up to the present we have been analysing the screw system by classifying the screws into groups of constant pitch. Some interesting features will be presented by adopting a new method of classification. We shall now divide the general system into groups of screws which are parallel to the same plane. We shall first prove that each of these groups is in general a cylindroid. For suppose a screw of infinite pitch normal to the plane, then all the screws of the group parallel to the plane are reciprocal to this screw of infinite pitch. But they are also reciprocal to any three screws of the original reciprocal system ; they, therefore, form a screw system of the second order ( 72) that is, they constitute a cylindroid. We shall prove this in another manner. A quadric containing a line must touch every plane passing through the line. The number of screws of the system which can lie in a given plane is, therefore, equal to the number of the quadrics of the system which can be drawn to touch that plane. 122 180 THE THEORY OF SCREWS. [178, The quadric surface whose equation is (p a - k) x- + (pp - k) y- + (p y - k) z- + (p* - k) (p? - k) (p y - fc) = 0, touches the plane Px + Qy + Rz + S = 0, when the following condition is satisfied : whence it follows that two values of k can be found, or that two quadrics can be made to touch the plane, and that, therefore, two screws of the system, and, of course, two reciprocal screws, lie in the plane. From this it follows that all the screws of the system parallel to a plane must in general lie upon a cylindroid. For, take any two screws parallel to the plane, and draw a cylindroid through these screws. Now, this cylindroid will be cut by any plane parallel to the given plane in two screws, which must belong to the system; but this plane cannot contain any other screws; therefore, all the screws parallel to a given plane must lie upon the same cylindroid. 179. Determination of a Cylindroid. We now propose to solve the following problem : Given a plane, deter mine the cylindroid which contains all the screws, selected from a screw system of the third order, which are parallel to that plane. Draw through the centre of the pitch quadric a plane A parallel to the given plane. We shall first show that the centre of the cylindroid required lies in A ( 174). Fig. 37. Let T l} T 2 (Fig. 37) be two points in which the two quadrics of constant pitch touch the plane of the paper, which may be regarded as any plane parallel to A ; then P is the intersection of the pair of screws belonging to the system PT l} PT 2 , which lie in that plane, and P is the intersection of the pair of reciprocal screws P R lt P R belonging to the reciprocal 179] FREEDOM OF THE THIRD ORDER. 181 system. Since P R^ is to be reciprocal to PT 2 , it is essential that ^ be a right angle; similarly ,R 2 is a right angle. The reciprocal cylindroid, whose axis passes through P , will be identical with the cylindroid belonging to the system whose axis passes through P ; but the two will be differently posited. If the angle at P be a right angle, the points T l and T 2 are at infinity ; therefore, the plane touches the quadrics at infinity ; it must, therefore, touch the asymptotic cone, and must, therefore, pass through the centre of the pitch quadric ; but P is the centre of the cylindroid in this case, and, therefore, the centre of the cylindroid must lie in the plane A. The position of the centre of the cylindroid in the plane A is to be found by the following construction : Draw through the centre a diameter of the pitch quadric conjugate to the plane A. Let this line intersect the pitch quadric in the points P 1} P 2 , and let S, S (Fig. 38) be the feet of the perpendiculars let fall from P 1} P 2 upon the plane A. Draw the asymptotes OL, OM to the section of the pitch quadric, made by the plane A. Through S and S draw lines in the plane A, ST, ST , S T, S T , parallel to the asymptotes, then T and T are the centres of the two required cylindroids which belong to the two reciprocal screw systems. This construction is thus demonstrated : Fig. 38. The tangent planes at P^ P 2 each intersect the surface in lines parallel to OL, OM. Let us call these lines PI-//I, P\Mi through the point P 1} and P.,L,, P Z M., through the point P. 2 . Then P^, PM< are screws belonging to the system, and P l M l , P. 2 L 2 are reciprocal screws. Since OL is a tangent to the pitch quadric, it must pass through the intersection of two rectilinear generators, which both lie in a plane which contains OL ; but since OL touches the pitch quadric at infinity, the two generators in question must be parallel to OL, and therefore their projections on the plane of A must be S T, ST . Similarly for ST, S T ; hence ST and S T are the projections of two screws belonging to the system, and therefore the centre of the cylindroid is at T . In a similar way it is proved that the centre of the reciprocal cylindroid is at T. Having thus determined the centre of the cylindroid, the remainder of the construction is easy. The pitches of two screws on the surface must be proportional to the inverse square of the parallel diameters of the section of the pitch quadric made by A. Therefore, the greatest and least pitches will be on screws parallel to the principal axes of the section. Hence, lines 182 THE THEORY OF SCREWS. [179- drawn through T parallel to the external and internal bisectors of the angle between the asymptotes are the two rectangular screws of the cylindroid. Thus the problem of finding the cylindroid is completely solved. It is easily seen that each cylindroid touches each of the quadrics in two points. We may also note that a screw of the system perpendicular to the plane passes through T. Thus given any cylindroid of the system the position of the screw of the system parallel to the axis of the cylindroid is determined*. 180. Miscellaneous Remarks. We are now in a position to determine the actual situation of a screw belonging to a screw system of the third order of which the direction is given. The construction is as follows : Draw through the centre of the pitch quadric a radius vector OR parallel to the given direction of 6, and cutting the pitch quadric in R. Draw a tangent plane to the pitch quadric in R. Then the plane A through OR, of which the intersection with the tangent plane is perpendicular to OR, is the plane which contains 0. For the section in which A cuts the pitch quadric has for a tangent at .R a line perpendicular to OR; hence the line OR is a principal axis of the section, and hence (179) one of the two screws of the system in the plane A must be parallel to OR. It remains to find the actual situation of 6 in the plane A. Since the direction of is known, its pitch is determinate, because it is inversely proportional to the square of OR. Hence the quadric can be constructed, which is the locus of all the screws which have the same pitch as 6. This quadric must be intersected by the plane A in two parallel * In a letter (10 April 1899) Professor C. Joly writes as follows : Any plane through the origin contains one pair of screws A and B belonging to the system intersecting at right angles and another pair A and B belonging to the reciprocal system. The group A, B, A , B form a rectangle of which the origin is the centre. The feet of the perpendiculars from on A and on B and the point of intersection of A and B will lie on the Steiner s quartic (b-c)-y-z z + (c-a) 2 z-x- + (a-b) 2 x z y 2 - +(b-c) (c-a) (a-b)xyz. The point of intersection of A and B and the feet of the perpendiculars on A and B will lie on the new Steiner s quartic (6 - c) 2 ?/ 2 z 2 + (c - ) z*-x*+(a - &) 2 zy= - (b - c) (c - a) (a - b) xyz. The locus of the feet of the perpendiculars on the screws of a three-system from any arbitrary origin whatever is still a Steiner s quartic, but its three double lines are no longer mutually rect angular. They are coincident with the three screws of the reciprocal three-system which passed through the origin. This quartic is likewise the locus of the intersection of the pairs of screws of the reciprocal system which are coplanar with the origin. There is a second Steiner s quartic whose double lines coincide with the three screws of the given system which pass through the origin and which is the locus of intersection of those pairs of screws of the given system which lie in planes through the origin. It is also the locus of the feet of perpendiculars on the screws of the reciprocal system. 181] FREEDOM OF THE THIRD ORDER. 183 lines. One of these lines is the required residence of the screw 0, while the other line, with a pitch equal in magnitude to that of 0, but opposite in sign, belonging, as it does, to one of the other system of generators, is a screw reciprocal to the system. The family of quadric surfaces of constant pitch have the same planes of circular section, and therefore every plane through the centre cuts the quadrics in a system of conies having the same directions of axes. The cylindroid which contains all the screws of the screw system parallel to one of the planes of circular section must be composed of screws of equal pitch. A cylindroid in this case reduces to a plane pencil of rays passing through a point. We thus have two points situated upon a principal axis of the pitch quadric, through each of which a plane pencil of screws can be drawn, which belong to the screw system. All the screws passing through either of these points have equal pitch. The pitches of the two pencils are equal in magnitude, but opposite in sign. The magnitude is that of the pitch of the screw situated on the principal axis of the pitch quadric*. 181. Virtual Coefficients. Let p be a screw of the screw system which makes angles whose cosines are /, a, h, with the three screws of reference a, /3, y upon the axes of the pitch quadric. Then, reference being made to any six co-reciprocals, we have for the co-ordinates of p, &c., &c., ps =/e +g@6 + hy6 Let ij be any given screw. The virtual coefficient of p and rj is Draw from the centre of the pitch quadric a radius vector r parallel to p, and equal to the virtual coefficient just written ; then the locus of the extremity of r is the sphere x 2 + \f + z* = #CT ar) + yet ft + zvr yrl . The tangent plane to the sphere obtained by equating the right-hand side of this equation to zero is the principal plane of that cylindroid which contains all the screws of the screw system which are reciprocal to 17. * If a, b, e be the three semiaxes of the pitch quadric, and +d the distances from the centre, on a, of the two points in question, it appears from 179 that 2 d 2 = (a 8 -i 2 ) (a 2 -c 2 ), which shows that d is the fourth proportional to the primary semiaxis of the surface, and to those of its focal ellipse and hyperbola. THE THEORY OF SCREWS. [182- 182. Four Screws of the Screw System. Take any four screws a, ft, 7, 8 of the screw system of the third order. Then we shall prove that the cylindroid (a, ft) must have a screw in common with the cylindroid (7, &). For twists of appropriate amplitudes about a, ft, 7, B must neutralise, and hence the twists about a, ft must be counter acted by those about 7, & ; but this cannot be the case unless there is some screw common to the cylindroids (a, ft) arid (7, 8). This theorem provides a convenient test as to whether four screws belong to a screw system of the third order. 183. Geometrical notes. The following theorem may be noted : Any ray 77 which crosses at right angles two screws a, ft of a three-system is the seat of a screw reciprocal to the system. For, draw the cylindroid a, ft, then of course 77, whatever be its pitch, is reciprocal to all the screws on this cylindroid. Through any point P on 77 there are two screws of the system which lie on the cylindroid, and there must be a third screw 7 of the system through P, which, certainly, does not lie on the cylindroid. If, therefore, we give 77 a pitch p y) it must be reciprocal to the three-system. In general, one screw of a three-system can be found which intersects at right angles any screw ivhatever 77. For 77 must, of course, cut each of the quadrics containing the screws of equal pitch in two points. Take, for example, the quadric with screws of pitch p. There are, therefore, two screws, a and ft of pitch p belonging to the system, which intersect 77. The cylindroid a, ft must belong to the system, and from the known property of the cylindroid the ray ij, which crosses the two equal pitch screws ( 22), must cross at right angles some third screw 7 on this cylindroid ; but this belongs to the three-system, and therefore the theorem has been proved. 184. Cartesian Equation of the Three-System. If we are given the co-ordinates of any three screws of a three-system with reference to six canonical co -reciprocals, we can calculate in the following manner the equation to the family of pitch quadrics of which the three-system is constituted. Let the three given screws be a, ft, 7, with co-ordinates respectively 184] FREEDOM OF THE THIRD ORDER. 185 !,...; ft l} ... /3; 71, ... 7 6 . Then if X, p, v be three variable parameters, the co-ordinates of the other screws of the three-system will be Xotj + yttySj + vji , Xa. 2 + /i$j + v%, ... Xa 6 + /Jift 6 + i>7 6 . We shall denote the pitch of this screw by p, and from 43 we have for the equations of this screw with reference to the associated Cartesian axes : = + (Xa 5 + pfa + vy, + Xa 6 + fj,j3 9 + vy 6 ) y (X 3 + fj,ft s + vj 3 + X 4 -1- pfti + v%) z (Xj + jjifii + vyi X 2 /A/3 a 1/72) a with two similar equations. From these we eliminate X, /*, v and the determinant thus arising admits of an important reduction. To effect this we multiply it by the determinant 4 , . I 7i + 7a . 73 + 74 For brevity we introduce the following notation : P = x [(ft, + &) (73 + 74) - 08, + A) (75 + 7.)] + y [(& + &) ( 75 + 7) - (& + ft) (71 + 7.)] + z [(& + &) ( 7l + 7.) - (^ + /3 2 ) (7, + 74 )] , with similar values for Q and R by cyclical interchange. We also make L aft = a(a 1 + a ) (A - &) + 6 ( 3 + 4 ) (/3 3 - /9 4 ) + c (a, + 6 ) (/3 5 - &), ^ = a (A + A) (i - a,) + & (& + /3 4 ) (a 3 - 4 ) + c (/3 5 + &) (a 8 - 6 ), with similar values for Z ay , Z ya , L fty , L^ by cyclical interchange. The equation to the family of pitch quadrics is then easily seen to be 0= If the three given screws a, ft, 7 had been co-reciprocal, then as L a p + Lp a = 2-57 a = 0, it follows that L af} and L fta only differ in sign, so that if 186 THE THEORY OF SCREWS. [184- the equation becomes = p a -p , R p cos (a/3), + Q p cos (017) R -p cos (aft), Pfi-p - Q - P cos ( a 7) > + P - p cos By expanding this as a cubic for p we see that the coefficient of p 2 divided by that of p 3 with its sign changed is p a sin 2 (ffy) +jp/3 sin 2 (yq) + jo Y sin 2 (off) sii4[(y) + ( 7 a) + (a/3)]sin|[^ This is accordingly the constant sum of the three pitches of the screws of the system which can be drawn through any point. 185. Equilibrium of Four Forces applied to a Rigid Body. If the body be free, the four forces must be four wrenches on screws of zero pitch which are members of a screw system of the third order. The forces must therefore be generators of a hyperboloid, all belonging to the same system ( 132). Three of the forces, P, Q, R, being given in position, S must then be a generator of the hyperboloid determined by P, Q, R. This proof of a well-known theorem (due to Mobius) is given to show the facility with which such results flow from the Theory of Screws. Suppose, however, that the body have only freedom of the fifth order, we shall find that somewhat more latitude exists with reference to the choice of S. Let X be the screw reciprocal to the screw system by which the freedom is defined. Then for equilibrium it will only be necessary that S belong to the system of the fourth order defined by the four screws P, Q, R, X. A cone of screws can be drawn through every point in space belonging to this system, and on that cone one screw of zero pitch can always be found ( 123). Hence one line can be drawn through every point in space along which S might act. If the body have freedom of the fourth order, the latitude in the choice of S is still greater. Let X ly X 2 be two screws reciprocal to the system, then S is only restrained by the condition that it belong to the screw system of the fifth order defined by the screws P, Q, R, X 1} X. 186] FREEDOM OF THE THIRD ORDER. 187 Any line in space when it receives the proper pitch is a screw of this system. Through any point in space a plane can be drawn such that every line in the plane passing through the point with zero pitch is a screw of the system ( 110). Finally, if the body has only freedom of the third order, the four equi librating forces P, Q, R, S may be situated anywhere. The positions of the forces being given, their magnitudes are determined ; for draw three screws X lt X. 2> X 3 reciprocal to the system, and find ( 28) the intensities of the seven equilibrating wrenches on 4j Q> -R> >> Xj, X 2 , X 3 . The last three are neutralised by the reactions of the constraints, and the four former must therefore equilibrate. Given any four screws in space, it is possible for four wrenches of proper intensities on these screws to hold a body having freedom of the third order in equilibrium. For, take the four given screws, and three reciprocal screws. Wrenches of proper intensities on these seven screws will equilibrate ; but those on the reciprocal screws are destroyed by the reactions, and, therefore, the four wrenches on the four screws equilibrate. It is manifest that this theorem may be generalised into the following : If a body have freedom of the kth order, then properly selected wrenches about any k+l screws (not reciprocal to the screw system) will hold the body in equilibrium. That a rigid body with freedom of the third order may be in equilibrium under the action of gravity, we have the necessary and sufficient condition, which is thus stated : The vertical through the centre of inertia must be one of the reciprocal system of generators on the pitch quadric. We see that the centre of inertia must, therefore, lie upon a screw of zero pitch which belongs to the screw system ; whence we have the following theorem : The restraints which are necessary for the equilibrium of a body which has freedom of the third order under the action of gravity, would permit rotation of the body round one definite line through the centre of inertia. 186. The Ellipsoid of Inertia. The momental ellipsoid, which is of such significance in the theory of the rotation of a rigid body about a fixed point, is presented in the Theory of Screws as a particular case of another ellipsoid, called the ellipsoid of inertia, which is of great importance in connexion with the general screw system of the third order. 188 THE THEORY OF SCREWS. [186- If we take three conjugate screws of inertia from the screw system as screws of reference, then we have seen (97) that, if 1} 0.,, 3 , be the co ordinates of a screw 0, we have where u lt u. 2 , u s are the values of u g with reference to the three conjugate screws of inertia. Draw from any point lines parallel to 0, and to the three conj ugate screws of inertia. If then a parallelepiped be constructed of which the diagonal is the line parallel to 0, and of which the three lines parallel to the conjugate screws are conterminous edges, and if r be the length of the diagonal, and x, y, z the lengths of the edges, then we have x _a V a z a r~ * IT = 2> r if* We see, therefore, that the parameter u appropriate to any screw is inversely proportional to the parallel diameter of the ellipsoid u.?z> = H, where H is a certain constant. Hence we have the following theorem : The kinetic energy of a, rigid body, when twisting with a given twist velocity about any screw of a system of the third order, is proportional to the inverse square of the parallel diameter of a certain ellipsoid, which may be called the ellipsoid of inertia ; and a set of three conjugate diameters of the ellipsoid are parallel to a set of three conjugate screws of inertia which belong to the screw system. We might also enunciate the property in the following manner: Any diameter of the ellipsoid of inertia is proportional to the twist velocity with which the body should twist about the parallel screw of the screw system, so that its kinetic energy shall be constant. 187. The Principal Screws of Inertia. It will simplify matters to consider that the ellipsoid of inertia is con centric with the pitch quadric. It will then be possible to find a triad of common conjugate diameters to the two ellipsoids. W T e can then determine three screws of the system parallel to these diameters ( 180), and these three screws will be co-reciprocal, and also conjugate screws of inertia. They will, therefore, ( 87), form what we have termed the principal screws of inertia. When the screw system reduces to a pencil of screws of zero pitch passing through a point, then the principal screws of inertia reduce to the well-known principal axes. 190] FREEDOM OF THE THIRD ORDER. 189 188. Lemma. If from a screw system of the nih order we select n screws A ly ... , A n , which are conjugate screws of inertia ( 87), and if 8 l be any screw which is reciprocal to A 2 ,...,A n , then an impulsive wrench on S Y will cause the body, when only free to twist about the screws of the system, to commence to twist about A lt Let 7^ be the screw which, if the body were perfectly free, would be the impulsive screw corresponding to A l as the instantaneous screw. R! must be reciprocal to A.,,...,A n ( 81). Take also 6 n screws of the reciprocal system B 1 ,...,B ti ^ n . Then the 8 n screws R l} S lt B l} ... , B 6 _ n must be reciprocal to the n 1 screws A 2 , ...,A n , and therefore the 8 n screws must belong to a screw system of the (7 ?i)th order. Hence an impulsive wrench upon the screw Si can be resolved into components on RI, BI, ... ,B 6 - n . Of these all but the first are neutralised by the reactions of the constraints, and by hypothesis the effect of an impulsive wrench upon Q is to make the body commence to twist about A 1} and therefore an impulsive wrench on Si would make the body twist about AI. 189. Relation between the Impulsive Screw and the Instan taneous Screw. A quiescent rigid body which possesses freedom of the third order is acted upon by an impulsive wrench about a given screw 77. It is required to determine the instantaneous screw 6, about which the body will commence to twist. The screws which belong to the system, and are at the same time reci procal to 77, must all lie upon a cylindroid, as they each fulfil the condition of being reciprocal to four screws. All the screws on the cylindroid are parallel to a certain plane drawn through the centre of the pitch quadric, which may be termed the reciprocal plane with respect to the screw 77. The reciprocal plane having been found, the diameter conjugate to this plane in the ellipsoid of inertia is parallel to the required screw 6. For let fi and v denote two screws of the system parallel to a pair of conjugate diameters of the ellipsoid of inertia in the reciprocal plane. Then 6, fi, v are a triad of conjugate screws of inertia ; but 77 is reciprocal to //, and v, and, therefore, by the lemma of the last article, an impulsive wrench upon i] will make the body commence to twist about 6. 190. Kinetic Energy acquired by an Impulse. We shall now consider the following problem : A quiescent rigid body of mass M receives an impulsive wrench of intensity rf" on a screw 77. We have now to determine the locus of a screw belonging to a screw system of the third order, such that, if the body be constrained to twist about 6, it 190 THE THEORY OF SCREWS. [190- shall acquire a given kinetic energy E, in consequence of the impulsive wrench. We have from 91 the equation 1 7/" 2 We can assign a geometrical interpretation to this equation, which will lead to some interesting results. Through the centre of the pitch quadric the plane A reciprocal to 77 is to be drawn. A sphere (181) is to be described touching the plane A at the origin 0, the diameter of the sphere being so chosen that the intercept OP made by the sphere on a radius vector parallel to any screw 6 is equal to ty^g (181). The quantity u e is inversely proportional to the radius vector OQ of the ellipsoid of inertia, which is parallel to 9 ( 186). Hence for all the screws of the screw system which acquire a given kinetic energy in consequence of a given impulse, we must have the product OP . OQ constant. From a well-known property of the sphere, it follows that all the points Q must lie upon a plane A , parallel to A. This plane cuts the ellipsoid of inertia in an ellipse, and all the screws required must be parallel to the generators of the cone of the second degree, formed by joining the points of this ellipse to the origin, 0. Since we have already shown how, when the direction of a screw belonging to a screw system of the third order is given, the actual situation of that screw is determined ( 180), we are now enabled to ascertain all the screws 6 on which the body acted upon by a given impulse would acquire a given kinetic energy. The distance between the planes A and A is proportional to OP . OQ, and therefore to the square root of E. Hence, when the impulse is given, the kinetic energy acquired on a screw determined by this construction is greatest when A and A are as remote as possible. For this to happen, it is obvious that A will just touch the ellipsoid of inertia. The group of screws will, therefore, degenerate to the single screw parallel to the diameter of the ellipsoid of inertia conjugate to A, But we have seen ( 130) that the screw so determined is the screw which the body will naturally select if permitted to make a choice from all the screws of the system of the third order. We thus see again what Euler s theorem ( 94) would have also told us, viz., that when a quiescent rigid body which has freedom of the third order is set in motion by the action of a given impulsive wrench, the kinetic energy which the body acquires is greater than it would have been had the body been restricted to any other screw of the system than that one which it naturally chooses. 192] FREEDOM OF THE THIRD ORDER. 191 191. Reaction of the Constraints. An impulsive wrench on a screw 77 acts upon a body with freedom of the third order, and the body commences to move by twisting upon a screw 6. It is required to find the screw X, a wrench on which constitutes the initial reaction of the constraints. Let </> denote the impulsive screw which, if the body were free, would correspond to 6 as the instantaneous screw. Then \ must lie upon the cylindroid (</>, 77), and may be determined by choosing on (<, 77) a screw reciprocal to any screw of the given screw system. 192. Impulsive Screw is Indeterminate. Being given the instantaneous screw 6 in a system of the third order, the corresponding impulsive screw 77 is indeterminate, because the impulsive wrench may be compounded with any reactions of the constraints. In fact 77 may be any screw selected from a screw system of the fourth order, which is thus found. Draw the diametral plane conjugate to a line parallel to 6 in the ellipsoid of inertia, and construct the cylindroid which consists of screws belonging to the screw system parallel to this diametral plane. Then any screw which is reciprocal to this cylindroid will be an impulsive screw corresponding to 6 as an instantaneous screw. Thus we see that through any point in space a whole cone of screws can be drawn, an impulsive wrench on any one of which would make the body commence to twist about the same screw. One impulsive couple can always be found which would make the body commence to twist about any given screw of the screw system. For a couple in a plane perpendicular to the nodal line of a cylindroid may be regarded as a wrench upon a screw reciprocal to the cylindroid ; and hence a couple in a diametral plane of the ellipsoid of inertia, conjugate to the diameter parallel to the screw 6, will make the body commence to twist about the screw 6. It is somewhat remarkable that a force directed along the nodal line of the cylindroid must make the body commence to twist about precisely the same screw as the couple in a plane perpendicular to the nodal line. If a cylindroid be drawn through two of the principal screws of inertia, then an impulsive wrench on any screw of this cylindroid will make the body commence to twist about a screw on the same cylindroid. For the impulsive wrench may be resolved into wrenches on the two principal screws. Each of these will produce a twisting motion about the same screw, which will, of course, compound into a twisting motion about a screw on the same cylindroid. 192 THE THEORY OF SCREWS. [193- 193. Quadric of the Potential. A body which has freedom of the third order is in equilibrium under the influence of a conservative system of forces. The body receives a twist of small amplitude 9 about a screw 9 of the screw system. It is required to determine a geometrical representation for the quantity of work which has been done in effecting the displacement. We have seen that to each screw 9 corresponds a certain linear parameter V B ( 102), and that the work done is represented by F^&\ We have also seen that the quantity v e ~ may be represented by where l} 2 , 9 3 are the co-ordinates of the screw 9 referred to three conjugate screws of the potential, and v lt v. 2 , v s , denote the values of v g for each of the three screws of reference ( 102). Drawing through the centre of the pitch quadric three axes parallel to the three screws of reference, we can then construct the quadric of which the equation is v^x z + v?y- + v 3 2 z- = H, which proves the following theorem : The work done in giving the body a twist of given amplitude from a position of equilibrium about any screw of a system of the third order, is proportional to the inverse square of the parallel diameter of a certain quadric which we may call the quadric of the potential, and three conjugate diameters of this quadric are parallel to three conjugate screws of the potential in the screw system. 194. The Principal Screws of the Potential. The three common conjugate diameters of the pitch hyperboloid, and the quadric of the potential, are parallel to three screws of the system which we call the principal screws of the potential. If the body be displaced by a twist about a principal screw of the potential from a position of stable equilibrium, then the reduced wrench which is evoked is upon the same screw. The three principal screws of the potential must not be confounded with the three screws of the system which are parallel to the principal axes of the ellipsoid of the potential. The latter are the screws on which a twist of given amplitude requires a maximum or minimum consumption of energy, and they are rectangular, which, of course, is not in general the case with the principal screws of the potential. 196] FREEDOM OF THE THIRD ORDER. 193 195. Wrench evoked by Displacement. By the aid of the quadric of the potential we shall be able to solve the problem of the determination of the screw on which a wrench is evoked by a twist about a screw 6 from a position of stable equilibrium. The construction which will now be given will enable us to determine the screw of the system on which the reduced wrench acts. Draw through the centre of the pitch quadric a line parallel to 6. Con struct the diametral plane A of the quadric of the potential conjugate to this line, and let X, p, be any two screws of the system parallel to a pair of conjugate diameters of the quadric of the potential which lie in the plane A. Then the required screw </> is parallel to that diameter of the pitch quadric which is conjugate to the plane A. For <f> will then be reciprocal to both X and //,; and as X, /A, 6 are conjugate screws of the potential, it follows that a twist about 6 must evoke a reduced wrench on <. 196. Harmonic Screws. When a rigid body has freedom of the third order, it must have ( 106) three harmonic screws, or screws which are conjugate screws of inertia, as well as conjugate screws of the potential. We are now enabled to construct these screws with facility, for they must be those screws of the screw system which are parallel to the triad of conjugate diameters common to the ellipsoid of inertia, and the quadric of the potential. We have thus a complete geometrical conception of the small oscillations of a rigid body which has freedom of the third order. If the body be once set twisting about one of the harmonic screws, it will continue to twist thereon for ever, and in general its motion will be compounded of twisting motions upon the three harmonic screws. If the displacement of the body from its position of equilibrium has been effected by a small twist about a screw on the cylindroid which contains two of the harmonic screws, then the twist can be decomposed into com ponents on the harmonic screws, and the instantaneous screw about which the body is twisting at any epoch will oscillate backwards and forwards upon the cylindroid, from which it will never depart. If the periods of the twist oscillations on two of the harmonic screws coincided, then every screw on the cylindroid which contains those harmonic screws would also be a harmonic screw. If the periods of the three harmonic screws were equal, then every screw of the system would be a harmonic screw. B. 13 194 THE THEORY OF SCREWS. [197 197. Oscillations of a Rigid Body about a Fixed Point*. We shall conclude the present Chapter by applying the principles which it contains to the development of a geometrical solution of the following important problem : A rigid body, free to rotate in every direction around a fixed point, is in stable equilibrium under the influence of gravity. The body is slightly disturbed : it is required to determine its small oscillations. Since three co-ordinates are required to specify the position of a body when rotating about a point, it follows that the body has freedom of the third order. The screw system, however, assumes a very extreme type, for the pitch quadric has become illusory, and the screw system reduces to a pencil of screws of zero pitch radiating in all directions from the fixed point. The quantity u e appropriate to a screw reduces to the radius of gyration when the pitch of the screw is zero ; hence the ellipsoid of inertia reduces in the present case to the well-known momental ellipsoid. The quadric of the potential ( 193) assumes a remarkable form in the present case. The work done in giving the body a small twist is propor tional to the vertical distance through which the centre of inertia is elevated. In the position of equilibrium the centre of inertia is vertically beneath the point of suspension, it is therefore obvious from symmetry that the ellipsoid of the potential must be a surface of revolution about a vertical axis. It is further evident that the vertical radius vector of the cylinder must be infinite, because no work is done in rotating the body around a vertical axis. Let be the centre of suspension, and 1 the centre of inertia, and let OP be a radius vector of the quadric of the potential. Let fall 1Q per pendicular on OP, and PT perpendicular upon 01, It is extremely easy to show that the vertical height through which / is raised is proportional to IQ 2 x OP 2 ; whence the area of the triangle OPI is constant, and there fore the locus of P must be a right circular cylinder of which 01 is the axis. We have now to find the triad of conjugate diameters common to the momental ellipsoid, and the circular cylinder just described. A group of three conjugate diameters of the cylinder must consist of the vertical axis, and any two other lines through the origin, which are conjugate diameters of the ellipse in which their plane cuts the cylinder. It follows that the triad required will consist of the vertical axis, and of the pair of conjugate * Trans. Roy. Irish Acad., Vol. xxiv, Science, p. 593 (1870). 197] FREEDOM OF THE THIRD ORDER. 195 diameters common to the two ellipses in which the plane conjugate to the vertical axis in the momental ellipsoid cuts the momental ellipsoid and the cylinder. These three lines are the three harmonic axes. As to that vertical axis which appears to be one of the harmonic axes, the time of vibration about it would be infinite. The three har monic screws which are usually found in the small oscillations of a body with freedom of the third order are therefore reduced in the present case to two, and we have the following theorem : A rigid body which is free to rotate about a fixed point is at rest under the action of gravity. If a plane S be drawn through the point of suspension 0, conjugate to the vertical diameter 01 of the momental ellipsoid, then the common conjugate diameters of the two ellipses in which 8 cuts the momental ellipsoid, and a circular cylinder whose axis is 01, are the two harmonic axes. If the body be displaced by a small rotation about one of these axes, the body will continue for ever to oscillate to and fro upon this axis, just as if the body had been actually constrained to move about this axis. To complete the solution for any initial circumstances of the rigid body, a few additional remarks are necessary. Assuming the body in any given position of equilibrium, it is first to be displaced by a small rotation about an axis OX. Draw the plane containing 01 and OX, and let it cut the plane S in the line OF. The small rotation around OX may be produced by a small rotation about 01, followed by a small rotation about OF. The effect of the small rotation about 01 is merely to alter the azimuth of the position, but not to disturb the equi librium. Had we chosen this altered position as that position of equilibrium from which we started, the initial displacement would be communicated by a rotation around F. We may, therefore, without any sacrifice of generality, assume that the axis about which the initial displacement is imparted lies in the plane S. We shall now suppose the body to receive a small angular velocity about any other axis. This axis must be in the plane S, if small oscillations are to exist at all, for the initial angular velocity, if not capable of being resolved into components about the two harmonic axes, will have a component around the vertical axis 01. An initial rotation about 01 would give the body a continuous rotation around the vertical axis, which is not admissible when small oscillations only are considered. If, therefore, the body performs small oscillations only, we may regard the initial axis of displacement as lying in the plane S, while we must have the initial instantaneous axis in that plane. The initial displacement may be resolved into two displacements, one on each of the harmonic axes, and 132 196 THE THEORY OF SCREWS. [197 the initial angular velocity may also be resolved into two angular velocities on the two harmonic axes. The entire motion will, therefore, be found by compounding the vibrations about the two harmonic axes. Also the instan taneous axis will at every instant be found in the plane of the harmonic axes, and will oscillate to and fro in their plane. Since conjugate diameters of an ellipse are always projected into con jugate diameters of the projected ellipse, it follows that the harmonic axes must project into two conjugate diameters of a circle on any horizontal plane. Hence we see that two vertical planes, each containing one of the harmonic axes, are at right angles to each other. We have thus obtained a complete solution of the problem of the small oscillations of a body about a fixed point under the influence of gravity. CHAPTER XV. THE PLANE REPRESENTATION OF FREEDOM OF THE THIRD ORDER*. 198. A Fundamental Consideration. Let x, y, z denote the Cartesian co-ordinates of a point in the body referred to axes fixed in space. When the body moves into an adjacent position these co-ordinates become, respectively, x + 8x, y + 8y, z + 82, and we have, by a well-known consequence of the rigidity of the body, Bx = a + gz hy, 8y = b + hx fz, 8z = c+fy- gx, where a, b, c, /, g, h may be regarded as expressing the six generalized co-ordinates of the twist which the body has received. If the body has only three degrees of freedom, its position must be capable of specification by three independent co-ordinates, which we shall call 6 lt 6.,, 6. A . The six quantities, a, b, c, f, g, h, must each be a function of #!, 2 , 3 , so that when the latter are given the former are determined. As all the movements are infinitely small, it is evident that these equations must in general be linear, and of the type a = A 1 1 + A,0, + A 3 0. J , in Avhich A lt A 2 , A 3 are constants depending on the character of the constraints. . We should similarly have b = B 1 1 + B& + B 3 6 3 , and so on for all the others. It is a well-known theorem that the new position of the body defined by 0i, 0-2, 3 may be obtained by a twist about a screw of which the axis is defined by the equations a + gz hy _ b + hx fz _ c +fy gx ~7~ 9 & * Trans. Roy. Irish Acad., Vol. xxix. p. 247 (1888). 198 THE THEORY OF SCREWS. [198- The angle through which the body has been rotated is (/ 2 + <7 2 + /* 2 )", and the distance of translation is af+ bg + ch while the pitch of the screw is af+bg + ch Every distinct set of three quantities, d l , #,, 3 , will correspond to a definite position of the rigid body, and to a group of such sets there will be a corresponding group of positions. Let p denote a variable parameter, and let us consider the variations of the set, according as p varies. To each value of p a corresponding position of the rigid body is appropriate, and we thus have the change of p associated with a definite progress of the body through a series of positions. We can give geometrical precision to a description of this movement. The equations to the axis of the screw, as well as the expression of its pitch, only involve the ratios of a, b, c,f, g, h. We have also seen that these quantities are each linear and homogeneous functions of l , #,, 3 . If, therefore, we substitute for #j, # 2 , # 3 the more general values the screw would remain unaltered, both in position and in pitch, though the angle of rotation and the distance of translation will each contain p as a factor. Thus we demonstrate that the several positions denoted by the set p6 l} p0. 2 , pO s are all occupied in succession as we twist the body continuously around one particular screw. 199. The Plane Representation. All possible positions of the body correspond to the triply infinite triad If, for the moment, we regard these three quantities as the co-ordinates of a point in space, then every point of space will be correlated to a position of the rigid body. We shall now sort out the triply infinite multitude of positions into a doubly infinite number of sets each containing a singly infinite number of positions. 200] PLANE REPRESENTATION OF THE THIRD ORDER. 190 If we fix our glance upon the screws about which the body is free to twist, the principle of classification will be obvious. Take an arbitrary triad 01, 2, 03, and then form the infinite group of triads for every value of p from zero up to any finite magnitude : all these triads will correspond to the positions attainable by twisting about a single screw. We may therefore regard ly 0. 2 , 6 3 as the co-ordinates of a screw, it being understood that only the ratios of these quantities are significant. We are already familiar with a set of three quantities of this nature in the well-known trilinear co-ordinates of a point in a plane. We thus see that the several screws about which a body with three degrees of freedom can be twisted correspond, severally, with the points of a plane. Each of the points in a plane corresponds to a perfectly distinct screw, about which it is possible for a body with three degrees of freedom to be twisted. Accordingly we have, as the result of the foregoing discussion, the statement that To each screw of a three-system corresponds one point in the plane. To develope this correspondence is the object of the present Chapter. 200. The Cylindroid. A twist of amplitude 6 on the screw 6 has for components on the three screws of reference 0i, 0. 2 , S ; a twist of amplitude < on some other screw < has the components When these two twists are compounded they will unite into a single twist upon a screw of which the co-ordinates are proportional to If the ratio of to & be X, we see that the twists about and < unite into a twist about the screw whose co-ordinates are proportional to 01 + \<f> ly 6. 2 + X._,, 0-j + \<> s . By the principles of trilinear co-ordinates this point lies on the straight line joining the points and <. As the ratio \ varies, the corresponding screw 200 THE THEORY OF SCREWS. [200- movcs over the cylindroid and the corresponding point moves over the straight line. Hence we obtain the following important result : The several screws on a cylindroid correspond to the points on a straight line. In general two cylindroids have no screw in common. If, however, the two cylindroids be each composed of screws taken from the same three-system, then they will have one screw in common. This is demonstrated by the fact that the two straight lines corresponding to these cylindroids necessarily intersect in a point which corresponds to the screw common to the two surfaces. Three twist velocities about three screws will neutralize and produce rest, provided that the three corresponding points lie in a straight line, and that the amount of each twist velocity is proportional to the sine of the angle between the two non-corresponding screws. Three wrenches will equilibrate when the three points corresponding to the screws are collinear, and when the intensity of each wrench is propor tional to the sine of the angle between the two non -corresponding screws. 201. The Screws of the Three-system. In any three-system there are three principal screws at right angles to each other, and intersecting in a point ( 173). It is natural to choose these as the screws of reference, and also as the axes for Cartesian co-ordinates. The pitches of these screws are p 1} p.,, p 3 , and we shall, as usual, denote the screw co-ordinates by 0,, a , 3 . The displacement denoted by this triad of co-ordinates is obtained by rotating the body through angles 1} 0. 2 , 3 around three axes, und then by translating it through distances p^, p,0. 2 , p 3 3 parallel to these axes. As these quantities are all small, we have, for the displace ments produced in a point x, y, z, Sy = p. 2 2 + x0 3 - z6 l , 8z = p s 3 + y0 1 -x0 2 ; these displacements correspond to a twist about a screw of which the axis has the equations pA + z0y - y0 3 _ p 2 2 + x0 3 - z0 l p 3 3 + yfl - x0. 2 0i 0, ~0T~ while the pitch p is thus given : 202] PLANE REPRESENTATION OF THE THIRD ORDER. 201 We have now to investigate the locus of the screws of given pitch, and as p is presumed to be a determinate quantity, we have (p.* - p) 2 + x0 3 = 0, whence, by eliminating 1} 2 , 3 we obtain, as the locus of the screws of pitch p, the quadric otherwise found in the previous chapter (p! -p) x z + (p,-p) y + (p.-p) z- + (pi-p)(p s -p)(p 3 -p) = 0. According as p varies, this family of quadrics will exhibit all the screws of the three-system which possess a definite pitch. 202. Imaginary Screws. To complete the inventory of the screws it is, however, necessary to add those of indefinite pitch, i.e. those whose co-ordinates satisfy both the equations M +M a +M 8 =o. 0s + e.? + <v=o. There are four triads of co-ordinates which satisfy these conditions, and, remembering that only the ratios are concerned, the values of 1} n , 3 may be written thus : The equations of the axis written without p are * (Of + 0J} - yOA - ^0 A + ( P* - p 3 ) 0,6, = 0, y (Of + 0s) - zOA - x6A + (p 3 - Pl ) 6A = o, z (6? + <9 2 ) - x0A - y0 3 0, + ( PI - p z ) 6,0, = 0, of which two are independent. If we substitute the values of 0,, 6.,, 3 for the first indeterminate screw, the three equations just written reduce to * ( P2 - #,)* + y ( p 3 - p$ + z ( Pl - p$ -(p 2 - p 3 ) h - (p-.-p^^p,- p$ - 0. 202 THE THEORY OF SCREWS. [202, If we make * = (P*-pa)* , @ = (p 3 -pi)* , f Y = (pi-prf, the equations of the four planes are expressed in the form + ax + fty + yz a/3y = 0, ax + fiy + jz afty = 0, + ax /3y + yz a/3y 0, + ax + (3y <yz afty = 0. It is remarkable that the three equations of the axis for each of these screws here coalesce to a single one. The screw of indeterminate pitch is thus limited, not to a line, but to a plane. The same may be said of each of the other three screws of indeterminate pitch ; they also are each limited to a plane found by giving variety of signs to the radicals in the equations just written. We have thus discovered that the complete locus of the screws of a three-system consists, not only of the family of quadrics, which contain the screws of real or imaginary, but definite pitch, but that it also contains a tetrahedron of four imaginary planes, each plane being the locus of one of the four screws of indefinite pitch. 203. Relation of the Four Planes to the Quadrics. The planes have an interesting geometrical connexion with the family of quadrics, which we shall now develop. The first theorem to be proved is, that each of the quadrics touches each of the planes. This is gcometrically obvious, inasmuch as each quadric contains all the screws of the system which have a given pitch p\ but each of the planes contains a system of screws of every pitch, among which there must be one of pitch p. There will thus be a ray in the plane, which is also a generator of the hyper- boloid but this, of course, requires that the plane be a tangent to the hyperboloid. It is easy to verify this by direct calculation. Write the quadric, ( Pi - p) a* + (p,- p) f + (p 3 -p)z~ + ( Pl - p) (p. 2 - p) (p 3 - p ) = 0. The tangent plane to this, at the point x, y , z, is ( p, - p) xx + (p,-p) yij + (^ 3 _ p) zz > + ( pl If we identify this with the equation ax + fiy + ryz a/3y = 0, 203] PLANE REPRESENTATION OF THE THIltD ORDER. 203 we shall obtain *- Pi)* (Pi- Pi)* - (PI-P)(P*-P) and as these values satisfy the equation of the quadric, the theorem has been proved. The family of quadric surfaces are therefore inscribed in a common tetra hedron, and they have four common points, as well as four common tangent planes. For, write the two cones #- + if + z- = 0, pj? + ihy" + ihz" = o. These cones have four generators in common, and the four points in which these generators cut the plane at infinity will lie on every surface of the type (Pi ~ P) ? + (P* ~ P) V" + (Pa ~p)2- + (pi - p) (p* - p) (p 3 -p) = 0. We now see the distribution of the screws in the imaginary planes. In each one of these planes there are a system of parallel lines ; each line of this system passes through the same point at infinity, which is, of course, one of the four points just referred to. Every line of the parallel set, when it receives appropriate pitch, belongs to the three-system. It thus appears that the ambiguity in the pitches of the screws in the planes is only apparent. The system of screw co-ordinates which usually defines a screw with absolute definiteness, loses that definiteness for the screws in these planes. Each plane contains a whole pencil of screws, radiating from a point at infinity, but the co-ordinates can only represent these screws collectively, for the three co-ordinates then represent, not a single screw, but a whole pencil of screws. As the pitches vary on every screw of the pencil, the co-ordinates can only meet this difficulty by representing the pitch as indeterminate. The proof that only a single screw of each pitch is found in the pencil is easily given. If there were two, then the same hyperboloid would have two generators in this plane of equal pitch ; but this is impossible, because, from the known properties of the three-system, only one of these generators belongs to the three-system, and the other to the reciprocal system. 204 THE THEORY OF SCREWS. [204, 204. The Pitch Conies. The discussion in 203 will prepare us for the plane representation of the screws of given pitch p, for we have P (0? + 0/ + 3 2 ) - M a - M 2 - M 2 = - This, of course, represents a conic section, and, accordingly, we have the following theorem : The locus of points corresponding to screws of given pitch is a conic section. A special case is that where the pitch is zero, in which case the locus is given by This we shall often refer to as the conic of zero -pitch. Another important case is that where p is infinite, in which case the equation is 0* + 3 *+0 3 *=o. The conic of zero-pitch and the conic of infinite pitch intersect in four points, and through these four points all the other conies must pass. The points, of course, correspond to the screws of indeterminate pitch : we may call them P,, P,, P,, 1\. Any conic through these four critical points will be a conic of equal- pitch screws. As a straight line cuts a conic in two points, we see the well-known theorem, that every cylindroid will contain two screws of each pitch. The two principal screws on a cylindroid are those of maximum and minimum pitch ; they will be found by drawing through P l} P 2 , P 3 , P 4 , the two conies touching the straight line corresponding to the cylindroid. The two points of contact are the screws required. If a and ft are the two principal screws on a cylindroid, then any pair of harmonic conjugates to a and ft represent a pair of screws of equal pitch. For if S + kS = be a system of conies, then it is well known that the pairs of points in which a fixed ray is cut by this system form a system in involution. The double points of this involution are the points of contact of the two conies of the system which touch the line. 205. The Angle between Two Screws. From the equations of the screw given in 201, we see that the direction 205] PLANE REPRESENTATION OF THE THIRD ORDER. 205 cosines are proportional to 8 } , # 2 > ;1 ; for if we take the point infinitely distant we find that the equations reduce to x _ y _ z 6 l &, $3 Accordingly, the line drawn parallel to the screw through the origin has its direction cosines proportional to 0,, 2 , 3 , and hence the actual direction cosines are ft ft 3 The cosine of the angle between two screws, 6 and </>, will therefore be By the aid of the conic of infinite pitch we can give to this a geometrical interpretation. The co-ordinates of a screw on the straight line joining 6 and <f> will be ft + X<j , # 2 + ^-$2> ft + X< 3 . If we substitute this in the equation to the conic of infinite pitch we obtain ft 2 + ft 2 + 9* -H 2X (#!</>, + 2 </> 2 + 3 3 ) + \- (fa- 4- </>.;- + </) = 0. Writing this in the form aX 2 + 2&X + c = 0, of which Xj and X 2 are the roots, we have, as the four values of X, corre sponding, respectively, to the points 6 and </>, and to the points in which their chord cuts the conic of infinite pitch, X 1( Xo, 0, oo. The anharmonic ratio is ^ V or b - V6 2 - ac b + V6 2 - ac If to be the angle between the two screws, 6 and <, then b COS G) = , Vac and the anharmonic ratio reduces to an*-, whence we deduce the following theorem : 206 THE THEORY OF SCREWS. [205- The angle between two screws is equal to \i times the logarithm of the an- ha,rmonic ratio in which their corresponding chord is divided by the infinite pitch conic. The reader will be here reminded of the geometry of non-Euclidian space, in which a magnitude, which in Chapter XXVI. is called the Intervene, analogous to the distance between two points, is equal to ^i times the logarithm of the anharmonic ratio in which their chord is divided by the absolute. We have only to call the conic of infinite pitch the absolute, and the angle between two screws is the intervene between their corresponding points. 206. Screws at Right Angles. If two screws, 9 and </>, be at right angles, then $]<l + 0. 2 <f).2 + 0;,,(f> 3 = 0. In other words, 6 and </> are conjugate points of the conic of infinite pitch, V + $+ &- & All the screws at right angles to a given screw lie on the polar of the point with regard to the conic of infinite pitch. Hence we see that all the screws perpendicular to a given screw lie on a cylindroid. This is otherwise obvious, for a screw can always be found with an axis parallel to a given direction. If, therefore, a cylindroid of the system be taken, a screw of the system parallel to the nodal axis of that cylindroid can also be found, and thus we have the cylindroid and the screw, which stand in the relation of the pole and the polar to the conic of infinite pitch. A point on the conic of infinite pitch must represent a screw at right angles to itself. Every straight line cuts the conic of infinite pitch in two points, and thus every cylindroid has two screws of infinite pitch, and each of these screws is at right angles to itself. In general, the direction cosines of the nodal axis of a cylindroid are proportional to the co-ordinates of the pole of the line corresponding to the cylindroid with respect to the conic of infinite pitch. 207. Reciprocal Screws. If lt 0,, 3 be the co-ordinates of a screw, and n </>,, </> 3 those of another screw, then it is known, 37, that the condition for these two screws to be reciprocal is We are thus led to the following theorem, which is of fundamental importance in the present investigation : 208] PLANE REPRESENTATION OF THE THIRD ORDER. 207 A pair of reciprocal screws are conjugate points with respect to the zero- pitch conic. From this theorem we can at once draw the following conclusions : All the screws of the system reciprocal to a given screw lie upon a cylindroid. For the locus of points conjugate to 9 is, of course, the polar of with respect to the zero-pitch conic, and this polar will correspond to a cylindroid. On any cylindroid one screw can always be found reciprocal to a given screw 9. For this will be the intersection of the polar of 9 with the line corresponding to the given cylindroid. A triad of co-reciprocal screws will correspond to a self-conjugate triangle of the conic of zero-pitch. 208. The Principal Screws of the System. Draw the conic of zero-pitch A, and the conic of infinite pitch B, which intersect in the four screws of indeterminate pitch, P,, P 2 , P 3 , P 4 (see fig. 39). Draw the diagonals of the complete quadrilateral, and let them intersect in Fig. 39. the points X, Y, Z. These three points are significant. Take any pair of them, X and F; then, by the known properties of conies, X and Y are con jugate points with respect to both of the conies A and B. The screws X 208 THE THEORY OF SCREWS. [208, and Fmust therefore be mutually perpendicular and reciprocal. If p be the pitches of these screws ; if to be the angle between them, and d their perpendicular distance, then the virtual coefficient is one-half of (Pe + Pt) cos > ~ do* sin &&gt; ; as they are reciprocal, this is zero, and as <o is a right angle, we must have d = ; in other words, the screws corresponding to X and Y must intersect at right angles. The same may be proved of either of the pairs X and Z or Y and Z. The points X, Y, Z must therefore correspond to three screws of the system mutually perpendicular, and intersecting at a point. But in the whole system there is only a single triad of screws possessing these properties. They are the axes in the equations of 201, and are known as the principal screws of the system. The three points X, Y, Z being the vertices of a self-conjugate triangle with respect to both the conies A and B, and hence to the whole system, we have the following theorem : The vertices of the conjugate triangle common to the system of pitch conies correspond to the three principal screws of the three-system. 209. Expression for the Pitch. Each conic drawn through the four points of indeterminate pitch, P 1} P 2 , P 3 , P 4 , is the locus of screws with a given pitch belonging to the system. We are thus led to connect the constancy of the pitch at each point of this conic with another feature of constancy, viz. that of the anharmonic ratio subtended by a variable point of the conic with the four fixed points. The connexion between the pitch and the anharmonic ratio will now be demonstrated. Let 1 , # 2 > 03 be the co-ordinates of any point on the conic, and let a, /3, 7 be the co-ordinates of one of the four points, say P 1 ; then if 0j, $ 2 , :i be the current co-ordinates, the equation of the line joining 9 to P l is <f>3 13, =0. As we are dealing with the anharmonic ratio of a pencil, we may take any section for the calculation of the ratios, and, accordingly, make <k = 0; and we have for the co-ordinates of the point in which the line joining 8 and Pj intersects </> :! = 0, the conditions, - i 7 209] PLANE REPRESENTATION OF THE THIRD ORDER. 209 By changing the sign of a, and then changing the signs of ft aud of 7, we shall obtain the four points in which the pencil 0(P 1 , P 2 , P 3 , P 4 ) cuts the axis <j> 3 = 0. If four values of j- 1 be represented by k, I, m, n, the required 02 anharmomc ratio is, of course, (n l)(m k) (n-m)(l-ky and after a few reductions we find that this becomes But we have _ Eliminating 0^, we find that 2 2 and 0/ disappear also when we make tf = p-2-p s , P a = p,-p 1) y 2 = pi-p,, and we obtain the following result : which gives the following theorem : Measure off distances p lf p.,, p s , p, from an arbitrary point on a straight line, then the anharmonic ratio of the four points thus obtained is equal to the anharmonic ratio subtended by any point of the p-pitch conic at the four points of indeterminate pitch. It is possible without any sacrifice of generality to make the zero-pitch conic a circle. For take three angles A, B, G whose sum is 180 and such that the equations sin2J. _ sin 2B _ sin 2(7 Pi Pi p 3 are satisfied where p l} p 2 , p s are the three principal pitches of the three- system. If the fundamental triangle has A, B, C for its angles then the equation a, 2 sin 2 A + 2 2 sin IB + a/ sin 2(7 = 0, is the equation of the zero-pitch conic. It is however a well-known theorem in conies that this equation represents a circle with its centre at the ortho- centre, that is, the intersection of the perpendiculars from the vertices of the triangle on its opposite sides. We thus have as the system of pitch conies a, 2 sin 24 + * 2 2 sin 2B + a 3 2 sin 2(7 - p (a, 2 + a 2 2 + a, 2 ) = 0. B. 14 210 THE THEORY OF SCREWS. [209 The centre of a conic of the system has for co-ordinates sin A sin B sin G sin 2A -p sin 25 -p sin 20 -p The locus of the centres of the system of conies is easily seen to pass through the vertices of the triangle of reference. It must also pass through the orthocentre, and hence by a well-known property it must be an equilateral hyperbola. It can also be easily shown that this hyperbola must pass through the " symmedian" point of the triangle, i.e. through the centre of gravity of three particles at the vertices of the triangle when the mass of each particle is proportional to the square of the sine of the corresponding angle. In Fig. 40 a system of pitch conies has been shown drawn to scale. The sides of the fundamental triangle are represented by the numbers 117, 189, 244 respectively. The equation to the system of conies, expressed in Cartesian co-ordinates for convenience of calculation, is = .- 1864116 - + y- ( 2-2135882 - - 6852041 ) V p i \ p J -1649571^ - 9 46700z - 25199-54 + * P Among critical conies of the system we may mention : 1. The two parabolas for which the pitches are respectively 8766 and "3089. 2. The three cases in which the conic breaks up into a pair of straight lines for the pitches sin 2 A, sin 25, sin 2(7, respectively. Of these, the first alone is a real pair corresponding to the pitch 8256034. The equations of these lines are x = 7 84y - 978, For convenience in laying down the curves the current co-ordinates on each conic are expressed by means of an auxiliary angle ; thus, for example, in computing points on the hyperbola with the pitch 748984 I used the equations x = 66 + 26-1 sec 6 + 132 tan 6, y = 161-5 + 40-7 sec 0. The ellipse with pitch 9 was constructed from the equations x = - 367 - 168 cos 351 sin 0, 209] PLANE REPRESENTATION OF THE THIRD ORDER. 211 142 212 THE THEORY OF SCREWS. [ 209, The following are the pitches of the several points and curves represented Vertices of the Triangle + 992, + 825, - 448, Ellipses + -96, + -92, + 1, - 4, Parabola + 309, Hyperbolas + 748984, + -8300467. The locus of the centres of the pitch conies is a^j sin (A - B) sin 2(7 + 2 a 3 sin (B - C) sin 1A + a.^ sm(C-A) sin 25 = 0. 210. Intersecting Screws in a Three-System. If two screws of a three-system intersect, then their two corresponding points must fulfil some special condition which we propose to investigate. Let a be one screw supposed fixed, then we shall investigate the locus of the point 6 which expresses a screw which intersects a. We can at once foresee a certain character of this locus. A ray through a can only cut it in one other point, for if it cut in two points, we should have three co-cylinclroidal screws intersecting, which is not generally possible. The locus is, as we shall find, a cubic and the necessary condition is secured by the fact that a is a double point on the cubic, so that a ray through a has only one more point of intersection with the curve. We can indeed prove that this curve must be a cubic from the fact that any screw meets a cylindroid in three points. Draw then a ray ( 200) corresponding to a cylindroid of the three-system. There must be in general three points of the locus on this ray. Therefore the locus must be a cubic. As a and 6 intersect we have since d 6a = 2<3- ea = (p a + p e ) cos 0<9). By substituting the values of the different quantities in terms of the co ordinates we have the following homogeneous equation of the cubic : = 2 (0!* + 2 2 + 3 2 ) (p^A +P&A + P&A) (a, 2 + 2 2 + a 3 2 ) a 3<?3) (ai 2 + 2 2 + a s 2 ) We first note that this cubic must pass through the four points of inter section of = 0,"+ <9./ + 6*, = pA* + p&i + pA 2 - But this might have been expected, because as we have shown ( 203) each of these four points corresponds, not to a single screw, but to a plane of screws. 210] PLANE REPRESENTATION OF THE THIRD ORDER. 213 In a certain sense therefore a must intersect each of these four screws, and accordingly the cubic has to pass through the four points. To prove that a is a double point we write for brevity p = 0^ + e:- + 3 -, R = p&A + p.&A + p 3 a 3 3 , Q = Pidi 1 + pA* + P-*0 /, 8 = ^0,+ a,8, + a 3 3 , L = p&S + p 2 aj + p s a 3 2 , H = a/ 2 + a, 2 + a 3 2 , and the equation is P(2HR-LS)-8QH=0. Differentiating with respect to 1} 0. 2 , 3 respectively and equating the results to zero we have = 20j [2RH -LS- aHS] + a, [2aPH -LP- HQ], = 20 8 [2RH -LS- bHS] + a 2 [2bPH -LP- HQ], = 20 3 [2RH -L8- cHS] + a 3 [2cPH-LP - HQ]. These are satisfied by 6 l = a l , 2 = 2 , 3 = a s which proves that a is a double point. The cubic equation is satisfied by the conditions =p ] a l 1 +p 2 a 2 2 +p 3 <x z 3 . This might have been expected because these equations mean that o and are both reciprocal and rectangular, in which case they must intersect. Thus we obtain the following result : If !, a 2 , a s are the co-ordinates of a screw a in the plane representation, then the co-ordinates of the screw which, together with a, constitute the principal screws of a cylindroid of the system are respectively Ps-p* Pi- Pi P*-PI 1 2 3 The following theorem may also be noted. Among the screws of a three- system which intersect one screw of that system there will generally be two screws of any given pitch. For the cubic which indicates by its points the screws that intersect a will cut any pitch conic in general in six points. Four of these are of course the four imaginary points referred to already. The two remaining inter sections indicate the two screws of the pitch appropriate to the conic which intersect a. The cubic P(2HR-LS)-SQH = Q, 214 THE THEORY OF SCREWS. [210, of course passes through the two points which lie at the intersections of 2HR LS = and Q = 0. Hence we deduce the following result. The cylindroid through the two screws of zero pitch which intersect a corresponds to the ray whose equation is 2( 1 2 +a, 2 +a 3 2 )(> 1 a 1 6> 1 +p,aA + p^-A)-(p^ +p,a.* +p&?} (a^ +a 2 2 +a 3 3 )=0, a will of course intersect a third screw on this cylindroid and be perpen dicular thereto. The cubic passes through the two points defined by = aA + oc,<9 2 + a 3 3 , but these points are the points of contact of the pair of tangents drawn from the point a to the conic of infinite pitch. These two points in addition to the four points on the same conic defined by its intersection with the conic of zero pitch, make six known points on the cubic. If however we are given six points on a cubic and also a double point on the curve, then it is determinate. Thus we obtain the following geometrical construction. In the plane representation of a three-system we draw the conic of zero pitch C and the conic of infinite pitch U. To find the locus of the screws which intersect a given screw a, it is necessary to draw the two tangents from a to If and through the two points of contact, and also the four points common to C and U then draw that single cubic which has a double point at a. See Appendix, note 5. 211. Application to Dynamics. By the aid of the plane representation we are enabled to solve certain problems in the dynamics of a rigid body which has freedom of the third order. Let an impulsive wrench act upon a quiescent rigid body ; it is required to determine the instantaneous screw about which the body will commence to twist. It has been shown ( 96) that the impulsive wrench, wherever situated, can generally be adequately represented by the reduced impulsive wrench on a screw of the three-system. The problem is therefore reduced to the determination of the point corresponding to the instantaneous screw, when that corresponding to the impulsive screw is known. 211] PLANE REPRESENTATION OF THE THIRD ORDER. 215 We have first to draw the conic of which the equation is This conic is of course imaginary, being in fact the locus of screws about which, if the body were twisting with the unit of twist velocity, the kinetic energy would nevertheless be zero. If two points 0, (ft are conjugate with respect to this conic, then The screws corresponding to 6 and $ are then what we have called conjugate, screws of inertia. This conic is referred to a self-conjugate triangle, the vertices of which are three conjugate screws of inertia. There is one triangle self- conjugate both to the conic of zero pitch, and to the conic of inertia just considered. The vertices of this triangle are of especial interest. Each pair of them correspond to a pair of screws which are reciprocal, as well as being conjugate screws of inertia. They are therefore what we have designated as the principal screws of inertia ( 87). They degenerate into the principal axes of the body when the freedom degenerates into the special case of rotation around a fixed point. When referred to this self-conjugate triangle, the relation between the impulsive point and the corresponding instantaneous point can be expressed with great simplicity. Thus the impulsive point <, whose co-ordinates are #iWi 2 -5- Pi ; 0*uf -j- p 2 ; 3 3 a -r p 3 , corresponds to the instantaneous point whose co-ordinates are 6 lt 2 , 3 . The geometrical construction is sufficiently obvious when derived from the theorem thus stated. If <f> denote an impulsive screw, and 6 the corresponding instantaneous screw, then the polar of <f> with regard to the conic of zero pitch is the same straight line as the polar of 6 with regard to the conic of inertia. If H be the virtual coefficient of two screws 6 and 77, then It follows that the locus of the points which have a given virtual coefficient with a given point is a conic touching the conic of infinite pitch at two points. If -v/r be the screw whose polar with regard to the conic of infinite pitch is identical with the polar of 77 with regard to the conic of zero pitch, then all the screws 6 which have a given virtual coefficient with 77 arc equally inclined to ^. It hence follows that all the screws of a three- system which have a given virtual coefficient with a given screw are parallel 216 THE THEORY OF SCREWS. [211 to the generators of a right circular cone. All the screws reciprocal to 77 form a cylindroid, and fy is the one screw of the system which is parallel to the nodal line of the cylindroid. The virtual coefficient of ^ and 17 is greater than that of 77 with any other screw. If 6 be a screw about which, when a body is twisting with a given twist velocity it has a given kinetic energy, then we must have U *e? + uje* + u 3 2 3 2 - E(e? + e.? + e/) = o, where E is a constant proportional to the energy. It follows that the locus of 6 must be a conic passing through the four points of intersection of the two conies u*d? + u?e? + u 3 2 6 3 2 = 0, The four points in which these two conies intersect correspond to the screws about which the body can twist with indefinite kinetic energy. These four points A, B, C, D being known, the kinetic energy appropriate to every point P can be readily ascertained. It is only necessary to measure the anharmonic ratio subtended by P, at A, B, C, D, and to set off on a straight line distances w x 2 , u, u 3 2 , h 2 , so that the anharmonic ratio of the four points shall be equal to that subtended by P. This will determine h 2 , which is proportional to the kinetic energy due to the unit twist velocity about the screw corresponding to P. A quiescent rigid body of mass M receives an impulsive wrench of given intensity on a given screw 77 ; we investigate the locus of the screw 6 belonging to the three-system, such that if the body be constrained to twist about 6, it shall acquire a given kinetic energy. It follows at once (91) that we must have where E is proportional to the kinetic energy. The required locus is there fore a conic having double contact with the conic of inertia. It is easy to prove from this that E will be a maximum if V#i : Ptfi = W 2 2 2 : p 2 i] 2 = u 3 2 3 : p s rj 3 ; whence again we have Euler s well-known theorem that if the body be allowed to select the screw about which it will twist, the kinetic energy acquired will be larger than when the body is constrained to a screw other than that which it naturally chooses ( 94). A somewhat curious result arises when we seek the interpretation of a tangent to the conic of infinite pitch. This tangent must, like any other straight line, correspond to a cylindroid ; and since it is the polar of the 211] PLANE REPRESENTATION OF THE THIRD ORDER. 217 point of contact, it follows that every screw on the cylindroid must be at right angles to the direction corresponding to the point of contact. The co-ordinates of the point of contact must therefore be proportional to the direction cosines of the nodal line of the cylindroid. If the body be in equilibrium under the action of a conservative system of forces, then there is a conic (analogous to the conic of inertia) which denotes the locus of screws about which the body can be displaced to a neighbouring position, so that even as far as the second order of small quantities no energy is consumed. The vertices of the triangle self-conjugate both to this conic and the conic of inertia correspond to the harmonic screws about which, if the body be once displaced, it will continue to oscillate. CHAPTER XVI. FREEDOM OF THE FOURTH ORDER. 212. Screw System of the Fourth Order. The most general type of a screw system of the fourth order is exhibited by the set of screws which are reciprocal to an arbitrary cylindroid ( 75). To obtain certain properties of this screw system it is, therefore, only necessary to re-state a few results already obtained. All the screws which belong to a screw system of the fourth order and which can be drawn through a given point are generators of a certain cone of the second degree ( 23). All the screws of the same pitch which belong to a screw system of the fourth order must intersect two fixed lines, viz. those two screws which, lying on the reciprocal cylindroid, have pitches equal in magnitude but opposite in sign to the given pitch ( 22). One screw of given pitch and belonging to a given screw system of the fourth order can be drawn through each point in space ( 123). As we have already seen that two screws belonging to a screw system of the third order can be found in any plane ( 178), so we might expect to find that a singly infinite number of screws belonging to a screw system of the fourth order can be found in any plane. We shall now prove that all these screws envelope a parabola. A theorem equivalent to this has been already proved in a different manner in 162. Take any point P in the plane, then the screws through P reciprocal to the cylindroid form a cone of the second order, which is cut by the plane in two lines. Thus two screws belonging to a given screw system of the fourth order can be drawn in a given plane through a given point. But it can be easily shown that only one screw of the system parallel to a given line can be found in the plane. Therefore from the point at infinity only a single finite tangent to the curve can be drawn. Therefore the other 212, 213] FREEDOM OF THE FOURTH ORDER. 219 tangent from the point must be the line at infinity itself, and as the line at infinity touches the conic, the envelope must be a parabola. In general there is one line in each screw system of the fourth order, which forms a screw belonging to the screw system, whatever be the pitch assigned to it. The line in question is the nodal line of the cylindroid reciprocal to the four-system. The kinematical statement is as follows : When a rigid body has freedom of the fourth order, there is in general one straight line, about which the body can be rotated, and parallel to which it can be translated. A body which has freedom of the fourth order may be illustrated by the particular case where one point P of the body is forbidden to depart from a given curve. The position of the body will then be specified by four quantities, which may be, for example, the arc of the curve from a fixed origin up to P, and three rotations about three axes intersecting in P. The reciprocal cylindroid will in this case assume an extreme form ; it has de generated to a plane, and in fact consists of screws of zero pitch on all the normals to the curve at P. It is required to determine the locus of screws parallel to a given straight line L, and belonging to a screw system of the fourth order. The problem is easily solved from the principle that each screw of the screw system must intersect at right angles a screw of the reciprocal cylindroid ( 22). Take, therefore, that one screw 6 on the cylindroid which is perpendicular to L. Then a plane through 6 parallel to L is the required locus. 213. Equilibrium with freedom of the Fourth Order. When a rigid body has freedom of the fourth order, it is both necessary and sufficient for equilibrium, that the forces shall constitute a wrench upon a screw of the cylindroid reciprocal to the given screw system. Thus, if a single force can act on the body without disturbing equilibrium, then this force must lie on one of the two screws of zero pitch on the cylindroid. If there were no real screws of zero pitch on the cylindroid that is, if the pitch conic were an ellipse, then it would be impossible for equilibrium to subsist under the operation of a single force. It is, however, worthy of remark, that if one force could act without disturbing the equilibrium, then in general another force (on the other screw of zero pitch) could also act without disturbing equilibrium. A couple which is in a plane perpendicular to the nodal line can be neutralized by the reaction of the constraints, and is, therefore, consistent with equilibrium. In no other case, however, can a body which has freedom of the fourth order be in equilibrium under the influence of a couple. 220 THE THEORY OF SCREWS. [213, We can also investigate the conditions under which five forces applied to a free rigid body can neutralize each other. The five forces must, as the body is free, belong to a screw system of the fourth order. Draw the cylindroid reciprocal to the system. The five forces must, therefore, intersect both the screws of zero pitch on the cylindroid. We thus prove the well-known theorem that if five forces equilibrate two straight lines can be drawn which intersect each of the five forces. Four of the forces will determine the two transversals, and therefore the fifth force may enjoy any liberty consistent with the requirement that it also intersects the same two lines. If A l ,...A 5 be the five forces, the ratio of any pair, let us say for example, A : A z is thus determined. Let P, Q be the two screws of zero pitch upon the cylindroid, i.e. the two common transversals of A ly ... A 5 . Choose any two screws X and Y reciprocal to both A! and J. 2 , but not reciprocal to A 3 , A 4 or A 5 . Choose any screw Z reciprocal to A 3 , A^, A 5 , but not reciprocal to A l or A 2 . Construct ( 25) the single screw / reciprocal to the five screws X, 7, P, Q, Z. The four screws X, Y, P, Q are reciprocal to the cylindroid A 1} A. 2 \ therefore /, which is reciprocal to X, Y, P, Q, must lie upon the cylindroid (A lt Aj($2Q Since P, Q, Z are all reciprocal to A 3 , A t , A 5 , it follows that / being reciprocal to P, Q, Z must belong to the screw system A 3 , A t , A 5 . Hence / is found on the cylindroid (A 1} A 3 ), and it must also belong to the system (A 3 , AI, A s ). If, therefore, forces along A 1 ,...A 5 are to equilibrate, the forces along A 1> A 3 must compound into a wrench on /. But / being known by construction the angles A Z I and A^I are known, and consequently the ratio of the sines of these angles, i.e. the relative intensities of the forces on A 1 and A 2 are determined ( 14). If a free rigid body is acted upon by five forces, the preceding con siderations will show in what manner the body could be moved so that it shall not do work against nor receive energy from any one of the forces. Let A!, ... A 5 be the five forces. Draw two transversals L, M intersecting A 1 ,...A i . Construct the cylindroid of which L, M are the screws of zero pitch ; find, upon this cylindroid, the screw X reciprocal to A 5 . Then the 214] FREEDOM OF THE FOURTH ORDER. 221 only movement which the body can receive, so as to fulfil the prescribed conditions, is a twist about the screw X. For X is then reciprocal to AU...AS, and therefore a body twisted about X will do no work against forces directed along A 1} ... A s . From the theory of reciprocal screws it follows that a body rotated around any of the lines A ly ... A 5 will not do work against nor receive energy from a wrench on X. In the particular case, where A l} ... A 5 have a common transversal, then X is that transversal, and its pitch is zero. In this case it is sufficiently obvious that forces on A^...A 5 cannot disturb the equilibrium of a body only free to rotate about X. 214. Screws of Stationary Pitch. We begin by investigating the screws in an ?i- system of which the pitch is stationary in the sense employed in the Theory of Maximum and Minimum. We take the case of n = 4. The co-ordinates O l ,... S of the screws of a four-system have to satisfy the two linear equations denning the system. We may write these equations in the form The screws of reference being co-reciprocal, we have for the pitch p e the equation SM -.Rp^O, where R is the homogeneous function of the second degree in the co ordinates which is replaced by unity ( 35) in the formulae after differ entiation. If the pitch be stationary, then by the ordinary rules of the differential calculus ( 38), As however belongs to the four-system, the variations of its co-ordinates must satisfy the two conditions Following the usual process we multiply the first of these equations by some indeterminate multiplier \, the second by another quantity p, and then 222 THE THEORY OF SCREWS. [214 add the products to the former equation. We can then equate the co efficients of 80!,... 8# 6 severally to zero, thus obtaining J~D 2p 6 6 - ja Pe + *A + A^e = 0. av 6 Choose next from the four-system any screw whatever of which the co ordinates are $ 15 ... <. Multiply the first of the above six equations by <j> 1} the second by < 2 , &c. and add the six products. The coefficients of X and //, vanish, and we obtain dR , dR The coefficient of p g is however merely double the cosine of the angle between 6 and <. This is obvious by employing canonical co-reciprocals in which .R = (0i + 0*y + (0, + e t y + (0, + 0,y, whence dR dR (0, + 2 )+2 (0 3 + 4 ) (0 3 + t ) + (0 8 + 00 (0, + 6 ) = 2 cos We thus obtain the following theorem, which must obviously be true for other values of n besides four. If (f) be any screw of an n-system and if 6 be a screw of stationary pitch in the same system then -ar^ = cos (6(f>)p e . Suppose that there were two screws of stationary pitch and in an ??- system. Then 13- = cos If p e and PCJ, are different these equations require that BJ^ = ; cos (#</>) = ; i.e. the screws are both reciprocal and rectangular and must therefore intersect. We have thus shown that if there are two stationary screws of different pitches in any w-system, then these screws must intersect at right angles. In general we learn that if any screw of an ?i-system has a pitch equal to that of a screw of stationary pitch in the same system, then and must intersect. For the general condition * = cos (#</>) p 6 214] FREEDOM OF THE FOURTH ORDER. 223 is of course (Pe + P*) cos W) - sin (0<f>) d^ = 2p e cos (0<j>), or (P<t> ~ Pe) cos (0<f>) - sin (0<f>) d 64> = 0. If then p^ = p 6 we must have sin (#(/>) c^ = 0, which requires that and must intersect at either a finite or an infinite distance. In the case where < is at right angles to 6 it follows from the formula ^ob cos (0<fi)p 6 that CT04, = 0, or that and are reciprocal. But two screws which are at right angles and also reciprocal must intersect, and hence we have the following theorem. If 6 be a screw of stationary pitch in an n-system, then any other screw belonging to the n-system and at right angles to Q must intersect 6. If (/> belongs to an w-system its co-ordinates must, on that account, satisfy 6 n linear equations. If it be further assumed that < has to be perpen dicular to 0, then the co-ordinates of < have to satisfy yet one more equa tion, i.e. . dR , dR ft>:-*;BETft In this case </> is subjected to 7 n linear equations. It follows ( 76) that (f> will have as its locus a certain (n l)-system, whence we have the following general theorem. If 6 is a screw of stationary pitch in an n-system P then among the (n Y)-sy stems included in P there is one Q such that every screw of Q intersects at right angles. These theorems can also be proved by geometrical considerations. If a screw 6 have stationary pitch in an w-system it follows a fortiori that 6 must have stationary pitch on any cylindroid through 6 and belonging wholly to the n-system. This means that must be one of the two principal screws on such a cylindroid. Choose any other screw < of the system and draw the cylindroid (0, </>) then 6 is a principal screw, and if 6 and the other principal screw on the cylindroid be two of the co-reciprocal screws of reference, then the co-ordinate of < with respect to is cos(0<) ( 40). But that co-ordinate must also have the general form -nr^ -rp l , whence at once we obtain Let be a screw of stationary pitch in a three-system, and let </> and ^r be any two other screws in that system. Then 6 is one of the principal screws on the cylindroid (#</>) ; let <j be the other principal screw on that 224 THE THEORY OF SCREWS. [214, cylindroid. In like manner let p be the other principal screw of the cylin- droid (0i/r). Then p and a determine the cylindroid (per) which belongs to the system, 6 must lie on the common perpendicular to p and cr, and hence the screws of the cylindroid (per) each intersect 6 at right angles. If is a screw of stationary pitch in a four-system, it can be shown that three screws p, cr, r not on the same cylindroid can be found in the same system, and such that they intersect 6 at right angles. In this case p, cr, r will determine a three-system, every screw of which intersects 6 at right angles. 215. Application to the Two-System. The principles of the last article afford a simple proof of many funda mental propositions in the theory. We take as the first illustration the well- known fact ( 76) that if the co-ordinates of a screw satisfy four linear equations then the locus of that screw is a cylindroid. From the general theorem we see by the case of n = 2 that in any two- system a screw of stationary pitch will be intersected at right angles by another screw of the two-system. These two screws may be conveniently taken as the first and third of the canonical co-reciprocal system lying on the axes of x and y. Hence we have as the co-ordinates of a screw of the system l , 0, # 3 , 0, 0, 0. The investigation has thus assumed a very simple form inasmuch as the four linear equations express that of the six co-ordinates of a screw of the system four are actually zero. Let X, fjb, v be the direction angles of the screw 6 with respect to the associated Cartesian axes then ( 44), a _ (Pe + a ) cos ^ ~ d ei sin X (p e a) cos X d ei sin X V\^ ) v) = I a a a (Pe + &) cos P - ^02 sin /u. (p e - b) cos p-d^ sin p e * = IT " ; ~TF~ - ; _ _ ( p e + c) cos v d es sin v _ _ (p 6 c) cos v - d es sin v c c The two last of these equations give cos v = ; d e3 = 0. Hence we learn that 6 must intersect the axis of z at right angles. 6 is thus parallel to the plane of xy at a distance d ei = d ez = z, and accordingly we have the equations ( p g a) cos X z sin X = 0, (p 6 b) cos /j. z sin /u, = 0, 215] FREEDOM OF THE FOURTH ORDER. whence eliminating z and observing that X //, = 90 we obtain, p d = a cos 2 X + 6 sin 2 X, and eliminating p e , (b a) sin X cos X = z. If we desire the equation of the surface we have y = x tan X, and hence finally 225 Thus again we arrive at the well-known equation of the cylindroid. We can also prove in the following manner the fundamental theorem that among the screws belonging to any two-system there are two which intersect at right angles ( 13). Let 6 be any screw of the two-system, and accordingly the six co-ordinates of 9 must satisfy four linear equations which may be written If be a screw which intersects 6 at right angles, then we must also have inasmuch as these screws are reciprocal as well as rectangular. From these six equations O l ,...0 6 can be eliminated, and we have the resulting equation in the co-ordinates of <f>, B. dR dR dR dR dR rf# * <% d(f 3 * ** d<f> r , ^Z, ^t, A 3 , A, A 5 , A K B,, B 2 > B 3 , % B 5} B B <?i, C z , G 3 , P,, c r> , c fi A, A, A, A, A, A = o. 15 226 THE THEORY OF SCREWS. [215- This equation involves the co-ordinates of < in the second degree. If this equation stood alone it would merely imply that $ belonged to the quadratic five-system ( 223) which included all the screws that intersected at right angles any one of the screws of the given cylindroid. If we further assume that <f> is to be a screw on the given cylindroid, then we have ... + (7 6 (/> 6 = 0, From these five equations two sets of values of <f> can be found. Thus among the system of screws which satisfy four linear equations there must be two screws which intersect at right angles. These are of course the two principal screws of the cylindroid. 216. Application to the Three-System. The equations of the three-system can be also deduced from the principle employed in 214 which enunciated for this purpose is as follows. If 6 be a screw of stationary pitch in a three-system P then there is a cylindroid belonging to P such that every screw of the cylindroid intersects 6 at right angles. It is obvious that this condition could only be complied with if lies on the axis of the cylindroid, and as the cylindroid has two intersecting screws at right angles we have thus a proof that in any three-system there must be one set of three screws which intersect rectangularly. Let their pitches be a, b, c, then on the first we may put a screw of pitch a, on the second a screw of pitch b, and on the third a screw of pitch c. Thus we arrive at a set of canonical co-reciprocals specially convenient for the particular three-system. We have therefore learned that whatever be the three linear equations defining the three-system it is always possible without loss of generality to employ a set of canonical co-reciprocals such that the 1st, 3rd and 5th screws shall belong to the system. These three screws will define the system. Any other screw of the system can be produced by twists about these three screws. Hence we see that for every screw of the system we must have 0, = ; 4 = 0; 6 = 0. 217] FREEDOM OF THE FOURTH ORDER. 227 If X, /j,, v be the direction angles of 6 we have therefore ( 44) fi _ (p e a) cos X d ei sin X _ c/ 2 (j a a (Pd - b) cos /u, - d e3 sin /i 4 - -g- :0, /, _ (P - c) cos v - d 65 sin v t/G = U. c The direction cosines of the common perpendicular to 6 and 1 arc cos v cos //, sin X sin X whence the cosine of the angle between this perpendicular and the radius vector to a point ac, y, z on is y cos v z cos /j, d 6l r sin X r sin X r or d ei sin X = y cos v z cos /x. We have thus the three conditions (p e a)cos\ +z cos //, ?/ cos z/ = (i), 2 cos X + (p 9 b) cos /i + cos v = (ii), + ycosX # cos //, -f ( p Q c) cos v = (iii), whence eliminating cos X, cos //,, cos v we obtain ( p e a) (p e b) (p e c) + (p 6 a)x 1 -\-(p e H)y- + (p e c)z" = 0. Thus we deduce the equation otherwise obtained in 174, for the family of pitch-hyperboloids on which are arranged according to their pitches the several screws of the three-system. 217. Principal pitches of the Reciprocal Cylindroid. From a system of the fourth order a system of canonical co-reciprocals can in general be selected which possesses exceptional facilities for the investi gation of the properties of the screws which form that four-system. Let OA and OB be the axes of the two principal screws of the reciprocal cylindroid. Let a and b be the pitches of these two principal screws and let c be any third linear magnitude. Let 00 be the axis of the cylindroid. Then the canonical co-reciprocal system now under consideration consists of Two screws on OA with pitches + a and - a. Two screws on OB with pitches + b and - b. Two screws on 00 with pitches + c and c. 152 228 THE THEORY OF SCREWS. [217- Of these the four screws with pitches a,b,+c,-c respectively are each reciprocal to the cylindroid. Each of these four screws must thus belong to the four-system. Further these four screws are co-reciprocal. If 0^ ... ({ be the six co-ordinates of a screw in the four-system referred to these canonical co-reciprocals, then we have l = 0, 3 = 0. For 0! = ie , but as the first screw of reference belongs to the reciprocal CL cylindroid we must have tzr ]0 = 0. In like manner vr 3g = 0, and therefore 0! = and #3 = are the two linear equations which specify this particular four-system. The pitch of any screw on the four-system expressed in terms of its co-ordinates is I^02^j>04 2 + c (0 5 2 - 6 2 ) *f+0t + & + lff of which the four stationary values are a, b, + oo , GO . We may remark that if the four co-ordinates here employed be taken as a system of quadriplanar co-ordinates of a point we have a representation of the four- system by the points in space. P^ach point corresponds to one screw of the system. The screws of given pitch p e are found on the quadric surfaces U+p e V=0, where ?7=0 is the quadric whose points correspond to the screws of zero pitch and where V= is an imaginary cone whose points correspond to the screws of infinite pitch. Conjugate points with respect to U = will cor respond to reciprocal screws. A plane will correspond to a three-system and a straight line to a two-system. The general theorem proved in 214 states that when is a screw of stationary pitch in an ra-system to which any other screw < belongs, then ^e* = Pe cos 0(/>. Let us now take a four-system referred to any four co -reciprocals and choose for $ in the above formula each one of the four co-reciprocals in succession, we then have Pi e, =p e {0, + 2 cos (12) + 6 3 cos (1.3) + 4 cos (14)}] p 2 2 = p e {6 l cos (1 2) + 2 +0 3 cos (23) + 4 cos (24)} p 3 3 = Pe {0i cos (1.3) + 2 cos (23) + a + 4 cos (34)} 2>404 = p s {0i cos (14) + 2 cos (24) + 6, cos (34) + 4 ] Eliminating 1( 2 , 3) 4 we deduce a biquadratic for p e . But we have 219] FREEDOM OF THE FOURTH OKDEK. 229 already seen that two of the roots of this must be infinite, whence this equation reduces to a quadratic, and its roots are as we have seen equal but opposite in sign to the pitches of the principal screws of the reciprocal cylindroid. After a few reductions and replacing p e by p we obtain the following equation P*(P!P* sin 2 (34) + p,p a sin 2 (24) + . . .) We thus deduce from any four co-reciprocal screws the quadratic equation which gives the pitches of the two principal screws of the cylindroid to which the given four-system is reciprocal. 218. Equations to the screw in a four-system </ The screws of the four-system are defined by the equations (p e + a) cos X + z cos yu, y cos v = 0, z cos X + ( p e + b) cos fj, + x cos v = 0, where p g is the pitch where cos X, cos p, cos v are the direction cosines and where oc, y, z is a point on the screw. By these equations the properties of the various screws of the system can be easily investigated. If p e be eliminated we obtain x cos X cos v + y cos p cos v z (cos 2 X + cos 2 p,) (a 6) cos X cos //., whence we obtain for the equation to the cone of screws which belongs to the four-system, and has its vertex at #, y 0) Z Q x (as - x,} (z - z,} + 7/0 (y - y ) (z - z,) - z, {(x - a? ) 3 + (y - y ) 2 } ~(a-b) (x - x ) (y - // ) = 0. This is of course the cone which has been referred to in 123. 219. Impulsive Screws and Instantaneous Screws. A body which is free to twist about all the screws of a screw system of the fourth order receives an impulsive wrench on the screw 77, the impulsive intensity being 77 ". It is required to calculate the co-ordinates of the screw 6 about which the body will commence to twist, and also the initial re actions of the constraints. Let X and /j, be any two screws on the reciprocal cylindroid, then the impulsive reaction of the constraints may be considered to consist of impulsive wrenches on X, p of respective intensities X ", //," . If we adopt 230 THE THEORY OF SCREWS. [219- the six absolute principal screws of inertia as screws of reference, ( 79) then the body will commence to move as if it were free, but had been acted upon by a wrench of which the co-ordinates are proportional to p^, ..., p 6 6 6 . It follows that the given impulsive wrench, when compounded with the reactions of the constraints, must constitute the wrench of which the co ordinates have been just written ; whence if h be a certain quantity which is the same for each co-ordinate, we have the six equations Multiply the first of these equations by X 1; the second by Xj, &c.: adding the six equations thus obtained, and observing that 6 is reciprocal to X, and that consequently 2M\i = 0, we obtain f} / " ^r} 1 \ 1 + X "^! 2 + //"SXj//,! = 0, and similarly multiplying the original equations by p 1 , ..., ^ 6 and adding, we obtain ^x, + /"S 2 = 0. From these two equations the unknown quantities X ", //" can be found, and thus the initial reaction of the constraints is known. Substituting the values of X ", //" in the six original equations, the co-ordinates of the required screw 9 are determined. 220. Principal Screws of Inertia in the Four-System. We have already given in Chapter VII. the general methods of deter mining the principal screws of inertia in an ?i-system. The following is a different process which though of general application is in this chapter set down for the case of the four-system. Choose four co-reciprocal screws a, ft, 7, 8 of the four-system and let their co-ordinates be as usual !,... ,fc; &,...,&; y n ...,7; 81, ...,8 6 ; referred to the six absolute principal screws of inertia ( 79). Let an impulsive wrench on one of the principal screws of inertia 6 in the four-system be decomposed into components on a, /3, 7, 8, and let the impulsive intensities be a ", ", 7 ", 8 ". Let X, p, be any two screws on the reciprocal cylindroid. Then the body will move as if it had been free and had received impulsive wrenches on the absolute principal screws of inertia, the impulsive intensities being a" a 6 + {3" j3 G + y " 7ti + B "S V + X /7/ X 6 221] FREEDOM OF THE FOURTH ORDER. 231 The co-ordinates of are proportional to /// , rt/rr r\ . ill , 5/"S> a a x + p & + 7 71 + o di /// . nni rt i i a a + /3 #, + 7 7e + <% As # is to be a principal screw of inertia it follows that the expressions last written multiplied severally by p l} ...,p 6 must be proportional to the intensities of the impulsive wrenches received by the body : whence we have the following equations in which h is a quantity which is the same for each of the co-ordinates. i + 7" 7i + 8 "^ = *" i + P"& + 7"Vi + S/// We are now to multiply these equations by a u . .., a fi respectively, and add. If we repeat the process using p\, ...,/3 6 ; 71, ..., 7el !,..., S 6 ; X ls ...,X 6 ; fr, ...,fj, 6 and if we remember that a is reciprocal to /3, 7, 8 because the system is co-reciprocal and that a is reciprocal to A, and p, because X and //, belong to the reciprocal system, then observing that like conditions hold for ft, 7, and S, we have the equations // S7 1 X 1 +/ // S7,/* 1 =0, / S8 1 X 1 + /i // SV 1 =0, V +/ // S\ 1 ^ 1 =0, From these equations a ", /S" , 7 ", 8 ", X" , /*" can be eliminated and the result is to give a biquadratic for h. Thus we have the four roots for the equation. Each of these roots will give a corresponding set of values for " , ", 7 ", 8 ", X ", p" thus we obtain which are proportional to the co-ordinates of the corresponding principal screw of inertia. The values of X " and ///" determine the impulsive reaction of the con straints. 221. Application of Euler s Theorem. It may be of interest to show how the co-ordinates of the instantaneous 232 THE THEORY OF SCREWS. [221- screw corresponding to those of a given impulsive screw can be deduced from Euler s theorem ( 94). If a body receive an impulsive wrench on a screw 7] while the body is constrained to twist about a screw 6, then we have seen in 91 that the kinetic energy acquired is proportional to If #j, 0. 2 , 3 , #4 be the co-ordinates of referred to the four principal screws of inertia belonging to the screw system of the fourth order, then (195,97) uf = uf + w;- <, 2 + u./* + ufOf. Hence we have to determine the four independent variables 1} 6.,, 3) # 4 , so that shall be stationary. This is easily seen to be the case when lt 0.,, 3 , 4 are respectively proportional to Jlfci *, |9t, ~^. U/l U 2 ^3 Ul These are accordingly, as we already know ( 97), the co-ordinates of the screw about which the body will commence to twist after it has received an impulsive wrench on ?/. This method might of course be applied to any order of freedom. 222. General Remarks. It has been shown in 80 how the co-ordinates of the instantaneous screw corresponding to a given impulsive screw can be determined when the rigid body is perfectly free. It will be observed that the connexion between the two screws depends only upon the three principal axes through the centre of inertia, and the radii of gyration about these axes. We may express this result more compactly by the well-known conception of the momental ellipsoid. The centre of the momental ellipsoid is at the centre of inertia of the rigid body, the directions of the principal axes of the ellipsoid are the same as the principal axes of inertia, and the lengths of the axes of the ellipsoid are inversely proportional to the corresponding radii of gyration. When, therefore, the impulsive screw is given, the momental ellipsoid alone must be capable of determining the corresponding instantaneous screw. A family of rigid bodies may be conceived which have a common FREEDOM OF THE FOURTH ORDER. 233 momental ellipsoid; every rigid body which fulfils nine conditions will belong to this family. If an impulsive wrench applied to a member of this family cause it to twist about a screw 0, then the same impulsive wrench applied to any other member of the same family will cause it likewise to twist about 0. If we added the further condition that the masses of all the members of the family were equal, then it would be found that the twist velocity, and the kinetic energy acquired in consequence of a given impulse, would be the same to whatever member of the family the impulse were applied ( 90, 91). 223. Quadratic n-systems. We have always understood by a screw system of the nth order or briefly an w-system, the collection of screws whose co-ordinates satisfy a certain system of 6 n linear homogeneous equations. We have now to introduce the conception of a screw system of the nth order and second degree or briefly a quadratic n-system (n < 6). By this expression we are to understand a collection of screws such that their co-ordinates satisfy 6 n homogeneous equations ; of these equations 5 n, that is to say, all but one are linear ; the remaining equation involves the co-ordinates in the second degree. Let #!,...,#<; be the co-ordinates of a screw belonging to a quadratic w-system. We may suppose without any loss of generality that the 5 n linear equations have been transformed into Q n+2 = ; n +3 = ; . . . K = 0. The remaining equation of the second degree is accordingly obtained by equating to zero a homogeneous quadratic function of A A t/j ... t7 7 l+l We express this equation which characterizes the quadratic ?i-system as All the screws whose co-ordinates satisfy the 5 n linear equations must themselves form a screw system of the 6 (5 n) = (n + l)th system. This screw system may be regarded as an enclosing system from which the screws are to be selected which further satisfy the equation of the second degree [70 = 0. The enclosing system comprises the screws which can be formed by giving all possible values to the co-ordinates 6 l , ...,0 n+l . Of course there may be as many different screw systems of the nth order and second degree comprised within the same enclosing system as there can be different quadratic forms obtained by annexing coefficients to the several squares and products of n + 1 co-ordinates. If n = 5, the enclosing system would consist of every screw in space. 234 THE THEORY OF SCREWS. [224, 224. Properties of a Quadratic Two-system. The quadratic two-system is constituted of screws whose coordinates satisfy three linear equations and one quadratic equation, and these screws lie generally on a surface of the sixth degree ( 225). If we take the plane representation of the three-system given in Chapter XV., then any conic in the plane corresponds to a quadratic two-system and all the points in the plane correspond to the enclosing three-system. Since any straight line in the plane corresponds to a cylindroid in the enclosing system and the straight line will, in general, cut a conic in the plane in two points, we have the following theorem. A quadratic two-system has two screws in common with any cylindroid belonging to the enclosing three-system. A pencil of four rays in the plane will correspond to four cylindroids with a common screw, which we may term a pencil of cylindroids. Any fifth transversal cylindroid belonging also to the same three-system will be intersected by a pencil of four cylindroids in four screws, which have the same anharmonic ratio whatever be the cylindroid of the three-system which is regarded as the transversal. We thus infer from the well-known anharmonic property of conies the following theorem relative to the screws of a quadratic two-system. If four screws a, /3, j, 8 be taken on a quadratic two-system, and also any fifth screw 77 belonging to the same system, then the pencil of cylindroids (770), (77/3), (^7), (?)&) will have the same anharmonic ratio whatever be the screw V). (See Appendix, note G.) The plane illustration will also suggest the instructive theory of Polar screws which will presently be stated more generally. Let 7=0 be the conic representing the quadratic two-system and let V= be the conic representing the screws of zero pitch belonging to the enclosing three-system. Let P be a point in the plane corresponding to an arbitrary screw 6 of the three-system. Draw the polar of P with respect to U=Q and let Q be the pole of this straight line Avith respect to V= 0, then Q will correspond to some screw </> of the enclosing three-system. From any given screw 6, then by the help of the quadratic two-system a corresponding screw $ is determined. We may term </> the polar screw of with respect to U0. Three screws of the enclosing system will coincide with their polars. These will be the vertices of the triangle which is self-conjugate with respect both to U and to V. A possible difficulty may be here anticipated. The equation V= is itself of course equivalent to a certain quadratic two-system and therefore should correspond to a surface of the sixth degree. We know however ( 173) that the locus of the screws of zero pitch in a three-system is an hyperboloid, so that in this case the expectation that the surface would rise to the sixth 225J FREEDOM OF THE FOURTH ORDER. 235 degree seems not to be justified. It is however shown in 202 that this hyperboloid is really not more than a part of the locus. There are also four imaginary planes which with the hyperboloid complete the locus, and the combination thus rises to the sixth degree. 225. The Quadratic Systems of Higher Orders. If we had taken n = 3, then of course the quadratic three-system would mean the collection of screws whose four co-ordinates satisfied an equation which in form resembles that of a quadric surface in quadriplanar co ordinates. A definite number of screws belonging to the quadratic three- system can in general be drawn through every point in space. We shall first prove that the number of those screws is six. Let l} ..., 8 be the co-ordinates of any screw referred to a canonical co-reciprocal system. Then if x , y , z be a point on 0, we have ( 43) (0 5 + 0.) y - (0 3 + 4 ) / = a (6, - 0,) - p e (e l + 0,), (0, + 0,) z 1 - (0 3 + (i ) x = & (0 3 - 4 ) - Pe (03 + 0.1 (0 3 + 04) x - (0, + 0,) y = c(0 6 - 6 ) - p e (0 5 + 6 ). If we express that belongs to the enclosing four-system we shall have two linear equations to be also satisfied by the co-ordinates of 0. These equations may be written without loss of generality in the form 2 = ; 4 = 0. We have finally the equation U g = characteristic of the quadratic three- system. From these equations the co-ordinates are to be eliminated. But the eliminant of k equations in (k l) independent variables is a homo geneous function of the coefficients of each equation whose order is, in general, equal to the product of the degrees of all the remaining equations*. In the present case, the coefficient of each of the first three equations must be of the second degree in the eliminant and hence, the resulting equation for p e is of the sixth degree, so that we have the following theorem. Of the screws which belong to a quadratic three-system, six can be drawn through any point. As the enclosing system in this case is of the fourth order, the screws of the enclosing system drawn through any point must lie on a cone of the second degree ( 218). Hence it follows that the six screws just referred to must all lie on the surface of a cone of the second degree. We may verify the theorem just proved by the consideration that if the function U 6 could be decomposed into two linear factors, each of those factors * Salmon, Modern Higher Algebra, p. 76, 4th Edition (1885). 236 THE THEORY OF SCREWS. [225 equated to zero would correspond to a three-system selected from the enclosing four-system. We know (| 176) that three screws of a three-system can be drawn through each point. We have, consequently, three screws through the point for each of the two factors of U e , i.e. six screws in all. The equation of the 6th degree in p e contains also the co-ordinates x , y , z in the sixth degree. Taking these as the current co-ordinates we may regard this equation as expressing the family of surfaces which, taken together, contain all the screws of the quadratic three-system. The screws of this system which have the same pitch p e are thus seen to be ranged on the generators of a ruled surface of the sixth degree. All these screws belong of course to the enclosing four-system, and as they have the same pitches, they must all intersect the same pair of screws on the reciprocal cylindroid ( 212). It follows that each of these pitch surfaces of the sixth degree must have inscribed upon it a pair of generators of the reciprocal cylindroid. Ascending one step higher in the order of the enclosing system we see that the quadratic four-system is composed of those screws whose co-ordinates satisfy one linear homogeneous equation L = 0, and one homogeneous equation of the second degree U Q. We may study these screws as follows. Let the direction cosines of a screw 6 be cos X, cos /u,, cos v. If the reference be made, as usual, to a set of canonical co-reciprocals we have cos X = B! + 6., ; cos //, = # :i + 64 ; cos v = 5 + # 6 . We therefore have for a point x , y 1 , z on 6 the equations ( 218) 2a0! = (a + p e } cos A, z cos JJL + y cos v , 2a0 2 = (a p e ) cos X + z cos /* y cos v, with similar expressions for 3 , # 4 , 5 , 6 fi . Substituting these expressions in L = and U = and eliminating p e , we obtain an homogeneous equation of the fourth degree in cos X, cos fi, cos v. If we substitute for these quantities x x, y y , z z , we obtain the equation of the cone of screws which can be drawn through x , y , z \ this cone is accordingly of the fourth degree. We verify this con clusion by noticing that if U = were the product of two linear functions, this cone would decompose into two cones of the second degree, as should clearly be the case ( 218). It remains to consider the Quadratic Five-system. In this case the enclosing system includes every screw in space, and the six co-ordinates of 225] FREEDOM OF THE FOURTH ORDER. 237 the screw 6 are subjected to no other relation than that implied by the quadratic relation U e = Q. As before we may substitute for lt ..., 6 6 from the equations 2a#j = (a 4- p e ) cos \ z cos fj> + y cos v, 2a# 2 = (a Pe) cos A. + 2 cos i*> y cos v, with similar expressions for 26^, 260 2 > &c. Introducing these values into U e = 0, we obtain a result which may be written in the form where A, B, C contain eosX, cos/i, cos v in the second degree, and where x , y , z enter linearly into B and in the second degree into G. Hence we see that on any straight line in space there will be in general two screws belonging to any quadratic five-system. For the straight line being given x , y , z are given, and so are cos X, cos //., cos v. The equation just written gives two values for a pitch which will comply with the necessary conditions. If we consider p e and also x , y , z as given, and if we substitute for cos X, cos /j,, cos v the expressions x af y y y , z z respectively, we obtain the equation of a cone of the second degree. Thus we learn that for each given pitch any point in space may be the vertex of a cone of the second degree such that the generators of the cone when they have received the given pitch are screws belonging to a given quadratic five-system. If the equation be satisfied, then the straight lines which satisfy this condition will be singular, inasmuch as each contains but a single screw belonging to the quadratic five-system. As cos \, cos /j,, cos v enter to the fourth degree into this equation it appears that each point in space is the vertex of a cone of the fourth degree, the generators of which when proper pitches are assigned to them will be singular screws of the quadratic five-system. If we regard cos X, cos p, cos v as given quantities in the equation then this will represent a quadric surface inasmuch as x , y , z enter to the second degree. This quadric is the locus of those singular screws of the quadratic five-system which are parallel to a given direction. Hence the equation must represent a cylinder. 238 THE THEORY OF SCREWS. [225, If B = the two roots of the equation in p e will be equal, but with opposite signs; as cos X, cos/i, cosy enter to the second degree in B it follows that through any point in space as vertex a cone of the second degree can be drawn such that each generator of this cone when the proper pitch is assigned to it will equally belong to the quadratic five-system, whether that pitch be positive or negative. If B = and (7 = 0, then both values of p e must be zero. Regarding as , y , z as fixed, each of these equations will correspond to a cone with vertex at x , y , z \ these cones will have four common generators, and hence we see that through any point in space four straight lines can in general be drawn such that with the pitch zero but not with any other pitch, these screws will be members of a given quadratic five- system. 226. Polar Screws. The general discussion of the quadratic screw-systems is a subject of interest both geometrical and physical. We shall here be content with a few propositions which are of fundamental importance. Let as before U e = Q be the homogeneous relation between the co-ordinates 1 ,...,0 n+1 of the screws which constitute a quadratic ?i-system. Let 77 and denote any two screws other than 6 and chosen from the enclosing w-system, from which the screws of the quadratic n-system are selected by the aid of the condition U 6 = 0. If then we adopt the fertile method of investigation introduced by Joachimsthal, we shall substitute in mU e = for 6 1} ..., 6 n+1 the respective values The result will be TT <* r, where U* = -^- + ... + l+1 -- . C"7i ar) n+l Solving this quadratic equation for I -f- m we obtain two values of this ratio and hence ( 119) we deduce the following theorem. Any cylindroid of a given (n + l)-system will possess generally two screws belonging to every quadratic n-system which the given (n + \)-system encloses. If the two screws 77 and had been so selected that they satisfied the condition 226] FREEDOM OF THE FOURTH ORDER. 239 then the two roots of the quadratic are equal but with opposite signs, and hence ( 119) we have the following theorem. If the condition U^ = is satisfied by the co-ordinates of two screws 77 and which belong to the enclosing (n + l)-system, then these two screws 77, and the tw.o screws which, lying on the cylindroid (rj, ), also belong to the quadratic ?i-system U 9 = Q, will be parallel to the four rays of an harmonic pencil. We are now to develop the conception of polar screws alluded to in 224, and this may be most conveniently done by generalizing from a well-known principle in geometry. Let be a point and S a quadric surface. Let any straight line through cut the quadric in the two points X 1 and X 2 . Take on this straight line a point P so that the section OXP^X^ is harmonic ; then for the different straight lines through the locus of P is a plane. This plane is of course the well-known polar of P. We have an analogous conception in the present theory which appears as follows. Take any screw 77 in the enclosing (n + l)-system. Draw a pencil of n cylindroids through 77, all the screws of each cylindroid lying in the enclosing (n+ l)-system. Each of these cylindroids will have on it two screws which belong to the quadratic w-systetn U e = 0. On each of these cylindroids a screw can be taken which is the harmonic conjugate with respect to 77 with reference to the two screws of the quadratic n-system which are found on the cylindroid. We thus have n screws of the f type, and these u screws will define an n-system which is of course included within the enclosing (n + l)-system. The equation of this n-system is obviously This equation is analogous to the polar of a point with regard to a quadric surface. We have here within a given enclosing (n + l)-system a certain re-system which is the polar of a screw 77 with respect to a certain quadratic n-system. The conception of reciprocal screws enables us to take a further im portant step which has no counterpart in the ordinary theory of poles and polars. The linear equation for the co-ordinates of f, namely tf* = 0, is merely the analytical expression of the fact that f is reciprocal to the 240 THE THEORY OF SCREWS. [226, screw of the enclosing (n + l)-system whose co-ordinates are proportional to 1 P\ rj p n+1 rj n+1 This we shall term the polar screw of rj with respect to the quadratic w-system. It is supposed, of course, that the screws of reference are co- reciprocals. If CL and ft be two screws of an enclosing (n + 1 )-system, and if i) and be their respective polar screws with reference to a quadratic n-system, then when a is reciprocal to % we shall have /3 reciprocal to 77. For we have, where h is a common factor, 1 dU a 1 dU a htji = -- r~ > ir )n+i i j P! da, p n+l da n+l whence h(p 1 1J 1 /3 1 + ... + Pn+i Vn+i Pn+l) = Uop- If therefore $ and rj are reciprocal the left-hand member of this equation is zero and so must the right-hand member be zero. But the symmetry shows that and a are in this case also reciprocal. We may in such a case regard a and ft as two conjugate screws of the quadratic ?i-system. As a first illustration of the relation between a screw and its polar, we shall take for U a = 0, the form Pitf + p*<tf + . . . + p 6 a<? - p (i 2 + 2 2 + . . . + 6 - + 2 1 2 cos (12) . . . ) = 0. This means of course that U a = denotes every screw which has the pitch p. Take any screw a and draw a cylindroid through a. The two screws of pitch p on this cylindroid belong to U and a fourth screw 9 may be taken on this cylindroid so that a, 6, and the two screws of pitch p form an harmonic pencil. By drawing another cylindroid through a. another screw of the 0-system can be similarly constructed. If these five cylindroids be drawn through we can construct five different screws of the ^-system. To these one screw will be reciprocal, and this is the polar of a. We have thus the means of constructing the polar of a. Seeing however that U a = includes nothing more or less than all the p-pitch screws in the universe and that in the construction just given for the polar of a there has been no reference to the screws of reference, sym metry requires that the polar of a must be a screw which though different from a must be symmetrically placed with reference thereto. The only method of securing this is for the polar of a with respect to this particular function to lie on the same straight line as a. 227] FREEDOM OF THE FOURTH ORDER. 241 Hence we deduce that the screw with co-ordinates i, Oj) 6> and the screw with co-ordinates proportional to .1 d JL 1 ^ 1 ^ p l d^ p 2 da z p 6 dot G in which U is the expression P^ + p 2 2 2 ... + p 6 a<? + X (i 2 + 02 2 ... + 2 ai a 2 cos (12) ...) must be collinear, and this is true for all values of X. We hence see that the co-ordinates of a screw collinear with a must be proportional to where E = a 1 2 + a 2 2 +... + 2a 1 a 2 cos (12) + ... Thus we obtain the results of 47 in a different manner. 227. Dynamical application of Polar Screws. We have seen ( 97) that the kinetic energy of a body twisting about a 7/n/ screw 6 with a twist velocity -^- and belonging to a w-system is w the screws of reference being the principal screws of inertia. If we make i< 1 2 1 2 + ... + u n 2 n 2 = 0, then 6 must belong to a quadratic -system. This system is, of course, imaginary, for the kinetic energy of the body when twisting about any screw which belongs to it is zero*. The polar 77 of the screw 0, with respect to this quadratic w-system, has co-ordinates proportional to u i n u n / U 1} ... p. Pi Pn Comparing this with 97, we deduce the following important theorem : A quiescent rigid body is free to twist about all the screws of an enclosing (n + \}-system A. If the body receive an impulsive wrench on a screw 17 * In a letter to the writer, Professor Klein pointed out many years ago the importance of the above screw system. He was led to it by expressing the condition that the impulsive screw should be reciprocal to the corresponding instantaneous screw. B. 16 242 THE THEORY OF SCREWS. [227, belonging to A, then the body will commence to twist about the screw 6, of which V) is the polar with respect to the quadratic n-system composed of the imaginary screws about which the body would twist with zero kinetic energy. If a rigid body which has freedom of the nth order be displaced from a position of stable equilibrium under the action of a system of forces by a twist of given amplitude about a screw 6, of which the co-ordinates referred to the n principal screws of the potential are O l ,... n , then the potential energy of the new position may, as we have seen ( 103) be expressed by If this expression be equated to zero, it denotes a quadratic rc-system, which is of course imaginary. We may term it the potential quadratic w-system. The potential quadratic w-system possesses a physical importance in every respect analogous to that of the kinetic quadratic n-system : by reference to ( 102) the following theorem can be deduced. If a rigid body be displaced from a position of stable equilibrium by a twist about a screw 6, then a wrench acts upon the body in its new position on a screw which is the polar of 6 with respect to the potential quadratic w-system. The constructions by which the harmonic screws were determined in the case of the second and the third orders have no analogies in the fourth order. We shall, therefore, here state a general algebraical method by which they can be determined. Let U=0 be the kinetic quadratic ?i-system, and F=0 the potential quadratic w-system, then it follows from a well-known algebraical theorem that one set of screws of reference can in general be found which will reduce both U and V to the sum of n squares. These screws of reference are the harmonic screws. We may here also make the remark, that any quadratic w-system can generally be transformed in one way to the sum of n square terms with co-reciprocal screws of reference; for if U and p e be transformed so that each consists of the sum of n square terms, then the form for the expression of p e ( 38) shows that the screws are co-reciprocal. 228. On the degrees of certain surfaces. We have already had occasion ( 210) to demonstrate that the general condition that two screws shall intersect involves the co-ordinates of each 22 8 J FREEDOM OF THE FOURTH ORDER. 243 of the screws in the third degree. We can express this condition as a determinant by employing a canonical system of co-reciprocals. For if two screws 6 and (f> intersect, then there must be some point x, y, z which shall satisfy the six equations ( 43) : ( 5 + ) ?/ - ( 3 + 4 ) z = a (! - 03) -p a (! + 2 ), (! + a 2 ) z - ( 5 + 6 ) x = b ( 3 - 4 ) - p a (a s 4- 04), (a s + a 4 ) x - (! + 03) y = c ( 5 - 6 ) -p a (o s + a,,), (0 B + 6 ) y - (0, + 0<) z = a (6, - 2 ) -p e (6, + 6> 2 ), From these equations we eliminate the five quantities x, y, z, p e , p a and the required condition that and a shall intersect, is given by the equa tion - ( 5 + 6 ), - ( 3 + 04), (! + a a ), , a (! - a 2 ) = 0. -(, + ,), , (! + >(), (a 3 + a 4 ), , 6(a 3 -a 4 ) (a 3 + 4), -(ati + Os), , (a 5 + a fi ), , c (a 5 - a 8 ) , (0 5 + 6 ), -(6 3 +6> 4 ), , (6, + e,}, a(0 1 -0 2 ) -(0 5 +0 6 ), , (0 1 + 2 \ , (6> 3 + ^ 4 ), b(0 3 -0 4 ) (0 3 +0<\ -& + 0J, 0,0, (^ 5 + ^ 6 ), c(0 5 -0 6 ) Four homogeneous equations between the co-ordinates of indicate that the corresponding screw lies on a certain ruled surface. Let us suppose that the degrees of these equations are I, m,n,r respectively, then the degree of the ruled surface must not exceed Slmnr. For express the condition that shall also intersect some given screw ct, we then obtain a fifth homogeneous equation containing the co-ordinates of in the third degree. The determination of the ratios of the six co-ordi nates 6-1, ... 6 is thus effected by five equations of the several degrees I, m, n, r, 3. For each ratio we obtain a system of values equal in number to the product of the degrees of the equations, i.e. to Slmnr. This is accord ingly a major limit to the number of points in which in general a pierces the surface, that is to say, it is a major limit to the degree of the surface. Of course we might affirm that it was the degree of the surface save for the possibility that through one or more of the points in Avhich a met the surface more than a single generator might pass. As an example, we may take the simple case of the cylindroid, in which I, m, n, r being each unity the locus is of the third degree. The screws of 162 244 THE THEORY OF SCREWS. [228 a three-system which satisfy an equation of the nth degree must have as their locus a surface of degree not exceeding 3n. The most important application of this is when n = 2, in which case the screws form a quadratic two-system. The degree of this surface cannot exceed six, on the other hand, if the quadratic condition which we may write A0? + B0 2 * + CB? + 2F0A + 200,6, + 2H0A = 0, should break up into two linear factors each of these linear factors will correspond to a cylindroid, i.e. a surface of the third degree. Hence the degree of the surface must in general be neither less than six nor greater than six, and hence we learn that the surface which is the locus of the screws of a quadratic two-system is of the sixth degree. A particular case of special importance arises when the pitches of all the screws on the surface are to be the same. The statement of this condition is of course one equation of the second degree in the co-ordinates of the screw. In the case of canonical co-reciprocals, this equation would be But the condition that Q and a shall intersect will now submit to modification. We sacrifice no generality by making a of zero pitch, so that if 6 has a given pitch p e , the condition that a and shall intersect is no longer of the third degree. It is the linear equation 2t3- ae = p e cos (a0). If therefore the co-ordinates of satisfy three homogeneous equations of degrees I, m, n respectively, in addition to the equation of the second degree expressing that the pitch is a given quantity, then the locus is a surface of degree not exceeding 2lmn. As the simplest illustration of this result we observe that if I, m, n be each unity, the locus in question is the locus of the screws of given pitch in a three-system. This locus cannot therefore be above the second degree, and we know, of course (Chapter XIV.) that the locus is a quadric. If I and m were each unity and if n = 2 we should then have the locus of screws of given pitch belonging to a four-system and whose co-ordinates satisfied a certain equation of the second degree. This locus is a surface of the fourth degree. In the special case where the given pitch is zero, the surface so defined is known in the theory of the linear complex. It is there presented as the locus of lines belonging to the complex and whose co ordinates further satisfy both a linear equation and a quadratic equation. Mr A. Panton has kindly pointed out to me that in this particular case the surface has two double lines which are the screws of zero pitch on the 228] FREEDOM OF THE FOURTH ORDER. 245 cylindroid reciprocal to the enclosing four-system. It has also eight singular tangent planes (four through each double line) touching all along a generator. The cylindroid is a very special case of this surface in which one of the double lines is at infinity. If the system be reciprocal to the cylindroid z(x 2 + y f ) + kx;y = Q, then the cylindroid to which the surface reduces is z(as * + y 2 ) kxy = Q. The singular tangent planes are represented by the two tangent planes at the limits of the cylindroid. CHAPTER XVII. FREEDOM OF THE FIFTH ORDER. 229. Screw Reciprocal to Five Screws. There is no more important theorem in the Theory of Screws than that which asserts the existence of one screw reciprocal to five given screws. At the commencement, therefore, of the chapter of which this theorem is the foundation, it may be well to give a demonstration founded on elementary principles. Let one of the five given screws be typified by j tch _ fc Pk 7* while the desired screw is defined by (pitch = p). x x _y y __ z - z P 7 The condition of reciprocity ( 20) produces five equations of the following type : k)7k From these five equations the relative values of the six quantities can be determined by linear solution. Introducing these values into the identity a. (yy (3z } + (az yx) 4 y (fix ay ) = 0, gives the equation which determines p. 229, 230] FREEDOM OF THE FIFTH ORDER. 247 To express this equation concisely we introduce two classes of subsidiary magnitudes. We write one magnitude of each class as a determinant. = P. /82 73 74 75 By cyclical interchange the two analogous functions Q and R are denned. - y 3 Cl 3> 73 74 By cyclical interchange the two analogous functions M and JV^ are denned. The equation for p reduces to The reduction of this equation to the first degree is an independent proof of the principle, that one screw, and only one, can be determined which is reciprocal to five given screws ; p being known, a, /3, 7 can be found, and also two linear equations between x, y , z , whence the reciprocal screw is completely determined. For the study of the screws representing a five-system we may take the first screw of a set of canonical coreciprocals to be the screw reciprocal to the system. Then the co-ordinates of a screw in the system are 0, 2 , 6 3 , ... 6 , while if X, p, v be the direction cosines of 6 and x, y, z a point thereon, and p e the pitch we have ( 43) (p e + a) cos \ z cos p + y cos v = 0. We can obtain at once the relation between the direction and the pitch of the screw belonging to the system and passing through a fixed point. If p e = and 2 and y be given, then the equation shows that the screw is limited to a plane ( 110). 230. Six Screws Reciprocal to One Screw. When six screws, A l} ... A 6 are reciprocal to a single screw T, a certain 248 THE THEORY OF SCREWS. [230 relation must subsist between the six screws. This relation may be ex pressed by equating the determinant of 39 to zero. The determinant (which may perhaps be called the sexiant) may be otherwise expressed as follows : The equations of the screw A k are oc XT, y i/ 1, z ZT. , . , , , - - = 3 ho J2 = - - (P^ch Pk ). * ft 7/fc We shall presently show that we are justified in assuming for T the equations The condition that A k and T be reciprocal is 77*) + ** (7& - P Writing the six equations of this type, found by giving k the values 1 to 6, and eliminating the six quantities P<*, p&, py, <*, ft 7) we obtain the result : #i ~ a i2A> a i ft. 7i 3/J3 + 732/3 - *3, 4/>4 + 742/4 - ft^4, ft/>4 + a 4 ^4 ~ 744 , 74/>4 + ft4 ~ ^4 , 4, ft, 74 a 5P5 + 75 3/5 - ftj^B, ftps + 4^5 - 75^5, 75/5 + ft^5 ~ ^S^/S, 5 , ft, 7 6 2/6, 6 , ft, 7e = 0- By transformation to cmy parallel axes the value of this determinant is unaltered. The evanescence of the determinant is therefore a necessary condition whenever the six screws are reciprocal to a single screw. Hence we sacrificed no generality in the assumption that T passed through the origin. Since the sexiant is linear in x l} y 1} z i} it appears that all parallel screws of given pitch reciprocal to one screw lie in a plane. Since the sexiant is linear in a 1} ft, 7^ we have another proof of Mobius theorem ( 110). The property possessed by six screws when their sexiant vanishes may be enunciated in different ways, which are precisely equivalent. (a) The six screws are all reciprocal to one screw. 230] FREEDOM OF THE FIFTH ORDER. 249 (6) The six screws are members of a screw-system of the fifth order and first degree. (c) Wrenches of appropriate intensities on the six screws equilibrate, when applied to a free rigid body. (d) Properly selected twist velocities about the six screws neutralize, when applied to a rigid body. (e) A body might receive six small twists about the six screws, so that after the last twist the body would occupy the same position which it had before the first. If seven wrenches equilibrate (or twists neutralize), then the intensity of each wrench (or the amplitude of each twist) is proportional to the sexiant of the six non-corresponding screws. For a rigid body which has freedom of the fifth order to be in equilibrium, the necessary and sufficient condition is that the forces which act upon the body constitute a wrench upon that one screw to which the freedom is reciprocal. We thus see that it is not possible for a body which has freedom of the fifth order to be in equilibrium under the action of gravity unless the screw reciprocal to the freedom have zero pitch, and coincide in position with the vertical through the centre of inertia. Sylvester has shown* that when six lines, P, Q, R, S, T, U, are so situated that forces acting along them equilibrate when applied to a free rigid body, a certain determinant vanishes, and he speaks of the six lines so related as being in involution^. Using the ideas and language of the Theory of Screws, this determinant is the sexiant of the six screws, the pitches of course being zero. If x m , y m , z m , be a point on one of the lines, the direction cosines of the same line being a m , /3 m ,y m , the condition is ii-#i7i> #i/3i-2/ii =0. , 72, y-fli- /3 3 , 73, y 3 y 3 - &, 74, 2/474 - &, 75, y 5 %- - #373, ~ 2/44 * Comptes Rendus, tome 52, p. 816. See also p. 741. t In our language a system of lines thus related consists of the screws of equal pitch belonging to a five-system. In the language of Pliicker (Neue Geometric des Raumes) a system of lines in involution forms a linear complex. It may save the reader some trouble to observe here that the word involution has been employed in a more generalised sense by Battaglini, and in quite a different sense by Klein. 250 THE THEORY OF SCREWS. [230- It must always be possible to find a single screw X which is reciprocal to the six screws P, Q, R, S, T, U. Suppose the rigid body were only free to twist about X, then the six forces would not only collectively be in equi librium, but severally would be unable to stir the body only free to twist about X. In general a body able to twist about six screws (of any pitch) would have perfect freedom ; but the body capable of rotating about each of the six lines, P, Q, R, S, T, U, which are in involution, is not necessarily perfectly free (Mobius). If a rigid body were perfectly free, then a wrench about any screw could move the body; if the body be only free to rotate about the six lines in involution, then a wrench about every screw (except X) can move it. The conjugate axes discussed by Sylvester are presented in the Theory of Screws as follows : Draw any cylindroid which contains the reciprocal screw X, then the two screws of zero pitch on this cylindroid are a pair of conjugate axes. For a force on any transversal intersecting this pair of screws is reciprocal to the cylindroid, and is therefore in involution with the original system. Draw any two cylindroids, each containing the reciprocal screw, then all the screws of the cylindroids form a screw system of the third order. Therefore the two pairs of conjugate axes, being four screws of zero pitch, must lie upon the same quadric. This theorem, due to Sylvester, is proved by him in a different manner. The cylindroid also presents in a clear manner the solution of the problem of finding two rotations which shall bring a body from one position to any other given position. Find the twist which would effect the desired change. Draw any cylindroid through the corresponding screw, then the two screws of zero pitch on the cylindroid are a pair of axes that fulfil the required conditions. If one of these axes were given the cylindroid would be defined and the other axis would be determinate. 231. Four Screws of a Five-system on every Quadric. On any single sheeted hyperboloid four screws of any given pitch p can in general be determined which belong to any given system of the fifth order. A pair of these screws lie on each kind of generator. Let X be the screw reciprocal to the system. Take any three generators A, B, C of one system on the hyperboloid, and regarding them as screws of pitch p draw the cylindroid XA and take on this A the second screw of pitch p. Then the two screws of pitch p which can be drawn as transversals across A, B, C, A are coincident with two generators of the hyperboloid 232] FREEDOM OF THE FJFTH ORDER. 251 while they are also reciprocal to the cylindroid because they cross two screws thereon with pitches equal in magnitude but opposite in sign. They are therefore reciprocal to X. In like manner it can be shown that two of the other system of generators possess the same property. On every cylindroid there is as we know ( 26) one screw of a given five- system. This important proposition may be otherwise proved as follows. Let 6 be the co-ordinates of a screw on the cylindroid, then these co-ordinates must satisfy four linear equations. There must be a fifth equation in the six quantities l} ... 6 6 inasmuch as 6 is to lie on the given five-system. Thus from these five equations one set of values of 8 lt ... 6 6 can be determined. On a quadratic two-system ( 224) there will always be two screws belonging to any given five-system. For the quadratic two-system is the surface whose screws satisfy four homogeneous equations of which three are linear and one is quadratic. If another linear equation be added two screws on the surface can, in general, be found which will satisfy that equation. 232. Impulsive Screws and Instantaneous Screws. We can determine the instantaneous screw corresponding to a given impulsive screw in the case of freedom of the fifth order by geometrical considerations. Let X, as before, represent the screw reciprocal to the freedom, and let p be the instantaneous screw which would correspond to X as an impulsive screw, if the body were perfectly free ; let 77 be the screw on which the body receives an impulsive wrench, and let be the screw about which the body would commence to twist in consequence of this impulse if it had been perfectly free. The body when limited to the screw system of the fifth order will commence to move as if it had been free, but had been acted upon by a certain unknown wrench on X, together with the given wrench on rj. The movement which the body actually acquires is a twisting motion about a screw 6 which must lie on the cylindroid (, p). We therefore determine 6 to be that one screw on the known cylindroid (, p) which is reciprocal to the given screw X. The twist velocity of the initial twisting motion about 6, as well as the intensity of the impulsive wrench on the screw X produced by the reaction of the constraints, are also determined by the same construction. For by 17 the relative twist velocities about 6, , and p are known; but since the impulsive intensity rj " is known, the twist velocity about is known ( 90) ; and therefore, the twist velocity about is known ; finally, from the twist velocity about p, the impulsive intensity X " is determined. 252 THE THEORY OF SCREWS. [233- 233. Analytical Method. A quiescent rigid body which has freedom of the fifth order receives an impulsive wrench on a screw 77 : it is required to determine the instantaneous screw 6, about which the body will commence to twist. Let X be the screw reciprocal to the freedom, and let the co-ordinates be referred to the absolute principal screws of inertia. The given wrench com pounded with a certain wrench on X must constitute the wrench which, if the body were free, would make it twist about 6, whence we deduce the six equations (h being an unknown quantity) Multiplying the first of these equations by X 1} the second by X 2 , &c., adding the six equations thus produced, and remembering that and X are reciprocal, we deduce i/"2%A.i + X" 2V = 0. This equation determines X " the impulsive intensity of the reaction of the constraints. The co-ordinates of the required screw 6 are, therefore, proportional to the six quantities Pi Pe 234. Principal Screws of Inertia. We can now determine the co-ordinates of the five principal screws of inertia ; for if be a principal screw of inertia, then in general . whence with similar values for ,, ... 6 . Substituting these values in the equation and making ^- = #, we have for sc the equation fv p l -co p 2 -x p 3 - x pt- a; p 5 - x p 6 - x This equation ts of the fifth degree, corresponding to the five principal screws of inertia. If x denote one of the roots of the equation, then the corresponding principal screw of inertia has co-ordinates proportional to Xj X-s X3 X^ _ X 5 X 6 ^~- x" PI-X" p 3 -x" pi-" Ps-x" PS- 235] FREEDOM OF THE FIFTH ORDER. 253 We can easily verify as in 84 that these five screws are co-reciprocal and are also conjugate screws of inertia. It is assumed in the deduction of this quintic that all the quantities XJ...XB are different from zero. If one of the quantities, suppose X l5 had been zero this means that the first absolute principal Screw of Inertia would belong to the w-system expressing the freedom. Let us suppose that Xj = then the equations are Of course one solution of this system will be V" = 0, , = ... = 0. This means that the first absolute principal Screw of Inertia is also one of the principal Screws of Inertia in the rc-system, as should obviously be the case. For the others = and we have an equation of the fourth degree in , P* - % In the general case we can show that there are no imaginary roots in the quintic, for since the screws ^1 ^-2 X and p 1 - x p 2 - x p s - x" are conjugate screws of inertia, we must have (81) If x = a. + if$ ; y = a ift then this equation reduces to v frV _ but as these are each positive terms their sum cannot be zero. This is a particular case of 86. (See Appendix, note 2.) 235. The limits of the roots. We can now show the limits between which the five roots, just proved to be real, must actually lie in the equation 254 THE THEORY OF SCREWS. [235, 11 11 substitute p , = . = . 6 = x = -\ ft ?> ft y and suppose qi, q z , qa, q*, q*, q& to be in descending order of magnitude. "X 2 -\ 2 "\ 2 Thus -JSL + _*_ + . ..+_*_=<). y - ?i y - & y - ft That is v(y - ft)(y - ?,)(y - ? 4 ) (y -?5)(y - &) + + V (y - ?0 (y - 9-2) (y - &) (y - ? 4 ) (y - ? B ) = 0. In the left-hand member of this equation substitute the values qi, q*, q a , ?4> q*, q* successively for y ; five of the six terms vanish in each case, and the values of the remaining term (and therefore of the whole member) are alternately positive and negative. The five values of y must therefore lie in the intervals between the six quantities q lt q 2 , ... q s , the roots are accordingly proved to be real and distinct (unless one of the quantities \ 1} \ 2 , X 3 , \ 4 , \ 5 , X 6 = and a further condition hold, or unless some of the quantities q 1} ... q e be equal). The values of p 1} ... p 6 are a, b, c; and we suppose a, b, c, positive and a > b > c. The values of y lie in the successive intervals between 1 1 1 _1 _1 _1 c b a a b c and consequently of the roots of the equation in x. Two are positive and lie between a and b, and between b and c respectively. Two are negative and lie between a and b, and between b and c respectively. The last is either positive and > a or negative and < a. 236. The Pectenoid. A surface of some interest in connection with the freedom of the fifth order may be investigated as follows. Let a be the pitch of the one screw &&gt;, to which the five system is reciprocal. Take any point on o> and draw through any two right lines OF, and OZ which are at right angles and which lie in the plane perpendicular to a). 236] FREEDOM OF THE FIFTH ORDER. 255 Then if 6 be a screw of the five-system with direction cosines cos X, cos //,, cos v, and if as, y, z be a point on the screw 6 and p e its pitch we must have ( 216) ( p e + a) cos X + z cos /* y cos v = 0. Fig. 41. Everything that we wish to specify about the five-system may be conveniently inferred from this equation. For example, let it be desired to find the locus of the screws of a five- system which can be drawn through a given point as , y , z and have the given pitch p e . We have ( p e + a) cos \-\-z cos p y cos v = 0. If os, y, z be a point on 6 we may substitute x x, y y, z z for cos X, cos ft, cos v, and we obtain whence we see that the locus is a plane, as has been already proved other wise. (When the pitch is zero, this is Mb bius theorem, 110.) If we change the origin to some other point P which may with complete generality be that point whose co-ordinates are o, h, o and call X, Y, Z the co-ordinates with these new axes, the equation becomes (p e + a)c 256 THE THEORY OF SCREWS. [236 Let the radius vector of length p g + a = R be marked off along each screw 6 drawn through P, then the equation becomes or squaring (Z 2 + F 2 + Z*) X* = h*Z\ This represents a surface of the fourth degree. A model of the surface has been constructed*. It is represented in Fig. 41, and from its resemblance to the valves of a scallop shell the name pectenoid is suggested. The geometrical nature of a pectenoid is thus expressed. Given a screw a of pitch p a and a point situated anywhere. If a screw 6 drawn through be reciprocal to a then the extremity of a radius vector from along 6 equal to p a + p e will trace out a pectenoid. All pectenoids are similar surfaces, they merely differ in size in accordance with the variations of the quantity h. The perpendicular from upon a is a nodal line, and this is the only straight line on the surface. The pectenoid though unclosed is entirely contained between the pair of parallel planes Z = + h, Z = h. Sections parallel to the plane of Z are hyperbolas. Any plane through the nodal line cuts the pectenoid in a circle. A straight wire at right angles to the nodal line marked on the model indicates the screw reciprocal to the five-system. A second wire starts from the origin and projects from the surface. It is introduced to show concisely what the pectenoid expresses. If this wire be the axis of a screw 6 whose pitch when added to the pitch of the screw a, is equal to the intercept from the origin to the surface then the two screws are reciprocal. The interpretation of the nodal line is found in the obvious truth that when two screws intersect at right angles they are reciprocal whatever be the sum of their pitches. One of the circular sections made by a plane drawn through the nodal line is also indicated in the model. The physical interpretation is found in the theorem already mentioned, that all screws of the same pitch drawn through the same point and reciprocal to a given screw will lie in a plane. With the help of the pectenoid we can give another proof of the theorem that all the screws of a four-system which can be drawn through a point lie on a cone of the second degree ( 123). Let be the point and let a and /3 be two screws on the cylindroid reciprocal to the system. Let 6 be a screw through belonging to the four-system and therefore reciprocal to a and to /9. Then for the pectenoid relating to and a, we have (p e + pa )M-kN=0, where M=0, N=0 represent planes passing through 0. * Transaction* of the Royal Irish Academy, Vol. xxv. Plate xn. (1871). 236] FREEDOM OF THE FIFTH ORDER. In like manner for the pectenoid relating to and /3, we have 257 where M = 0, N = also represent planes passing through 0, whence eliminating p e we have (p a -pe) MM - kNM + k N M= 0. The equation of the pectenoid can also be deduced directly as follows. Let five screws of the five-system be given. Take a point on one of these screws (a) and through draw four screws /3, 7, 8, e which belong to the four-system defined by the remaining four screws of the original five. Let there be any three rectangular axes drawn through 0. Let ct l , 2 , a 3 be the direction cosines of a and let /3 1( /3 2 , /3 3 be the direction cosines of /?, and similarly for 7, 8, e. Let 6 be some other screw of the five-system which passes through and let 1} 6 2 , 3 be its direction cosines, then if twists of amplitudes a, ft , 7 , 5 , e , & neutralize we must have 77i ee 2 a 3 + + 773 + 3 + ee s because the rotations neutralize, and also a.p a a. 2 whence by elimination of a , /3 , . . . 6 , we have a 2 @ 2 72 S 2 e 2 83 >3 73 63 63 i3 2 = 0, 3 = 0, f p 9 1 = 0, 6 p e 6 z = 0, p e & 3 = 0, = 0. This equation has the form Pe L e. + M e. + N e, Let p e = p /i and l = x-^- p, 6 z = y-^p, 3 = z H- p then by reduction and transformation of axes we obtain where y and 2 are planes at right angles and a is constant. This is the equation of the pectenoid. 17 a CHAPTER XVIII. FREEDOM OF THE SIXTH ORDER. 237. Introduction. When a rigid body has freedom of the sixth order, it is perfectly free. The screw system of the sixth order includes every screw in space. The statement that there is no reciprocal screw to such a system is merely a different way of asserting the obvious proposition that when a body is perfectly free it cannot remain in equilibrium, if the forces which act upon it have a resultant. 238. Impulsive Screws. Let A lt A 2 , ... denote a series of instantaneous screws which correspond respectively to the impulsive screws R lt R 2 , ... the body being perfectly free. Corresponding to each pair A 1} RI is a certain specific parameter. This parameter may be conveniently defined to be the twist velocity pro duced about A! by an impulsive wrench on R^, of which the intensity is one unit. If six pairs, A lt jR T ; A a , R. 2 , ... be known, and also the corresponding specific parameters, then the impulsive wrench on any other screw R can be resolved into six impulsive wrenches on R l ,...R 6 , these will produce six known twist velocities on A 1} ... A G , which being compounded determine the screw A, the twist velocity about A, and therefore the specific para meter of R and A. We thus see that it is only necessary to be given six corresponding pairs, and their specific parameters, in order to determine completely the effect of any other impulsive wrench. If seven pairs of corresponding instantaneous and impulsive screws be given, then the relation between every other pair is absolutely determined. It appears from 28 that appropriate twist velocities about A^,...A 7 can neutralise. When this is the case, the corresponding impulsive wrenches on R^^.R?, must equilibrate, and therefore the relative values of the intensities are known. It follows that the specific parameter of each pair At, RI is proportional to the quotient obtained by dividing the sexiant of 237-239] FREEDOM OF THE SIXTH ORDER, 259 A 2 ,...A R , by the sexiant of R. 2 ,...R 6 . With the exception of a common factor, the specific parameter of every pair of screws is therefore known, when seven corresponding screws are known. It will be shown in Chap. XXI. that three corresponding pairs are really sufficient. When seven instantaneous screws are known, and the corresponding seven impulsive screws, we are therefore enabled by geometrical construction alone to deduce the instantaneous screw corresponding to any eighth impulsive screw and vice versa. A precisely similar method of proof will give us the following theorem : If a rigid body be in position of stable equilibrium under the influence of a system of forces which have a potential, and if the twists about seven given screws evoke wrenches about seven other given screws, then, without further information about the forces, we shall be able to determine the screw on which a wrench is evoked by a twist about any eighth screw. We may present the results of the present section in another form. We must conceive two corresponding systems of screws, of which the correspond ence is completely established, when, to any seven screws regarded as belonging to one system, the seven corresponding screws in the other system are known. To every screw in space viewed as belonging to one system will correspond another screw viewed as belonging to the other system. Six screws can be found, each of which coincides with its correspondent. To a screw system of the nth order and rath degree in one system will correspond a screw system of the nth order and rath degree in the other Sj stem. We add here a few examples to illustrate the use which may be made of screw co-ordinates. 239. Theorem. When an impulsive force acts upon a free quiescent rigid body, the directions of the force and of the instantaneous screw are parallel to a pair of conjugate diameters in the momental ellipsoid. Let f}i,...i] 6 be the co-ordinates of the force referred to the absolute principal screws of inertia, then ( 35) and from ( 41) it follows that the direction cosines of 77 with respect to the principal axes through the centre of inertia are 172 260 THE THEORY OF SCREWS. [239- If a, b, c be the radii of gyration, then the instantaneous screw cor responding to i] has for co-ordinates , % _fh ,Va _ r h ,^5 _^s I y y I T > 71 I i a a o o c c The condition that 77 and its instantaneous screw shall be parallel to a pair of conjugate diameters of the momental ellipsoid is or But if the impulsive wrench on 77 be a force, then the pitch of 77 is zero, whence the theorem is proved. 240. Theorem. When an impulsive wrench acting on a free rigid body produces an instantaneous rotation, the axis of the rotation must be perpendicular to the impulsive screw. Let i)!, ... i) 6 be the axis of the rotation, then 2^ V = 0, or a (77! - 7; 2 ) (77! + O + b (773 - 774) (773 + 774) + c (775 - 77 6 ) (775 + 77 6 ) = 0, whence the screw of which the co-ordinates are + ar) l , arj. 2 , + brj 3 , ... is perpendicular to 77, and the theorem is proved. From this theorem, and the last, we infer that, when an impulsive force acting on a rigid body produces an instantaneous rotation, the direction of the force, and the axis of the rotation, are parallel to the principal axes of a section of the momental ellipsoid. 241. Principal Axis. If 77 be a principal axis of a rigid body, it is required to prove that SjH*y0, reference being made to the absolute principal screws of inertia. For in this case a force along a line Q intersecting 77, compounded with a couple in a plane perpendicular to 77, must constitute an impulsive wrench to which 77 corresponds as an instantaneous screw, whence we deduce ( 120), h and k being the same for each coordinate, ., h dR h dR 242] FKEEDOM OF THE SIXTH OIIDER. 261 Expressing the condition that p e = 0, we have but we have already seen ( 131) that the two last terms of this equation are zero, whence the required theorem is demonstrated. The formula we have just proved may be written in the form This shows that if the body were free, then an impulsive force suitably placed would make the body commence to rotate about 77. Whence we have the following theorem*: A rigid body previously in unconstrained equilibrium in free space is supposed to be set in motion by a single impulsive force ; if the initial axis of twist velocity be a principal axis of the body, the initial motion is a pure rotation, and conversely. It may also be asked at what point of the body one of the three principal axes coincides with 77 ? This point is the intersection of 6 and 77. To determine the co-ordinates of 6 it is only necessary to find the relation between h and k, and this is obtained by expressing the condition that 6 is reciprocal to 77, whence we deduce Zh + kuj = 0. Thus is known, and the required point is determined. If the body be fixed at this point, and then receive the impulsive couple perpendicular to 77, the instantaneous reaction of the point will be directed along 0. 242. Harmonic Screws. We shall conclude by stating for the sixth order the results which are included as particular cases of the general theorems in Chapter IX. If a perfectly free rigid body be in equilibrium under the influence of a conservative system of forces, then six screws can generally be found such that each pair are conjugate screws of inertia, as well as conjugate screws of the potential, and these six screws are called harmonic screws. If the body be displaced from its position of equilibrium by a twist of small amplitude about a harmonic screw, and if the body further receive a small initial twisting motion about the same screw, then the body will continue for ever to perform small twist oscillations about that screw. And, more generally, whatever be the initial circumstances, the movement of the body is com pounded of twist oscillations about the six harmonic screws. * Townsend, Educational Times Reprint, Vol. xxi. p. 107. CHAPTER XIX. HOMOGRAPHIC SCREW SYSTEMS*. 243. Introduction. Several of the most important parts of the Theory of Screws can be embraced in a more general theory. I propose in the present chapter to sketch this general theory. It will be found to have points of connexion with the modern higher geometry ; in particular the theory of Homographic Screws is specially connected with the general theory of correspondence. I believe it will be of some interest to show how these abstract geometrical theories may be illustrated by dynamics. 244. On Plane Homographic Systems. It may be convenient first to recite the leading principle of the purely geometrical theory of homography. We have already had to mention a special case in the Introduction. Let a be any point in a plane, and let ft be a corresponding point. Let us further suppose that the correspondence is of the one-to-one type, so that when one a is given then one ft is known, when one ft is given then it is the correspondent of a single a. The relation is not generally interchangeable. Only in very special circumstances will it be true that ft, regarded as in the first system, will correspond to a in the second system. The general relation between the points a and ft can be expressed by the following equations, where a 1} a. 2 , 3 are the ordinary trilinear co-ordinates of a, and J3 1} /3 a , fi 3 , the co-ordinates of ft, ft = (11)0! +(12)0, + (13) a,, ft = (31) 0^(32) a, + (33) 03. In these expressions (11), (12), &c., are the constants defining the particular character of the homographic system. * Proc. Hoy. Irish Acad. Ser. n. Vol. HI. p. 435 (1881). 243-246] iioMOGiiAPHic SCREW SYSTEMS. 263 There are in general three points, which coincide with their corre spondents. These are found by putting & = Pi ; ft* = pa., ; j3 3 = pa a . Introducing these values, and eliminating a l , a. 2> a s , we obtain the following equation for p : 0-| (11) -p, (12), (13) (21), (22) -p, (23) (31), (32), (33) -p If we choose these three points of the vertices of the triangle of reference, the equations relating y with x assume the simple form, & = /i i ; & =/ 2 <* 2 ; & =/ 3 a , where /!,/ 2 ,/ 3 are three new constants. 245. Homographic Screw Systems. Given one screw a, it is easy to conceive that another screw ft correspond ing thereto shall be also determined. We may, for example, suppose that the co-ordinates of ft ( 34) shall be given functions of those of a. We might imagine a geometrical construction by the aid of fixed lines or curves by which, when an a is given, the corresponding ft shall be forthwith known : again, we may imagine a connexion involving dynamical conceptions such as that, when a is the seat of an impulsive wrench, ft is the instantaneous screw about which the body begins to twist. As a moves about, so the corresponding screw ft will change its position and thus two corresponding screw systems are generated. Regarding the connexion between the two systems from the analytical point of view, the co-ordinates of a and ft will be connected by certain equations. If it be invariably true that a single screw ft corresponds to a single screw a, and that conversely a single screw a corresponds to a single screw ft ; then the two systems of screws are said to be homographic. A screw a. in the first system has one corresponding screw ft in the second system ; so also to ft in the first system corresponds one screw in the second system. It will generally be impossible for a and a to coincide, but cases may arise in which they do coincide, and these will be discussed further on. 246. Relations among the Co-ordinates. From the fundamental property of two homographic screw systems the co-ordinates of ft must be expressed by six equations of the type 264 THE THEORY OF SCREWS. [246- If these six equations be solved for Oj, ... otg we must have a, =., .... As a single a is to correspond to a single /3, and vice versa, these equations must be linear : whence we have the following important result : In two homographic screw systems the co-ordinates of a screw in one system are linear functions with constant coefficients of the co-ordinates of the corre sponding screw in the other system. If we denote the constant coefficients by the notation (11), (22), &c., then we have the following system of equations : 13, = (11) a, + (12) a, + (13) o 3 + (14) 4 + (15) a 5 + (16) 6 , & = (21) a + (22) as + (23) a 3 + (24) 4 + (25) a 5 + (26) a,, & = (61) a, + (62) a, + (63) a 3 + (64) a 4 + (65) a 5 + (66) cv 247. The Double Screws. It is now easy to show that there are in general six screws which coincide with their corresponding screws; for if ^ 1 = p%i, j3 2 = pa. 2 , &c., we obtain an equation of the sixth degree for the determination of p. We therefore have the following result : In two homographic screw systems six screws can in general be found, each of which regarded as a screw in either system coincides with its correspondent in the other system. 248. The Seven Pairs. In two homographic rows of points we have the anharmonic ratio of any four points equal to that of their correspondents. In the case of two homographic screw systems we have a set of eight screws in one of the systems specially related to the corresponding eight screws in the other system. We first remark that, given seven pairs of corresponding screws in the two systems, then the screw corresponding to any other given screw is deter mined. For from the six equations just written by substitution of known values of ail, ... 6 and /3 1; ... /3 6 , we can deduce six equations between (11), (12), &c. As, however, the co-ordinates are homogeneous and their ratios are alone involved, we can use only the ratios of the equations so that each pair of screws gives five relations between the 36 quantities (11), (12), &c. The 249] HOMOGRAPHIC SCREW SYSTEMS. 265 seven pairs thus give 35 relations which suffice to determine linearly the ratios of the coefficients. The screw y9 corresponding to any other screw a is completely determined ; we have therefore proved that When seven corresponding pairs of screws are given, the two homographic screw systems are completely determined. A perfectly general way of conceiving two homographic screw systems may be thus stated : Decompose a wrench of given intensity on a screw a into wrenches on six arbitrary screws. Multiply the intensity of each of the six component wrenches by an arbitrary constant ; construct the wrench on the screw /3 which is the resultant of the six components thus modified; then as a moves into every position in space, and has every fluctuation in pitch, so will /3 trace out the homographic screw system. It is easily seen that in this statement we might have spoken of twist velocities instead of wrenches. 249. Homographic n-systems. The seven pairs of screws of which the two systems are defined cannot be always chosen arbitrarily. If, for example, three of the screws were co- cylindroidal, then the three corresponding screws must be co-cylindroidal, and can only be chosen arbitrarily subject to this imperative restriction. More generally we shall now prove that if any n + 1 screws belong to an n -system (69), then the n + 1 corresponding screws will also belong to an n-system. If n + 1 screws belong to an ?i-system it will always be possible to determine the intensities of certain wrenches on the n + 1 screws which when compounded together will equilibrate. The conditions that this shall be possible are easily expressed. Take, for example, n = 3, and suppose that the four screws a, fi, 7, 8 are such that suitable wrenches on them, or twist velocities about them, neutralize. It is then obvious ( 76) that each of the determinants must vanish which is formed by taking four columns from the expression i, -,, o 3> a,, a 5 , 2 6 76 It is, however, easy to see that these determinants will equally vanish for the corresponding screws in the homographic system ; for if we take as screws of reference the six common screws of the two systems, then we have at once for the co-ordinates of the screw corresponding to a (ll)a lf (22)0,, (33) a,, (44) 4 , (55) a., (66)*. 2GG THE THEORY OF SCREWS. [249- Whcri these substitutions are made in the determinants it is plain that they still vanish ; we hence have the important result that The screws corresponding homographically to the screws of an n-system form another n-system. Thus to the screws on a cylindroid will correspond the screws on a cylindroid. It is, however, important to notice that two reciprocal screws have not in general two reciprocal screws for their correspondents. We thus see that while two reciprocal screw systems of the nth and (6 ?i)th orders respectively have as correspondents systems of the same orders, yet that their connexion as reciprocals is divorced by the homographic transforma tion. Reciprocity is not, therefore, an invariantive attribute of screws or screw systems. There are, however, certain functions of eight screws analogous to anharmoriic ratios which are invariants. These functions are of considerable interest, and they are not without physical significance. 250. Analogy to Anharmonic Ratio. We have already ( 230) discussed the important function of six screws which is called the Sexiant. This function is most concisely written as the determinant (a^^Js^s^s) where a, /3, 7, B, e, are the screws. In Sylvester s language we may speak of the six screws as being in involution when their sexiant vanishes. Under these circumstances six wrenches on the six screws can equilibrate ; the six screws all belong to a 5-system, and they possess one common reciprocal. In the case of eight screws we may use a very concise notation; thus 12 will denote the sexiant of the six screws obtained by leaving out screws 1 and 2. It will now be easy to show that functions of the following form are invariants, i.e. the same in both systems: 12 . 34 13. 24 It is in the first place obvious that as the co-ordinates of each screw enter to the same degree in the numerator and the denominator, no embarrassment can arise from the arbitrary common factor with which the six co-ordinates of each screw may be affected. In the second place it is plain that if we replace each of the co-ordinates by those of the corresponding screw, the function will still remain unaltered, as all the factors (11), (22), &c., will divide out. We thus see that the function just written will be absolutely unaltered when each screw is changed into its corresponding screw. By the aid of these invariant functions it is easy, when seven pairs of screws are given, to construct the screw corresponding to any given eighth 252] HOMOGRAPHIC SCREW SYSTEMS. 2G7 screw. We may solve this problem in various ways. One of the simplest will be to write the five invariants 12.38 13.48 14\58 15.68 16.78 13.28 14.38 15.48 16.58 IT . 68* These can be computed from the given eight screws of one system ; hence we have five linear equations to determine the ratios of the coefficients of the required eighth screw of the other system. It would seem that of all the invariants of eight screws, five alone can be independent. These five invariants are attributes of the eight-screw system, in the same way that the anharmonic ratio is an attribute of four collinear points. 251. A Physical Correspondence. The invariants are also easily illustrated by considerations of a me chanical nature. To a wrench on one screw corresponds a twist on the corresponding screw, and the ratio of the intensities of the wrench and twist is to be independent of those intensities. We may take a particular case to illustrate the argument : Suppose a free rigid body to be at rest. If that body be acted upon by an impulsive system of forces, those forces will constitute a wrench on a certain screw a. In consequence of these forces the body will commence to move, and its instantaneous motion cannot be different from a twist velocity about some other screw /3. To one screw a will correspond one screw 0, and (since the body is perfectly free) to one screw /3 will correspond one screw a. It follows, from the definition of homo- graphy, that as a. moves over every screw in space, ft will trace out an homo- graphic system.... From the laws of motion it will follow, that if F be the intensity of the impulsive wrench, and if V be the twist velocity which that wrench evokes, then F~ V will be independent of F and V, though, of course, it is not independent of the actual position of a and /3. 252. Impulsive and Instantaneous Systems. It is known ( 230) that when seven wrenches equilibrate (or when seven twist velocities neutralize), the intensity of the wrench (or the twist velocity) on any one screw must be proportional to the sexiant of the six non- corresponding screws. Let F 1S , F., s , ... F 7S be the intensities of seven impulsive wrenches on the screws 1, 2, ... 7, which equilibrate, then we must have 18 28 78 268 THE THEORY OF SCREWS. [252- Similarly, by omitting the first screw, we can have seven impulsive wrenches which equilibrate, where 18 hence we have 13.28 FK.F& Let the instantaneous twist velocity corresponding to F 1S be denoted by F 18 , then, as when seven wrenches equilibrate, the seven corresponding twist velocities must also equilibrate, we must have in the corresponding system, 12. 38 = VnV* 13.28 ViV But we must have the twist velocity proportional to the impulsive intensity ; hence, from the second pair of screws we have and from the third pair, F V F V ^38 38 * 13 13 ) hence we deduce VlZ ^38 _ ^12 ff 1^13 ^28 -^13 ^28 and, consequently, the function of the eight impulsive screws 12.38 13.28 must be identical with the same function of the instantaneous screws. It should, however, be remarked, that the impulsive and instantaneous screws do not exhibit the most general type of two homographic systems. A more special type of homography, and one of very great interest, characterizes the two sets of screws referred to. 253. Special type of Homography. If the general linear transformation, which changes each screw a into its correspondent 6, be specialized by the restriction that the co-ordinates of 6 are given by the equations fi- 1 "i Pi I <* 6 da 6 254] HOMOGRAPHIC SCEEW SYSTEMS. 269 where U is any homogeneous function of the second order in a lt ...a 6 , and where p lt ...p 6 are the pitches of the screws of reference, then the two systems are related by the special type of homography to which I have referred. The fundamental property of the two special homographic systems is thus stated : Let a and /3 be any two screws, and let 6 and <j> be their correspondents, then, when a is reciprocal to <j>, /3 will be reciprocal to 9. We may, without loss of generality, assume that the screws of reference are co-reciprocal, and in this case the condition that ft and 6 shall be co- reciprocal is = ; but by substituting for 1} ... 6 , this condition reduces to dU Similarly, the condition that a and < shall be reciprocal is dU dU ~ = It is obvious that as U is a homogeneous function of the second degree, these two conditions are identical, and the required property has been proved. 254. Reduction to a Canonical form. It is easily shown that by suitable choice of the screws of reference the function U may, in general, be reduced to the sum of six square terms. We now proceed to show that this reduction is generally possible, while still retaining six co-reciprocals for the screws of reference. The pitch p a of the screw a is given by the equation ( 38), the six screws of reference being co-reciprocals, the function p a must retain the same form after the transformation of the axes. The discriminant of the function equated to zero will give six values of X ; these values of X will determine the coefficients of U in the required form. I do not, however, enter further into the discussion of this question, which belongs to the general theory of linear transformations. 270 THE THEORY OF SCREWS. [254- The transformation having been effected, an important result is im mediately deduced. Let the transformed function be denoted by then we have ft=- PI PI whence it appears that the six screws of reference are the common screws of the two systems. We thus find that in this special case of homography The six common screws of the two systems are co-reciprocal. The correspondence between impulsive screws and instantaneous screws is a particular case of the type here referred to. The six common screws of the two systems are therefore what we have called the principal screws of inertia, and they are co-reciprocal. 255. Correspondence of a Screw and a system. We shall sometimes have cases in which each screw of a system cor responds not to a single screw but to a system of screws. For the sake of illustration, suppose the case of a quiescent rigid body with two degrees of freedom and let this receive an impulsive wrench on some screw situated anywhere in space. The movement which the body can accept is limited. It can, indeed, only twist about one of the singly infinite number of screws, which constitute a cylindroid. To any screw in space will correspond one screw on the cylindroid. But will it be correct to say, that to one screw on the cylindroid corresponds one screw in space ? The fact is, that there are a quadruply infinite number of screws, an impulsive wrench on any one of which will make the body choose the same screw on the cylindroid for its instantaneous movement. The relation of this quadruply infinite group is clearly exhibited in the present theory. It is shown in 128 that, given a screw a on the cylindroid, there is, in general one, but only one screw 6 on the cylindroid, an impulsive wrench on which will make the body commence to twist about a. It is further shown that any screw whatever which fulfils the single condition of being reciprocal to a single specified screw on the cylindroid possesses the same property. The screws corresponding to a thus form a five-system. The correspondence at present before us may therefore be enunciated in the following general manner. To one screw in space corresponds one screw on the cylindroid, and to one screw on the cylindroid corresponds a five-system in space. 257] HOMOGRAPHIC SCREW SYSTEMS. 271 256. Correspondence of m and n systems . We may look at the matter in a more general manner. Consider an w-system (J.) of screws, and an w-system (B) (m>n). (If we make ra = 6 and n = 2, this system includes the system we have been just discussing.) To one screw in A will correspond one screw in B, but to one screw in B will correspond, not a single screw in A, but an (m + 1 ?i)-system of screws. If m = n, we find that one screw of one system corresponds to one screw of the other system. Thus, if m = n = 2, we have a pair of cylindroids, and one screw on one cylindroid corresponds to one screw on the other. If m = 3, and n = 2, we see that to each screw on the cylindroid will cor respond a whole cylindroid of screws belonging to the three-system. For example, if a body have freedom of the second order and a screw be indicated on the cylindroid which defines the freedom, then a whole cylindroid full of screws can always be chosen from any three-system, an impulsive wrench on any one of which will make the body commence to twist about the indicated screw. 257. Screws common to the two systems. The property of the screws common to the two homographic systems will of course require some modification when we are only considering an wi-system and an ?i-system. Let us take the case of a three-system on the one hand, and a six-system, or all the screws in space, on the other hand. To each screw a of the three-system A must correspond, a four-system, B, so that a cone of the screws of this four-system can be drawn through every point in space. It is interesting to note that one screw /3 can be found, which, besides belonging to B, belongs also to A. Take any two screws reciprocal to B, arid any three screws reciprocal to A, then the single screw /3, which is reciprocal to the five screws thus found, belongs to both A and B. We thus see that to each screw a of A, one corresponding screw in the same system can be determined. The result just arrived at can be similarly shown generally, and thus we find that when every screw in space cor responds to a screw of an ?i-system, then each screw of the n-system will correspond to a (7 ?i)-system, and among the screws of this system one can always be found which lies on the original n-system. As a mechanical illustration of this result we may refer to the theorem ( 96), that if a rigid body has freedom of the nth order, then, no matter what be the system of forces which act upon it, we may in general combine the resultant wrench with certain reactions of the constraints, so as to produce a wrench on a screw of the n-system which defines the freedom of the body, and this wrench will be dynamically equivalent to the given system of forces. 272 THE THEORY OF SCREWS. [258, 258. Corresponding Screws defined by Equations. It is easy to state the matter analytically, and for convenience we shall take a three-system, though it will be obvious that the process is quite general. Of the six screws of reference, let three screws be chosen on the three- system, then the co-ordinates of any screw on that system will be a 1( 2 , 3 , the other three co-ordinates being equal to zero. The co-ordinates of the corresponding screw ft must be indeterminate, for any screw of a four-system will correspond to ft. This provision is secured by /3 4) /3 5 , /3 f) remaining quite arbitrary, while we have for @ lt j3 2 , @ 3 the definite values, If we take /3 4 , /3 5 , /3 6 all zero, then the values of ($ l} /3 2 , /3 3 , just written, give the co-ordinates of the special screw belonging to the three-system, which is among those which correspond to a. As a moves over the three-system, so will the other screw of that system which corresponds thereto. There will, however, be three cases in which the two screws coincide ; these are found at once by making Pi = p<*i , /3 2 = p* 2 ; /3 3 = pa 3 , whence we obtain a cubic for p. It is thus seen that generally n screws can be found on an ?z-system, so that each screw shall coincide with its correspondent. As a dynamical illustration we may give the important theorem, that when a rigid body has n degrees of freedom, then n screws can always be found, about any one of which the body will commence to twist when it receives an impulsive wrench on the same screw. These screws are of course the principal screws of inertia ( 84). 259. Generalization of Anharmonic Ratio. We have already seen the anharmonic equality between four screws on a cylindroid, and the four corresponding screws ; we have also shown a quasi anharmonic equality between any eight screws in space and their cor respondents. More generally, any n + 2 screws of an w-system are connected with their n + 2 correspondents, by relations which are analogous to an harmonic properties. The invariants are not generally so simple as in the eight-screw case, but we may state them, at all events, for the case of n = 3. Five screws belonging to a three-system, and their five correspondents 259] HOMOGKAPHIC SCREW SYSTEMS. 273 are so related, that when nine are given, the tenth is immediately deter mined ; for this two data are required, that being the number required to specify a screw already known to belong to a given three-system. We may, as before, denote by 12 the condition that the screws 3, 4, 5 shall be co-cylindroidal. This, indeed, requires no less than four distinct conditions, yet, as pointed out ( 76), functions can be found whose evanes cence will supply all that is necessary. Nor need this cause any surprise, when it is remembered that the evanescence of the sine of an angle between two lines contains the two conditions necessary that the direction cosines are identical. The function 12.34 13.24 can then be shown to be an invariant which retains its value unaltered when we pass from one set of five screws in a three-system to the corresponding set in the other system. B - 18 CHAPTER XX. EMANANTS AND PITCH INVARIANTS. 260. The Dyname. If we wish to speak of a magnitude which may be a twist or a wrench or a twist velocity it is convenient to employ the word Dyname used by Pliicker* and by other writers. The Dyname a is completely expressed by its components a l} ... a 6 n the six screws of reference. These six quantities are quite independent. They may be considered as the co-ordinates of the Dyname. Let a be the intensity of the Dyname on a ; then of is a factor in each of !, ... a 6 , and if the Dyname be replaced by another on the same screw a, but of intensity #a , the co-ordinates of this new Dyname will be #!, ... XO.Q. Let ft be a second Dyname on another screw quite arbitrary as to its position and as to its intensity ft . Let the co-ordinates of ft, referred to the same screws of reference, be ft 1} ... /3 6 . If we suppose a Dyname of intensity yft on the screw ft, then its co-ordinates will be yft 1} ... yft 6 . Let us now compound together the two Dynames of intensities oca and yft on the screws a. and ft. They will, according to the laws for the composition of twists and wrenches ( 14), form a single Dyname on a third screw lying on the same cylindroid as a and ft. The position of the resultant screw is such that it divides the angle between a and ft into parts whose sines have the ratio of y to x. The intensity of the resultant Dyname is also determined (as in the parallelogram of force) to be the diagonal where x and y are the sides, and the angle between them is the angle between a and ft. It is important to notice that in the determination of this resultant the screws to which the co ordinates are referred bear no part ; the position of the resultant Dyname on the cylindroid as well as its intensity each depend solely upon the two original Dynames, and on the numerical magnitudes x and y. * Pliicker, Fundamental views regarding Mechanics, Phil. Trans. 1866, Vol. CLVI. pp. 361 380. 260, 261] EMANANTS AND PITCH INVARIANTS. 275 We have now to form the co-ordinates of the resulting Dyname, or its components when decomposed along the six screws of reference. The first Dyname has a component of intensity x^ on the first screw ; and as the second Dyname has a component y^ 1} it follows that the sum of these two must be the component of the resultant. Thus we have for the co-ordinates of the resultant Dyname the expressions 261. Emanants. Let us suppose that without in any particular altering either of the Dynames a and ft we make a complete change of the six screws of reference. Let the co-ordinates of a with regard to these new screws be \, ... \ 6 , and those of (3 be //, 1} ... //,. Precisely the same argument as has just been used will show that the composition of the Dynames xo! and yfi will produce a Dyname whose co-ordinates are x\^ + y/j, lt . . . x\ 6 + y(j, s . We thus see that the Dyname defined by the co-ordinates x^ + yfti, ... xa 6 + y{3 6 , referred to the first group of reference screws is absolutely the same Dyname as that defined by the co-ordinates X,j + y^, ... x\ 6 + yv 6 referred to the second group of reference screws, and that this must remain true for every value of x and y. In general, let 1} ... # 6 denote the co-ordinates of a Dyname in the first system, and <j> l} ... </> 6 denote those of the same Dyname in the second system. Let/(0!, ... 6 ) denote any homogeneous function of the first Dyname, and let JP (</>!, ... < 6 ) be the same function transformed to the other screws of refer ence. Then we have as an identical equation which must be satisfied whenever the Dyname de fined by lt ... 6 is the same as that defined by < u ... </> 6 . We must there fore have f(xa.i + yfi-i , . . . aJOe + y/3 6 ) = These expressions being homogeneous, they may each be developed in ascending powers of - . But as the identity must subsist for every value of oc this ratio, we must have the coefficients of the various powers equal on both sides. The expression of this identity gives us a series of equations which are all included in the form* d d * * See Proceedings Roy. Irish Acud., Ser. n. Vol. in. ; Science, p. 601 (1882). 18-2 276 THE THEORY OF SCREWS. [261- The functions thus arising are well known as " emanants " in the theory of modern algebra. The cases which we shall consider are those of n = 1 and n = 2. In the former case the emanant may be written - df n df 262. Angle between Two Screws. It will of course be understood that/ is perfectly arbitrary, but results of interest may be most reasonably anticipated when / has been chosen with special relevancy to the Dyname itself, as distinguished from the influence due merely to the screws of reference. We shall first take for / the square of the intensity of the Dyname, the expression for which is found ( 35) to be where (12) denotes the cosine of the angle between the first and second screws of reference, which are here taken to be perfectly arbitrary. The second group of reference screws we shall take in a special form. They are to be a canonical co-reciprocal system, so that R = (\ + X 2 ) 2 + (\ 3 + X 4 ) 2 + (X 5 + X 6 ) 2 . Introducing these values, we have, as the first emanant, X 2 ) + (p a 4- /i 4 ) (X 3 + X 4 ) + (fjL 6 + fi t ) (X 5 + X 6 ) ; but in the latter form the expression obviously denotes the cosine of the angle between a and /3 where the intensities are both unity ; hence, whatever be the screws of reference, we must have for the cosine of the angle between the two screws the result 263. Screws at Right Angles. In general we have the following formula for the cosine of the angle between two Dynames multiplied into the product of their intensities : dR n dR dR This expression, equated to zero, gives the condition that the two Dynames be rectangular. 265] EMANANTS AND PITCH INVARIANTS. 277 If three screws, a, @, y, are all parallel to the same plane, and if 9 be a screw normal to that plane, then we must have dR dR dR dfr dR dR 264. Conditions that Three Screws shall be parallel to a Plane. ^ * Since a screw of a three-system can be drawn parallel to any direction, it will be possible to make any three of the quantities 6 l , ... 6 6 equal to zero. Hence, we have as the condition that the three screws, a, /3, 7 shall be all parallel to a plane the evanescence of all the determinants of the type dR dR dR d 7l > dR dR dR dR dR dR 265. Screws on the same Axis. The locus of the screws d perpendicular to a is represented by the equation If we assume that the screws of reference are co-reciprocal, then the equation just written can only denote all the screws reciprocal to the one screw whose co-ordinates are Pi di " PS da 6 It is manifest that all the screws perpendicular to a given line cannot be reciprocal to a single screw unless the pitch of that screw be infinite, other wise the condition (p a +p e ) cos (f> d sin < = could not be fulfilled. We therefore see that the co-ordinates just written can only denote those of a screw of infinite pitch parallel to a. 278 THE THEORY OF SCREWS. [265, If a? be a variable parameter, then the co-ordinates x dR a; dR Oti + -. ~ 7 i #6 "T ~i ~9 4p, da, 4p 6 da 6 must denote a screw of variable pitch x on the same screw as or. We are thus conducted to a more general form of the results previously obtained ( 47). These expressions may be written ! + COS flj , or a + COS O.J, . . . ^ 2j? 2 where a lf a 2 , ... are the angles which a makes with the screws of reference. 266. A general Expression for the Virtual Coefficient. We may also consider that function of the co-ordinates of a Dyname which, being always proportional to the pitch, becomes exactly equal to the pitch when the intensity is equal to unity. More generally, we may define the function to be equal to the pitch multiplied into the square of the intensity, and it is easy to assign a physical meaning to this function. It is half the work done in a twist against a, wrench, on the same screw, where the amplitude of the twist is equal to the intensity of the wrench. Referred to any co-ordinates, we denote this function by V expressed in terms of Xj,... X 6 . If we express the same function by reference to six co-reciprocal axes with co-ordinates cfi, ..., we have the result p 1 a. 1 s + ...> 6 a 2 = V. Forming now the first emanant, we have 2pi i A + . . . + 2p, 6 /3 6 = ^ -^- . . . + ^ 6 ; but the expression on the left-hand side denotes the product of the two intensities into double the virtual coefficient of the two screws; hence the right-hand member must denote the same. If, therefore, after the differentiations we make the intensities equal to unity, we have for the virtual coefficient between two screws X and yu, referred to any screws of reference whatever one-half the expression dV dV Suppose, for instance, that X is reciprocal to the first screw of reference, then 266] EMANANTS AND PITCH INVARIANTS. 279 This can be verified in the following manner. We have V = p\"\ dv / d and, therefore, if X be reciprocal to the first screw of reference, the formula to be proved is A few words will be necessary on the geometrical signification of the differentiation involved. Suppose a Dyname A, be referred to six co-ordinate screws of absolute generality, and let us suppose that one of these co ordinates, for instance X 1; be permitted to vary, the corresponding situation of X also changes, and considering each one of the co-ordinates in succession, we thus have six routes established along which X will travel in correspond ence with the growth of the appropriate co-ordinate. Each route is, of course, a ruled surface ; but the conception of a surface is not alone adequate to express the route. We must also associate a linear magnitude with each generator of the surface, which is to denote the pitch of the corresponding screw. Taking X and another screw on one of the routes, we can draw a cylindroid through these two screws. It will now be proved that this cylindroid is itself the locus in which X moves, when the co-ordinate cor related thereto changes its value. Let 9 be the screAV arising from an increase in the co-ordinate Xjj a wrench on 6 of intensity 6" has components of intensities #/ , . . . 6 ". A wrench on X has components X/ , . . . X 6 ". But from the nature of the case, If therefore & be suitably chosen, we can make each of these ratios 1, so that when 6" and X" are each resolved along the six screws of reference, all the components except $/ , X/ shall neutralize. But this can only be possible if the first reference screw lie on the cylindroid containing and X. Hence we deduce the result that each of the six cylindroids must pass through the corresponding screw of reference ; and thus we have a complete view of the route travelled by a screw in correspondence with the variation of one of its co-ordinates. Let the six screws of reference be 1, 2, 3, 4, 5, 6. Form the cylindroid (X, 1), and find that one screw 77 on this cylindroid which has with 2, 3, 4, 5, G, a common reciprocal ( 26). From a point draw a pencil of four rays parallel to four screws on the cylindroid. Let OA be parallel to one of the principal screws ; OX be parallel to X, Otj to 77, and Oh to the first screw of reference. 280 THE THEORY OF SCREWS. [266, Let the angle AOh be denoted by A, the angle ^40?; by B, and the angle A OX by <f). To find the component \ we must decompose A, , a twist on X, into two components, one on 77, the other on the first screw of reference. The component on 77 can be resolved along the other five screws of reference, since the six form one system with a common reciprocal. If we denote by 77 the component on 77, we then have X \! 77 sin (B - A) = sin (< - B) = sin(</>-J) and if a and 6 be the pitches of the two principal screws on the cylindroid, we have for the pitch of X the equation p = a cos 2 </> + b sin 2 <f> ; also -3^- = ~ V , because the effect of a change in X, is to move the screw aXj d(f> ctXj along this cylindroid. Air u , sin (0 - .B) We have Xj = 77 -r } --- A , sm (0- A) and as the other co-ordinates are to be left unchanged, it is necessary that 77 be constant, so that d\ _ ,sm(B A) ~d$~ rj sin^(<f>-A) dp . . sin 2 (<4 A) and hence ,^- = (6 - a) sin 2<f> , . ^ - 4r . ctXj ^T)sm(B-A) A , d\ d\ dd> Also = ^_ = _ cos ( ( f ) _^) j aXj rf0 rfXj Hence, substituting in the equation we deduce a = b tan </> tan A : but this is the condition that X and the first screw of reference shall be reciprocal ( 40). 267. Analogy to Orthogonal Transformation. The emanants of the second degree are represented by the equation when F is the function into which / becomes transformed when the co ordinates are changed from one set of screws of reference to another. If we take for / either of the functions already considered, these equations 267] EMANANTS AND PITCH INVARIANTS. 281 reduce to an identity ; but retaining / in its general form, we can deduce some results of very considerable interest. The discussion which now follows was suggested by the reasoning employed by Professor W. S. Burnside* in the theory of orthogonal transformations. Let us suppose that we transform the function f from one set of co- reciprocal screws of reference to another system. Let p 1} ... p 6 be the pitches of the first set, and q lt ... q 6 be those of the second set. Then we must have for each merely denotes the pitch of the Dyname multiplied into the square of its intensity. Multiply this equation by any arbitrary factor x and add it to the preceding, and we have d_ } f -( 2 \ i A.J d, \ 6 1 Regarding &, ... /3 6 as variables, the first member of this equation equated to zero would denote a certain screw system of the second degree. If that system were "central" it would possess a certain screw to which the polars of all other screws would be reciprocal, and its discriminant would vanish ; but the screw $ being absolutely the same as p, it is plain that the discriminant of the second side must in such case also vanish. We thus see that the ratios of the coefficients of the various powers of x in the following well-known form of determinant must remain unchanged when one co-reciprocal set of screws is exchanged for another. In writing the d z f determinant we put 12 for -= , &c. 16 1=0. 26 36 46 56 66 + ape Take for instance the coefficient of of divided by that of x, which is easily seen to be 1 d 2 / I d 2 f PI da.1 2 p 6 da s 2 * Williamson, Differential Calculus, p. 412. 11- h a;p 1 , 1 2 , 13 , 14 15 21 , 22 + xp 2 , 23 ,24 25 31 , 32 , 33 + ps, 34 35 41 , 42 V 43 , 44 + xp 4 , 45 51 , 52 , 53 , 54 , 55 61 , 62 , 63 , 64 65 282 THE THEORY OF SCREWS. [267, and we learn that this expression will remain absolutely unaltered provided that we only change from one set of co-reciprocals to another. In this / is perfectly arbitrary. 268. Property of the Pitches of Six Co-reciprocals. We may here introduce an important property of the pitches of a set of co-reciprocal screws selected from a screw system. There is one screw on a cylindroid of which the pitch is a maximum, and another screw of which the pitch is a minimum. These screws are parallel to the principal axes of the pitch conic ( 18). Belonging to a screw system of the third order we have, in like manner, three screws of maximum or minimum pitch, which lie along the three principal axes of the pitch quadric ( 173). The general question, therefore, arises, as to whether it is always possible to select from a screw system of the ?tth order a certain number of screws of maximum or minimum pitch. Let 1} ... # 6 be the six co-ordinates of a screw referred to n co-reciprocal screws belonging to the given screw system. Then the function p e , or is to be a maximum, while, at the same time, the co-ordinates satisfy the condition ( 35) 20! s + 220 A cos (12) = 1, which for brevity we denote as heretofore by Applying the ordinary rules for maxima and minima, we deduce the six equations dR 9 - = From these six equations O l , ... 9 6 can be eliminated, and we obtain the determinantal equation which, by writing x= 1 +po, becomes 1 %PI, cos (21), cos (31), cos (41), cos (51), cos (61) cos (12), l-#p a , cos (32), cos (42), cos (52), cos (62) cos (13), cos (23), l-a;p 3) cos (43), cos (53), cos (63) cos (14), cos (24), cos (34), lasp t , cos (54), cos (64) cos (15), cos (25), cos (35), cos (45), lacp s , cos (65) cos (16), cos (26), cos (36), cos (46), cos (56), 1 - ay> 6 = 268] EMANANTS AND PITCH INVARIANTS. 283 It is easily seen that this equation must reduce to the form In fact, seeing it expresses the solution of the problem of finding a screw of maximum pitch, and that the choice may be made from a system of the sixth order, that is to say, from all conceivable screws in the universe it is obvious that the equation could assume no other form. What we now propose to study is the manner in which the necessary evanescence of the several coefficients is provided for. After the equation has been expanded we shall suppose that each term is divided by the coefficient of a? that is, by From any point draw a pencil of rays parallel to the six screws. On four of these rays, 1, 2, 3, 4, we can assign four forces which equilibrate at the point. Let these magnitudes be X 1} X. 2 , X 3 , X 4 . We can express the necessary relations by resolving these four forces along each of the four directions successively. Hence X, + X, cos (12) + X s cos (13) + X, cos (14) = 0. X, cos (21) + X 2 +X, cos (23) + X, cos (24) - 0. X l cos (31) + X z cos (32) + X. + Z 4 cos (34) = 0. X, cos (41) + X, cos (42) + X s cos (43) + X 4 = 0. Eliminating the four forces we have 1, cos (12), cos (13), cos (14) cos (21), 1, cos (23), cos (24) I cos (31), cos (32), 1, cos (34) cos (41), cos ^42), cos (43), 1 Thus we learn that every determinant of this type vanishes identically. Had we taken live or six forces at the point it would, of course, have been possible in an infinite number of ways to have adjusted five or six forces to equilibrate. Hence it follows that the determinants analogous to that just written, but with five and six rows of elements respectively, are all zero. These theorems simplify our expansion of the original harmonic deter minant. In fact, it is plain that the coefficients of x*, of x, and of the absolute term vanish identically. The terms which remain are as follows : x ti + Ao? + Ex A + C ic 8 = 0. 284 THE THEORY OF SCREWS. [268- , 1 where A = 2, , V sin 2 (l, 2) in which 1, cos (12), cos (13) cos (12), 1, cos (23) cos (13), cos (23), 1 If by S (123) we denote the scalar of the product of three unit vectors along 1, 2, 3, then it is easy to show that We thus obtain the following three relations between the pitches and the angular directions of the six screws of a co-reciprocal system*, Pi The first of these formulae gives the remarkable result that, the sum of the reciprocals of the pitches of the six screws of a co-reciprocal system is equal to zero. The following elegant proof of the first formula was communicated to me by my friend Professor Everett. Divide the six co-reciprocals into any two groups A and B of three each, then it appears from 174 that the pitch quadric of each of these groups is identical. The three screws of A are parallel to a triad of conjugate diameters of the pitch quadric, and the sum of the reciprocals of the pitches is proportional to the sum of the squares of the conjugate diameters ( 176). The three screws of B are parallel to another triad of conjugate diameters of the pitch quadric, and the sum of the reciprocals of the pitches, with their signs changed, is proportional to the sum of the squares of the conjugate diameters. Remembering that the sum of the squares of the two sets of conjugate diameters is equal, the required theorem is at once evident. * Proceedings of the Royal Irish Academy, Series in. Vol. i. p. 375 (1890). A set of six screws are in general determined by 30 parameters. If those screws be reciprocal 15 conditions must be fulfilled. The above are three of the conditions, see also 271. 270] EMANANTS AND PITCH INVARIANTS. 285 269. Property of the Pitches of n Co-reciprocals. The theorem just proved can be extended to show that the sum of the reciprocals of the pitches of n co-reciprocal screws, selected from a screw system of the nth order, is a constant for each screw system. Let A be the given screw system, and B the reciprocal screw system, Take 6 n co-reciprocal screws on B, and any n co-reciprocal screws on A. The sum of the reciprocals of the pitches of these six screws must be always zero ; but the screws on B may be constant, while those on A are changed, whence the sum of the reciprocals of the pitches of the n co-reciprocal screws on A must be constant. Thus, as we have already seen from geometrical considerations, that the sum of the reciprocals of the pitches of co-reciprocals is constant for the screw system of the second and third order ( 40, 176), so now we see that the same must be likewise true for the fourth, fifth, and sixth orders. The actual value of this constant for any given screw system is evidently a characteristic feature of that screw system. 270. Theorem as to Signs. If in one set of co-reciprocal screws of an n-system there be k screws with negative pitch and n k screws with positive pitch, then in every set of co-reciprocal screws of the same system there will also be k screws with negative pitch and n k screws with positive pitch. To prove this we may take the case of a five-system, and suppose that of five co-reciprocals A l , A 2 , A 3 , A 4 , A 5 the pitches of three are positive, say mf, ra 2 2 , TO/, while the pitches of the two others are negative, say ra 4 2 , Let 8 be any screw of the system, then if 1} ... # 5 be its co-ordinates with respect to the five co-reciprocals just considered, we have for the pitch of 6 the expression raM 2 + w 2 2 2 2 + ra 3 2 <9 3 2 - m 4 2 4 2 - m 5 2 5 2 . Let us now take another set of five co-reciprocals B 1} B 2 , B 3 , B 4 , B 5 belonging to the same system, then the pitches of three of these screws must be + and the pitches of two must be . For suppose this was not so, but that the five pitches were, let us say n^, n^, w 3 2 , v? 4 2 , w s 2 . Let the co-ordinates of with respect to these new screws of reference be <f> 1} <f> 2 , ... B , then the pitch will be V& 2 + n.*<f> 2 2 + n s a 3 2 + nty* - n 5 2 </> 5 2 . 286 THE THEORY OF SCREWS. [270- Equating these two values of the pitch we ought to have for every screw S - n^ + M 3 2 < 2 2 + w 3 2 < 3 2 -f n 4 2 < 4 2 + m* But it can easily be seen that this equation is impossible. Let H be the screw to which all the screws of the five-system are re ciprocal, and let us choose for 8 the screw reciprocal to A 1} A 2 , A 3 , B 6 , H. The fact that S is reciprocal to H is of course implied in the assumption that 8 belongs to the five-system, while the fact that S is reciprocal to each of the screws A lt A 2 . A 3 , B 5 gives us 1= =0, 2 = 0, 3 = 0, 8 = 0. Hence we would have the equation which would require that all the co-ordinates were zero, which is im possible. In like manner any other supposition inconsistent with the theorem of this article would be shown to lead to an absurdity. The theorem is there fore proved. We can hence easily deduce the important theorem that three of the screws in a complete co-reciprocal system of six must have positive pitch and three must have negative pitch*. For in the canonical system of co-reciprocals the pitches are + a, a, 4- b, b, + c, c, i.e. three are positive and three are negative, and as in this case the w-system being the six -system includes every screw in space we see that of any six co -reciprocals three of the pitches must be positive and three must be negative. 271. Identical Formulae in a Co-reciprocal System. Let any screw a be inclined at angles cxi, a2, ... aG to the respective six screws of a co-reciprocal system. Then we have for the co-ordinate a n _ (p a +p n )cos al d al sin al ^ ~~~ * This interesting theorem was communicated to me by Klein, who had proved it as a property of the parameters of "six fundamental complexes in involution" (Math. Ann. Band. i. p. 204). 273] EM AN ANTS AND PITCH INVARIANTS. 287 If we substitute these values for a l , ... a n in the expression we obtain the equation cos 2 al cos 2 a2 cos 2 a6~ + - + ...+ - Pi P* P f =/>a cos a6 (p 6 cos a6 d a6 sin a6) _|_ __ _ . ^ JP ( p l cos a l d al sin al) 2 ( p 6 cos a6 d a6 sin a6) 2 As al, &c., da, &c., >!, &c. are independent of p a we must have the three co-efficients of this quadratic in p a severally equal to zero. 272. Three Pitches Positive and Three Negative. The equation cos 2 al cos 2 a2 cos 2 a6 _ Pi P-2 p% also shows that three pitches of a set of six co-reciprocals must be positive and three must be negative. For, suppose that the pitches of four of the co-reciprocals had the same sign, and let a be a screw perpendicular to the two remaining co-reciprocals, then the identity just written would reduce to the sum of four positive terms equal to zero. From this formula and also 11 1 --+- + ... + -=0 Pl P-2 P6 sin 2 ai sin 2 a2 sin 2 6 we have h + . . . H = Pi PI PS 273. Linear Pitch Invariant Functions. We propose to investigate the linear functions of the six co-ordinates of a screw which possess the property that they remain unaltered notwith standing an alteration in the pitch of the screw which the co-ordinates denote. It will first be convenient to demonstrate a general theorem which introduces a property of the six screws of a co-reciprocal system. The virtual coefficient of two screws is, as we know, represented by half the expression (p a + pp) cos 6 d sin 6, where p a and p ft are the pitches, is the angle between the two screws, and d the shortest perpendicular distance. The pitches only enter into 288 THE THEORY OF SCREWS. [273, this expression by their sum; and, consequently, if p a be changed into p a + x, and pp be changed into p$ x, the virtual coefficient will remain unaltered whatever x may be. We have found, however ( 37), that the virtual coefficient admits of representation in the form Pii/3i+ ... + profit- To augment the pitch of a by x, we substitute for a l} a..,, ... the several values ( 265), SY> fit* a, + - cos a,!, a 2 + -^ cos a 2 , ... 2^] 2p 2 where a 1( a 2 , ... are the angles made by the screw a with the screws of reference. Similarly, to diminish the pitch of ft by x, we substitute for &, /3 2 , . the several values OC OG &-H-COS&!, &-a- cos& 2 , &c. Zpi Zp 2 With this change the virtual coefficient, as above expressed, becomes x \ ( Q x + 9~ COS a - COS \ ^Pi or, CO o v/ ^j COS ttj + p 2 COS a 2 + ...! COS Oj 2 COS 2 . . . ) Z s ! cos &! cos a 2 cos & 2 cos a e cos 6, We have already shown that such a change must be void of effect upon the virtual coefficient for all values of x. It therefore follows that the coefficients of both x and x* in the expressions just written must be zero. Hence we obtain the two following properties : = (p\ cos j + ... + /3 6 cos a 6 ) (^ cos h+ ... + a 6 cos 6 6 ), _ cos a : cos bi cos a e cos 6 6 The second of the two formulas is the important one for our present purpose. It will be noted that though the two screws, a and @, are com pletely arbitrary, yet the six direction cosines of a. with regard to the screws of reference, and the six direction cosines of /3 with regard to the same screws of reference, must be connected by this relation. Of course the equation in this form is only true when the six screws of reference are co-reciprocal. In the more general case the equivalent identity would be of a much more complicated type. 274] EMANANTS AND PITCH INVARIANTS. 289 274. A Pitch Invariant. Let h lt ... h 6 be the direction angles of any ray whatever with regard to six co-reciprocal screws of reference, then the function U = ! cos h-i + . . . + a s cos h s is a pitch invariant. For, if we augment the pitch of a by x, we have to write for a lf ... a 6 the expressions x x j + 5 COS ! . . . 6 + COS 6 , API Ap Q and then U becomes ! COS A! + . . . + COS h K x /cos a a cos ^ cos a cos A, ~r o I T H -- Pi but from what we have just proved, the coefficient of x is zero, and hence we see that ! cos ^ -|- . . . + 6 cos h 6 remains unchanged by any alteration in the pitch of a. If we take three mutually rectangular screws, a, /3, 7, then we have the three pitch invariants L = 1 cos ^ + . . . + 6 cos a 6 , M = #! cos &J + ... + # 6 cos 6 6 , N = O l COS Ci + . . . + # 6 COS C 6 . It is obvious that any linear function of L, M, N, such as fL + gM+hN, is a pitch invariant. We can further show that this is the most general type of linear pitch invariant. For the conditions under which the general linear function ^0,+ ... +A n n shall be a pitch invariant are that equations of the type A l cos a, A 6 cos a a _ e -- r . . . + - = U ; dec. Pi P shall be satisfied for all possible rays. Though these equations are infinite in number, yet they are only equi valent to three independent equations ; in other words, if these equations are satisfied for three rays, a, b, c, which, for convenience, we may take to be rectangular, then they are satisfied for every ray. B. 19 290 THE THEORY OF SCREWS. [274- For, take a ray e, which makes direction-angles X, /A, v with a, b, c, then we have COS j = COS X COS ! + COS /A COS &! + COS V COS Cj , cos e 6 = cos X cos a 6 + cos /u, cos 6 6 + cos v cos c 6 . Hence A 6 cos e 6 ^ A ! COS 0^ ( ^^ ^.^IjCOSO! Pi Pi Pi + r>na 11 > Pi If, therefore, we have r 4i cos i ^ A l cos I i . v^i cosc i_ , *w Pi then, for every ray, we shall have cos ft It thus follows that the coefficients of a linear function which possesses the property of a pitch invariant must be subjected to three conditions. There are accordingly only three coefficients left disposable in the most general type of linear pitch invariant. Now, fL+gM + hN is a pitch invariant which contains three disposable quantities, f, g, h; it therefore represents the most general form of linear function which possesses the required property. We have thus solved the problem of finding a perfectly general expression for the linear pitch invariant function of the co-ordinates of a screw. It is convenient to take the three fundamental rays as mutually rect angular; but it is, of course, easy to show that any linear pitch invariant can be expressed in terms of three pitch invariants unless their determining rays are coplanar. We may express the result thus : Let L, M, N, be four linear pitch invariants, no three of which have coplanar determining rays. Then it is always possible to find four parameters, X, /*, v, p, such that the following equation shall be satisfied identically : \L + fiM + vN + pO = 0. 275. Geometrical meaning. The nature of the pitch invariant function can be otherwise seen. It is well known that in the composition of two or more twist velocities we 276] EMANANTS AND PITCH INVARIANTS. 291 discover the direction of the resultant screw and the magnitude of the resultant twist velocity by proceeding as if the twist velocities were vectors. Neither the pitches of the component screws nor their situations affect the magnitude of the resultant twist velocity or the direction of the resultant screw. This principle is, of course, an immediate consequence of the law of composition of twist velocities by the cylindroid. Let any ray a make an angle A, with the ray 6, and angles a 1} ... a 6 with the six screws of reference. The twist velocity $ on 6 if resolved on a has a component 0cos\. This must be equal to the sum of the several com ponents 1} # 2 , ... resolved on a; whence we have cos X = #! cos a-i + ... + G cos a 6 . If we make = unity, we obtain cos \=0 1 cos a t + ... +0 6 cos a s . This gives a geometrical meaning to the pitch invariant. It is simply the cosine of the angle between the screws 6 and a. As, of course, the pitch is not involved in the notion of this angle, it is, indeed, obvious that the expression for any function of the angle must be a pitch invariant. We now see the meaning of the equation obtained by equating the pitch invariant to zero. If we make 1 COS !+...+ # 6 COS C1 6 = it follows that a. and must be at right angles. The equation therefore signifies the locus of all the screws that are at right angles to a. The two equations 1 cos !+... + 6 cos a 6 = 0, 0! cos &!+... -f # 6 cos b 6 = 0, denote the screws perpendicular to the two directions of a and /3. In other words, these two equations define all the screws perpendicular to a given plane. 276. Screws at infinity. Let us now take the case where a, ft, 7 are three rectangular screws, and examine the conditions satisfied by 1} ..., 6 when subjected to the three following equations : #1 cos (&!+ ... + 6 cos a 6 = 0, 0! COS h + ... + 6 COS b 6 = 0, l COS G! + ... + 6 COS C 6 = 0. The screws which satisfy these conditions must all be perpendicular to the 192 292 THE THEORY OF SCREWS. [276, three directions of o, j3, 7. For real and finite rays this is impossible ; for real and finite rays could not be perpendicular to each of three rays which were themselves mutually rectangular. This is only possible if the rays denoted by 1} ... 6 K are lines at infinity. It follows that the three equations, L = 0; M=Q; N=Q, obtained by equating the three fundamental pitch invariants to zero, must in general express the collection of screws that are situated in the plane at infinity. We can write the three equations in an equivalent form by the six equations ., ,,COSi COS&j 7 COSCi 0i =/ + g- -+A- -, Pi Pi Pi n , cos a s cos 6 6 7 cos c 6 t/6 =/ - + g + fi - , Pa p 6 p s where f, g, h are any quantities whatever; for it is obvious that, by substi tuting these values for 1 , ... 6 in either L, or M, or N, these quantities are made to vanish by the formula of the type X cos a 6 cos 6 Pi We have, consequently, in the expressions just written for B lt ... 6 , the values of the co-ordinates of a screw which lies entirely in the plane at infinity. 277. Expression for the Pitch. It is known that if a, 0, 7 be the direction-angles of a ray, and if P, Q, R be its shortest perpendicular distances from three rectangular axes, then P sin a cos a + Q sin /3cosfi + R sin 7 cos 7 = 0. Let 77, , be three screws of zero pitch, which intersect at right angles, and let 6 be another screw, then, if vr^ be the virtual coefficients of 77 and 0, 2"5T,,0 = p 6 cos a P sin a, whence, by the theorem just mentioned, we have p e = Zvr^o cos a + 2tjy| e cos + 2^ cos 7. Let a 1} ... a 6 be the angles made by 77 with the six co-reciprocal screws of reference, then cos a = L = 6 1 cos a x + . . . + 6 cos a a , and, similarly, for the two other angles, cos yS = M= e i cos &J + ...+ 6 cos 6 6 , cos 7 = N = l cos d + . . . + B 6 cos c 6 , 277] EM AN ANTS AND PITCH INVARIANTS. 293 and L 2 + M 2 -\- N*= 1, whence we have for the pitch the homogeneous ex pression It appears from this that the three equations, 57,0 = ; -GTf fl = ; Tf fl = 0, indicate that 6 must be one of a pencil of rays of zero pitch radiating from a point. The equations Z = ; lf=0; N=Q, define a screw of indeterminate pitch. Why the screws in the plane at infinity ( 46) should in general present themselves with indeterminate pitch is a point which requires some ex planation. The twist about such a screw, as around any other, consists, of course, of a rotation and a translation. If, however, the finite parts of the body are only to be moved through a finite distance, the amplitude of the twist must be infinitely small, for a finite rotation around an axis at infinity would, of course, imply an infinitely great displacement of parts of the body which were at finite distances. The amplitude of the rotation is therefore infinitely small, so that, if the pitch is finite, the displacement parallel to the axis of the screw is infinitely small also. It thus appears that the effect of a small twist about a screw of any finite pitch at infinity is to give the finite parts of the body two displacements, one of which is infinitely insig nificant as regards the other. We can therefore overlook the displacement due to the pitch, and consequently the pitch of the screw unless infinite is immaterial ; in other words, in so far as the screw is the subject of our investigation, its pitch is indeterminate. In like manner we can prove that a screw in the plane at infinity, when regarded as the seat of a wrench, must, when finite forces are considered, be regarded as possessing an indeterminate pitch. For, let the force apper taining to the wrench be of finite magnitude, then its effect on bodies at finite distances would involve a couple of infinite moment. It therefore follows that the force on the screw at infinity must be infinitely small if the effects of the wrench are finite. The moment of the couple on the screw of finite pitch is therefore infinitely small, nor is its magnitude increased by importation from infinity ; therefore, at finite distances, the effect of the couple part of the wrench may be neglected in comparison with that of the force part of the wrench. But the pitch of the screw is only involved so far as the couple is concerned ; and hence whatever be the pitch of the screw lying in the plane at infinity, its effect is inoperative so far as finite operations are concerned. 294 THE THEORY OF SCREWS. [277, There is here a phenomenon of duality which, though full of significance in non-Euclidian space, merely retains a shred of its importance in the space of ordinary conventions. A displacement, such as we have been considering, may of course arise either from a twist about a screw of infinite pitch at an indefinite distance, or a twist about a screw of indefinite pitch at an infinite distance. 278. A System of Emanants which are Pitch Invariants*. From the formula 2tzr a/3 = (p a + pp) cos (a/3) - d a $ sin (a/3), we obtain sin () = i (p a + p ft ) (a, ^ + . . . + 6 ^-J -I* ,-+...+* -}ft^}\ d/3, dftJ V JR. r or from symmetry We thus obtain an emanant function of the co-ordinates of a and /3 which expresses the product of the shortest distance between a and /8 into the sine of the angle between them. The evanescence of this emanant is of course the condition ( 228) that a and /3 intersect. This emanant is obviously a pitch invariant for each of the two screws involved. It will be a pitch invariant for a whatever be the screw /3. Let us take for /3 the first screw of reference so that & = 1; & = 0... /3 6 = 0. Then A (P*+PI\ da, \ \/R a ) must be a pitch invariant. It may be written 2 da, This article is due to Mi- A. Y. G. Campbell. 278] EM AN ANTS AND PITCH INVARIANTS. 295 but we know that the last term is itself a pitch invariant, and hence we have the following result. If Pa be the pitch of a screw a expressed in terms of the co-ordinates, and if R a denote the function a + ... + 2 + 2^0, cos (12) + ... = 1, then the several functions &_ _Pa da, remain unaltered if instead of j . . . a the co-ordinates of any other screw on the same straight line as a should be substituted. This is easily verified by the known formulae that if a be any screw and another screw on the same axis as a whose pitch is p a + ac, then x dR Q _ x dR 01 = ai + ^ 1 d^ i " 6 - a6 + 4p 6 da 6 whence - s - 2 + * ~ * + A> cos al CHAPTER XXL DEVELOPMENTS OF THE DYNAMICAL THEORY. 279. Expression for the Kinetic Energy. Let us suppose that a body of mass M is twisting around a screw a with the twist velocity a. It is obvious that the kinetic energy of the body must be the product of Md 2 and some expression which has the dimensions of the square of a linear magnitude. This expression has a particular geometrical significance in the Theory of Screws, and the symbols of the theory afford a representation of the expression in an extremely concise manner. Let 77 be the impulsive screw which corresponds to a as an instantaneous screw, the body being supposed to be perfectly unconstrained. As usual p a is the pitch of a and (a?/) is the angle between a and 77. From the formulae of 80 we have, where H is a common factor, H^ = + aa^; Hv]2 = a 2 ; #773 = + ba 3 ; Hr) 4 = - 6a 4 ; Hr) 5 = + ca & ; #77,3 = -ca 6 ; whence H [(771 + 7? 2 ) (! + 2 ) + (r; 3 + 774) (a 3 + a 4 ) + (775 + 77 6 ) (a fl + a e )] = a (! 2 - a/) + b (a 3 2 - a/) + c (a 5 2 - a 6 2 ) =p a and we obtain cos The kinetic energy is in " cos (an) cos * Trans. Roy. Irish Acad., Vol. xxxi. p. 99 (1896). 279, 280] DEVELOPMENTS OF THE DYNAMICAL THEORY. 297 which is the required expression for the kinetic energy. It is remarkable that the co-ordinates of the rigid body are introduced by the medium of the impulsive screw alone. 280. Expression for the Twist Velocity. If an impulsive wrench of unit intensity on a screw 77 be applied to a quiescent rigid body of unit mass which in consequence commences to twist about an instantaneous screw a, it is required to find the initial twist velocity a. The impulsive wrench may be replaced by component impulsive forces T]I, ,.. rj 6 on the six principal screws of inertia and component impulsive couples with moments 0%, atj^, br} 3 , 6774, crj 5 , cij s about those screws of inertia. The force ^ is expressed by the velocity it produces in the unit mass parallel to the direction of 77. The component twist velocity of a is di about the first principal screw, and accordingly the velocity of translation parallel to that screw is adaj. Hence we have but ! = ~-. T?I, cos (a?;) whence we obtain* cos (OCT?) f* . . _ v / P It will be noted that in this expression the co-ordinates of the rigid body are introduced through the medium of the impulsive screw alone. A special case arises when the impulsive wrench is a couple, in which case of course p^= oo . As the effect of an impulsive couple is to produce a pure rotation only, we must under these circumstances have p a = 0. Poinsot s well-known construction exhibits the axis of the initial rotation as the diameter of the mornental ellipsoid conjugate to the plane of the impulsive couple. As three conjugate diameters of an ellipsoid could not lie in the same plane, it follows that in the case of p^ = oo we can never have a and 77 at right angles. As p a is zero while cos (777) is not zero, we must have d infinite. This might have been inferred from the fact that as the intensity of the impulsive wrench was not zero while the pitch of the screw on which it lay was infinite, the moment of the impulsive couple was infinite and conse quently the initial twist velocity must be infinite. * Trans. Roy. Irish Acad., Vol. xxxi. p. 100 (1896). 298 THE THEORY OF SCREWS. [280- Unless in this exceptional case where p^ is infinite it is always true that when p a is zero, a and 77 are at right angles. It is universally true that when the impulsive screw and the instan taneous screw are at right angles (the body being quite free), the pitch of the instantaneous screw must be zero. For if p a were not zero when cos (a?;) was zero then a. must be zero. As some motion must result from the impulse (the mass of the body being finite) we must have p a infinite. The initial motion is thus a translation. Therefore the impulse must have been merely a force through the centre of gravity ; a and 77 must be parallel and cos (a?;) could not be zero. The expression for the kinetic energy in 279, cos assumes an indeterminate form when the impulsive wrench reduces to a couple. For we then have p a = 0, but as cos (a?;) is not zero the expression for v? ari , i.e. 2 {(POL + pj cos (CM?) - d ar , sin (arj)}, becomes infinite. The expression for the kinetic energy arising from an impulsive wrench of unit intensity on a screw 77 applied to a free body of unit mass which thereupon begins to twist with an instantaneous movement about a screw a has the concise form Po 281. Conditions to be fulfilled by two pairs of Impulsive and Instantaneous Screws. Let a be a screw about which a free rigid body is made to twist in consequence of an impulsive wrench administered on some other screw, 77. Let /3 be another instantaneous screw corresponding in like manner to as an impulsive screw. Then we have to prove that the two following formulas are satisfied * : cos^) cos W + ~To^ cos () = 2l Pa / \ w DT) / / i <- \ ** cos (ttq) cos (pt) * Proceedings of the Camb. Phil. Soc., Vol. ix. Part iii. p. 193. 282] DEVELOPMENTS OF THE DYNAMICAL THEORY. 299 To demonstrate the first of these formulae. Expand the left-hand side and it becomes ft + &) (17, + i + ,) (ft + ft) + (a + ,) (ft + ft) + ( B + a.) (ft + ft)}. But, as already shown, cos (a?;) cos (a?;) whence, by substitution, the expression reduces to + a (A + A) (i - 2 ) + a (! + a.,) (A - /3 2 ) + 6 (A + ft) (. - 4 ) + 6 (a. + a 4 ) (/8, - /3 4 ) + c (/3 6 + A) ( 5 - a e ) + c ( B + 6 ) (/3 5 - A) 4 + 2ca 5 /? 5 - To prove the second formula it is only necessary to note that each side reduces to It will be observed that these two theorems are quite independent of the particular screws of reference which have been chosen. 282. Conjugate Screws of Inertia. We have already made much use of the important principle that is implied in the existence of conjugate screws of inertia. If a be reciprocal to then must 17 be reciprocal to . This theorem implied the existence of some formula connecting -nr a f and CT^. We see this formula to be Pa Pft cos ewj cos We have now to show that if ^^ = 0, then must w a f = 0. Let us endeavour to satisfy this equation when tn-^ is zero otherwise than by making uj af zero. Let us make p a infinite, then -n^ will reduce to %p a cos (af ) (for we may exclude the case in which p ( is also infinite because in that case r af = 0, inasmuch as any two screws of infinite pitch are necessarily reciprocal). 300 THE THEORY OF SCREWS. [282, The formula becomes, when p a is very large, Pa- P? 1 / *-\ *-r r ura = - ~~ir. I p a cos (a|). cos(cc?7) cos(/3|) " In this case as the twist about a is merely a translation, we must have cos err) 1, so that is to vanish, but this cannot be secured by making p? zero, because that cannot happen without cos (/3) being zero, except the pitch of be infinite ( 280) which is the case already excluded. It is therefore necessary that cos (a) be zero, but this requires that a and be reciprocal, i.e. that vr a = 0. Let us now suppose that we try to satisfy the original equations by making OT^ = 0, pp = 0. Here again we find that Pfs = entails cos (/3) zero, except p$ = GO . This in general makes -CT^ infinite so that the equation is not satisfied. If a and were at right angles then no doubt the equation would be satisfied, but then -S7 a | is zero. We thus see that notwithstanding the special form of the fundamental equation ( 281) it implies no departure from the complete generality of the principle that whenever is^ is zero then must <r f be also zero. 283. A Fundamental Theorem. Let us suppose that a rigid body is either entirely free or constrained in any manner whatever. Let r) be an impulsive screw whose pitch p^ is not infinite. Let 77 " be the intensity of an impulsive wrench on that screw, it being understood that ?/" is to be neither zero nor infinity. Let a be the instantaneous screw about which the body, having been previously quiescent, will commence to twist with an instantaneous twist velocity a. It is also supposed that p a is neither zero nor infinity. Let be the impulsive screw similarly related to /9, and let the affiliated symbols have the corresponding significations and limitations. Let be the impulsive screw similarly related to 7, and let the affiliated symbols have the corresponding significations and limitations. The instantaneous movement of the body must necessarily be the same as if it had been quite free and had received in addition to the impulsive wrench of intensity 77 " on the screw rj, an impulsive wrench of intensity p" situated on some screw p belonging to the system of screws reciprocal to the freedom of the body. Let these two wrenches compound into a single wrench of intensity to " on a screw w. 283] DEVELOPMENTS OF THE DYNAMICAL THEORY. 301 Then we have ( 279), , cos (aco) Ct = CO - and also ( 278), Pi<*i f x p 2 a-2 x p (i a 6 f , &&gt;! = cos (&)), eo 2 = ~ cos (CLCO), . . . o> 6 = cos (aw). Pa Pa Pa But from the fact that to " is the resultant of ?/" and p" we must have by resolving along the screws of reference / / / / /// /// /// /// / / /// // /.\ CO C0 1 = T) 77J + P PI, CO C0 2 =T) 1J 2 + p p 2 , . . . CO CO = r) T] ti + p p 6 ...... (1), whence we obtain by substitution, >!! = W + p "pi, dp. 2 CL 2 = if" I* + p"p2, djOflOe = rj "r} 6 + p "p K . . .(ii). If we multiply the first of these equations by^/Su the second by^ 2 /3 2 , &c., and then add, we obtain as however p is on the reciprocal system we must have, except when p" = <x> to be subsequently considered, d^p^a^^r) "^^. In like manner, d2p 1 2 a 1 7i = >/" C3 Vr We shall similarly find ivi = r"^> faptfi* = ?"* } } ............... (Hi), l 1 = r^> 7^ 2 7i#i = ?""K I whence by multiplication But we have chosen the intensities rj ", % ", % " so that no one of them is either zero or infinity, whence T\P Sy ^ = OT iy OT far^ ........................... (iv). It remains to see whether this formula will continue to be satisfied in the cases excepted from this demonstration. Let us take the case in which p^ is infinite, which makes ^ ... infinite. We have in the case of p^ very large, ffr, cos (771) * = ~2p^> the equations (ii) become TJ"p^ cos (771 ) . T; "^,, cos (776) = Z = 302 THE THEORY OF SCREWS. [283, multiplying the equations severally by pi,2h> an d adding, we get dSpiXA = W Pi (Pi cos ("ni ) + & cos (772 )+...+ &j cos (176)) = ^"TSfa (since p^ is indefinitely large), whence we proceed as before and we see that the theorem (iii) remains true, even if p^ or p$ or pg be infinite. If p a be zero, then in general cos aeo is zero. But in this case p a -f- cos aw becomes d a the length of the perpendicular from the centre of gravity upon a. Hence we have and the proof proceeds as before so that in this case also the theorem holds good. Finally, let jj a be infinite, <u must then be of zero pitch and pass through the centre of gravity and dp a = CD ". We have o> 1 = cosai, o) 3 = cos so that the equations (i) become | a>" cos (ai ) = 77" rj l + p "pi , \u>" cos (ai ) = r) "t] 2 + p "p 2 , | w" cos (as ) = 7/"7? 3 + p^Vs, 2 <u/ " cos ( a 3 ) = 7y" 74 + p "pi, \<a>" COS (as) = r) "<r)- a + p "p 5 , \<o" COS (05) = ^ "^ + p"p s . Multiplying these equations by +a^ lt a/3 2 , +b/3 3 , 6/3 3 , ... and adding, we have | <o" [a (fa - /8 a ) cos (ai ) + b (j3 3 - /3 4 ) cos (as ) + c (/8 5 - /S 6 ) cos (as )] = 17 "^ Let a- be the screw belonging to the reciprocal system on which there is an impulsive wrench of intensity a " due to the reactions when an impulsive wrench is administered on . Then we have /3a/3i = ^ "^i + o-" o-j ; - $afi t = %" % z + o-"V 2 , whence /8a (fii y8 2 ) cos (ai ) = f " cos (|i ) cos (ai ) + a" cos (<ri ) cos (ai ), with similar expressions for the two other pairs, whence by addition /8 {a (fr - yS 2 ) cos (ai )+ b (/3 3 - /9 4 ) cos (as) + c (J3 S - yS 6 ) cos (as)] = %" cos (a|), for since a and a- are reciprocal and p a = oo we must have cos (a<r) = 0. 284] DEVELOPMENTS OF THE DYNAMICAL THEORY. 303 We thus obtain 1 / / and similarly whence 7 cos()_ tsr,, wiieuut; - ^ -- - -- = - COS (0 OT^ y or remembering that p a is infinite, j-/// 2L CTg * _ OT i0 fa " a V,y But we had already from (iii), whence we deduce that in this case also the formula remains true. We thus obtain the following general theorem. If 1), , be three impulsive screws and a, /3, 7 the three corresponding instantaneous screws, then in all cases, no matter how the movements of the body may be limited by constraints, the following formula holds good*: It is easily shown that this relation subsists when the correspondence between ?/ and a is of the more general type implied by the equations dU where U is any homogeneous function of the second degree in the co ordinates. 284. Case of a Constrained Rigid Body. Let 77 and be, as before, a pair of impulsive screws, and let a and ft be the corresponding pair of instantaneous screws. Let p be the screw on which a reaction is contributed by the constraints at the moment when the impulsive wrench is applied on 77. The movement of the body twisting about a is therefore the same as if it had been free, and one impulsive wrench had been imparted about 77 and another simultaneously about p, so that the following conditions are satisfied : * Trans. Eoy. Irish Acad., Vol. xxx. p. 575 (1894). 304 THE THEORY OF SCREWS. [284- Multiplying by p^, ...p (i a , respectively, and adding, we have <*Uaa = ^ "tff^ , where u^ = pftf + . . . + p<? <*<? ; because, as p belongs to the reciprocal system, we must have OT O = 0. Similarly, if we multiplied the six equations by p^i, ...p 6 /3 6 , respectively, and added, we should get, since p is reciprocal to /3 also, where u aft = p^a^ + . . . + p?a t . Eliminating d and rj " we have the concise result*, Uaa. &pT, ~ Ua^ar,. In a similar way we can deal with the pair of screws, /3 and , and by eliminating <r, the reaction of the constraints in this case, we obtain the result Finally, from these two equations we can eliminate w a/3 , and we obtain This formula is a perfectly general relation, connecting any two pairs of impulsive and instantaneous screws 77, a and , /3. It holds whether the body be free or constrained in any way whatever. If the body be perfectly free, then it is easy to show that it reduces to the result already found, viz. P* PP ooBfo) * cos(/3) 285. Another Proof. From the theory of impulsive and instantaneous screws in an n-system we know (97) that if a lf ... ct n be the co-ordinates of an instantaneous screw, then the co-ordinates i) 1} ... 17 w of the reduced impulsive screw may be deter mined as follows : tr w i 2 #,, = -* *- v a - Pn Multiplying severally by p l a l) ... p n a n , and adding, we have H^r,a = U aa . * Trans. Roy. Irish Acad., Vol. xxx. p. 573 (1894). 286] DEVELOPMENTS OF THE DYNAMICAL THEORY. 305 Multiplying similarly by p^P^, ...p n /3 n , and adding, Eliminating H, we find UaaVTpr, - Uafi Srar, = 0. We may also prove this formula by physical consideration. Let a, /3 be the two screws which correspond, as instantaneous screws, to 77 and , as impulsive screws. Let us take on the cylindroid a, @, a screw 9, which is conjugate to a with respect to inertia ( 81). Then, by known principles, the screw 6 so defined must be reciprocal to 77. Hence Prf& + ... +p n r) n n = Q. As, however, a and 6 are conjugate, we have also, since 6 is co-cylindroidal with a and , there must be relations of the kind Substituting these in the two previous equations, we get = ; = ; whence, as before, UaatVpT, U a ptff ayl = 0. 286. Twist Velocity acquired by an Impulse. From the fact that the twist velocity a. acquired by a free body in consequence of an impulsive wrench of unit intensity on a screw 77 is expressed ( 280) by the equation cos (otr?) a = - ^- L Pa we see that the second of the two formulae of 281 may be expressed thus : The proof thus given of this expression has assumed that the body is quite free. It is however a remarkable fact that this formula holds good whatever be the constraints to which the body is submitted. If the body receive the unit impulsive wrench on a screw 77, the body will commence to twist about . 20 306 THE THEORY OF SCREWS. [286- a screw a. But the initial velocity of the body in this case will not generally be cos (a.rj) +PO.- It may be easily shown to be But we have also whence in all cases /3-&PT, = O-57 a f . This formula is therefore much more general besides being more concise than that of 281. 287. System with Two Degrees of Freedom. Let A, B, C, X, &c., and A , B , C , X , &c., be two homographic systems of points on a circle. These correspond respectively to two homographic systems of screws on the cylindroid according to the method of representation in Chap. XII. Then it is known, from geometrical principles, that if any two pairs, such as A, A and B, B , be taken, the lines AB , BA intersect on a definite straight line, which is the axis of the homography. In general this axis may occupy any position whatever ; if, however, it should pass through 0, the pole of the axis of pitch, then the homography will assume a special type which it is our object to investigate. In the first place, we may notice that under these circumstances the homography possesses the following characteristic : Let A, B be two screws, and A , B their two correspondents ; then, if A be reciprocal to B , B must be reciprocal to A . For in this case AB must pass through 0, and therefore BA must pass through also, i.e. B and A must be reciprocal. This cross relation suggests a name for the particular species of homo graphy now before us. The form of the letter ^ indicates so naturally the kind of relation, that I have found it convenient to refer to this type of homography as Chiastic. No doubt, in the present illustration I am only discussing the case of two degrees of freedom, but we shall presently see that chiastic homography is significant throughout the whole theory. 288. A Geometrical Proof. It is known that in the circular representation the virtual coefficient of two screws is proportional to the perpendicular distance of their chord from the pole of the axis of pitch ( 61). 290] DEVELOPMENTS OF THE DYNAMICAL THEORY. 307 Let a, ft, 7 be three screws of one system, and let 77, f, be the three corresponding screws, and, as usual, let r a f represent the virtual coefficient of a and . Then whenever the homography is chiastic : This is geometrically demonstrated when the following theorem is proved : If six points be inscribed on a circle, then the continued product of the three perpendiculars let fall from any point in a Pascal line formed from these six points upon three alternate sides of the corresponding hexagon is equal to the continued product of the three perpendiculars let fall from the same point on the other three sides. Let act , ft ft , 77 be the three pairs of sides, and write the equation afty = a ft y , then this represents a cubic curve through the nine points a a , aft , ..., and this cubic can only be the circle and the Pascal line. 289. Construction of Chiastic Homography on the Cylindroid. It is first obvious that, if two corresponding pairs of screws be arbitrarily selected, it will always be possible to devise one chiastic homography of which those two pairs are corresponding members. The circular construction shows this at once for, join AB and A B, they intersect at T, then the line TO is the homographic axis, and the correspondent to X is found by drawing A X, and then AX through the intersection of A X and OT. 290. Homographic Systems on Two Cylindroids. The fundamental theorem for the two cylindroids is thus expressed : Take any two screws, ct and ft, on one cylindroid, and any two screws, 77 and , on the other, it will then be possible to inscribe one, and in general only one chiastic homography on the two surfaces, such that a and rj shall be correspondents, and also ft and . For, write the general equation If, then, a, ft, 77, are known, and if 7 be chosen arbitrarily on the first cylindroid, it will then be always possible to find one, but only one, screw on the second cylindroid which satisfies the required condition. If a body had two degrees of freedom expressed by a cylindroid A, and if an arbitrary cylindroid B were taken, then an impulsive wrench ad ministered by any screw on B would make the body commence to twist 202 308 THE THEORY OF SCREWS. [290- about some corresponding screw on A, and the two systems of screws would have chiastic homography. If the body were given both in constitution and in position, then, of course, there would be nothing arbitrary in the choice of the corresponding screws. Suppose, however, that a screw i) had been chosen arbitrarily on B to correspond to a screw a on A, it would then be generally possible to design and place a rigid body so that it should begin to twist about a in consequence of the impulse on ??. There would, however, be no arbitrary element remaining in the homography. Thus, we see that, while for homography, in general, three pairs of correspondents can be arbitrarily assigned, there can only be two pairs so assigned for chiastic homography, while for such a particular type as that which relates to impulsive screws and the corresponding instantaneous screws, only one pair can be arbitrarily chosen. 291. Case of Normal Cylindroids. We have already had occasion ( 118), to remark on the curious relation ship of two cylindroids when a screw can be found on either cylindroid which is reciprocal to all the screws on the other. If, for the moment, we speak of two such cylindroids as " normal," then we have the following theorem : Any homography of the screws on two cylindroids must be chiastic if the two cylindroids are normal. Let a, /3, 7 be any three screws on one cylindroid, and 77, , any three screws on the other ; then, since the cylindroids are normal, we have whence we obtain GJ >f ( /nr af 5J 0i) 5 J "yf sf at af P 1s yr,) = , unless therefore is reciprocal to /3, we must have SJ a^^ SJ-yf ^a^ft^yyt = 0. If, however, had been reciprocal to /3, then one of these screws (suppose /3) must have been the screw on its cylindroid reciprocal to the entire group of screws on the other cylindroid. In this case we must have 5% = ; ts p$ = 0, so that even in this case it would still remain true that . = 0. It is, indeed, a noteworthy circumstance that, for any and every three pairs of screws on two normal cylindroids, the relation just written must be fulfilled. 292] DEVELOPMENTS OF THE DYNAMICAL THEORY. 309 In general, when two pairs of screws are given on two cylindroids, the chiastic homography between the surfaces is determined. If, however, it were possible to determine two chiastic homographies having two pairs in common, then every homography is chiastic, and the cylindroids are normal. Let a, 77 and ft, be the two pairs of correspondents, and let 7 have the correspondents and , then we have whence " i.e. the two cylindroids are normal. 292. General Conditions of Chiastic Homography. We shall now discuss the relations of chiastic homography between two systems of screws in the same w-system. The first point to be demonstrated is, that in such a case every pair of the double screws are reciprocal. Take a and (3 as two of the double screws, and 77 and will coincide with them ; whence the general condition, becomes = 0. One or other of these factors must be zero. We have to show that in general it is impossible for to vanish. For, take 7 reciprocal to a but not to ft, then r av = ; but OT^ Y is not zero, and therefore -sr a f would have to be zero ; in other words f must be reciprocal to a. But this cannot generally be the case, and hence the other factor must vanish, that is UTaft = 0. In like manner it can be shown that every pair of the double screws must be reciprocal. Conversely it can be shown that if the double screws of two homo- graphic systems are co-reciprocal, then the homography is chiastic. Let the w-double screws of the two systems be taken as the screws of reference ; then if one screw in one system be denoted by the co-ordinates !, ... On, 310 THE THEORY OF SCREWS. [292, its correspondent in the other system will be XAj !, ... \h n ct n . Similarly, the correspondent to &, ... /3 n will have for its co-ordinates Mi/Si, Mn/3n, and the correspondent to 7i> 7n will have for its co-ordinates where A,, /n, v, are the constants requisite to make the co-ordinates fulfil the fundamental conditions as to dimensions. We thus compute and similarly for the other terms. Whence, by substitution, we find the following equation identically satisfied : It may be noted that, in a three-system, two homographies are chiastic when, in the plane representation by points, the double points of the two systems form a triangle which is self-conjugate with respect to the pitch conic. 293. Origin of the formulae of 281*. Let a be a screw about which a free rigid body is made to twist in consequence of an impulsive wrench administered on some other screw 77. Except in the case where a and 77 are reciprocal, it will always be possible (in many different ways) to design and place a rigid body so that two arbitrarily chosen screws a and 77 will possess the required relation. Let now /3 and be two other screws (not reciprocal) : we may consider the question as to whether a rigid body can be designed and placed so that a shall be the instantaneous screw corresponding to 77 as an impulsive screw, while ft bears the same relation to . It is easy to see that it will not generally be possible for a, /3, 77, to stand in the required relations. For, taking a and /3 as given, there are five * Proceedings of the Cambridge Phil. Soc. Vol. ix. Part iii. p. 193. 293] DEVELOPMENTS OF THE DYNAMICAL THEORY. 311 disposable quantities in the choice of rj, and five more in the choice of f. We ought, therefore, to have ten disposable co-ordinates for the designing and the placing of the rigid body. But there are not so many. We have three for the co-ordinates of its centre of gravity, three for the direction of its principal axes, and three more for the radii of gyration. The other circumstances of the rigid body are of no account for our present purpose. It thus appears that if the four screws had been chosen arbitrarily we should have ten conditions to satisfy, and only nine disposable co-ordinates. It is hence plain that the four screws cannot be chosen quite arbitrarily. They must be in some way restricted. We can show as follows that these restrictions are not fewer than two. Draw a cylindroid A through a, fi, and another cylindroid P through rj. Then an impulsive wrench about any screw &&gt; on P will make the body twist about some screw on A. As eo moves over P, so will its corre spondent 6 travel over A. It is shown in 125 that any four screws on P will be equianharmonic with their four correspondents on A, and that consequently the two systems are homographic. In general, to establish the homography of two cylindroids, three cor responding pairs of screws must be given ; and, of course, there could be a triply infinite variety in the possible homographies. It is, however, a somewhat remarkable fact that in the particular homography with which we are concerned there is no arbitrary element. The fact that the rigid body is supposed quite free distinguishes this special case from the more general one of 290. Given the cylindroids A and P, then, without any other considerations whatever, all the corresponding pairs are determined. This is first to be proved. If the mass be one unit, and the intensity of the impulsive wrench on &&gt; be one unit, then the twist velocity acquired by 6 is ( 280) cos (#&&gt;) ~~^~ where cos(#o>) denotes the cosine of the angle between the two screws and ft>, and where p g is the pitch of 6. If, therefore, p g be zero, then cos (#o>) must be zero. In other words, the two impulsive screws co ly o> 2 on P, which correspond to the two screws of zero pitch d l , 6 2 on A, must be at right angles to them, respectively. This will in general identify the correspondents on P to two known screws on A. We have thus ascertained two pairs of correspondents, and we can now determine a third pair. For if o> 3 be a screw on P reciprocal to # 2 , then its correspondent 3 will be reciprocal to o> 2 . Thus we have three pairs 6 lt 2 , # 3 on A, and their three correspondents co l , &&gt; 2 , o>, on P. This establishes the 312 THE THEORY OF SCREWS. [293- homography, and the correspondent 6 to any other screw &&gt; is assigned by the condition that the anharmonic ratio of (a^^co is the same as that of a a A A 1/11/2(73(7. Reverting to our original screws a and rj, ft and , we now see that they must fulfil the conditions when the quantities in the brackets denote the anharmonic ratios. It can be shown that these equations lead to the formulae of 281. 294. Exception to be noted. We have proved in the last article an instructive theorem which declares that when two cylindroids are given it is generally possible in one way, but in only one way, to correlate the several pairs of screws on the two surfaces, so that when a certain free rigid body received an impulse about the screw on one cylindroid, movement would commence by a twisting of the body about its correspondent on the other cylindroid. It is, however, easily seen that in one particular case the construction for correlation breaks down. The exception arises whenever the principal planes of the two cylindroids are at right angles. The two correspondents on P to the zero-pitch screws on A had been chosen from the property that when p a is zero the impulsive wrench must be perpendicular to a. We thus take the two screws on P which are respec tively perpendicular to the two zero-pitch screws. But suppose there are not two screws on P which are perpendicular to the two zero-pitch screws on A. Suppose in fact that there is one screw on P which is parallel to the nodal axis of A, then the construction fails. We would thus have a single screw on P with two corresponding instantaneous screws for the same body. This is of course impossible, and accordingly in this particular case, which happens when the principal planes of P and A are rectangular, it is impos sible to adjust the correspondence. 295. Impulsive and Instantaneous Cylindroids. Let X, X be two screws on a cylindroid whereof a and jB are the two principal screws. Let 0, 6 be the angles which X and X respectively make with a. We shall take the six absolute screws of inertia as the screws of reference and we have as the co-ordinates of X ! cos 6 + & sin 6, . . . a cos 6 + /3 6 sin 6, 295] DEVELOPMENTS OF THE DYNAMICAL THEORY. 313 and of X ! cos + & sin , ... a 6 cos & + /3 6 sin &. In like manner, let p and p be two screws on a cylindroid, of which the two principal screws are rj and f. Let <f>, < be the angles which p and p make respectively with . Then the co-ordinates of p are r) l cos </> + f j sin (j), ... rj 6 cos </> + 6 sin <, and of p 7?! cos </> + j sin </> , ... 77,3 cos + 6 sin < , &c. We shall now suppose that the two cylindroids a, /3 and 77, are so circumstanced that the latter is the locus of the impulsive wrenches cor responding to the several instantaneous screws on the former with respect to the rigid body which is to be regarded as absolutely free. We shall further assume that p is the impulsive screw which has X as its instantaneous screw, and that the relation of p to X is of the same nature. If, however, the four screws X, X , p, p possess the relations thus indi cated, it is necessary that they satisfy the conditions already proved ( 281). These are two-fold, and they are expressed by the following equations, as already shown : cos (\p ) + P,*,. cos (\p f ) = 2r A v, cos (\p) cos p\ p\ We shall arbitrarily choose X and p, so as to satisfy the conditions A /P = 0, tnv = 0, and thus the second of the two equations is satisfied. These two equations will give & as a function of <, and </> as a function of 6. We can thus eliminate & and < from the first of the two equations, and the result will be a relation connecting 6 and $. This equation will exhibit the relation between any instantaneous screw 6 on one cylindroid, and the corresponding impulsive screw </> on the other. It will be observed that when the two cylindroids are given, the required equation is completely denned. The homographic relations of p and X is thus completely determined by the geometrical relations of the two cylin droids. 314 THE THEORY OF SCREWS. [295, The calculation* presents no difficulty and the result is as follows : = cos 6 cos (f> + cos 6 sin (f> + sin 6 cos </> + sin 9 sin +p a cos cos - -S7 a cos cos (a??) [r a , cos (a) *3- j cos (a?;)] ***, [cos (a) cos (77) - cos (a?;) cos +p a cos r a , cos - OT a cos cos (a) [r a , cos (a) nr a f cos (CM?)] -GTpt [cos (a) cos (/ify) cos (arj) cos cos (at)) \ixfr cos (a) -BT^ cos (a?;)] + p a COS (77) [tjp, cos a, [cos (a) cos (/ify) cos (atj) cos + PP cos (a^) [or^, cos (a^) tsfc cos (a??)] cos / r p , cos - ^ j cos _+ ^-B3-a| [cos (af ) cos (firf) cos (a??) cos 296. An exceptional Case. A few remarks should be made on the failure of the correspondence when the principal planes of the two cylindroids are at right angles ( 294). It will be noted that though this equation suffers a slight reduction when the principal planes of the two cylindroids are at right angles yet it does not become evanescent or impossible. For any value of 6 defining a screw on one cylindroid, the equation provides a value of < for the correspondent on the other cylindroid. Thus we seem to meet with a contradiction, for while the argument of 294 shows that in such a case the homography is impossible, yet the homographic equation seemed to show that it was possible and indeed fixed the pairs of correspondents with absolute definiteness. It is certainly true that if two cylindroids A and P admit of the cor relation of their screws into pairs whereof those on P are impulsive screws and those on A are instantaneous screws, the pairs of screws by which the homographic equation is satisfied will stand to each other in the desired relation. If, however, the screws on two cylindroids be correlated into pairs in accordance with the indications of the homographic equation, though it will generally be true that there may be corresponding impulsive screws and instantaneous screws, yet in the case where the principal planes of the cylindroids are at right angles no such inference can be drawn. The case is a somewhat curious one. It will be seen that the calculation See Trans. Eoy. Irish Acad. Vol. xxx. p. 112 (1894). 296] DEVELOPMENTS OF THE DYNAMICAL THEORY. 315 of the homographic equation is based on the fact that if X, \ be two instantaneous screws and p, p the corresponding impulsive screws, then the formula COS (X + P * t , x COS (\p f ) = 2tsr AX , , t , x cos (X/o) cos \Kff) must be satisfied. And generally it is satisfied. In the case of two cylindroids with normal planes it is however easy to show that there are certain pairs of screws for which this formula cannot obtain. For in such a case there is one screw X on A which is perpendicular to every screw on P, so that whatever be the p corresponding to X, cos (\p) 0. Since no other screw X can be perpendicular to any screw on P we cannot have either cos (X p), or cos (A///), zero. Hence this equation cannot be satisfied and the argument that the homo- graphic equation defines corresponding pairs is in this case invalid. We might have explained the matter in the following manner. When the principal planes of A and P are normal there is one screw X on A which is perpendicular to all the screws on P. If therefore the two cylindroids were to be impulsive and instantaneous, there must be a screw on P which corresponds to X. It can be shown in general ( 301) that d\ = p\ tan (X0) when dx is the perpendicular from the centre of gravity on X; it follows that when (A.0) = 90 we must have either p^ zero or d\ infinite. But of course it will not generally be the case that X. happens to be one of the screws of zero pitch on A. Hence we are reduced to the other alternative d*. = infinity. This means that the centre of gravity is to be at infinity. But when the centre of gravity of the body is at infinity a remarkable consequence follows. All the instantaneous screws must be parallel. For if 6 be the impulsive wrench corresponding to X as the instantaneous screw, then we know that di=p*. tan(X0), and that the centre of gravity lies in a right line parallel to X and distant 316 THE THEORY OF SCREWS. [296- from it by d^. In like manner if </> be an impulsive screw corresponding to yu, as instantaneous screw we have another locus parallel to p for the centre of gravity. But as the centre of gravity is at infinity these two loci must there intersect, i.e. they must be parallel and so must X and fi, and hence all instantaneous screws must be parallel. Thus we see that all the screws on A must be parallel, i.e. that A must have degraded into an extreme type of cylindroid. 297. Another extreme Case. .Given any two cylindroids A and P it is, as we have seen, generally possible to correlate in one way the several screws on A to those on P so that an impulsive wrench given to a certain rigid body about any screw on P would make that body commence to move by twisting about its cor respondent on A. One case of failure has just been discussed. The case now to be considered is not indeed one of failure but one in which any two pairs of screws on A and P will stand to each other in the desired relations. Suppose that A and P happened to fulfil the single condition that each of them shall contain one screw which is reciprocal to the other cylindroid. We have called the cylindroids so circumstanced " normal." Let A, be the screw on A which is reciprocal to every screw on P. If then P and A are to stand to each other in the required relation, A. must be reciprocal to its impulsive screw. But this is only possible on one condition. The mass of the body must be zero. In that case, if there is no mass involved any one of the screws on P may be the impulsive screw corresponding to any one of the screws on A . Here again the question arises as to what becomes of the homographic equation which defines so precisely the screw on P which corresponds to the screws on A ( 295). It might have been expected that in the case of two normal cylindroids this homographic equation should become evan escent. But it does not do so. But there is no real contradiction. The greater includes the less. If every screw on P will suit as correspondent every screw on A then d fortiori will the pairs indicated by the homography fulfil the conditions requisite. That any two pairs of screws will be correspondents in this case is obvious from the following. 298] DEVELOPMENTS OF THE DYNAMICAL THEORY. 317 Let X be the screw on A which is reciprocal to P, S .................. P ........................ A. Then any screw //, on A and any screw cj> on P fulfil the conditions WA$ = 0, TOV,, = 0. Hence < is the impulsive screw corresponding to fj, as the instantaneous screw. 298. Three Pairs of Correspondents. Let a, T\\ ft, J; ; 7, be three pairs of impulsive and instantaneous screws ; let 9, </> be another pair. Then, if we denote by L a p = 0, and M a p = 0, the two fundamental equations C08 Pa Pfi cos (XT ** ~ cos we shall obtain six equations of the type L 6a = 0, L 9li = 0, L^ = 0, Jlfe a = 0, Jlftf = 0, M ey = 0. From these six it might be thought that <f> lt ... < 6 could be eliminated, and thus it would, at first sight, seem that there must be an equation for 6 to satisfy. It is, however, obvious that there can be no such condition, for 6 can of course be chosen arbitrarily. The fact is, that these equations have a peculiar character which precludes the ordinary algebraical inference. Since ,;; ft, ; 7, ; are three pairs of screws, fulfilling the necessary six conditions, a rigid body can be adjusted to them so that they are respectively impulsive and instantaneous. We take the six principal screws of inertia of this body as the screws of reference. We thus have, where p a , pp, p y are certain factors, By putting the co-ordinates in this form, we imply that they satisfy the six equations of condition above written. Substituting the co-ordinates in L 0a = 0, we get = + (a, + a 2 ) (pefa + p 9 fa) + (a, + a,) (p e <f> 3 + p e $ t ) + ( + a.) (p e <j> t + (0i + 0a) (ai - 2> + (0 + 04> (b<*> ~ 6*4) + (0 5 + 6 ) (c 8 - ca 6 ) - 2 (aa^ - a^6 2 ) - 2 (6o0 - ba,e 4 ) - 2 (c 5 ^ 5 - ca,0). 318 THE THEORY OF SCREWS. [298, Let ! a6 l = X ly 4 4- 6# 4 = X t , c0 6 = X 6 , and the equation becomes = (! + 2 ) (X, + X,} + ( 3 + 4 ) (X 3 and the two other L equations give = (A + &) (X, + X 2 ) + (0, + &) (X 3 = (71 + 7 5 + 6 ) (X 5 + X 6 ) ; /3 6 ) (X, a) + (73 + 74) (-^s + -^4) + (75 4- 7 6 ) (X s + X 6 ). If we eliminate X^ + X i} X 3 + X t , X S + X S from these equations, we should have = Otj + 85 0(3 + 4 Qfg + Ct 6 A 4/3, & 4- A & 4 7i +7s 7s + 74 7s + 7e But this would only be the case if a, /3, 7 were parallel to a plane, which is not generally true. Therefore, we can only satisfy these equations, under ordinary circumstances, by the assumption In like manner, the equations of the M type give Pa^Or, = 0, Substituting, in the first of these, we get - p a (017! 0j - a?? 2 ^ 2 4- br} 3 3 - 6774 4 + cv) s s - cy^e) = ; which reduces to ac^Zj - a 2 Z 2 + ba 3 X s - 6a 4 Z 4 + ca s X s - ca 6 X e = ; but we have already seen that X^ -+ X 2 = 0, &c., whence we obtain Xi (a! + aoz) + X 3 (6a 3 + 6 4 ) + X 5 (c 6 + ca 6 ) = ; with the similar equations X l (a/9, + a/8 2 ) + X 3 (b/3 3 + bfr) + X 5 (cyS 5 + c&) = 0, ^! (ay l + ay 2 ) + X 3 (by, + by 4 ) + X 5 (c% + cy 6 ) = 0. These prove that, unless a, @, y be parallel to a plane, we must have 299] DEVELOPMENTS OF THE DYNAMICAL THEORY. 319 X 1 = 0, X 3 = 0, X s = 0. Combining these conditions with the last, we draw the general conclusion that or &c. Thus we demonstrate that if a pair of screws 6, $> satisfy the six conditions, they stand to each other in the relation of impulsive screws and instantaneous screws. 299. Cylindroid Reduced to a Plane. Suppose that the family of rigid bodies be found which make a, 77 and /?, impulsive and instantaneous. Let there be any third screw, 7, and let us seek for the locus of its impulsive screw, , for all the different rigid bodies of the family. must satisfy the four equations cos (777) + / cos (a?) = 2sr ay , cos (arj) cos -^008(^0 = COS (yC) cos (ar;) Y>) cos As there are four linear equations in the coordinates of , we have the following theorem. If a, 77 and /3, f be given pairs of impulsive and instantaneous screws, then the locus of the impulsive screw corresponding to 7, as an instan taneous screw, is a cylindroid. But this cylindroid is of a special type. It is indeed a plane surface rather than a cubic. The equations for can have this form : cos (a?) = A cos (yf), vr a( = C cos (y ), COS (f ) = B COS (y), CT^ = D COS (yf ), in which A, B, C, D are constants. The fact that cos (af) and cos (7^) have one fixed ratio, and cos (/3) and cos (yf) another, shows that the direction of is fixed. The cylindroidal locus of , therefore, degenerates to a system of parallel lines. At first it may seem surprising to find that CT of is constant. But the 320 THE THEORY OF SCREWS. [299- necessity for this arrangement is thus shown. If not constant, then there would generally have been some screw , for which tsr a ^ was zero. In this case, of course, ^ yn would be generally zero also. But 7 and tj being both given, this is of course not generally true. The only escape is for r af to be constant. 300. A difficulty removed. Given a and 77, @ and and also 7, then the plane of is determined from the equations of the last article. As OT a and ts^ are constant, both a and /3 must be parallel to the plane already considered. But as an impulsive screw could not be reciprocal to an instantaneous screw, it would seem that w y ^ must never be zero, but this condition can only be fulfilled by requiring that must be parallel to the same plane. Whence a, /3, 7 must be parallel to the same plane. But these three screws are quite arbitrary. Here then would seem to be a contradiction. The difficulty can be explained as follows : Each rigid body, which conformed to the condition that a, /3 and 77, f shall be two pairs of corresponding impulsive and instantaneous screws, will have a different screw corresponding to a given screw 7. Thus, among the various screws , in the degraded cylindroid, each will correspond to one rigid body. In general, of course, it would be impossible for f to be reciprocal to 7. It would be impossible for an impulsive wrench to make a body twist about a screw reciprocal thereto. Nevertheless, it seemed certain that, in general, there must be a screw reciprocal to 7. For otherwise, a, /3, 7 should be all parallel to a plane, which, of course, is not generally true. If, however, a, or b, or o were zero, then the body will have no mass ; consequently no impulse would be necessary to set it in motion. This clearly is the case when is reciprocal to 7. We have thus got over the difficulty. and 7 are reciprocal, in the case when the rigid body is such that a, or 6, or c is zero. 301. Two Geometrical Theorems. The perpendicular from the centre of gravity on any instantaneous screw is parallel to the shortest distance between that instantaneous screw and the corresponding impulsive screw. The perpendicular from the centre of gravity on any instantaneous screw is equal to the product of the pitch of that screw, and the tangent of the angle between it and the corresponding impulsive screw. 301] DEVELOPMENTS OF THE DYNAMICAL THEORY. 321 Let a be the instantaneous screw and d a the length of the perpendicular thereon from the centre of gravity. If cos A,, cos /i, cos v be the direction cosines of d a then d a cos X = ( 5 - a 6 ) (a, + 4 ) c - ( 5 + a 6 ) ( 3 - o 4 ) b, d a cos /*=(!- 2 ) (a, + a e )a- fa + o^) (a 5 - 6 ) c, d a cos v = ( 3 4 ) (ttj + a 2 ) & ( 3 + 4 ) (i 2 ) a. But if 77 is the impulsive screw corresponding to a as the instantaneous screw we have ! = - ^-\*hi -C& 2 = - ^ N^"> &C., &C., cos (a?;) cos (a?;) whence *) da COS X = CQS Y . ((T/., + 77 fi ) (173 + 4 ) - ( 5 + e) (173 + 1; 4 )), 2) rf a cos /^ = / ?. ((% + 7? 2 ) ( 5 + 6 ) - (! + 2 ) (775 + 77 6 )), d COS " = ^T~\ (^s + ^4> (i + On) - (s + 4 ) (77! + 77 2 )). COo \Jjiij} But (% + %) ( 3 + 4 ) - ( B + 6> (?3 + 7 4 ) = sin (077) cos X , with similar expressions for sin (0(77) cos /* and sin (377) cos v where cos X , cos p, and cos v are the direction cosines of the common perpendicular to and 77. We have therefore v d a cos X = v r sin (an) cos X , cos in d a coKu,= ~ . sin (77)cos /A cos (at}) rn d a cos v = *? - sin (a77) cos v, cos (277) whence cos X = cos X ; cos /it = cos pf ; cos v cos v ; and d a = p a tan (77), which proves the theorems. B. 21 CHAPTER XXII. THE GEOMETRICAL THEORY*. 302. Preliminary. IT will be remembered how Poinsot advanced our knowledge of the dynamics of a rigid system by a beautiful geometrical theory of the rotation of a rigid body about a fixed point. We now specially refer to the geometrical construction by which he determined the instantaneous axis about which the body commenced to rotate when the plane of the instantaneous couple was given. We may enunciate with a generality, increasing in successive steps, the problem which, in its simplest form, Poinsot had made classical. From the case of a rigid body which is constrained to rotate about a fixed point we advance to the wider conception of a body which has three degrees of freedom of the most general type. We can generalize this again into the case in which the body, instead of having a definite number of degrees of freedom has any number of such degrees. The range extends from the first or lowest degree, where the only movement of which the body is capable is that of twisting about a single fixed screw, up to the case in which the body being perfectly free, or in other words, having six degrees of freedom, is able to twist about every screw in space. It will, of course, be borne in mind that only small movements are to be understood. In a corresponding manner we may generalize the forces applied to the body. In the problem solved by Poinsot the effective forces are equivalent to a couple solely. For the reaction of the fixed point is capable of reducing any system of forces whatever to a couple. But in the more generalized problems with which the theory of screws is concerned, we do not restrict the forces to the specialized pair which form a couple. We shall assume that the forces are of the most general type and represented by a wrench upon a screw. Thus, by generalizing the freedom of the rigid body, as well as the forces which act upon it, we may investigate the geometrical theory of the motion when a rigid body of the most general type, possessing a certain number of degrees of freedom of the most general type, is disturbed from a * Trans. Royal Irish Acad. Vol. xxi. (1897) p. 185. 302, 303] THE GEOMETRICAL THEORY. 323 position of rest by an impulsive system of forces of the most general type. This is the object of the present chapter. 303. One Fair of Impulsive and Instantaneous Screws. Let it be supposed that nothing is known of the position, mass, or other circumstances of an unconstrained rigid body save what can be deduced from the fact that, when struck from a position of rest by an impulsive wrench on a specified screw 77, the effect is to make the body commence to move by twisting around a specified screw a. As a, like every other screw, is defined by five coordinates, the knowledge of this screw gives us five data towards the nine data that are required for the complete specification of the rigid body and its position. We have first to prove that the five elements which can be thence inferred with respect to the rigid body are in general (1) A diameter of the momental ellipsoid. This is clearly equivalent to two elements, inasmuch as it restricts the position of the centre of gravity to a determinate straight line. (2) The radius of gyration about this diameter. This is, of course, one element. (3) A straight line in the plane conjugate to that diameter. A point in the plane would have been one element, but a straight line in the plane is equivalent to two. If the centre of gravity were also known, we should at once be able to draw the conjugate plane. Draw a plane through both the instantaneous screw a and the common perpendicular to a and 77. Then the centre of gravity of the rigid body must lie in that plane ( 301). It was also shown that if p a be the pitch of a, and if (ar)) represent the angle between a and 77, then the perpendicular distance of the centre of gravity from a. will be expressed by p a tan ((277) ( 301). This expression is completely known since a and 77 are known. Thus we find that the centre of gravity must lie in a determinate ray parallel to a. There will be no ambiguity as to the side on which this straight line lies if it be observed that it must pass between a and the point in which 77 is met by the common perpendicular to 77 and a. In this manner from knowing a and 77 we discover a diameter of the momental ellipsoid. If a be the twist velocity with which a rigid body of mass M is twisting about any screw a. If 77 be the corresponding impulsive screw, and if Ts ar> denote as usual the virtual coefficient of a and 77, then it is proved in 279 that the kinetic energy of the body MCt 2 -, r GJ an- cos (077) 212 324 THE THEORY OF SCREWS. [303- We can now determine the value of p a * where p a is the radius of gyration about an axis parallel to a through the centre of gravity. For the kinetic energy is obviously P/d a (/t>a a +^. 2 + a 2 )- By equating the two expressions we have a 2 = 2 cos But when a and rj are known the three terms on the right-hand side of this equation are determined. Thus we learn the radius of gyration on the diameter parallel to a. It remains to show how a certain straight line in the plane which is conjugate to this diameter in the momental ellipsoid is also determined. Let a screw 6, of zero pitch, be placed on that known diameter of the momental ellipsoid which is parallel to or. Draw a cylindroid through the two screws 6 and 77. Let </> be the other screw of the zero pitch, which will in general be found on the same cylindroid. We could replace the original impulsive wrench on 77 by its two com ponent wrenches on any two screws of the cylindroid. We choose for this purpose the two screws of zero pitch 6 and <. Thus we replace the wrench on 77 by two forces, whose joint effect is identical with the effect that would have been produced by the wrench on 77. As to the force along the line 6 it is, from the nature of the con struction, directed through the centre of gravity. Such an impulsive force would produce a velocity of translation, but it could have no effect in pro ducing a rotation. The rotatory part of the initial twist velocity must there fore be solely the result of the impulsive force on <. But when an impulsive force is applied to a quiescent rigid body we know, from Poinsot s theorem, that the rotatory part of the instantaneous movement must be about an axis parallel to the direction which is conjugate in the momental ellipsoid to the plane which contains both the centre of gravity and the impulsive force. It follows that the ray (f> must be situated in that plane which is conjugate in the momental ellipsoid to the diameter parallel to a. But, as we have already seen, the position of </> is completely defined on the known cylindroid on which it lies. We have thus obtained a fixed ray in the conjugate plane to a known diameter of the momental ellipsoid. The three statements at the beginning of this article have therefore been established. We have, accordingly, ascertained five distinct geometrical data towards the nine which are necessary for the complete specification of the rigid body. These five data are inferred solely from our knowledge of a single pair of corresponding impulsive and instantaneous screws. 305] THE GEOMETRICAL THEORY. 325 304. An Important Exception. If p a = 0, then (a?;) is 90, and consequently p a tan (a?;) is indefinite. If, therefore, the pitch of the instantaneous screw be zero, then we are no longer entitled to locate the centre of gravity in a certain ray. All we know is that it lies in the plane through a perpendicular to 77. In general the knowledge of the impulsive screw corresponding to a given instantaneous screw implies five data, yet this ceases to be the case if p a is zero, for as 77 must then be perpendicular to a there are really only four independent data given when 77 is given. We have, therefore, in this case one element the less towards the determination of the rigid body. 305. Two Pairs of Impulsive and Instantaneous Screws. Let us next suppose that we are given a second pair of corresponding impulsive and instantaneous screws. We shall examine how much further we are enabled to proceed by the help of this additional information towards the complete determination of the rigid body in its abstract form. Any data in excess of nine, if not actually impossible, would be superfluous. If, therefore, we are given a second pair of impulsive and instantaneous screws, the five data which they bring cannot be wholly independent of the five data brought by the preceding pair. It is therefore plain that the quartet of screws forming two pairs of corresponding impulsive screws and instantaneous screws cannot be chosen arbitrarily. They must submit to at least one purely geometrical condition, so that the number of data independent of each other shall not exceed nine. It is, however, not so obvious, though it is certainly true, as we found in 281, that the two pairs of screws must conform not merely to one, but to no less than two geometrical conditions. In fact, if 77, be two impulsive screws, and if a, /3 be the two corresponding instantaneous screws, then, when the body acted upon is perfectly free, the following two formulae must be satisfied : P Pf* cos + cos cos (a??) cos We can enunciate two geometrical properties of the two pairs of screws, which are equivalent to the conditions expressed by these equations. In the first place, each of the pairs of screws determines a diameter of the momental ellipsoid. The fact that the two diameters, so found, must intersect each other, is obviously one geometrical condition imposed on the system a, 77 and /3, . 326 THE THEORY OF SCREWS. [305, Let G be this intersection, and draw OP parallel to a and equal to the radius of gyration about GP, which we have shown to be known from the fact that a and ij are known. Let X be the plane conjugate to GP in the moraental ellipsoid, then this plane is also known. In like manner, draw GQ parallel to ft and equal to the radius of gyration about GQ. Let Y be the plane, conjugate to GQ, in the momental ellipsoid. Let PI and P 2 be the perpendiculars from P, upon X and Y respec tively. Let Q l and Q 2 be the perpendiculars from Q, upon X and Y respec tively. Then, from the properties of the ellipsoid, it is easily shown that PI ^2 = Qi Qv This is the second geometrical relation between the two pairs of screws a, ?; and ft, . Subject to these two geometrical conditions or to the two formulse to which they are equivalent the two pairs of screws might be chosen arbitrarily. As these two relations exist, it is evident that the knowledge of a second pair of corresponding impulsive screws and instantaneous screws cannot bring five independent data as did the first pair. The second pair can bring no more than three. From our knowledge of the two pairs of screws together we thus obtain no more than eight data. We are consequently short by one of the number requisite for the complete specification of the rigid body in its abstract form. It follows that there must be a singly infinite number of rigid bodies, every one of which will fulfil the necessary conditions with reference to the two pairs of screws. For every one of those bodies a is the instantaneous screw about which twisting motion would be produced by an impulsive wrench on 77. For every one of those bodies ft is the instantaneous screw about which twisting motion would be produced by an impulsive wrench on f. 306. A System of Rigid Bodies. We have now to study the geometrical relations of the particular system of rigid bodies in singly infinite variety which stand to the four screws in the relation just specified. Draw the cylindroid (a, ft) which passes through the two screws a and ft. Draw also the cylindroid (q, ) which passes through the two corresponding impulsive screws 17 and It is easily seen that every screw on the first of these cylindroids if regarded as an instantaneous screw, with respect to the same rigid body, will have its corresponding impulsive screw on the second 306] THE GEOMETRICAL THEORY. 327 cylindroid. For any impulsive wrench on (77, ) can be decomposed into impulsive wrenches on 77 and . The first of these will generate a twist velocity about a. The second will generate a twist velocity about /3. These two can only compound into a twist velocity about some other screw on the cylindroid (a, /3). This must, therefore, be the instantaneous screw corre sponding to the original impulsive wrench on (77, ). It is a remarkable point about this part of our subject that, as proved in 293, we can now, without any further attention to the rigid body, corre late definitely each of the screws on the instantaneous cylindroid with its correspondent on the impulsive cylindroid. We thus see how, from our knowledge of two pairs of correspondents, we can construct the impulsive screw on the cylindroid (77, ) corresponding to every screw on the cylindroid (a, /3). It has been already explained in the last article how a single known pair of corresponding impulsive and instantaneous screws suffice to point out a diameter of the momental ellipsoid, and also give its radius of gyration. A second pair of screws will give another diameter of the momental ellipsoid, and these two diameters give, by their intersection, the centre of gravity. As we have an infinite number of corresponding pairs, we thus get an infinite number of diameters, all, however, being parallel to the principal plane of the instantaneous cylindroid. The radius of gyration on each of these diameters is known. Thus we get a section 8 of the momental ellipsoid, and we draw any pair of conjugate diameters in that section. These diameters, as well as the radius of gyration on each of them, are thus definitely fixed. When we had only a single pair of corresponding impulsive and instan taneous screws, we could still determine one ray in the conjugate plane to the diameter parallel to the instantaneous screw. Now that we have further ascertained the centre of gravity, the conjugate plane to the diameter, parallel to the instantaneous axis, is completely determined. Every pair of corresponding impulsive and instantaneous screws will give a conjugate plane to the diameter parallel to the instantaneous screw. Thus we know the conjugate planes to all the diameters in the plane S. All these planes must intersect, in a common ray Q, which is, of course, the conjugate direction to the plane S. This ray Q might have been otherwise determined. Take one of the two screws, of zero pitch, in the impulsive cylindroid (77, ). Then the plane, through this screw and the centre of gravity, must, by Poinsot s theorem already referred to, be the conjugate plane to some straight line in S. Similarly, the plane through the centre of gravity and the other screw of zero pitch, on the cylindroid (77, ), will also be the conjugate plane to some 328 THE THEORY OF SCREWS. [306 ray in S. Hence, we see that the ray Q must lie in each of the planes so constructed, and is therefore determined. In fact, it is merely the transversal drawn from the centre of gravity to intersect both the screws of zero pitch on the cylindroid (77, ). We have thus proved that when two pairs of corresponding impulsive screws and instantaneous screws are given, we know the centre of the momental ellipsoid, we know the directions of three of its conjugate diameters, and we know the radii of gyration on two of those diameters. The radius of gyration on the third diameter remains arbitrary. Be that radius what it may, the rigid body will still fulfil the condition rendering a, ?? ond /3, | respective pairs of instantaneous screws and impulsive screws. We had from the first foreseen that the data would only provide eight coordinates, while the specification of the body required nine. We now learn the nature of the undetermined coordinate. It appears from this investigation that, if two pairs of impulsive screws and the corresponding instantaneous screws are known, but that if there be no other information, the rigid body is indeterminate. It follows that, if an impulsive screw be given, the corresponding instantaneous screw will not generally be determined. Each of the possible rigid bodies will have a different instantaneous screw, though the impulsive screw may be the same. It was, however, shown ( 299), that all the instantaneous screws which pertain to a given impulsive screw lie on the same cylindroid. It is a cylindroid of extreme type, possessing a screw of infinite pitch, and degenerating to a plane. Even while the body is thus indeterminate, there are, nevertheless, a system of impulsive screws which have the same instantaneous screw for every rigid body which complies with the expressed conditions. Among these are, of course, the several screws on the impulsive cylindroid (rj. f) which have each the same corresponding screw on the instantaneous cylin droid (a, /3), whatever may be the body of the system to which the impulsive wrench is applied. But the pairs of screws on these two cylindroids are indeed no more than an infinitesimal part of the total number of pairs of screws that are circumstanced in this particular way. We have to show that there is a system of screws of the fifth order, such that an impulsive wrench on any one of those screws rj will make any body of the system com mence to twist about the same screw a. As already explained, the system of rigid bodies have a common centre of gravity. Any force, directed through the centre of gravity, will produce a linear velocity parallel to that force. This will, of course, apply to every body of the system. All possible forces, which could be applied to one point, form a system of the third order of a very specialized type. Each one 306] THE GEOMETRICAL THEORY. 329 of the screws of this system will have, as its instantaneous screw, a screw of infinite pitch parallel thereto. We have thus a system of impulsive screws of the third order, and a corresponding system of instantaneous screws of the third order, the relation between each pair being quite independent of whatever particular rigid body of the group the impulsive wrench be applied to. This system of the third order taken in conjunction with the cylindroid (?;, ) will enable us to determine the total system of impulsive screws which possess the property in question. Take any screw 6, of zero pitch, passing through the centre of gravity, and any screw, (f>, on the cylindroid (w, ). We know, of course, as already explained, the instantaneous screws corre sponding to 9 and <. Let us call them \, /j,, respectively. Draw the cylindroid (6, <), and the cylindroid (X, //,). The latter of these will be the locus of the instantaneous screws, corresponding to the screws on the former as impulsive screws. From the remarkable property of the two cylindroids, so related, it follows that every impulsive screw on (9, <) will have its corresponding instantaneous screw on (X, p) definitely fixed. This will be so, notwithstanding the arbitrary element remaining in the rigid body. From the way in which the cylindroid (9, (f>) was constructed, it is plain that the screws belonging to it are members of the system of the fifth order, formed by combinations of screws on the cylindroid (rj, ) with screws of the special system of the third order passing through the centre of gravity. But all the screws of a five-system are reciprocal to a single screw. The five-system we are at present considering consists of the screws which are reciprocal to that single screw, of zero pitch, which passes through the centre of gravity and intersects both the screws, of zero pitch, on the impulsive cylindroid (77, ). The corresponding instantaneous screws will also form a system of the fifth order, but it will be a system of a specialized type. It will be the result of compounding all possible displacements by translation, with all possible twists about screws on the cylindroid (a, /3). The resulting system of the fifth order consists of all screws, of whatsoever pitch, which fulfil the single condition of being perpendicular to the axis of the cylindroid (a, /3). Hence we obtain the following theorem : If an impulsive cylindroid, and the corresponding instantaneous cylin droid, be known, we can construct, from these two cylindroids, and without any further information as to the rigid body, two systems of screws of the fifth order, such that an impulsive wrench on a given screw of one system will produce an instantaneous twist velocity about a determined screw on the other system. It is interesting to note in what way our knowledge of but two corre sponding pairs of impulsive screws and instantaneous screws just fails to give complete information with respect to every other pair. If we take any 330 THE THEORY OF SCREWS. [306, ray in space, and assign to it an arbitrary pitch, the screw so formed may be regarded as an impulsive screw, and the corresponding instantaneous screw will not, in general, be defined. There is, however, a particular pitch for each such screw, which will constitute it a member of the system of the fifth order. It follows that any ray in space, when it receives the proper pitch, will be such that an impulsive wrench thereon would set any one of the singly infinite system of rigid bodies twisting about the same screw a. 307. The Geometrical Theory of Three Pairs of Screws. We can now show how, when three pairs of corresponding impulsive screws and instantaneous screws are given, the instantaneous screw, corre sponding to any impulsive screw, is geometrically constructed. The solution depends upon the following proposition, which I have set down in its general form, though the application to be made of it is somewhat specialized. Given any two independent systems of screws of the third order, Pand Q. Let &) be any screw which does not belong either to P or to Q, then it is possible to find in one way, but only in one, a screw 6, belonging to P, and a screw <j>, belonging to Q, such that o>, 6 and (f> shall all lie on the same cylin- droid. This is proved as follows. Draw the system of screws of the third order, P , which is reciprocal to P, and the system Q , which is reciprocal to Q. The screws belonging to P , and which are at the same time reciprocal to a>, constitute a group reciprocal to four given screws. They, therefore, lie on a cylindroid which we call P . In like manner, since Q is a system of the third order, the screws that can be selected from it, so as to be at the same time reciprocal to &&gt;, will also form a cylindroid which we call Q . It is generally a possible and determinate problem to find, among the screws of a system of the third order, one screw which shall be reciprocal to every screw, on an arbitrary cylindroid. For, take three screws from the system reciprocal to the given system of the third order, and two screws on the given cylindroid. As a single screw can be found reciprocal to any five screws, the screw reciprocal to the five just mentioned will be the screw now desired. We apply this principle to obtain the screw 6, in the system P, which is reciprocal to the cylindroid Q . In like manner, we find the screw </>, in the system Q, which is reciprocal to the cylindroid P . From the construction it is evident that the three screws 0, <f>, and <w are all reciprocal to the two cylindroids P and Q . This is, of course, equivalent to the statement that 0, <j>, a> are all reciprocal to the screws of a system of 307] THE GEOMETRICAL THEORY. 331 the fourth order. It follows that, 6, </>, w must lie upon the same cylin- droid. Thus, 6, </> are the two screws required, and the problem has been solved. It is easily seen that there is only one such screw 0, and one such screw <>. Or we might have proceeded as follows : Take any three screws on P, and any three screws on Q. Then by a fundamental principle a wrench on <y can be decomposed into six component wrenches on these six screws. But the three component wrenches on P will compound into a single wrench on some screw 6 belonging to P. The three component wrenches on Q will compound into a single wrench on some screw </> belonging to Q. Thus the original wrench on <w may be completely replaced by single wrenches on 6 and <f>. But this proves that 6, </>, and w are co-cylindroidal. In the special case of this theorem which we are now to use one of the systems of the third order assumes an extreme type. It consists simply of all possible screws of infinite pitch. The theorem just proved asserts that in this case a twist velocity about any screw <w can always be replaced by a twist velocity about some one screw belonging to any given system of the third order P, together with a suitable velocity of translation. In the problem before us we know three corresponding pairs of impulsive screws and instantaneous screws (rj, 2), (, /3), (, 7), and we seek the impul sive screw corresponding to some fourth instantaneous screw 8. It should be noticed that the data are sufficient but not redundant. We have seen how a knowledge of two pairs of corresponding impulsive screws and instantaneous screws provided eight of the coordinates of the rigid body. The additional pair of corresponding screws only bring one further co-ordinate. For, though the knowledge of 7 appropriate to a given f might seem five data, yet it must be remembered that the two pairs (??, a) and (f, 7) must fulfil the two fundamental geometrical conditions, and so must also the two pairs (, /3) and (, 7) ; thus, as 7 has to comply with four conditions, it really only conveys a single additional coordinate, which, added to the eight previously given, make the nine which are required for the rigid body. We should therefore expect that the knowledge of three corresponding pairs must suffice for the determination of every other pair. Let the unit twist velocity about 8 be resolved by the principles ex plained in this section into a twist velocity on some screw S belonging to a, /3, 7, and into a velocity of translation on a screw x of infinite pitch. We have already seen that the impulsive screw corresponding to 8 must lie on the system of the third order defined by 77, , and and that it is definitely determined. Let us denote by -^ this known impulsive screw which would make the body commence to twist about B . 332 THE THEORY OF SCREWS. [307- Let the centre of gravity be constructed as in the last section ; then an impulsive force through the centre of gravity will produce the velocity of translation on 8j. Let us denote by % the screw of zero pitch on which this force lies. We thus have % as the impulsive screw corresponding to the instan taneous screw S^ while i/r is the impulsive screw corresponding to the instantaneous screw S . Draw" now the cylindroids (%, i/r) and (8 1} S ). The first of these is the locus of the impulsive screws corresponding to the instantaneous screws on the second. As already explained, we can completely correlate the screws on two such cylindroids. We can, therefore, construct the impulsive screw on (^, ^) which corresponds to any instantaneous screw on (S 1; S ). It is, however, obvious, from the construction, that the original screw B lies on the cylindroid (S 1} S ). Hence we obtain the impulsive screw which corresponds to B as the instantaneous screw, and the problem has been solved. 308. Another method. We might have proceeded otherwise as follows : From the three given pairs of impulsive screws and instantaneous screws rja, %J3, 7 we can find other pairs in various ways. For example, draw the cylindroids (a, #) and (, ); then select, by principles already explained, a screw B on the first cylindroid, and its correspondent 6 on the second. In like manner, from the cylindroids (a, 7) and (17, ), we can obtain another pair (</>, e). We have thus five pairs of correspondents, ??, /3, 7, 08, <f>e. Each of these will give a diameter of the momental ellipsoid, and the radius of gyration about that diameter. Thus we know the centre of the momental ellipsoid and five points on its surface. The ellipsoid can be drawn accordingly. Its three principal axes give the principal screws of inertia. All other pairs of correspondents can then be determined by a construction given later on (311). 309. Unconstrained motion in system of second order. Suppose that a cylindroid be drawn through any two (not lying along the same principal axis) of the six principal screws of inertia of a free rigid body. If the body while at rest be struck by an impulsive wrench about any one of the screws of the cylindroid it will commence to move by twisting about a screw which also lies on the cylindroid. For the given impulsive wrench can be replaced by two component wrenches on any two screws of the cylindroid. We shall, accordingly, take the component wrenches of the given impulse on the two principal screws of inertia which, by hypothesis, are contained on the cylindroid. Each of those components 309] THE GEOMETRICAL THEORY. 333 will, by the property of a principal screw of inertia, produce an instantaneous twist velocity about the same screw. But the two twist velocities so generated can, of course, only compound into a single twist velocity on some other screw of the cylindroid. We have now to obtain the geometrical relations characteristic of the pairs of impulsive and instantaneous screws on such a cylindroid. In previous chapters we have discussed the relations between impulsive screws and instantaneous screws, when the movements of the body are confined, by geometrical constraint, to twists about the screws on a cylindroid. The problem now before us is a special case, for though the movements are no other than twists about the screws on a cylindroid, yet this restriction, in the present case, is not the result of constraint. It arises from the fact that two of the six principal screws of inertia of the rigid body lie on the cylindroid, while the impulsive wrench is, by hypothesis, limited to the same surface. To study the question we shall make use of the circular representation of the cylindroid, 50. We have there shown how, when the several screws on the cylindroid are represented by points on the circumference of a circle, various dynamical problems can be solved with simplicity and convenience. For example, when the impulsive screw is represented on the circle by one point, and the instantaneous screw by another, we have seen how these points are connected by geometrical construction ( 140). In the case of the unconstrained body, which is that now before us, it is known that, whenever the pitch of an instantaneous screw is zero, the corre sponding impulsive screw must be at right angles thereto ( 301). In the circular representation, the angle between any two screws is equal to the angle subtended in the representative circle by the chord whose extremities are the representatives of the two screws. Two screws, at right angles, are consequently represented by the extremities of a diameter of the representative circle. If, therefore, we take A, B, two points on the circle, to represent the two screws of zero pitch, then the two points, P and Q, diametrically opposite to them, are the points indicating the corresponding impulsive screws. It is plain from 287 that AQ and BP must intersect in the homographic axis, and hence the homographic axis is parallel to AQ and EP, and as it must contain the pole of AB it follows that the homographic axis XY must be the diameter perpendicular to AB. The two principal screws of the cylindroid X and Y are, in this case, the principal screws of inertia. Each of them, when regarded as an impulsive screw, coincides with its corresponding instantaneous screw. The diameter XY bisects the angle between AP and BQ. 334 THE THEORY OF SCREWS. [309, It is shown ( 137) that the points which represent the instantaneous screws, and the points which represent the corresponding impulsive screws, form two homographic systems. A well-known geometrical principle asserts ( 146), that if each point on a circle be joined to its homographic corre spondent, the chord will envelop a conic which has double contact with the circle. It is easily seen that, in the present case, the conic must be the hyperbola which touches the circle at the ends of the diameter XY, and has the rays AP and BQ for its asymptotes. The hyperbola is completely defined by these conditions, so that the pairs of correspondents are uniquely determined. Every tangent, 1ST, to this hyperbola will cut the circle in two points.. I and S, such that 8 is the point corresponding to the impulsive screw, and / is the point which marks out the instantaneous screw. We thus obtain a concise geometrical theory of the connexion between the pairs of cor responding impulsive screws and instantaneous screws on a cylindroid which contains two of the principal screws of inertia of a free rigid body. For completeness, it may be necessary to solve the same problem Avhen the cylindroid is defined by two principal screws of inertia lying along the same principal axis of the rigid body. It is easy to see that if, on the principal axis, whose radius of gyration was a, there lay any instantaneous screw whose pitch was p a , then the corresponding impulsive screw would be also on the same axis, and its pitch would be p n where p n x p a = a?. 310. Analogous Problem in a Three-system. Let us now take the case of the system of screws of the third order, which contains three of the six principal screws of inertia of a free rigid body. Any impulsive wrench, which acts on a screw of a system of the third order, can be decomposed into wrenches on any three screws of that system, and consequently, on the three principal screws of inertia, which in the present case the three-system has been made to contain. Each of these component wrenches will, from the property of a principal screw of inertia, generate an initial twist velocity of motion around the same screw. The three twist velocities, thence arising, can be compounded into a single twist velocity about some other screw of the system. We desire to obtain the geometrical relation between each such resulting instantaneous screw and the corresponding impulsive screw. It has been explained in Chap. XV. how the several points in a plane are in correspondence with the several screws which constitute a system of the third order. It was further shown, that if by the imposition of geometrical constraints, the freedom of a rigid body was limited to twisting 310] THE GEOMETRICAL THEORY. 335 about the several screws of the system of the third order, a geometrical construction could be obtained for determining the point corresponding to any instantaneous screw, when the point corresponding to the appropriate impulsive screw was known. We have now to introduce the simplification of the problem, which results when three of the principal screws of inertia of the body belong to the system. But a word of caution, against a possible misunderstanding, is first necessary. It is of course a fundamental principle, that when a rigid system has freedom of the ?ith order, there will always be, in the system of screws expressing that freedom, n screws such that an im pulsive wrench administered on any one of those screws will immediately make the body begin to move by twisting about the same screw. These are the n principal screws of inertia. But in the case immediately under consideration the rigid body is sup posed to be free, and it has, therefore, six principal screws of inertia. The system of the third order, at present before us, is one which contains three of these principal screws of inertia of the free body. Such a system of screws possesses the property, that an impulsive wrench on any screw belonging to it will set the body twisting about a screw which also belongs to the same system. This is the case even though, in the total absence of constraints, there is no kinematical difficulty about the body twisting about any screw whatever. As there are no constraints, we know that each instantaneous screw, of zero pitch, must be at right angles to the corresponding impulsive screw ( 301). This condition will enable us to adjust the particular homography in the plane wherein each pair of correspondents represents an impulsive screw and the appropriate instantaneous screw. The conic, which is the locus of points corresponding to the screws of a given pitch p, has as its equation ( 204) 3 *-p(6? + 6* + 6> 3 2 ) = 0. The families of conies corresponding to the various values of p have a common self-conjugate triangle. The vertices of that triangle correspond to the three principal screws of inertia. The three points just found are the double points of the homography which correlate the points representing the impulsive screws with those representing the instantaneous screws. Let us take the two conies of the system, corresponding to p = and p = oo . They are 3 2 = ........................... (i), 3 2 = ........................... (ii). 336 THE THEORY OF SCREWS. [310, Two conjugate points to conic (i) denote two reciprocal screws. Two con jugate points to conic (ii) denote two screws at right angles. Let A be any point representing an instantaneous screw. Take the polar of A, with respect to conic (i). Let P be the pole of this ray, with respect to conic (ii). Then P will correspond to the impulsive screw, while A corresponds to the appropriate instantaneous screw. For this is clearly a homography of which A and P are two correspondents. Further, the double points of this homography are the vertices of the common conjugate triangle to conies (i) and (ii). If A lie on (i), then its polar is the tangent to (i) ; and as every point on this polar will be conjugate to P, with respect to conic (ii), it follows that A and P are conjugate, with respect to (ii) that is, A and P are correspondents of a pair of screws at right angles. As the pitch of the screw, corresponding to A, is zero, we have thus obtained the solution of our problem. 311. Fundamental Problem with Free Body. We now give the geometrical solution of the problem so fundamental in this present theory which may be thus stated : A perfectly free body at rest is struck by an impulsive wrench upon a given screw. It is required to construct the instantaneous screw about which the body will commence to twist. The rigid body being given, its three principal axes are to be drawn through its centre of gravity. The radii of gyration a, b, c about these axes are to be found. On the first principal axis two screws of pitches + a and a respectively are to be placed. Similarly screws of pitches + b, b, and +c, c are to be placed on the other two principal axes. These are, of course, the six principal screws of inertia: call them A 0> A l} A. 2 , A 3 , A 4> A 5 . We then draw the five cylindroids AoA 1} A A 2 , A A 3> A Q At, A A B . It is always possible to find one screw on a cylindroid reciprocal to any given screw. In certain cases, however, of a special nature, more than a single screw can be so found. Under such circumstances the present process is inapplicable, but the exceptional instances will be dealt with presently. Choose on the cylindroid A A l a screw 1 which is reciprocal to the given impulsive screw ?;, which is, of course, supposed to lie anywhere and be of any pitch. In like manner, choose on the other four cylindroids screws 2 , 3 , # 4 , 6 6 , respectively, all of which are also reciprocal to 77. 311] THE GEOMETRICAL THEORY. 337 Let us now think of 9 l as an instantaneous screw ; it lies on the cylindroid A A lt and this cylindroid contains two principal screws of inertia. It follows from 309 that the corresponding impulsive screw fa lies on the same cylin droid. That screw fa can be determined by the construction there given. In like manner we construct on the other four cylindroids the screws <j> 2 , fa, fa, fa, which are the impulsive screws corresponding respectively to 2 , 3 , # 4 , 6 , as instantaneous screws. Consider then the two pairs of corresponding impulsive screws and in stantaneous J screws (77, a) and (fa, ^). We have arranged. the construction so that 6 l is reciprocal to 77. Hence, by the fundamental principle so often employed, a and d l are conjugate screws of inertia, so that a must be reciprocal to fa. In like manner it can be proved that the instantaneous screw a for which we are in search must be reciprocal to fa, fa, fa, fa. We have thus dis covered five screws, fa, fa, fa, fa, fa, to each of which the required screw a must be reciprocal. But it is a fundamental point in the theory that the single screw reciprocal to five screws can be constructed geometrically ( 25). Hence a is determined, and the geometrical solution of the problem is complete. It remains to examine the failure in this construction which arises when any one or more of the five screws fa ... fa becomes indeterminate. This happens when 77 is reciprocal to two screws on the cylindroid in question. In this case 77 is reciprocal to every screw on the cylindroid. Any one of such screws might be taken as the corresponding fa and, of course, would have been also indefinite, and a could not have been found. In this case 77 would have been reciprocal to the two principal screws of inertia, suppose A , A l which the cylindroid contained. Of course still more indeterminateness would arise if 77 had been also reciprocal to other screws of the series A , A l} A a , A 3 , A 4 , A 5 . No screw could, however, be reciprocal to all of them. If?; had been reciprocal to five, namely, A l} A a , A s , A,, A 5 , then 77 could be no screw other than A , because the six principal screws of inertia are co- reciprocal ; 77 would then be its own instantaneous screw, and the problem would be solved. We may therefore, under the most unfavourable conditions, take 77 to be reciprocal to four of the principal screws of inertia A , A lt A a , A 3> but not to A 4 or .-1 5 . We now draw the five cylindroids, A A t , A,A 4 , A 2 A 4 , A 3 A 4 , A A 5 . We know that 77 is reciprocal to no more than a single screw on each cylindroid. We therefore proceed to the construction as before, first finding 0, ... 5 , one on each cylindroid ; then deducing fa ... fa, and thus ultimately obtaining a. Thus the general problem has been solved. B. 22 338 THE THEORY OF SCREWS. [312- 312. Freedom of the First or Second Order. If the rigid body have only a single degree of freedom, then the only movements of which it is capable are those of twisting to and fro on a single screw a. If the impulsive wrench 77 which acted upon the body happened to be reciprocal to a, then no movement would result. The forces would be destroyed by the reactions of the constraints. In general, of course, the impulsive screw 77 will not be reciprocal to a. A twisting motion about a will therefore be the result. All that can be said of the instantaneous screw is that it can be no possible screw but a. In the next case the body has two degrees of freedom which, as usual, we consider to be of the most general type. It is required to obtain a con struction for the instantaneous screw a about which a body will commence to twist in consequence of an impulsive wrench 77. The peculiarity of the problem when the notion of constraint is introduced depends on the circumstance that, though the impulsive screw may be situated anywhere and be of any pitch, yet that as the body is restrained to only two degrees of freedom, it can only move by twisting about one of the screws on a certain cylindroid. We are, therefore, to search for the in stantaneous screw on the cylindroid expressing the freedom. Let A be the given cylindroid. Let B be the system of screws of the fourth order reciprocal to that cylindroid. If the body had been free it would have been possible to determine, in the manner explained in the last section, the impulsive screw corresponding to each screw on the cylindroid A. Let us suppose that these impulsive screws are constructed. They will all lie on a cylindroid which we denote as P. In fact, if any two of such screws had been found, P would of course have been denned by drawing the cylindroid through those two screws. Let Q be the system of screws of the fourth order which is reciprocal to P. Select from Q the system of the third order Q t which is reciprocal to 77. We can then find one screw ^ which is reciprocal to the system of the fifth order formed from A and Qj. It is plain that -^ must belong to B, as this contains every screw reciprocal to A. Take also the one screw on the cylindroid A which is reciprocal to 77, and find the one screw rj 2 on the cylindroid P which is reciprocal to this screw on A. Since 77, 77! and ?7 2 are all reciprocal to the system of the fourth order formed by A l and Q 1} it follows that 77, 77^ and 773 must all lie on the same cylindroid. We can therefore resolve the original wrench on 77 into two com ponent wrenches on y^ and 772. 314] THE GEOMETRICAL THEORY. 339 But it is of the essence of the theory that the reactions of the constraints by which the motion of the body is limited to twists about screws on the cylindroid A must be wrenches on the reciprocal system B. So far, therefore, as the body thus constrained is concerned, the reactions of the constraints will neutralize the wrench on TJ I . Thus the wrench on r} 2 is the only part of the impulsive wrench which need be considered. But we already know from the construction that an impulsive wrench on^ will produce an instantaneous twist velocity about a determined screw a on A. Thus we have found the initial movement, and the investigation is geo metrically complete. 313. Freedom of the Third Order. We next consider the case in which a rigid body has freedom of the third order. We require, as before, to find a geometrical construction for the in stantaneous screw a corresponding to a given impulsive screw 77. Let A be the system of screws of the third order about which the body is free to twist. Let B be the system of screws of the third order reciprocal to A. We must first construct the system of the third order P which consists of the impulsive screws that would have made the body, if perfectly free, twist about the several screws of A. As already explained ( 307) we can, in one way, but only in one way, resolve the original wrench on 77 into wrenches 7^ on B, and 772 on P. The former is destroyed by the reactions of the constants. The latter gives rise to a twist velocity about a determinate screw on A. Thus the problem has been solved. 314. General Case. We can obviously extend a similar line of reasoning to the cases where the body had freedom of the remaining degrees. It will, however, be as simple to write the general case at once. Let A be a system of screws of the ?ith order, about which a body is free to twist, any other movements being prevented by constraints. If the body receive an impulsive wrench, on any screw 77, it is required to determine the instantaneous screw, of course belonging to A, about which the body will commence to twist. Let B be the system of screws of the (6 - w)th order, reciprocal to A. The wrenches arising from the reaction of the constraints must, of course, be situated on the screws of the system B. Let P be the system of screws of the nth order, which, in case the body 222 340 THE THEORY OF SCREWS. [314- had been free, would have been the impulsive screws, corresponding to the instantaneous screws belonging to A. Let Q be the system of screw of the (6 - n)th order, which are reciprocal to P. Take from A the system of the (n- l)th order, reciprocal to 77, and call it A,. Take from Q the system of the (5 ?i)th order, reciprocal to 77, and call it Q,. As A is of the nth order, and Q x of the (5 - w)th, they together define a system of the fifth order. Let ^ be the single screw, reciprocal to this system of the fifth order. As Jj is of the (n-l)th order, and Q is of the (6 - w)th order, they together define a system of the fifth order. Let r} 2 be the single screw, reciprocal to this system of the fifth order. 77! is reciprocal to A l of the (n l)th order, because J.j forms part of A. It is reciprocal to Qj of the (5 n)th order, because it was so made by con struction. Thus 77! is reciprocal to both A l and Q lt that is to a system of the fourth order. In like manner, it can also be shown that rj 2 is reciprocal to both A^ and Q lt A l and Q 1 were originally chosen so as to be reciprocal to 77. It thus appears that the three screws, rj, tj^, 772, are all reciprocal to the same system of the fourth order. They are, therefore, co-cylindroidal. The initial wrench on 77 can therefore be adequately replaced by two components on ^ and ?7 2 . The former of these is destroyed by the reaction of the constraints. The latter gives rise to an initial movement on a determined screw of A. Thus, the most general problem of the effect of an impulsive wrench on a constrained rigid body has been solved geo metrically. 315. Freedom of the Fifth Order. The special case, where the rigid body has freedom of the fifth order, may be viewed as follows. Let p be the screw reciprocal to the screw system of the fifth order, about which the body is free to twist. Let A, be the instantaneous screw, determined in the way already explained, about which the body, had it been free, would have commenced to twist in consequence of an impulsive wrench on p. 316] THE GEOMETRICAL THEORY. 341 Let 77 be any screw on which an impulsive wrench is imparted, and let a be the corresponding instantaneous screw, about which the body would have begun to twist had it been free. Draw the cylindroid through a and X, and choose on this cylindroid the screw /JL, which is reciprocal to p. Then ^ is the instantaneous screw about which the body commences to twist, in consequence of the impulsive wrench on 77. For (77, p) is a cylindroid of impulsive screws, and (a, X) are the corre sponding instantaneous screws. As p is reciprocal to p, it belongs to the system of the fifth order. The corresponding impulsive screw must lie on (77, p). The actual instantaneous motion could therefore have been produced by impulsive wrenches on 77 and p. The latter would, however, be neutralized by the reactions of the constraints. We therefore find that 77 is the impulsive screw, corresponding to a as the instantaneous screw. 316. Principal Screws of Inertia of Constrained Body. There is no more important theorem in this part of the Theory of Screws than that which affirms that for a rigid body, with n degrees of freedom, there are n screws, such that if the body when quiescent receives an impulsive wrench about one of such screws, it will immediately commence to move by twisting about the same screw. We shall show how the principles, already explained, will enable us to construct these screws. We commence with the case in which the body has two degrees of freedom. We take three screws, 77, , , arbitrarily selected on the cylindroid, which expresses the freedom of the body. We can then de termine, by the preceding investigation, the three instantaneous screws, , ft, 7, on the same cylindroid, which correspond, respectively, to the impulsive screws. Of course, if 77 happened to coincide with a, or with ft, or f with 7, one of the principal screws of inertia would have been found. But, in general, such pairs will not coincide. We have to show how, from the knowledge of three such pairs, in general, the two principal screws of inertia can be found. We employ the circular representation of the points on the cylindroid, as explained in 50. The impulsive screws are represented by one system of points, the corresponding instantaneous screws are represented by another system of points. It is an essential principle, that the two systems of points, so related, are homographic. The discovery of the principal screws of inertia is thus reduced to the well-known problem of the discovery of the double points of two homographic systems on a circle. 342 THE THEORY OF SCREWS. [316, The simplest method of solving this problem is that already given in 139, in which we regard the six points, suitably arranged, as the vertices of a hexagon ; then the Pascal line of the hexagon intersects the circle in two points which are the points corresponding to the principal screws of inertia. 317. Third and Higher Systems. We next investigate the principal screws of inertia of a body which has three degrees of freedom. We have first, by the principles already ex plained, to discover four pairs of correspondents. When four such pairs are known, the principal screws of inertia can be constructed. Perhaps the best method of doing so is to utilize the plane correspondence, as explained in Chap. xv. The corresponding systems of impulsive screws and instantaneous screws, in the system of the third order, are then repre sented by the homographic systems of points in the plane. When four pairs of such correspondents are known, we can construct as many additional pairs as may be desired. Let a, 0, 7, 8 be four points in the plane, and let 77, , f, be the points corresponding, so that ?/ represents the impulsive screw, and a the instantaneous screw, and similarly for the other pairs. Let it be required to find the impulsive screw <, which corresponds to any fifth instantaneous screw e. Since anharmonic ratios are the same in two corresponding figures, we have a (0, 7, 8, 6) = ,K ?, 0, (/>), thus we get one ray r)<f>, which contains <. We have also (, 7, , <0 = f07, C, 0. <), which gives a second ray <, containing </>, and thus <f> is known. A construction for the double points of two homographic systems of points in the same plane is as follows: Let and be a pair of corresponding points. Then each ray through will have, as its correspondent, a ray through . The locus of the intersection of these rays will be a conic S. This conic S must pass through the three double points, and also through and . Draw the conic 8 , which is the locus of the points in the second system corresponding to the points on S, regarded as in the first system. Then since lies on S, we must have on S . But S must also pass through the three double points. is one of the four intersections of S and S , and the three others are the sought double points. Thus the double points are constructed. And in this manner we obtain the three principal screws of inertia in the case of the system of the third order. 317] THE GEOMETRICAL THEORY. 343 If a rigid body be free to move about screws of any system of the fourth order, we may determine its four principal screws of inertia as follows. We correlate the several screws of the system of the fourth order with the points in space. The points representing impulsive screws will be a system homographic with the points representing the corresponding instantaneous screws. If we have five pairs of correspondents (a, 77), (@> )> (% 0> (S, &), (e, <p), in such a homography we can at once determine the correspondent ^ to any other screw X. Draw a pencil of four planes through a, /3, and the four points j, B, e, X, respectively. Draw also a pencil of four planes through ij, , and the four points , 0, (j), T/T, respectively. These two pencils will be equianharmonic. Thus we discover one plane which contains i/r. In like manner we can draw a pencil of planes through a, y, and /3, 8, e, X, respectively, and the equi anharmonic pencil through 77, , and , 6, <f>, ^, respectively. Thus we obtain a second plane which passes through ty. A third plane may be found by drawing the pencil of four planes through a, S, and the four points /3, y, e, X, respectively, and then constructing the equianharmonic pencil through 77, 6, and , , 0, \^, respectively. From the intersection of these three planes, ^r is known. In the case of two homographic systems in three dimensions, there are, of course, four double points. These may be determined as follows. Let and be two corresponding rays. Then any plane through will have, as its correspondent, a plane through . It is easily seen that these planes intersect on a ray which has for its locus a quadric surface S, of which and are also generators. This quadric must pass through the four double points. Let 8 be the quadric surface which contains all the points in the second system corresponding to the points of S regarded as the first system. Then will lie on 8 , and the rest of the intersection of 8 and S will be a twisted cubic G, which passes through the four double points. Take any point P on C, and draw any plane through P. Then every ray of the first system of the pencil through P in this plane will have as its correspondent in the second system the ray in some other plane pencil L. One, at least, of the rays in the pencil L will cut the cubic C. Call this ray X , and draw its correspondent X in the first system passing through P. We thus have a pair of corresponding rays X and X , each of which intersects the twisted cubic C. 344 THE THEORY OF SCREWS. [317, Draw pairs of corresponding planes through X and X . The locus of their intersection will be a quadric S", which also contains the four double points. S" and C, being of the second and the third order respectively, will intersect in six points. Two of these are on X and X , and are thus dis tinguished. The four remaining intersections will be the required double points, and thus the problem has been solved. These double points correspond to the principal screws of inertia, which are accordingly determined. In the case of freedom of the fifth order, the geometrical analogies which have hitherto sufficed are not available. We have to fall back on the general fact that the impulsive screws and the corresponding instantaneous screws form two homographic systems. There are five double screws be longing to this homography. These are the principal screws of inertia. 318. Correlation of Two Systems of the Third Order. It being given that a certain system of screws of the third order, P, is the locus of impulsive screws corresponding to another given system of the third order, A, as instantaneous screws, it is required to correlate the corre sponding pairs on the two systems. We have already had frequent occasion to use the result demonstrated in 293, namely, that when two impulsive and instantaneous cylindroids were known, we could arrange the several screws in corresponding pairs without any further information as to the rigid body. We have now to demonstrate that when we are given an impulsive system of the third order, and the corresponding instantaneous system, there can also be a similar adjustment of the corresponding pairs. It has first to be shown, that the proposed problem is a definite one. The data before us are sufficient to discriminate the several pairs of screws, that is to say, the data are sufficient to point out in one system the corre spondent to any specified screw in the other system. We have also to show that there is no ambiguity in the solution. There is only one rigid body ( 293) which will comply with the condition, and it is not possible that there could be more than one arrangement of corresponding pairs. Let a, /3, 7 be three instantaneous screws from A, and let their corre sponding impulsive screws be 77, , in P. In the choice of a screw from a system of the third order there are two disposable quantities, so that, in the selection of three correspondents in P, to three given screws in A, there would be, in general, six disposable coordinates. But the fact that a, ?; and @, g are two pairs of correspondents necessitates, as we know, 318J THE GEOMETRICAL THEORY. 345 the fulfilment of two identical conditions among their coordinates. As there are three pairs of correspondents, we see at once that there are six equations to be fulfilled. These are exactly the number required for the determination of rj, , , in the system P. To the same conclusion we might have been conducted by a different line of reasoning. It is known that, for the complete specification of a system of the third order, nine co-ordinates are necessary ( 75). This is the same number as is required for the specification of a rigid body. If, therefore, we are given that P, a system of the third order, is the collection of impulsive screws, corresponding to the instantaneous screws in the system A, we are given nine data towards the determination of a rigid body, for which A and P would possess the desired relation. It therefore follows that we have nine equations, while the rigid body involves nine unknowns. Thus we are led to expect that the number of bodies, for which the arrangement would be possible, is finite. When such a body is de termined, then of course the correlation of the screws on the two systems is immediately accomplished. It thus appears that the general problem of correlating the screws on any two given systems of the third order, A and P, into possible pairs of impulsive screws and instantaneous screws, ought not to admit of more than a finite number of solutions. We are now to prove that this finite number of solutions cannot be different from unity. For, let us suppose that a screw X, belonging to A, had two screws 6 and <f>, as possible correspondents in P. This could, of course, in no case be possible with the same rigid body. We shall show that it could not even be possible with two rigid bodies, M { and M 2 . For, if two bodies could do what is suggested, then it can be shown that there are a singly infinite number of possible bodies, each of which would afford a different solution of the problem. We could design a rigid body in the following manner : Increase the density of every element of Mj in the ratio of p^ : 1, and call the new mass M. Increase the density of every element of M 2 in the ratio of p 2 : 1, and call the new mass M 2 . Let the two bodies, so altered, be conceived bound rigidly together by bonds which are regarded as imponderable. Let ty be any screw lying on the cylindroid (6, <j>). Then the impulsive wrench of intensity, ty " on i/r, may be decomposed into components , sin (^r-<J>) , , sin (6 - ^) V /d ,( on 9, and iK -^ ^ *g on <f>. sin (6 - </>) sm(0 - <) 346 THE THEORY OF SCREWS. [318, If the former had been applied to M^ it would have generated about a ( 280) a twist velocity represented by , sin (A/T - <f>) J^ cos(0a) r sin (6 r -</>) M t p a If the latter had been applied to the body M 2 , it would have generated a twist velocity about the same screw, a, equal to , sin (6 ^r) J^ cos ((fta) * sin (0-0) J/7 "~ Pa Suppose that these two twist velocities are equal, it is plain that the original wrench on ty would, if it had been applied to the composite rigid body, produce a twisting motion about a. The condition is sin (^r </>) _ sin (6 -fy) MI cos ((pa) ~ M 3 cos (0a) We thus obtain tan i/r in terms of MI : M a . As the structure of the composite body changes by alterations of the relative values of p l and p. z , so will T/T move over the various screws of the cylindroid (6, <p). This result shows that, if three screws, a, ft, 7 be given, then the possible impulsive screws, 77, , which shall respectively correspond to a, /3, 7 in a given system of the third order P, are uniquely determined. For, suppose that a second group of screws, 77 , % > > could also be deter mined which fulfilled the same property. We have shown how another rigid body could be constructed so that another screw, ^, could be found on the cylindroid (77, 77 ), such that an impulse thereon given would make the body twist about a. It is plain that, for this body also, the impulsive wrench, corresponding to ft, would be some screw on the cylindroid (f, ). But all screws on this cylindroid belong to the system P. In like manner, the instantaneous screw 7 would correspond for the composite body to some screw on the cylindroid (, ") Hence it follows that, for each different value of the ratio p^ : p 2 , we would have a different set of impulsive screws for the instantaneous screws a, ft, 7. We thus find that, if there were more than one set of such impulsive screws to be found in the system P, there would be an infinite number of such sets. But we have already shown that the number of sets must be finite. Hence there can only be one set of screws, 77, , , in the system P, which could be impulsive screws corresponding to the instantaneous screws, a, ft, 7. We are thus led to the following important theorem, which will be otherwise proved in the next chapter. Given any two systems of screws of the third order. It is generally pos sible, in one way, but only in one, to design, and place in a particular position a 319] THE GEOMETRICAL THEORY. 347 rigid body such that, if that body, while at rest and unconstrained, receive an impulsive wrench about any screw of the first system, the instantaneous move ment will be a twist about a screw of the second system. The two systems of corresponding impulsive and instantaneous screws on the two systems of the third order, form two homographic systems. There are, of course, infinite varieties in the possible homographic cor respondences between the screws of two systems of the third order. The number of such correspondences is just so many as the number of possible homographic correspondences of points in two planes. There is, however, only one correspondence which will fulfil the peculiar requirements when one of the systems expresses the instantaneous screws, and the other the impulsive screws severally corresponding thereto. If we are given one pair of corresponding impulsive and instantaneous screws, the body is not by such data fully determined. We are only given five coordinates, and four more remain, therefore, unknown. If we are given two corresponding impulsive cylindroids and instantaneous cylindroids, the body is still not completely specified. We have seen how eight of its coordinates are determined, but there is still one remaining indeterminate. If we are given a system of the fourth order of impulsive screws, and the corresponding system of the fourth order of instantaneous screws, the body, as in the other cases, remaining perfectly free, there are also, as we shall see in the next section, a singly infinite number of rigid bodies which fulfil the necessary conditions. In like manner, it will appear that, if we are given a system of the fifth order consisting of impulsive screws, and a corresponding system of the fifth order consisting of instantaneous screws, the body has really as much indeterminateness as if we had only been given a single pair of corresponding screws. But the case of two systems of the third order is exceptional, in that when it is known that one of these is the locus of the instantaneous screws, which correspond to the screws of the other system regarded as impulsive screws, the rigid body for which this state of things is possible is completely and uniquely specified as to each and every one of its nine coordinates. 319. A Property of Reciprocal Screw Systems. Given a system of the fourth order A and another system of the fourth order P. If it be known that the latter is the locus of the screws on which must lie the impulsive wrenches which would, if applied to a free rigid body, cause instantaneous twist velocities about the several screws on A, let us consider what can be inferred as to the rigid body from this fact alone. Let A be the cylmdroid which is composed of the screws reciprocal to A. 348 THE THEORY OF SCREWS. [319, Let P be the cylindroid which is composed of the screws reciprocal to P. Let P l} P 2 , P 3 , P 4 be any four impulsive screws on P. Let A 1} A 2 , A 3 , A 4 be the four corresponding instantaneous screws on A. Take any screw a. on the cylindroid P . Let 77 be the corresponding impulsive screw. Since a is reciprocal to all the screws on P it must be reciprocal to Pj. It follows from the fundamental property of conjugate screws of inertia, that 77 must be reciprocal to A^. In like manner we can show that 77 is reciprocal to A 2 , A z , and A t . It follows that 77 is reciprocal to the whole system A, and therefore must be contained in the reciprocal cylindroid A. Hence we obtain the following remarkable result, which is obviously generally true, though our proof has been enunciated for the system of the fourth order only. Let P and A be any two systems of screws of the nth order, and P and A their respective reciprocal systems of the (ft~n)th order. If P be the collec tion of impulsive screws corresponding severally to the screws of A as the instantaneous screws for a certain free rigid body ; then, for the same free rigid body A will be the collection of impulsive screws which correspond to the screws of P as instantaneous screws. 320. Systems of the Fourth Order. Thus we see that when we are given two systems of the fourth order P and A as correspondingly impulsive and instantaneous, we can immediately infer that, for the same rigid body, the screws on the cylindroid A are the impulsive screws corresponding to the instantaneous screws on the cylindroid P . We can now make use of that instructive theorem ( 293) which declares that when two given cylindroids are known to stand to each other in this peculiar relation, we are then able, without any further information, to mark out on the cylindroids the corresponding pairs of screws. We can then determine the centre of gravity of the rigid body on which the impulsive wrenches act. We can find a triad of conjugate diameters of the momental ellipsoid, and the radii of gyration about two of those diameters. Hence we have the following result : If it be given that a certain system of the fourth order is the locus of the impulsive screws corresponding to the instantaneous screws on another given system of the fourth order, the body being quite unconstrained, we can then determine the centre of gravity of the body, we can draw a triad of the conjugate diameters of its momental ellipsoid, and we can find ike radii of gyration about two of those diameters. There is still one undetermined element in the rigid body, namely, the 320] THE GEOMETRICAL THEORY. 349 radius of gyration about the remaining conjugate diameter. The data before us are not adequate to the removal of this indefiniteness. It must be remembered that t/he data in such a case are just so many but no more than suffice for the specification of the n-system A. The number of data neces sary to define an n-system is n (6 n). If, as in the present case, n = 4, the number of data is 8. We are thus one short in the number of data necessary to specify a rigid body. Thus we confirm the result previously obtained. We can assert that for any one of the singly infinite number of rigid bodies which fulfil the necessary conditions, the system A will be the locus of the instantaneous screws which correspond to the screws of the system P as impulsive screws. Though in the two cylindroids A and P we are able to establish the several pairs of correspondents quite definitely, yet we must not expect, with the data before us, to be able to correlate the pairs of screws in A and P definitely. If this could be done then the rigid body would be quite deter minate, which we know is not the case. There is, however, only a single indeterminate element left in the correlation of the screws in A with the screws of P. This we prove as follows : Let < be any screw of P on which an impulsive wrench is to act. Let 8 be the instantaneous screw in A about which the movement commences. We shall now show that though 8 cannot be completely defined, in the absence of any further data, yet it can be shown to be limited to a certain cylindroid. Let G be the centre of gravity. Then we know that an impulsive force directed through G will generate a movement of translation in a direction parallel to the force. Such a movement may, of course, be regarded as a twist about a screw of infinite pitch. Draw through G a plane normal to </>. Any screws of infinite pitch in this plane will be reciprocal to <. It follows from the laws of conjugate screws of inertia that the impulsive forces in this plane, by which translations could be produced, must lie on screws of zero pitch which are reciprocal to 8. Take any two of such screws : then we know that 8 is reciprocal to these two screws and also to P . It follows that 8 is reciprocal to the screws of a determinate system of the fourth order, and therefore 8 must lie on a deter mined cylindroid. We may commence to establish the correspondence between P and A by choosing some arbitrary screw <f> on P, and then drawing the cylindroid on A, on which we know that the instantaneous screw corresponding to P must lie. Any screw on this cylindroid may be selected as the instantaneous screw which corresponds to </>. Once that screw 8 had been so chosen there 350 THE THEORY OF SCREWS. [320- cau be no further ambiguity. The correspondent in A to every other screw in P is completely known. To show this it is only necessary to take two pairs from A and P and the pair just found. We have then three corre sponding pairs. It has been shown in 307 how the correspondence is completely determined in this case. Of course the fact that 8 may be any screw on a cylindroid is connected with the fact that in this case the rigid body had one indeterminate element. For each of the possible rigid bodies & would occupy a different position on its cylindroidal locus. 321. Systems of the Fifth Order. It remains to consider the case where two screw systems of the fifth order are given, it being known that one of them P is the locus of the impulsive screws which correspond to the several screws of the other system A regarded as instantaneous screws. Let P be the screw reciprocal to P, and A the screw reciprocal to A. Then from the theorem of 319 it follows that an impulsive wrench on A would make the body commence to move by twisting about P . We thus know five of the coordinates of the rigid body. There remain four inde terminate elements. Hence we see that, when the only data are the two systems P and A , there is a fourfold infinity in the choice of the rigid body. There are conse quently four arbitrary elements in designing the correspondence between the several pairs of screws in the two systems. We may choose any two screws 77, , on P, and assume as their two corre spondents in A any two arbitrary screws a and ft, provided of course that the three pairs A , B , rj, a, and , ft fulfil the six necessary geometrical conditions ( 304). Two of these conditions are obviously already satisfied by the circumstance that A and P are the reciprocals to the systems A and P. This leaves four conditions to be fulfilled in the choice of a. and ft. As each of these belongs to a system of the fifth order there will be four coordinates required for its complete specification. Therefore there will be eight disposable quantities in the choice of o and ft. Four of these will be utilized in making them fulfil the geometrical conditions, so that four others may be arbitrarily selected. When these are chosen we have four coordinates of the rigid body which, added to the five data provided by A and P , completely define the rigid body. 322. Summary. We may state the results of this discussion in the following manner : If we are given two systems of the first, or the second, or the third order 323] THE GEOMETRICAL THEORY. 351 of corresponding impulsive screws and instantaneous screws, all the corre sponding pairs are determined. There is no arbitrary element in the correspondence. There is no possible rigid body which would give any different correspondence. If we are given two systems of the fourth order of corresponding impulsive screws and instantaneous screws then the essential geometrical conditions ( 281), not here making any restriction necessary, we can select one pair of correspondents arbitrarily in the two systems, and find one rigid body to fulfil the requirements. If we are given two systems of the fifth order of corresponding impulsive screws and instantaneous screws then subject to the observance of the geo metrical conditions we can select two pairs of correspondents arbitrarily in the two systems, and find one rigid body to fulfil the requirements. If we are given two systems of the sixth order of corresponding impul sive screws and instantaneous screws then subject to the observance of the geometrical conditions we can select three pairs of correspondents arbitrarily in the two systems, and find one rigid body to fulfil the requirements. The last paragraph is, of course, only a different way of stating the results of 307. 323. Two Rigid Bodies. We shall now examine the circumstances under which pairs of impulsive and instantaneous screws are common to two, or more, rigid bodies. The problem before us may, perhaps, be most clearly stated as follows : Let there be two rigid bodies, M and M . If M be struck by an impulsive wrench on a screw 6, it will commence to twist about some screw X. If M had been struck by an impulsive wrench on the same screw 6, the body would have commenced to twist about some screw /u,, which would of course be generally different from \. If 6 be supposed to occupy different positions in space (the bodies remaining unaltered), so will \ and p move into corre spondingly various positions. It is proposed to inquire whether, under any circumstances, 6 could be so placed that X and //, should coincide. In other words, whether both of the bodies, M and M , when struck with an impulsive wrench on 6, will respond by twisting about the same instantaneous screw. It is obvious, that there is at least one position in which 6 fulfils the required condition. Let 6^ G<> be the centres of gravity of M and M . Then a force along the ray G l 6r 2 , if applied either to M or to M , will do no more than produce a linear velocity of translation parallel thereto. Hence it 352 THE THEORY OF SCREWS. [323 follows, that a wrench on the screw of zero pitch, which lies on the ray G l G 2 , will have the same instantaneous screw whether that wrench be applied to M or to M . We have now to examine whether there can be any other pair of im pulsive and instantaneous screws in the same circumstances. Let us suppose that when 6 assumes a certain position 77, we have A, and /u, coalescing into the single screw a. We know that the centre of gravity lies in a plane through a, and the shortest distance between a and 77. We know, also, that d a =p a tan (a??), where d a is the distance of the centre of gravity from a. It therefore follows that a must be parallel to GiG 2 . We have, however, already had occasion ( 303) to prove that, if p a be the radius of gyration of a body about a ray through its centre of gravity, parallel to a, 2p a sr a ,, , pa 2 = -^f \ da ~ Pa- cos (377) Hence it appears that, for the required condition to be satisfied, each of the two bodies must have the same radius of gyration about the axis through its centre of gravity, which is parallel to a. Of course this will not generally be the case. It follows that, in general, there cannot be any such pair of impulsive screws and instantaneous screws, as has been supposed. Hence we have the following result : Two rigid bodies, with different centres of gravity, have, in general, no other common pair of impulsive screws and instantaneous screws than the screw, of zero pitch, on the ray joining the centres of gravity, and the screw of infinite pitch parallel thereto. We shall now consider what happens when the exceptional condition, just referred to, is fulfilled, that is, when the radius of gyration of the ray G 1 G 2 is the same for each of the bodies. In each of the momental ellipsoids about the centres of gravity of the two bodies, draw the plane conjugate to the ray G^G 2 . Let these planes intersect in a ray T. Suppose that an impulsive force, directed along T, be made to act on the body whose centre of gravity is O l . It is plain, from Poinsot s well-known theory, that the rotation produced by such an impulse will be about a ray parallel to G 1 G 2 . If this impulsive wrench had been applied to the body whose centre of gravity is G 2 , the instantaneous screw would also be parallel to G 1 G 2 . If we now introduce the condition that the radius of gyration of each of the bodies, about G 1 G 2 , is the same, it can be easily deduced that the two instantaneous screws are identical. Hence we see that T, regarded as an impulsive screw of zero pitch, will have the same instantaneous screw for each of the two bodies. 323] THE GEOMETRICAL THEORY. 353 If we regard T and G 1 G 2 as two screws of zero pitch, and draw the cylindroid through these two screws, then any impulsive wrench about a screw on this cylindroid will have the same instantaneous screw for either of the two bodies to which it is applied. For such a wrench may be decomposed into forces on T and on G 1 G 2 ] these will produce, in either body, a twist about a, and a translation parallel to a, respectively. We therefore obtain the following theorem : If two rigid bodies have different centres of gravity, G { and 6r 2 , and if their radii of gyration about the ray G^ z are equal, there is then a cylindroid of screws such that an impulsive wrench on any one of these screws will make either of the rigid bodies begin to twist about the same screw, and the instantaneous screws which correspond to the several screws on this cylindroid, all lie on the same ray Gfi^, but with infinitely varied pitch. It is to be remarked that under no other circumstances can any im pulsive screw, except the ray GiG z , with zero pitch, have the same instan taneous screw for each of the two bodies, so long as their centres of gravity are distinct. We might have demonstrated the theorem, above given, from the results of 303. We have there shown that, when an impulsive screw and the corresponding instantaneous screw are given, the rigid body must fulfil five conditions, the nature of which is fully explained. If we take two bodies which comply with these conditions, it appears that the ray through their centre of gravity is parallel to the instantaneous screw, and we also find that their radii of gyration must be equal about the straight line through their centres of gravity. If two rigid bodies have the same centre of gravity, then, of course, any ray through this point will be the seat of an impulsive wrench on a screw of zero pitch such that it generates a twist velocity on a screw of infinite pitch, parallel to the impulsive screw. This will be the case to whichever of the two bodies the force be applied. We have therefore a system of the third order (much specialized no doubt) of impulsive screws, each of which has the same instantaneous screw for each of the two bodies. In general there will be no other pairs of common impulsive and instantaneous screws beyond those indicated. Under certain circumstances, however, there will be other screws possess ing the same relation. We may suppose the two momental ellipsoids to be drawn about the common centre of gravity. These ellipsoids will, by a well-known property, possess one triad of common conjugate diameters. In general, of course, the B. 23 354 THE THEORY OF SCREWS. [323 radii of gyration of the two bodies, around any one of these three diameters, will not be equal. If, however, it should happen that the radius of gyration of one body be equal to that of the other body about one OX of these three common conjugate diameters, it can be shown that any screw, parallel to OX, whatever be its pitch regarded as an instantaneous screw, will have the same impulsive screw for either of the two bodies. If the radii of gyration about two of the common conjugate diameters were equal for the two bodies, it will then appear that any instantaneous screw which is parallel to the plane of the common conjugate diameters, will have the same impulsive screw for each of the two bodies. The corresponding impulsive screws belong to the system of the fifth order, which is defined by being reciprocal to a screw of zero pitch on the third of the three common conjugate diameters. Of course, if the radii of gyration coincide on this third diameter, then the two rigid bodies, regarded from our present point of view, would be identical. CHAPTER XXIII. VARIOUS EXERCISES. 321 The Co-ordinates of a Rigid Body. We have already explained ( 302) how nine co-ordinates define a rigid body sufficiently for the present theory. One set of such co-ordinates with respect to any three rectangular axes may be obtained as follows. Let the element dm have the co-ordinates x, y, z, then causing the integrals to extend over the whole mass, we compute the nine quantities fxdm = Mx ; fydm = My ; fzdm = Mz ; jyzdm = Ml? ; fxzdm = M1 2 2 ; fay dm = M1 3 2 ; j(y* + z 2 ) dm = Mp, 2 ; JO 2 + z 2 ) dm = Mp 2 2 ; f(x 2 + f) dm = Mp 3 2 . The nine quantities #, y , z , I?, 1 2 2 , 1 3 2 , pf, p.?, p/ constitute an adequate system of co-ordinates of the rigid body. If 0J, 2 , ... 6 S be the canonical co-ordinates of a screw about which twists a rigid body whose co-ordinates are x , y , z , If, If, 1 3 2 , pf, pf, p 3 * with respect to the associated Cartesian axes, then the kinetic energy is Mu e 2 d 2 , where M is the mass, $ the twist velocity, and where V = a?e? + a?G? + b 2 3 2 + W + c 2 6> 5 2 + c 2 6 2 + 6^0 (^3 - #4) (0* + 0*) ~ ex. (0 5 - 6 ) (0 3 + t ) + cy (6, - 6 ) (0, + 6,} - ay, (0, - 0,) (0, + 0.) + az (0, - 2 ) (0 3 + 0.) - bz (0 3 - 4 ) (0, + 6> 2 ) + i (/>! 2 - 2 ) (0 l + <9 2 ) 2 + i (pj - &) (0 t + 6tf + \ (p 3 2 - c 2 ) (0. + 6 ) 2 - V (0* + 4 ) (O, + 0.) ~ ^ (0* + 0.) (0i + 0) - tt (0i + 0*) (0* + 04)- 232 356 THE THEORY OF SCREWS. [325- 325. A Differential Equation satisfied by the Kinetic Energy. If the pitch p of the screw 6 about which a body is twisting receive a small increment 8p while the twist velocity is unaltered the change in kinetic energy is MpSpv*. But the addition of 8p to p has the effect ( 264) of changing each canonical co-ordinate 0^ into The variation thus arising in the kinetic energy equated to that already found gives the following differential equation which must be satisfied by uf, a (Of - 0f) + b (6? - 0f) + c (0? - Oft _ dul\ 03 + 04 fduf _ du G fduf _ duf\ \d0 5 d0J _ d0 1 d0 2b d0 3 d0 2c If we assume that u e - must be a rational homogeneous function of the second order in 1) ...0 6 we can, by solution of this equation, obtain the value of UQ- given in the last Article. 326. Co-ordinates of Impulsive Screw in terms of the Instan taneous Screw. If a lt ... 6 be the canonical co-ordinates of an instantaneous screw and 771, ... r) 6 the corresponding co-ordinates of the impulsive screw, then we have ( ( J9)> 1 du a * 1 duf , e?/! = - -j , e?; 2 = --- j , &c., a d^ a da 2 and we obtain the following : + ea^ = (+ pf + a 2 ) ^ (+ p? - a 2 ) a 2 + (az - bz - If) 3 + (az, + bz - 1 3 2 ) a 4 + (- ay + cy - I?) a 5 + (- ay, - cy - If) a c - eaT;, = (+ pi 2 - a 2 ) ^ (+ pf + a 2 ) 2 + (- az - bz - 1 3 Z ) a 3 (- az + bz - I/) a 4 + (+ ay + cy - If) 6 + (+ ay, - cy - If) a G + eby 3 = (+ az, - bz, - 1 3 -) a, + (- az - bz Q - If) a 2 + (+ pf + 6 2 ) a 3 (+ p.? - b 2 ) 4 + (+ bx - cx - I*) a 5 + (6^0 + cx - /, 8 ) 6 - ebr) 4 = (+ az Q -f bz - 1 3 ) a, + (- az + bz - If) 2 (+ p 2 2 - b 2 ) a 3 (+ p./ -f b 2 ) 4 -f (- bx - cx - l^) a 5 + (- fo + cx - li 2 ) a ti + ecvjr, = (- ay + cy - If) a a + (+ ay + cy - If) 2 + (+ bx - cx - If} <* 3 (- bx - cx - If) a, + (+ pf + c 2 ) 5 (+ pf - c 2 ) 8 - ecrj e = (- ay, - cy - If) a, + (ay, - cy - If) a 2 + (+ bx + cx - If) 3 (- bx, + ex, - If) 4 + (+ pf - c 2 ) 5 + (pf + c 2 ) <V 32 9 J VARIOUS EXERCISES. 357 327. Another proof of article 303. As an illustration of the formulae just given we may verify a theorem of 303 showing that when we know the instantaneous screw corresponding to a given impulsive screw, then a ray along which the centre of gravity must lie is determined. For subtracting the second equation from the first and repeating the process with each of the other pairs, we have - 2 ) + 2^ ( 3 + 4 ) - 2y (a-, + (i ), e (773 + *7 4 ) = 26 (ots - 04) + 2x ( 5 + a ) - 2^ (! + 02), e Ofc + %) = 2c (a e - ) + 2y (j + a 2 ) - 2# ( 3 + a 4 ). Eliminating e we have two linear equations in x^y^z^ thus proving the theorem. If we multiply these equations by a. l + a^, a 3 + a 4 , ar, + 6 respectively and add, we obtain e cos (OLVJ) = 2p a , thus giving a value for e. 328. A more general Theorem. If an instantaneous screw be given while nothing further is known as to the rigid body except that the impulsive screw is parallel to a given plane A, then the locus of the centre of gravity is a determinate plane. Let A,, //,, v be the direction cosines of a normal to A, then At (^ 3 + ifc) + v (%, + i/) = 0, whence by substitution from the equations of the last Article we have a linear equation for X Q , y , z . 329. Two Three-Systems. We give here another demonstration of the important theorem of .318, which states that when two arbitrary three-systems U and V are given, it is in general possible to design and place a rigid body in one way but only in one way, such that an impulsive wrench delivered on any screw 77 of V shall make the body commence to move by twisting about some screw a of U. Let the three principal screws of the system U have pitches a, b, c and take on the same three axes screws with the pitches a, b, c respectively. These six screws lying in pairs with equal and opposite pitches form the canonical co-reciprocals to be used. 358 THE THEORY OF SCREWS. [329- As 77 belongs to the three-system V we must have the six co-ordinates of i) connected by three linear equations ( 77) ; solving these equations we have 772 = ^77! +.8773 +775, 774 = A i ll + B rj 3 + G rj s , The nine coefficients A, B, C, A , B , G , A", B", G" are essentially the co ordinates of the three-system V. We now seek the co-ordinates of the rigid body in terms of these quantities. Take the particular screw of U which has co-ordinates 1, 0, 0, 0, 0, 0. Then the co-ordinates of the corresponding impulsive screw are 77!, 772, ... where + ecu?! = p! 2 - a 2 ; + e&77 3 = az - bz - Z 3 2 ; + eC77 5 = - ay + cy - I? ; - ea77 2 = pj 2 - a 2 ; - &ii 4 = az + bz - / 3 2 ; - ec77 B = a y - cy Q - 1 2 2 . Since by hypothesis this is to belong to V, the following equations must be satisfied : 2 ~ Pi 2 = A a *_P* + B az <> ~ bzp - 1 3 2 c cy - ay, - 1* a a b c - az - bz + 1 3 2 _ , ttM-p 2 az - bz - 1 3 2 cy - ay, - I? T -a- - h -O - j- ----- HO - - b c R ,, az - z - cy - ay - cab c In like manner by taking successively for a the screws wiih co-ordinates 0, 0, 1, 0, 0, and 0, 0, 0, 0, 1, 0, we obtain six more equations of a similar kind. As these equations are linear they give but a single system of co-ordinates x , y 0> z , If, I*, 1 3 2 , P*> P*, Pa 2 for the rigid body. The theorem has thus been proved, for of course if three screws of U correspond to three screws of V then every screw in U must have its correspondent restricted to V. 330. Construction of Homographic Correspondents. If the screws in a certain three -system U be the instantaneous screws whose respective impulsive screws form the three-system V, then when three pairs of correspondents are known the determination of every other pair of correspondents may be conveniently effected as follows. 331] VARIOUS EXERCISES. 359 We know ( 279) that to generate the unit twist velocity on an instan taneous screw a an impulsive wrench on the screw r\ is required, of which the intensity is COS the mass being for convenience taken as unity. Let a, ft, 7 be three of the instantaneous screws in U, and let 77, , be their respective impulsive screws in V. Let d, ft, 7 be the component twist velocities on a, ft, y of a twist velocity p on any other screw p, belonging to the system U. Then the impulsive wrench on V, which has p as its instantaneous screw will have as its components on 77, , f the respective quantities 7 \ ^> ~ / 7T^\ P) "/ L,\ 7- cos (a?7) cos (p) cos (7^) These are accordingly the co-ordinates of the required impulsive wrench. 331. Geometrical Solution of the same Problem. When three pairs of correspondents in the two impulsive and instan taneous systems of the third order V and U are known we can, in general, obtain the impulsive screw in V corresponding to any instantaneous screw p in U as follows. Choose any screw other than p in the three- system U and draw the cylindroid H through that screw arid p. Every screw on a cylindroid thus obtained must of course belong to U. Then H must have a screw in common with the cylindroid (a/3) drawn through a and ft, for this is necessarily true of any two cylindroids which lie in the same three-system. In like manner H must also have a screw in common with the cylindroid (ay) drawn through a and 7. But by the principle of 292 the several pairs of correspondents on the instantaneous cylindroid (aft) and the impulsive cylindroid (77 ) are determined. Hence the impulsive screw corresponding to one of the screws in H is known. In like manner the known pairs on the two cylindroids (ay) and (77^) will discover the impulsive screw corresponding to another instantaneous screw on H. As therefore we know the impulsive screws corresponding to two of the screws on H we know the cylindroid H which contains all the impulsive screws severally corresponding to instan taneous screws on H, of which of course p is one. But by 293 we can now correlate the pairs on H and H , and thus the required correspondent to p is obtained. 360 THE THEORY OF SCREWS. [332, 332. Co-reciprocal Correspondents in two Three-systems. If U be an instantaneous three-system and V the corresponding im pulsive three-system it is in general possible to select one set of three co-reciprocal screws in U whose correspondents in V are also co-reciprocal. As a preliminary to the formal demonstration we may note that the number of available constants is just so many as to suggest that some finite number of triads in U ought to fulfil the required condition. In the choice of a screw a in U we have, of course, two disposable quantities. In the choice of /3 which while belonging to U is further reciprocal to a there is only one quantity disposable. The screw belonging to U, which is reciprocal both to a and /?, must be unique. It is in fact reciprocal to five independent screws, i.e. to three of the screws of the system reciprocal to U, and to a and /3 in addition. We have thus, in general, neither more nor fewer than three disposable elements in the choice of a set of three co-reciprocal screws a, /3, 7 in U. This is just the number of disposables required for the adjustment of the three correspondents rj, , in V to a co-reciprocal system. We might, therefore, expect to have the number of solutions to our problem finite. We are now to show that this number is unity. Taking the six principal screws of inertia of the rigid body as the screws of reference, we have as the co-ordinates of any screw in U Xa 6 4- fA/3 6 -|- vy 6) where X, p,, v are numerical parameters. The co-ordinates of the corresponding screw in V are P! (Xctj + fji/Sj. + i/ 7l ), p 2 (Xa 2 + pfa where for symmetry p 1} . . . p 6 are written instead of + a, a, + b, b, &c. Three screws in U are specified by the parameters X , //, z/; X", //,", v"; X ", p", v". If these screws are reciprocal, we have = 2 P1 (Va, + /& + i/ 7l ) (X" ai + /*"& + *" 7l ), or = \ \"p a + n ^ pt + v v "p y + (X>" + XV) *r*p + (XV + XV) OTay + (ii and two similar equations. 333] VARIOUS EXERCISES. 361 If the corresponding impulsive screws are reciprocal, then o = xv^v + /*y SfV/Si 2 + * v Spi v + (*>" + vy ) SiVaA + (XV" + XV) SlvXTi + (pv" + ^ V and two similar equations. Take the two conies whose equations are = p a = a these conies will generally have a single common conjugate triangle. If the co-ordinates of the vertices of this triangle be X , ///, v ; X", // , z/ ; X ", //", v" \ then the equations just given in these quantities will be satisfied ; and as there is only one such triangle, the required theorem has been proved. It can be easily proved that a similar theorem holds good for a pair of impulsive and instantaneous cylindroids. 333. Impulsive and Instantaneous Cylindroids. If a given cylindroid U be the locus of the screws about which a free rigid body would commence to twist if it had received an impulsive wrench about any screw on another given cylindroid V, it is required to calculate so far as practicable the co-ordinates of the rigid body. Let us take our canonical screws of reference so that the two principal screws of the cylindroid U have as co-ordinates 1, 0, 0, 0, 0, 0, 0, 0, 1, 0, 0, 0. The co-ordinates of any other screw on U will be a lt 0, 3 , 0, 0, 0. The cylindroid F will be determined by four linear equations in the co-ordinates of rj. These equations may with perfect generality be written thus ( 77), where A, B, A , B , A", B", A ", B " are equivalent to the eight co-ordinates defining the cylindroid V. The screw on U with co-ordinates 1, 0, 0, 0, 0, 362 THE THEORY OF SCREWS. [333, will have its corresponding impulsive screw defined by the equations ( 326) + ear]! = pi 2 + a? ; - ea^ = p x 2 - a 2 ; + ebrjs = az bz - I? ; ebrj 4 = az + bz l s 2 ; + ecrj 5 = cy - ay -1 2 2 ; - ecr) 6 = - ay - cy - Z 2 2 . By substituting these in the equations just given, we obtain az - bz - l s 2 _ . a? + pi* ^ a 2 - pi 2 b a a - az n - bz + 1 3 2 , a? + p? , a 2 - Pl 2 - - . - a cy - ay - I? = > , a 2 + pi 2 ay + cy, + 1? _ A> ,, a? + p, 2 + B// , d? - pf c a a In like manner from the screw on U 0, 0, 1, 0, 0, we obtain + arj l = az Q bz ti I/ , ur)-> = az bz / 3 2 ; + brj 3 = p, 2 + 6 2 ; -6174= p-?-b*; + crj 5 = bx CX l*\ Crf = bx + CC If. Introducing these into the equations for 77, we have az - bz - I/ 7 az + bz + 1 3 2 = A -- --- h x> a a 6 2 - p 2 2 . , az - bz - 1 3 2 D , az + bz , r = A +n a a - bz - Z 3 2 az + bz r caa - bx - cx + /j 2 . , az - bz - l<? n ,,, az + bz + 1 3 * J\. i -*- c a a Thus we have eight equations while there are nine co-ordinates of the rigid body. This ambiguity was, however, to be expected because, as proved in 306, there is a singly infinite number of rigid bodies which stand to the two cylindroids in the desired relation. The equations, however, contain one short of the total number of co ordinates ; aa , y , z , I, 2 , I, 2 , 1 3 2 , p, 2 , p 2 2 are all present but p 3 2 is absent. 334] VARIOUS EXERCISES. 363 Hence from knowing the two cylindroids eight of the co-ordinates of the rigid body are uniquely fixed while the ninth remains quite indeter minate. Every value for p 3 2 will give one of the family of rigid bodies for which the desired condition is fulfilled. We have already deduced geometrically ( 306) the relations of these rigid bodies. We now obtain the same results otherwise. The momental ellipsoid around the centre of gravity has as its equation (x - x o y- pS +(y- 7/ ) 2 p.? + (z- ztf p s 2 - 2 (y - y ) (z - z,) I? - 2 (z - z ) (as - ) 4 2 - 2 (x - a? ) (y - y,} 1 3 2 - (yx, - xytf - ( z y - y z *f - ( xz - zx T = & This may be written in the form tf(z-ztf = R, where p 3 2 does not enter into R. As /> 3 2 varies this equation represents a family of quadrics which have contact along the section of R = by the plane z z^ = 0. This proves that a plane through the common centre of gravity and parallel to the principal plane of the cylindroid U passes through the conic along which the momental ellipsoids of all the different possible bodies have contact. All these quadrics touch a common cylinder along this conic. The infinite point on the axis of this cylinder is the pole of the plane z - Z Q for each quadric. Every chord parallel to the axis of the cylinder passes through this pole and is divided harmonically by the pole and the plane z z = 0. As the pole is at infinity it follows that in every quadric of the system a chord parallel to the axis of the cylinder is bisected by z z . Hence a diameter parallel to the axis of the cylinder is conjugate to the plane z z in every one of the quadrics. Thus by a different method we arrive at the theorems of 306. 334. The Double Correspondents on Two Cylindroids. Referring to the remarkable homography between the impulsive screws on one cylindroid V and the corresponding instantaneous screws on another cylindroid U we have now another point to notice. If the screws on U were the impulsive screws, while those on V were the instantaneous screws, there would also have been a unique homography, the rigid bodies involved being generally distinct. But of course these homographies are in general quite different, that is to say, if A be a screw in U the instantaneous cylindroid, and B be its corre spondent in V the impulsive cylindroid, it will not in general be true that if 364 THE THEORY OF SCREWS. [334- A be a screw in U the impulsive cylindroid, then B will be its instantaneous screw in V the instantaneous cylindroid. It is however to be now shown that there are two screws H 1 a,nd H 2 on U, and their correspondents K 1 and K 3 on V, which possess the remarkable characteristic that whether V be the impulsive cylindroid and U the instan taneous cylindroid or vice versa, in either case H l and K l are a pair of corre spondents, and so are H 2 and K z . Let B 1} B 2 , B 3 , &c. be the screws on U corresponding severally to the screws A l} A. 2 , A 3 , &c., on V when V is the impulsive cylindroid and U the instantaneous cylindroid. Let G l} C 2 , C 3 , &c., be the screws on U corresponding severally to the screws A l} A 2 , A 3 , &c., on V when U is now the impulsive cylindroid, and V the instantaneous cylindroid. The systems A lt A 3 , A,, &c., and B,, B.,, B 3 , &c., are homographic. The systems C lt a , C s , &c., and A lt A s , A 3 , &c., are homographic. Hence also, The systems B lt B. 2 , B 3 , &c., and C lt C*, C 3 , &c. are homographic. Let 7/j, HZ be the two double screws on U belonging to this last homo- graphy, then their correspondents K l} K 2 on V will be the same whether U be the impulsive cylindroid and V the instantaneous cylindroid or vice versa. There can be no other pairs of screws on the two cylindroids possessing the same property. 335. A Property of Co-reciprocals. Let a, /3, 7 be any three co-reciprocal screws. If 77, ff, are the three screws on which impulsive wrenches would cause a free rigid body to twist about a, /3, 7 respectively, then cos (af ) cos (17) cos ( 7 ) + cos (a) cos () cos (77;) = 0. We have from 281 the general formula cos fy + cos cos a?; cos but as a and /3 are reciprocal each side of this equation must be zero. We thus have Pa cos , = - -- cos ^ -/ cos (017) cos 337] VARIOUS EXERCISES. 365 and similarly, COS (yf;) = --,- _ COS COS ( 7 ) Pv i v\ P- / _ cos(a) = . N cos cos ( 7 ) cos (a?;) whence we obtain cos (a) cos (fir)) cos ( 7 f ) + cos (a) cos (/3) cos (yrf) = 0, for it is shown in 283 that p a -:- cos (a??) or the other similar expressions can never be zero. 336. Instantaneous Screw of Zero Pitch. Let a be an instantaneous screw of zero pitch. Let two of the canonical co-reciprocals lie on a, then the co-ordinates of a are i, i o, o, o, o. The co-ordinates of the impulsive screw ij are given by the formulae of 32G which show that We thus have (i + Oa) (Vi + fc) + ( 3 + 04) (ife + ^4) + ( 5 + ) (77, + 77 6 ) = 0, which proves what we already knew, namely, that a and 77 are at right angles (S 293). We also have 2/0 (l?3 + ^4) + ^0 (l?5 + %) = 0, which proves the following theorem : If the instantaneous screw have zero-pitch then the centre of gravity of the body lies in the plane through the instantaneous screw and perpendicular to the impulsive screw. 337. Calculation of a Pitch Quadric. If a, fi, 7 be three instantaneous screws it is required to find with respect to the principal axes through the centre of gravity, the equation to the pitch quadric of the three-system which contains the three impulsive screws corre sponding respectively to a, @, 7 . The co-ordinates of these screws are expressed with reference to the six principal screws of inertia. We make the following abbreviations : A = a? (a* - 2 2 ) + b* ( 3 2 - 4 2 ) + c 3 ( 5 2 - a 6 2 ), B = a? (&*- /3 2 2 ) + 6 3 (/3 3 - - &*) + c s (& 2 - & a ), C=a? ( 7l 2 - 366 THE THEORY OF SCREWS. [337 P = + bcx ((A - A) (73 - 74) ~ (A - A) ( 7s - 7.)), + ca y ((75 7) (& ~ &) ~~ (71 ~ 72) (& A))> Q = + bcx ((a, - a 4 ) (75 - 7 6 ) - (a 5 - a 6 ) (73 - 7,)), + acy ((71 - 7 2 ) ( 5 - 6 ) - (i - <* 2 ) (75 - 7e)) + abz ((! - 2 ) (73 - 74) - (a, - 4 ) (7! - 7,,)) ; - a a) (A" A) (& /3 2 ) ( 5 tte)), ^ = a 3 (: + a) (A - &) + 6 s (a, + a 4 ) (A - A) + c 3 (* 5 + a 6 ) (/3 6 - /3 6 ), Z^ a = a 3 (A + /3 2 ) (aj - 2 ) + 6 3 (/3 3 + A) ( 8 - "4) + c 3 (A + A) ( a s - e) I Z ay = a 3 (d + a) (71 - 72) + b 3 ( 3 + 4 ) (73 - 74) + c 3 (cc 5 + 6 ) (75 - 7), ^ya = tt 3 (7x + 7 2 ) (! - a s ) + 6 3 (7s + 74) (3 ~ 4 ) + C 3 (75 + 7e) (s - a e) I X 0y = a 3 (A + A) (7i - 72) + ^ 3 (A + &) (73 - 74) + c 3 (A + A) (7s ~ 7e), The required equation is then as follows : = A, -R + L^, R + L afi , B, - Q + L ay , P + Lfiy , C CHAPTER XXIV. THE THEORY OF SCREW-CHAINS*. 338. Introduction. In the previous investigations of this volume the Theory of Screws has been applied to certain problems in the dynamics of one rigid body. I propose to show in the present chapter to what extent the conceptions and methods of the Theory of Screws may be employed to elucidate certain problems in the dynamics of any material system whatever. By such a system I mean an arbitrary arrangement of /j, rigid bodies of any form or construction, each body being either entirely free or con strained in any manner by relations to fixed obstacles or by connexions of any kind with one or more of the remaining p 1 pieces. For convenience we may refer to the various bodies in the system by the respective numerals 1, 2, ... /n. This numbering may be quite arbitrary, and need imply no reference whatever to the mechanical connexions of the pieces. The entire set of material parts I call for brevity a mass-chain, and the number of the bodies in a mass-chain may be anything from unity to infinity. I write, as before, of only small movements, but even with this limitation problems of equilibrium, of small oscillations and of impulsive movements are included. By the order of the freedom of the mass-chain, I mean the number of generalized co-ordinates which would be required to specify a position which that mass-chain was capable of assuming. The order cannot be less than one (if the mass- chain be not absolutely fixed), while if each element of the mass-chain be absolutely free, the order will be as much as 6/i. Starting from any arbitrary position of the mass-chain, let it receive a small displacement. Each element will be displaced from its original position to an adjacent position, compatible of course with the conditions * Transactions Royal Irish Acad. Vol. xxvm. p. 99 (1881). 368 THE THEORY OF SCREWS. [338- imposed by the constraints. The displacement of each element could, however, have been effected by a twist of appropriate amplitude about a screw specially correlated to that element. The total effect of the displace ment could, therefore, have been produced by giving each element a certain twist about a certain screw. 339. The Graphic and Metric Elements. In the lowest type of freedom which the mass-chain can possess (short of absolute fixity) the freedom is of the first order, and any position of the mass-chain admits of specification by a single co-ordinate. In such a case the screw appropriate to each element is unique, and is completely determined by the constraints both in position and in pitch. The ratio of the amplitude of each twist to the amplitudes of all the other twists is also prescribed by the constraints. The one co-ordinate which is arbitrary may be conveniently taken to be the amplitude of the twist about the first screw. To each value of this co-ordinate will correspond a possible position of the mass-chain. As the ratios of the amplitudes are all known, and as the first amplitude is given, then all the other amplitudes are known, and consequently the position assumed by every element of the mass-chain is known. The whole series of screws and the ratios of the amplitudes thus embody a complete description of the particular route along which the mass-chain admits of displacement. The actual position of the mass-chain is found by adding to the purely graphic element which describes the route a metric element, to indicate the amplitude through which the mass-chain has travelled along that route. This amplitude is the arbitrary co-ordinate. 340. The Intermediate Screw. It will greatly facilitate our further progress to introduce a conventional process, which will clearly exhibit the determinate character of the ratios of the amplitudes in the screw series. Consider the two first screws, i and or 2 of the series. Draw the cylindroid (o. l , 2 ) which contains these two screws. Since a l and 2 are appropriated to two different elements of the mass-chain, no kinematical significance can be attached to the composition of the two twists on j and 2 . If, however, the two twists on j and a 2 , having the proper ratio of amplitudes, had been applied to a single rigid body, the dis placement produced is one which could have been effected by a single twist about a single screw on the cylindroid (a l} et 2 ). If this inter mediate screw be given, the ratio of the amplitudes of the twists on the given screws is determined. It is in fact equal to the ratio of the sines of the angles into which the intermediate screw divides the angle between the two given screws. With a similar significance we may conceive an intermediate screw inserted between every consecutive pair of the p original screws. 342] THE THEORY OF SCREW-CHAINS. 369 341. The definition of a Screw-chain. It will be convenient to have a name which shall concisely express the entire series of /A original screws with the //, 1 intermediate screws whose function in determining the amplitudes has just been explained. We may call it a screw-chain. A twist about a screw-chain will denote a displace ment of a mass-chain, produced by twisting each element about the corresponding screw, through an amplitude whose ratio to the amplitudes on the two adjacent screws is indicated by the intermediate screws. The amplitude of the entire twist will, as already mentioned, be most conveniently expressed by the twist about the first screw of the chain. We hence have the following statement : The most general displacement of which a mass-chain is capable can be produced by a twist about a screw-chain. 342. Freedom of the first order. Given a material system of p elements more or less connected inter se, or related to fixed points or supports : let it be required to ascertain the freedom which this material system or mass-chain enjoys. The freedom is to be tested by the capacity for displacement which the mass-chain possesses. As each such displacement is a twist about a screw-chain, a complete examina tion of the freedom of the mass-chain will require that a trial be made to twist the mass-chain about every screw-chain in space which contains the right number of elements /u,. If in the course of these trials it be found that the mass-chain cannot be twisted about any screw-chain, then the system is absolutely rigid, and has no freedom whatever. If after all trials have been made, one screw-chain, and only one, has been discovered, then the mass-chain has freedom of the first order, and we have the result thus stated : When a mass-chain is so limited by constraints, that its position can be expressed by a single co-ordinate, then the mass-chain is said to have freedom of the first order, and its possible movements are solely those which could be accomplished by twisting about one definite screw-chain. By this method of viewing the question we secure the advantage of eliminating, as it were, the special characters of the constraints. The essential moving parts of a steam-engine, for example, have but one degree of freedom. Each angular position of the fly-wheel necessarily involves a definite position of all the other parts. A small angular motion of the fly wheel necessarily involves a definite small displacement of each of the other parts. Complicated as the mechanism may be, it is yet always possible to construct a screw-chain, a twist about which would carry each element from its original position into the position it assumes after the displacement has been effected. B. 24 370 THE THEORY OF SCREWS. [343 343. Freedom of the second order. Suppose that after one screw-chain has been discovered, about which the mass-chain can be twisted, the search is continued until another screw-chain is detected of which the same can be asserted. We are now able to show, without any further trials whatever, that there must be an infinite number of other screw -chains similarly circumstanced. For, compound a twist of amplitude a on one chain, a, with the twist of amplitude /3 on the other, /?. The position thus attained could have been attained by a twist about some single chain 7. As a and /3 are arbitrary, it is plain that 7 can be only one of a system of screw-chains at least singly infinite in number about which twisting must be possible. The problem to be considered may be enunciated in a somewhat more symmetrical manner, as follows : To determine the relations of three screw-chains, a, /3, 7, such that if a mass-chain be twisted with amplitudes of, ft , 7 , about each of these screw- chains in succession, the mass-chain will regain the same position after the last twist which it had before the first. This problem can be solved by the aid of principles already laid down (Chap. H.). Each element of the mass-chain receives two twists about a and /3 ; these two twists can be compounded into a single twist about a screw lying on the cylindroid defined by the two original screws. We thus have for each element a third screw and amplitude by which the required screw-chain 7 and its amplitude 7 can be completely determined. A mass-chain free to twist to and fro on the chains a and /3 will therefore be free to twist to and fro on the chain 7. These three chains being known, we can now construct an infinite number of other screw-chains about which the mass-chain must be also able to twist. Let 8 be a further screw-chain of the system, then the screws OL I} /3 1( 7^ 8 1 which are the four first screws of the four screw-chains must be co- cylindroidal ; so must 2 > A, y 2 , 8 2 and each similar set. We thus have ^ cylindroids determined by the two first chains, and each screw of every chain derived from this original pair will lie upon the corresponding cylindroid. We have explained ( 125) that by the anharmonic ratio of four screws on a cylindroid we mean the anharmonic ratio of a pencil of four lines parallel to these screws. If we denote the anharmonic ratio of four screws such as i> &, 7i> Si b y tne symbol [i, fii, 71, $1], then the first theorem to be now demonstrated is that [i, &, 71, S,]=[ 2 , &, 72> &&gt;] = &c. = [a M , $1, 7 M , M ], or that the anharmonic ratio of each group is the same. 343] THE THEORY OF SCREW-CHATNS. 371 This important proposition can be easily demonstrated by the aid of fundamental principles. The two first chains, a and /3, will be sufficient to determine the entire series of cylindroids. When the third chain, 7, is also given, the construction of additional chains can proceed by the anharmonic equality without any further reference to the ratios of the amplitudes. When any screw, 8 l} is chosen arbitrarily on the first cylindroid, then 8 2 , 6 3 , &c., ... 8^, are all determined uniquely; for a twist about ^ can be decomposed into twists about x and &. The amplitudes of the twists on ofj and & determine the amplitudes on or 2 and /3 2 by the property of the intermediate screws which go to make up the screw-chains, and by com pounding the twists on a., and /8 2 we obtain S 2 . If any other screw of the series, for example, 8 2 , had been given, then it is easy to see that ^ and all the rest, 8 3 , ... B^, are likewise determined. Thus for the two first cylindroids, we see that to any one screw on either corresponds one screw on the other. If one screw moves over the first cylindroid then its correspondent will move over the second and it will now be shown that these two screws trace out two homographic systems. Let us suppose that each screw is specified by the tangent of the angle which it makes with one of the principal screws of its cylindroid. Let l , fa be the angles for two corresponding screws on the first arid second cylindroids, then we must have some relation which connects tan 1 and tan^j. But this relation is to be consistent with the condition that in every case one value of tan l is to correspond to one value of tan fa, and one value of tan fa to one value of tan lf If for brevity we denote tan 6 l by x and tan fa by x then the geometrical conditions of the system will give a certain relation between x and x . The one-to-one condition requires that this relation must be capable of being expressed in either of the forms x=U ; x =U, where U is some function of x and where U is a function of x. From the nature of the problem it is easily seen that these functions are algebraical and as they must be one valued they must be rational. If we solve the first of these equations for x the result that we obtain cannot be different from the second equation. The first equation must therefore contain x only in the first degree in the form (see Appendix, Note 7) / / / px +q The relation between tan 0^ and tan fa will therefore have the form which may generally be thus expressed, a tan 1 tan fa+b tan l + c tan <f> 1 + d = 0. 242 372 THE THEORY OF SCREWS. [343 Let &!, 6.,, :j , 4 be the angles of four screws on the first cylindroid, then the anharmonic ratio will be sin (0 4 -6> 3 ) sin (02-00 From the relation just given between tan0 1( tau^, which applies of course to the other corresponding pair, it will be easily seen that this anharmonic ratio is unaltered when the angles < 1; < 2 , &c., are substituted for 1? 2 , &c. We have, therefore, shown that the anharmonic ratio of four screws on the first cylindroid is equal to that of the four corresponding screws on the second cylindroid, and so on to the last of the //, cylindroids. As soon, therefore, as any arbitrary screw Sj has been chosen on the first cylindroid, we can step from one cylindroid to the next, merely guided in choosing S 2 , S 3 , &c., by giving a constant value to the anharmonic ratio of the screw chosen and the three other collateral screws on the same cylindroid. Any number of screw-chains belonging to the system may be thus readily constructed. This process, however, does not indicate the amplitudes of the twists appropriate to S lt S 2 , & 3 , &c. One of these amplitudes may no doubt be chosen arbitrarily, but the rest must be all then determined from the geometrical relations. We proceed to show how the relative values of these amplitudes may be clearly exhibited. The first theorem to be proved is that in the three screw-chains a, ft, 7 the screws intermediate to ! and 2 , to /3j and (3. 2 , to y 1 and j 2 are co- cylindroidal. This important step in the theory of screw-chains can be easily inferred from the fundamental property that three twists can be given on the screw-chains a, /3, 7, which neutralize, and that consequently the three twists on the screws a 1 , j3 1} <y l will neutralize, as will also those on a 2 , /3 2 , 72- These six twists must neutralize when compounded in any way whatever. We shall accordingly compound a x and a 2 into one twist on their intermediate screw, and similarly for /^ and /3 2 , and for y l and 73. We hence see that the three twists about the three intermediate screws must neutralize, and consequently the three intermediate screws must be co-cylindroidal. We thus learn that in addition to the several cylindroids containing the primary screws of each of the system of screw-chains about which a mass- chain with two degrees of freedom can twist, there are also a series of secondary cylindroids, on which will lie the several intermediate screws of the system of screw-chains. If Sj be given, then it is plain that the intermediate screw between Sj and 8 2 , as well as all the other screws of the chain and their intermediate 343] THE THEORY OF SCREW-CHAINS. 373 screws, can be uniquely determined. If, however, the intermediate screw between S x and 8 2 be given, the entire chain 8 is also determined, yei it is not immediately obvious that that determination is unique. We can, however, show as follows that this is generally the case. Let S 12 denote the given intermediate screw, and let this belong, not only to the chain S 1} 8 2 , &c., but to another chain &/, 8 2 , &c. We then have S 1} <5 12 , 8. 2 co-cylindroidal, and also S/, 8^, 8 2 co-cylindroidal. Decom pose any arbitrary twist of amplitude 6 on S 12 into twists on 8 L and 2 , and a twist of amplitude 6 on the same 8 12 into twists on 8/ and S 2 . Then the four twists must neutralize ; but the two twists on S/ and S t compound into a twist on a screw on the first cylindroid of the system ; and / and 6 2 into a twist on the second cylindroid of the system ; and as these two resultant twists must be equal and opposite it follows that they must be on the same screw, and that, therefore, the cylindroids belonging to the first and second elements of the system must have a common screw. It is, however, not generally the case that two cylindroids have a common screw. It is only true when the two cylindroids are themselves included in a three-system, this could only arise under special circumstances, which need not be further con sidered in a discussion of the general theory. It follows from the unique nature of the correspondence between the intermediate cylindroids and the primary cylindroids that one screw on any cylindroid corresponds uniquely to one screw on each of the other cylindroids; the correspondence is, therefore, homographic. We have now obtained a picture of the freedom of the second order of the most general type both as to the material arrangement and the character of the constraints : stating summarily the results at which we have arrived, they are as follows : A mass-chain of any kind whatever receives a small displacement. This displacement is under all circumstances a twist about a screw-chain. If the mass-chain admits of a displacement by a twist about a second screw- chain, then twists about an infinite number of other screw-chains must also be possible. To find, in the first place, a third screw-chain, give the mass- chain a small twist about the first chain ; this is to be followed by a small twist about the second chain : the position of the mass-chain thus attained could have been reached by a twist about a third screw-chain. The system must, therefore, be capable of twisting about this third screw-chain. When three of the chains have been constructed, the process of finding the re mainder is greatly simplified. Each element of the mass-chain is, in each of the three displacements just referred to, twisted about a screw. These three screws lie on one cylindroid appropriate to the element, and there are just so many of these cylindroids as there are elements in the mass-chain. 374 THE THEORY OF SCREWS. [343- Betvveen each two screws of a chain lies an intermediate screw, introduced for the purpose of defining the ratio of the amplitudes of the two screws of the chain on each side of it. In the three chains two consecutive elements will thus have three intermediate screws. These screws are co-cylindroidal. We thus have two series of cylindroids : the first of these is equal in number to the elements of the mass-chain (/it), each cylindroid corresponding to one element. The second series of cylindroids consists of one less than the entire number of elements (^ - 1). Each of these latter cylindroids corre sponds to the intermediate screw between two consecutive elements. An entire screw-chain will consist of fju primary screws, and //, 1 intermediate screws. To form such a screw-chain it is only necessary to inscribe on each of the 2yu, 1 cylindroids a screw which, with the other three screws on that cylindroid, shall have a constant anharmonic ratio. Any one screw on any one of the 2/^1 cylindroids may be chosen arbitrarily ; but then all the other screws of that chain are absolutely determined, as the anharmonic ratio is known. The mass-chain which is capable of twisting about two screw-chains cannot refuse to be twisted about any other screw-chain con structed in the manner just described. It may, however, refuse to be twisted about any screw-chains not so constructed ; and if so, then the mass-chain has freedom of the second order. 344. Homography of Screw-systems. Before extending the conception of screw-chains to the examination of the higher orders of freedom, it will be necessary to notice some extensions of the notions of homography to the higher orders of screw systems. On the cylindroid the matter is quite simple. As we have already had occasion to explain, we can conceive the screws on two cylindroids to be homo- graphically related, just as easily as we can conceive the rays of two plane pencils. The same ideas can, however, be adapted to the higher systems of screws the 3rd, the 4th, the 5th while a case of remarkable interest is presented in the homography of two systems of the 6th order. The homography of two three-systems is completely established when to each screw on one system corresponds one screw on the other system, and conversely. We can represent the screws in a three-system by the points in a plane (see Chap. xv.). We therefore choose two planes, one for each of the three-systems, and the screw correspondence of which we are in search is identical with the homographic point-correspondence between the two planes. We have already had to make use in 317 of the fundamental property that when four pairs of correspondents in the two planes are given then the correspondence between every other pair of points is determined by 345] THE THEORY OF SCREW-CHAINS. 375 rigorous construction. Any fifth point in one plane being indicated, the fifth point corresponding thereto in the other plane can be determined. It therefore follows that when four given screws on one three-system are the correspondents of four indicated screws on the other system, then the correspondence is completely established, and any fifth screw on one system being given, its correspondent on the other is determined. 345. Freedom of the third order. We are now enabled to study the small movements of any mass-chain which has freedom of the third order. Let such a mass-chain receive any three displacements by twists about three screw-chains. It will, of course, be understood that these three screw-chains are not connected in the specialized manner we have previously discussed in freedom of the second order. In such a case the freedom of the mass-chain would be of the second order only and not of the third. The three screw-chains now under consideration are perfectly arbitrary ; they may differ in every con ceivable way, all that can be affirmed with regard to them is that the number of primary screws in each chain must of course be equal to fj,, i.e. to the number of material elements of which the mass-chain consists. It may be convenient to speak of the screws in the different chains which relate to the same element (or in the case of the intermediate screws, the same pair of elements) as homologous screws. Each set of three homologous screws will define a three-system. Compounding together any three twists on the screw-chains, we have a resultant displacement which could have been effected by a single twist about a fourth screw-chain. The first theorem to be proved is, that each screw in this fourth screw-chain must belong to the three-system which is defined by its three homologous screws. So far as the primary screws are concerned this is immediately seen. Each element having been displaced by three twists about three screws, the resultant twist must belong to the same three-system, this being the im mediate consequence of the definition of such a system. Nor do the inter mediate screws present much difficulty. It must be possible for appropriate twists on the four screw-chains to neutralize. The four twists which the first element receives must neutralize : so must also the four twists imparted to the second element. These eight twists must therefore neutralize, however they may be compounded. Taking each chain separately, these eight twists will reduce to four twists about the four intermediate screws : these four twists must neutralize ; but this is only possible if the four intermediate screws belong to a three-system. On each of fj, primary three-systems, and on each of yu, 1 intermediate three-systems four screws are now supposed to be inscribed. We are to 376 THE THEORY OF SCREWS. [345, determine a fifth screw about which the system even though it has only freedom of the third order, must still be permitted to twist. To begin with we may choose an arbitrary screw in any one of the three- systems. In the exercise of this choice we have two degrees of latitude; but once the choice has been made, the remainder of the screw-chain is fixed by the following theorem : If each set of five homologous screws of five screw-chains lies on a three- system, and if a mass-chain be free to twist about four of these screw-chains, it will also be free to twist about the fifth, provided each set of homologous screws is homographic with every other set. Let 8 denote the fifth screw-chain. If 8 l be chosen arbitrarily on the three-system which included the first element, then a twist about 8 l can be decomposed into three twists on a t> /8 lf 7,. By the intermediate screws these three twists will give the amplitudes of the twists on all the other screws of the chains a, /3, y, and each group of three homologous twists being compounded, will give the corresponding screws on the chain 8. We thus see that when 8, is given, 8 2 , 8 3 , &c., are all determinate. It is also obvious that if S 2 , or any other primary screw of the chain, were given, then all the other screws of the chain would be determined uniquely. If, however, an intermediate screw, 8 12 , had been given, then, although the conditions are, so far as number goes, adequate to the determination of the screw-chain, it will be necessary to prove that the determination is unique. This is proved in the same manner as for freedom of the second order ( 343). If there were two screw-chains which had the same inter mediate screw, then it must follow that the two primary three-systems must have a common screw, which is not generally the case. We have thus shown that when any one screw of the chain 8, whether primary or intermediate, is given, then all the rest of the screws of the chain are uniquely determinate. Each group of five homologous screws must therefore be homographic. It is thus easy to construct as many screw-chains as may be desired, about which a mass-chain which has freedom of the third order must be capable of twisting. It is only necessary, after four chains have been found, to inscribe an arbitrary screw on one of the three-systems, and then to construct the corresponding screw on each of the other homologous systems. In choosing one screw of the chain we have two degrees of latitude: we may, for example, move the screw chosen over the surface of any cylindroid embraced in the three-system: the remaining screws of the screw-chain, primary and intermediate, will each and all move over the surface of corre sponding cylindroids. 346] THE THEORY OF SCREW-CHAINS. 377 If the mass-chain cannot be twisted about any screw- chain except those we have now been considering, then the mass-chain is said to have freedom of the third order. If, however, a fourth screw-chain can be found, about which the system can twist, and if that screw-chain does not belong to the doubly infinite system just described, then the mass-chain must have freedom of at least the fourth order. 346. Freedom of the fourth order. The homologous screws in the four screw-chains about which the mass- chain can twist form each a four-system. All the other chains which can belong to the system m.ust consist of screws, one of which lies on each of the four-systems. It will facilitate the study of the homography of two four-systems to make use of the analogy between the homography of two spaces and the homography of two four-systems as already we had occasion to do in 317. A screw in a four-system is defined by four homogeneous co-ordinates whereof only the ratios are significant. Each screw of such a system can therefore be represented by one point in space. The homography of two spaces will be completely determined if five points, a, b, c, d, e in one space, and the five corresponding points in the other space, a, b , c , d , e are given. From the four original screw-chains we can construct a fifth by com pounding any arbitrary twists about two or more of the given chains. When five chains have been determined, then, by the aid of the principle of homo graphy, we can construct any number. That each set of six homologous screws is homographic with every other set can be proved, as in the other systems already discussed. With respect to the intermediate screws a different proof is, however, needed to show that when one of these screws is given the rest of the chain is uniquely de termined. The proof we now give is perhaps simpler than that previously used, while it has the advantage of applying to the other cases as well. Let a, /3, 7, 8 be four screw-chains, and let e I2 , an intermediate screw of the chain e, be given. We can decompose a twist on e 12 into components of definite amplitude on a I2 , &,, 7,3, 8 K . The first of these can be decomposed into twists on c^ and a. 2 ; the second on & and /3 2 , &c. Finally, the four twists on !, &, 7!, 8 1 can be compounded into one twist, e,, and those on 2, &, 7 2 , 8-2 compounded into a twist on e 2 . In this way it is obvious that when e 12 is given, then ej and e 2 are uniquely determined, and of course the same reasoning applies to the whole of the chain. We thus see that when any screw of the chain is known, then all the rest are uniquely determined, and therefore the principle of homography is applicable. 378 THE THEORY OF SCREWS. [346- In the choice of a screw-chain about which a mass-chain with four degrees of freedom can twist there are three arbitrary elements. We may choose as the first screw of the chain any screw from a given four-system. If one screw of the chain be moved over a two-system, or a three-system included in the given four-system, then every other screw of the chain will also describe a corresponding two-system or three-system. 347. Freedom of the fifth order. In discussing the movements of a system which has freedom of the fifth order, the analogies which have hitherto guided us appear to fail. Homo- graphic pencils, planes, and spaces have exhibited graphically the relations of the lower degrees of freedom ; but for freedom of the fifth degree these illustrations are inadequate. No real difficulty can, however, attend the extension of the principles we have been considering to the freedom of the fifth order. We can conceive that two five-systems are homographically related, such that to each screw on the one corresponds one screw on the other, and conversely. To establish the homography of the two systems it will be necessary to know the six screws on one system which correspond to six given screws on the other : the screw in either system corresponding to any seventh screw in the other is then completely determined. In place of the methods peculiar to the lower degrees of freedom, we shall here state the general analytical process which is of course available in the lower degrees of freedom as well. A screw 6 in a five-system is to be specified by five co-ordinates 1 , # 2 , B 3 , 64, B 5 . These co-ordinates are homogeneous; but their ratios only are con cerned, so they are equivalent to four data. The five screws of reference may be any five screws of the system. Let <f> be the screw of the second system which is to correspond to 6 in the first system. The co-ordinates of <f> may be referred to any five screws chosen in the second system. It will thus be seen that the five screws of reference for <j> are quite different from those of 6. The geometrical conditions expressing the connection between </> and 9 will give certain equations of the type where t/j, ..., U 5 are homogeneous functions of B lt ..., 9 5 . These equations express that one 9 determines one <f>. As however one < is to determine one 9 we must have also equations of the type where //, ..., U 6 are functions of <f> 1} ..., </> 5 . From the nature of the problem these functions are algebraical and as they must be one valued they must be rational functions. We have therefore 348] THE THEORY OF SCREW-CHAINS. 379 a case of "Rational Transformation" (see Salmon s Higher Plane Curves, Chap. VIII.). The theory is however here much simplified. In this case none of the special solutions are admissible which produce the critical cases. Consider the equations U. 2 = Q, ..., U 5 = 0. They will give a number of systems of values for lf ..., 9 5 equal to the product of the degrees of C/2 > U 5 . Each of these 6 screws would be a correspondent to the same <j) screw 1, 0, 0, 0, 0. But in the problems before us this <f> as every other < can have only one correspondent. Hence all the functions U lt U 2 , etc. Ui, 17%, etc. must be linear. We may express the first set of equations thus : fa = (11) 0, + (12) a + (13) e 3 + (14) 4 + (15) 6 t , fa = (21) 1 + (22) 2 + (23) e. A + (24) 0, + (25) 9 5 , fa = (31) 0, + (32) 9, + (33) 3 + (34) 6, + (35) t , fa = (41) 0, + (42) 0, + (43) 3 + (44) 4 + (45) t , fa = (51) 0, + (52) 6, + (53) B, + (54) 9, + (55) . For the screw (j> to be known whenever 9 is given, it will be necessary to determine the various coefficients (11), (12), &c. These are to be determined from a sufficient number of given pairs of corresponding screws. Of these co efficients there are in all twenty-five. If we substitute the co-ordinates of one given screw 9, we have five linear equations between the co-ordinates. Of these equations, however, we can only take the ratios, for each of the co ordinates may be affected by an arbitrary factor. Each of the given pairs of screws will thus provide four equations to aid in determining the co efficients. Six pairs of screws being given, we have twenty-four equations between the twenty-five coefficients. These will be sufficient to determine the ratios of the coefficients. We thus see that by six pairs of screws the homography of two five-systems is to be completely defined. To any seventh screw on one system corresponds a seventh screw on the other system, which can be constructed accordingly. 348. Application of Parallel Projections. It will, however, be desirable at this point to introduce a somewhat different procedure. We can present the subject of homography from another point of view, which is specially appropriate for the present theory. The notions now to be discussed might have been introduced at the outset. It was, however, thought advantageous to concentrate all the light that could be obtained on the subject ; we therefore used the point-homography of lines, of planes, and of spaces, so long as they were applicable. The method which we shallnow adopt is founded on an extension of what are known as " parallel projections " in Statics. We may here recall 380 THE THEORY OF SCREWS. [348 the outlines of this theory, with the view of generalizing it into one adequate for our purpose. We can easily conceive of two systems of corresponding forces in two planes. To each force in one plane will correspond one force in the other plane, and vice versa. To any system of forces in one plane will correspond a system of forces in the other plane. We are also to add the condition that if one force x vanishes, the corresponding force x will also vanish. The fundamental theorem which renders this correspondence of im portance is thus stated : If a group offerees in one of the planes would equilibrate when applied to a rigid body, then the corresponding group of forces in the other plane would also equilibrate when applied to a rigid body. Draw any triangle in each of these planes, then any force can be de composed into three components on the three sides of the triangle. Let x, y, z be the components of such a force in the first plane, and let x, y , z be the components of the corresponding force in the second plane ; we must then have equations of the form x = ax + by + cz, y = a x + b y + c z, z = a"x -f b"y + c"z, where a, b, c, &c., are constants. These equations do not contain any terms independent of the forces, because x, y , z must vanish when x, y, z vanish. They are linear in the components of the forces, because otherwise one force in one plane will not correspond uniquely with one force in the other. Let a? 1} y-i, z^ ac 2 , y 2 , z. 2 ; ... x n , y n , z n be the components of forces in the first plane. Let Xi, yi, Zi] #/, y 2 , z.\ ... x n , y n , z n be the components of the corre sponding forces in the second plane. Then we must have k = a-r k + by k + cz k , yk = a xk + b y k -f c z k , z k = a"x k +- b"y k + c"z k , where k has every value from 1 to n. If therefore we write and 348] THE THEORY OF SCREW-CHAINS. 381 with similar values for % % , 2z, 2/ then the above equations give 2a? = a 2x + b % + c %z, % = a 2a? + 6 % + c/ ^z, 2s = a"2a? + &"2y + c"2*. If the system of forces in the first plane equilibrate, the following con ditions must be satisfied : 2tf = 0, % = 0, ^z = 0, and from the equations just written, these involve 2a> =0, % =0, 2* =0, whence the corresponding system in the other plane must also equilibrate. To determine the correspondence it will be necessary to know only the three forces in the second plane which correspond to three given forces in the first plane. We shall then have the nine equations which will be sufficient to determine the nine quantities a, b, c, &c. It appears, from the form of the equations, that the ratio of the intensity of a force to the intensity of the corresponding force is independent of those intensities, i.e. it depends solely upon the situation of the lines in which the forces act. Take any four straight lines in one system, and let four forces, X 1} X 2 , X 3 , X^, on these four straight lines equilibrate. It is then well known that each of these forces must be proportional to certain functions of the positions of these straight lines. We express these functions by A ly A. 2 , A 3> A. The four corresponding forces will be X^, X 2 t X 3 , X 4 , and as they must equilibrate, they must also be in the ratio of certain functions AJ, AJ, A 3 , A of the positions. We thus have the equations Xi _ X 2 _X 3 _ -A-4 A! A A 3 AI Xi _ X 2 _ X 3 _ X A 1 A 2 A 3 A We can select the ratio of X l to X^ arbitrarily : for example, let this ratio be /A; then whence the ratio of X 3 to X. 2 is known. Similarly the ratio of the other intensities X 3 : X 3 , and X 4 : X t is known. And generally the ratio of every pair of corresponding forces will be determined. 382 THE THEORY OF SCREWS. [348, It thus appears that four straight lines in one system may be chosen arbitrarily to correspond respectively with four straight lines in the other system ; and that one force being chosen on one of these straight lines in one system, the corresponding force may be chosen arbitrarily on the corre sponding straight line in the other system. This having been done, the relation between the two systems is completely defined. From the case of parallel projections in two planes it is easy to pass to the case which will serve our present purpose. Instead of the straight lines in the two planes we shall take screws in two ^-systems. Instead of the forces on the lines we may take either twists or wrenches on the screws. More generally it will be better to use Plucker s word " Dyname," which we have previously had occasion to employ ( 260) in the sense either of a twist or a wrench, or even a twist velocity. We shall thus have a Dyname in one system corresponding to a Dyname in the other. Let us suppose that a Dyname on a screw of one n-system corresponds uniquely to a different Dyname on a screw of another ?i-system. The two n-systems may be coincident but we shall treat of the general case. In the first place it can be shown that if any number of Dynames in the first system neutralize, their corresponding Dynames in the second system must also neutralize. Take n screws of reference in one system, and also n screws of reference in the corresponding system. Let 6 be the Dyname in one system which corresponds to (f> in the other ; 6 can be completely resolved into component Dynames of intensities 1} ... 6 n on the n screws of reference in the first system and in like manner <f> can be resolved into n components of intensities fa, ... <f> n on the screws of reference in the second system (n = < 6). From the fact that the relation between and <f> is of the one-to-one type the several components <j> l} ...<f> n are derived from 1 ,...0 n by n equations which may be written fa t = ( ? *1) 0, + ( W 2) ,... S 4 (nn) 6 n , in which (11), (12), &c. must be independent of both and <, for otherwise the correspondence would not be unique. If there be a number of Dynames in the first system the sums of the intensities of their components on the n screws of reference may be expressed as S#!, ... ^0 n respectively. In like manner the sums of the intensities of the components of their correspondents on the screws of reference of the second system may be represented by "fa, ... 2</> n respectively. We therefore 349] THE THEORY OF SCREW-CHAINS. 383 obtain the following equations by simply adding the equations just written for each separate -screw 20 H = (1) 20! + (w2) 20, . . . + (nn) 20 n . If the Dynamos in the first system neutralize then their components on the screws of reference must vanish or But it is obvious from the equations just written that in this case and therefore the corresponding Dynames will also neutralize. Given n pairs of corresponding Dynames in the two systems, we obtain ?i 2 linear equations which will be adequate to determine uniquely the ?i 2 constants of the type (11), (12), &c. It is thus manifest that n given pairs of Dynames suffice to determine the Dyname in either system, corresponding to a given Dyname in the other. It is of course assumed that in this case the intensities of the two corresponding Dynames in each of the ?i-pairs are given as well as the screws on which they lie. 349. Properties of this correspondence. To illustrate the distinction between this Dyname correspondence and the screw correspondence previously discussed, let us take the case of two cylindroids. We have already seen that, given any three pairs of corre sponding screws, the correspondence is then completely defined ( 343). Any fourth screw on one of the cylindroids will have its correspondent on the other immediately pointed out by the equality of two anharmonic ratios. The case of the Dyname correspondence is, however, different inasmuch as we require more than two pairs of corresponding Dynames on the two cylindroids, in order to completely define the correspondence. For any third Dyname 6 on one of the cylindroids can be resolved into two Dynames 6 l and 2 on the two screws containing the given Dynames. These com ponents will determine the components ^^^ on the corresponding cylindroid, which being compounded, will give <f> the Dyname corresponding to 0. It is remarkable that two pairs of Dynames should establish the corre spondence as completely as three pairs of screws. But it will be observed that to be given a pair of corresponding screws on the two cylindroids is in reality only to be given one datum. For one of the screws may be chosen arbitrarily; and as the other only requires one parameter to fix it 384 THE THEORY OF SCREWS. [349, on the cylindroid to which it is confined its specification merely gives a single datum. To be given a pair of corresponding Dynamos is, however, to be given really two data one of these is for the screws themselves as before, while the other is derived from the ratio of the amplitudes. Thus while three pairs of corresponding screws amount to three data, two pairs of corresponding Bynames amount to no less than four data ; the additional datum in this case enabling us to indicate the intensity of each correspondent as well as the screw on which it is situated. It can further be shown in the most general case of the correspondence of the Bynames in two w-systems that the number of pairs of Bynames required to define the correspondence is one less than the number of pairs of screws which would be required to define merely a screw correspondence in the same two w-systems. In an n -system a screw has n l disposable co-ordinates. To define the correspondence we require n + 1 pairs of screws. Of course those on the first system may have been chosen arbitrarily, so that the number of data required for the correspondence is A Byname in an w-system has n arbitrary data, viz., n 1 for the screw, and one for the intensity : hence when we are given n pairs of corresponding Bynames we have altogether n 2 data. We thus see that the n pairs of corresponding Bynames really contribute one more datum to the problem than do the n + l pairs of corresponding screws. The additional datum is applied in allotting the appropriate intensity to the sought Byname. We can then use either the n pair of Byname correspondents or the (n + l) pairs of screw correspondents. In previous articles we have used the latter; we shall now use the former. 350. Freedom of the fifth order. In the higher orders of freedom the screw correspondence does not indeed afford quite so simple a means of constructing the several pairs of corre sponding screws as we obtain by the Byname correspondence. In two five-systems the correspondence is complete when we are given five Bynames in one and the corresponding five Bynames in the other. To find the Byname X in the second system, corresponding to any given Byname A in the first system, we proceed as follows: Decompose A into Bynames on the five screws which contain the five given Bynames on the first system. This is always possible, and the solution is unique. These components will correspond to determinate Bynames on the five corresponding screws : these Bynames compounded together will give the required Byname X both in intensity and position. In the general case where a mass-chain possesses freedom of the fifth 350] THE THEORY OF SCREW-CHAINS. 385 order we may, by trial, determine five screw-chains about which the system can be twisted. Each set of five homologous screws will determine a five-system. In this method of proceeding we need not pay any attention to the intermediate screws : it will only be necessary to inscribe one Dyname (in this case a twist) in each of the homologous five-systems so that the group of six shall be homographic. The set of twists so found will form a displacement which the system must be capable of receiving. This is perhaps the simplest geometrical presentment of which the question admits. One more illustration may be given. Suppose we have a series of planes, and three arbitrary forces in each plane. We insert in one of the planes any arbitrary force, and its parallel projection can then be placed in all the other planes. Suppose a mechanical system, containing as many distinct elements as there are planes, be so circumstanced that each element is free to accept a rotation about each of the three lines of force in the plane, and that the amplitude of the rotation is proportional to the intensity of the force ; it must then follow that the system will be also free to accept rotations about any other chain formed by an arbitrary force in one plane and its parallel projections in the rest. We may, however, also examine the case of a mass-chain with freedom of the fifth order by the aid of the screw correspondence without intro duction of the Dyname. We find, as before, five independent screw-chains which will completely define all the other movements which the system can accept. To construct the subsequent screw-chains, which are quadruply infinite in variety, we begin by first finding any sixth screw-chain of the system by actual composition of any two or more twists about two or more of the five screw-chains. When a sixth chain has been ascertained the construction of the rest is greatly simplified. Each set of six homologous screws lie in a five-system. Place in each of these five-systems another screw which, with the remaining six, form a set which is homographic with the corresponding set in each of the other five-systems. These screws so determined then form another screw-chain about which the system must be free to twist. In the choice of the first screw with which to commence the formation of any further screw-chains of the five-system we have only a single condition to comply with : the screw chosen must belong to a given five-system. This implies that the chosen screw must be reciprocal merely to one given screw. On any arbitrary cylindroid a screw can be chosen which is reciprocal to this screw, and consequently on any cylindroid one screw can always be selected wherewith to commence a screw-chain about which a mass-chain with freedom of the fifth order must be free to twist. B. 25 386 THE THEORY OF SCREWS. [351, 351. Freedom of the sixth order. In freedom of the sixth order we select at random six displacements of which the mass-chain admits, and then construct the six corresponding screw- chains. The homologous screws in this case lie on six-systems, but a six- system means of course every conceivable screw. It is easily shown ( 248) that if to one screw in space corresponds another screw, and conversely, then the homography is completely established when we are given seven screws in one system, and the corresponding seven screws in the other. Any eighth screw in the one system will then have its correspondent in the other imme diately determined. It is of special importance in the present theory to dwell on the type of homography with which we are here concerned. If on the one hand it seems embarrassing, from the large number of screws concerned, on the other hand we are to recollect that the question is free from the complication of regarding the screws as residing on particular n-systems. Seven screws may be drawn anywhere, and of any pitch ; seven other screws may also be chosen anywhere, and of any pitch. If these two groups be made to corre spond in pairs, then any other screw being given, its corresponding screw will be completely determined. Nor is there in this correspondence any other condition, save the simple one, that to one screw of one system one screw of the other shall correspond linearly. Six screw-chains having been found, a seventh is to be constructed. This being done, the construction of as many screw-chains as may be desired is immediately feasible. From the homographic relations just referred to we have appropriate to each element of the system seven homologous screws, and also appropriate to each consecutive pair of elements we have the seven homologous intermediate screws. An eighth screw, appropriate to any element, may be drawn arbitrarily, and the corresponding screw being con structed on each of the other systems gives at once another screw-chain about which the system must be free to twist. When a mass-chain has freedom of the sixth order we see that any one element may be twisted about any arbitrary chosen screw, but that the screw about which every other element twists is then determined, and so are also the ratios of the amplitudes of the twists, by the aid of the inter mediate screws. 352. Freedom of the seventh order. Passing from the case of six degrees of freedom to the case of seven degrees, we have a somewhat remarkable departure from the phenomena shown by the lower degrees of freedom. Give to the mass-chain any seven arbitrary displacements, and construct the seven screw-chains, a, /3, 7, B, e, 352] THE THEORY OF SCREW-CHAINS. 387 t) by twists about which those displacements could have been effected. In the construction of an eighth chain, 0, we may proceed as follows : Choose any arbitrary screw lm Decompose a twist on 1 into components on !, &, ry 1( $ lt GI , . This must be possible, because a twist about any screw can be decomposed into twists about six arbitrary screws, for we shall not discuss the special exception when the six screws belong to a system of lower order. The twists on a^ ... , &c., determine the twists on the screw-chains ,... and therefore the twists on the screws a 2 , ... ,, which compound into a twist on <9 2 , similarly for 3 , &c.; consequently a screw-chain of which #! is the first screw, and which belongs to the system, has been constructed. This is, however, only one of a number of screw-chains belonging to the system which have 6 l for their first screw. The twist on l might have been decomposed on the six screws, &, 7l , S lt l , , 77,, and then the screws 2 , &c., might have been found as before. These will of course not be identical with the corresponding screws found previously. Or if we take the whole seven screws, o^, ... 77!, we can decompose a twist on 1 in an infinite number of ways on these seven screws. We may, in fact, choose the amplitude of the twist on any one of the screws of reference, oq , for example, arbitrarily, and then the amplitudes on all the rest will be determined. It thus appears that where l is given, the screw 2 is not determined in the case of freedom of the seventh order ; it is only indicated to be any screw whatever of a singly infinite number. The locus of 2 is therefore a ruled surface ; so will be the locus of 3 , &c. and we have, in the first place, to prove that all these ruled surfaces are cylindroids. Take three twists on 1} such that the arithmetic sum of their amplitudes is zero, and which consequently neutralize. Decompose the first of these into twists on a 1} &, 7l , S l} , ^, the second on a,, ft, 7l , 8 1} e ,, 17,, and the third on a 1} ft, %, 8 ly e 1} . It is still open to make another supposition about the twists on 6^ let us suppose that they are such as to make the two components on ^ vanish. It must then follow that the total twists on each of the remaining six screws, viz. 1} ft, 7l) 8^ e ly shall vanish, for their resultant cannot otherwise be zero. All the amplitudes of the twists about the screw-chains of reference must vanish, and so must also the amplitudes of the resultant twists when compounded. We should have three different screws for 2 corresponding to the three different twists on 0^ and as the twists on these screws must neutralize, the three screws must be co- cylindroidal. We can, therefore, in constructing a screw-chain of this system, not only choose #! arbitrarily, but we can then take for 6 2 any screw on a certain cylindroid : this being done, the rest of the screw-chain is fixed, including the intermediate screws. 252 388 THE THEORY OF SCREWS. [353, 353. Freedom of the eighth and higher orders. If the freedom be of the eighth order, then it is easily shown that the first screw of any other chain may be taken arbitrarily, and that even the second screw may be chosen arbitrarily from a three-system. Passing on to the twelfth order of freedom, the two first screws of the chain, as well as the amplitudes of their twists, may be chosen quite arbitrarily, and the rest of the chain is fixed. In the thirteenth order of freedom we can take the two first twists arbitrarily, while the third may be chosen anywhere on a cylindroid. It will not now be difficult to trace the progress of the chain to that unrestrained freedom it will enjoy when the mass-chain has G^ degrees of freedom, when it is able to accept any displacement whatever. In the last stage, prior to that of absolute freedom, the system will have its position defined by 6/j, - 1 co-ordinates. A screw-chain can then be chosen which is perfectly arbitrary in every respect, save that one of its screws must be reciprocal to a given screw. 354. Reciprocal Screw-Chains. We have hitherto been engaged with the discussion of the geometrical or kinematical relations of a mass-chain of p elements : we now proceed to the dynamical considerations which arise when the action of forces is considered. Each element of the mass-chain may be acted upon by one or more external forces, in addition to the internal forces which arise from the reaction of constraints. This group of forces must constitute a wrench appropriated to the particular element. For each element we thus have a certain wrench, and the entire action of the forces on the mass-chain is to be represented by a series of /j, wrenches. Recalling our definition of a screw-chain, it will be easy to assign a meaning to the expression, wrench on a screw-chain. By this we denote a series of wrenches on the screws of the chain, and the ratio of two consecutive intensities is given by the intermediate screw, as before. We thus have the general statement : The action of any system of forces on a mass-chain may be represented by a wrench on a screw-chain. Two or more wrenches on screw-chains will compound into one wrench on a screw-chain, and the laws of the composition are exactly the same as for the composition of twists, already discussed. Take, for example, any four wrenches on four screw-chains. Each set of four homologous screws will determine a four-system; the resulting wrench- chain will consist of a series of wrenches on these four-systems, each being the "parallel projection" of the other. 354] THE THEORY OF SCREW-CHAINS. 389 Let a and /3 be two screw-chains, each consisting of ^ screws, appro priated one by one to the p elements of the mass-chain. If the system receive a twist about the screw-chain /3, while a wrench acts on the screw- chain a, some work will usually be lost or gained ; if, however, no work be lost or gained, then the same will be true of a twist around a acting on a wrench on /3. In this case the screw-chains are said to be reciprocal. The relation may be expressed somewhat differently, as follows : If a mass-chain, only free to twist about the screw-chain a, be in equilibrium, notwithstanding the presence of a wrench on the screw-chain j3, then, conversely, a mass-chain only free to twist about the screw-chain ft will be in equilibrium, notwithstanding the presence of a wrench on the screw-chain a. This remarkable property of two screw-chains is very readily proved from the property of two reciprocal screws, of which property, indeed, it is only an extension. Let ! . . . a M be the screws of one screw-chain, and /3] . . . yS^ those of the other. Let a^, a. 2 , ... a M denote amplitudes of twists on a 1} 2 , &c., and let a i"> 82", &c., denote the intensities of wrenches on a 1} a 2 , &c. Then, from the nature of the screw-chain, we must have / : / = < : a 2 "=a3 : a 8 ", &c., A : A" = & :&" = & :&", &c.; for as twists and wrenches are compounded by the same rules, the inter mediate screws of the chain require that the ratio of two consecutive amplitudes of the twists about the chain shall coincide with the ratio of the intensities of the two corresponding wrenches. Denoting the virtual coefficient of c^ and j3i by the symbol Br ai /3 lJ we have for the work done by a twist about a, against the screw-chain /3, &c., while for the work done by a twist about ft against the screw-chain a we have the expression 2a 1 // A / OTaiPl + 2a 2 ^>a^ 2) &c. If the first of these expressions vanishes, then the second will vanish also. It will now be obvious that a great part of the Theory of Screws may be applied to the more general conceptions of screw-chains. The following theorem can be proved by the same argument used in the case when only a single pair of screws are involved. If a screw-chain 6 be reciprocal to two screw-chains a and /3, then 6 will be reciprocal to every screw-chain of the system obtained by compounding twists on a. and /3. 390 THE THEORY OF SCREWS. [354, A screw-chain is defined by 6/4 1 data ( 353). It follows that a finite number of screw-chains can be determined, which shall be reciprocal to 6/i 1 given screw-chains. It is, however, easy to prove that that number must be one. If two chains could be found to fulfil this condition, then every chain formed from the system by composition of two twists thereon would fulfil the same condition. Hence we have the important result One screw-chain can always be determined which is reciprocal to 6//- 1 given screw-chains. This is of course only the generalization of the fundamental proposition with respect to a single rigid body, that one screw can always be found which is reciprocal to five given screws ( 25). 355. Twists on 0/^ + 1 screw-chains. Given 6/^+1 screw-chains, it is always possible to determine the ampli tudes of certain twists about those chains, such that if those twists be applied in succession to a mass-chain of /u, elements, the mass-chain shall, after the last twist, have resumed the same position which it had before the first. To prove this it is first necessary to show that from the system formed by composition of twists about two screw-chains, one screw-chain can always be found which is reciprocal to any given screw-chain. This is indeed the generalization of the statement that one screw can always be found on a cylindroid which is reciprocal to a given screw. The proof of the more general theorem is equally easy. The number of screw-chains produced by composition of twists about the screw-chains a and /3 is singly infinite. There can, therefore, be a finite number of screw-chains of this system reciprocal to a given screw-chain 6. But that number must be one ; for if even two screw-chains of the system were reciprocal to 6, then every screw- chain of the system must also be reciprocal to 8. The solution of the original problem is then as follows : Let a. and /3 be two of the given 6/z, + 1 chains, and let 6 be the one screw-chain which is reciprocal to the remaining 6/i 1 chains. Since the 6/* + 1 twists are to neutralize, the total quantity of work done against any wrench-chain must be zero. Take, then, any wrench-chain on 6. Since this is reciprocal to 6/4 1 of the screw-chains, the twists about these screw-chains can do no work against a twist on 6. It follows that the amplitudes of the twists about a and @ must be such that the total amount of work done must be zero. For this to be the case, the two twists on a and /3 must compound into one twist on the screw-chain v, which belongs to the system (a/3), and is also reciprocal to 0. This defines the ratio of the amplitudes of the two twists on a and /3. We may in fact draw any cylindroid containing three homologous screws of a, /3, and 7, then the ratio of the sines of the angles into which 7 divides the angle between a and @ is the ratio of the amplitudes of the twists on a. and /8. In a 355] THE THEORY OF SCREW-CHAINS. 391 similar manner the ratio of the amplitudes of any other pair of twists can be found, and thus the whole problem has been solved. We are now able to decompose any given twist or wrench on a screw - chain into 6//. components on any arbitrary 6//, chains. The amplitudes or the intensities of these G/A components may be termed the 6/i co-ordinates of the given twist or wrench. If the amplitude or the intensity be regarded as unity, then the 6/A quantities may be taken to represent the co-ordinates of the screw-chain. In this case only the ratios of the co-ordinates are of consequence. If the mass-chain have only n degrees of freedom where n is less than 6/1, then all the screw-chains about which the mass-chain can be twisted are so connected together, that if any n + 1 of these chains be taken arbitrarily, the system can receive twists about these n 4- 1 chains of such a kind, that after the last twist the system has resumed the same position which it had before the first. In this case n co-ordinates will be sufficient to express the twist or wrench which the system can receive, and n co-ordinates, whereof only the ratios are concerned, will be sufficient to define any screw-chain about which the system can be twisted. G/j, n screw-chains are taken, each of which is reciprocal to n screw- chains about which a mass-chain with freedom of the nth order can twist. The two groups of n screw-chains on the one hand, and 6/i - n on the other, may each be made the basis of a system of chains about which a mechanism could twist with freedom of the nth order, or of the (6/i - ?i)th order, re spectively. These two systems are so related that each screw-chain in the one system is reciprocal to all the screw-chains in the other. They may thus be called two reciprocal systems of screw-chains. Whatever be the constraints by which the freedom is hampered, the reaction of the constraints upon the elements must constitute a wrench on a screw-chain. It is a fundamental point of the present theory that this screw-chain belongs to the reciprocal system. For, as no work is done against the constraints by any displacement which is compatible with the freedom of the mass-chain, it must follow, from the definition, that the wrench-chain which represents the reactions must be reciprocal to all possible displacement chains, and must therefore belong to the reciprocal system. For a wrench-chain applied to the mass-chain to be in equilibrium it must, if not counteracted by some other external wrench-chain, be counter acted by the reaction of the constraints. Thus we learn that 392 THE THEORY OF SCREWS. [355, Of two reciprocal screw-chain systems, each expresses the collection of ivrench-chains of which each one will equilibrate when applied to a mass-chain only free to twist about all the chains of the other system. This is, perhaps, one of the most comprehensive theorems on Equilibrium which could be enunciated. 356. Impulsive screw-chains and instantaneous screw-chains. Up to the present we have been occupied with considerations involving kinematics and statics : we now show how the principles of kinetics can be illustrated by the theory sketched in this chapter. We shall suppose, as before, that the mechanical arrangement which we call the mass-chain consists of jj, elements, and that those elements are so connected together that the mass-chain has n degrees of freedom. We shall also suppose that the mass-chain is acted upon by a wrench about any screw- chain whatever. The first step to be taken is to show that the given wrench-chain may be replaced by another more conveniently circumstanced. Take any n chains of the given system, and 6/u, n chains of the reciprocal system, then the given wrench-chain can be generally decomposed into components on the n + (6/z - n) chains here specified. The latter, being all capable of neutralization by the reaction of the constraints, may be omitted, while the former n wrench-chains admit of being compounded into a single wrench-chain. We hence have the following important proposition : Whatever be the forces which act on a mass-chain, their effect is in general equivalent to that of a wrench on a screw-chain which belongs to the system of screw-chains expressing the freedom of the mass-chain. The application of this theorem is found in the fact that, while we still retain the most perfect generality, it is only necessary, either for twists or wrenches, to consider the system, defined by n chains, about which the mass- chain can be twisted. Let us consider the mass-chain at rest in a specified position, and suppose it receives the impulsive action of any set of forces, it is required to determine the instantaneous motion which the system will acquire. The first operation is to combine all the forces into a wrench-chain, and then to transform that wrench-chain, in the manner just explained, into an equivalent wrench- chain on one of the screws of the system. Let 6 be the screw-chain of the system so found. In consequence of this impulsive action the mass-chain, previously supposed to be at rest, will commence to move ; that motion can, however, be nothing else than an instantaneous twist velocity about a screw- chain a. We thus have an impulsive screw-chain 6 corresponding to an instantaneous screw-chain a. In the same way we shall have the impulsive screw-chains <, i/r, &c., correlated to the instantaneous chains, /3, y, &c. 356] THE THEORY OF SCREW-CHAINS. 393 The first point to be noticed is, that the correspondence is unique. To the instantaneous chain a one impulsive screw-chain 6 will correspond. There could not be two screw-chains 6 and 6 which correspond to the same instan taneous screw-chain a. For, suppose this were the case, then the twist velocity imparted by the impulsive wrench on 6 could be neutralized by the impulsive wrench on 6 . We thus have the mass-chain remaining at rest in spite of the impulsive wrenches on 6 and 6 . These two wrenches must therefore neutralize, and as, by hypothesis, they are on different screw- chains, this can only be accomplished by the aid of the reactions of the constraints. We therefore find that 6 and 6 must compound into a wrench-chain which is neutralized by the reactions of the constraints. This is, however, impossible, for 6 and 6 can only compound into a wrench on a screw-chain of the original system, while all the reactions of the constraints form wrenches on the chains of the wholly distinct reciprocal system. We therefore see that to each instantaneous screw-chain a only one impulsive screw-chain 6 will correspond. It is still easier to show that to each impulsive screw-chain 6 only one instantaneous screw-chain a will correspond. Suppose that there were two screw-chains, a and a. , either of which would correspond to an impulsive wrench on 6. We could then give the mass-chain, first, an impulsive wrench on d of intensity X, and make the mass-chain twist about a, and we could simultaneously give it an im pulsive wrench on the same screw-chain 6 of intensity X, and make the mass-chain twist about a . The two impulses would neutralize, so that as a matter of fact the mass-chain received no impulse whatever, but the two twist velocities could not destroy, as they are on different screw-chains. We would thus have a twist velocity produced without any expenditure of energy. We have thus shown that in the w-system of screw-chains expressing the freedom of the mass-chain, one screw-chain, regarded as an instantaneous screw-chain, will correspond to one screw-chain, regarded as an impulsive screw-chain, and conversely, and therefore linear relations between the co-ordinates are immediately suggested. That there are such relations can be easily proved directly from the laws of motion (see Appendix, note 7). We therefore have established a case of screw-chain homography between the two systems, so that if 1} ...0 n denote the co-ordinates of the impulsive screw-chain, and if a a , ... a n denote the co-ordinates of the corresponding instantaneous screw-chain, we must have n equations of the type 0, = (11) ttl + (12) a 2 + (13) 3 . .. + (1 ) a B> (nn) B , 394 THE THEORY OF SCREWS. [356, where (11), (12), &c., are n? coefficients depending on the distribution of the masses, and the other circumstances of the mass-chain and its constraints. The equations having this form, the necessary one-to-one correspondence is manifestly observed. 357. The principal screw-chains of Inertia. We are now in a position to obtain a result of no little interest. Just as we have two double points in two homographic rows on a line, so we have n double chains in the two homographic chain systems. If we make, in the foregoing equations, 0i = p*i 5 #2 = p 2 , &c., we obtain, by elimination of a 1} ... a n , an equation of the nth degree in p. The roots of this equation are n in number, and each root substituted in the equations will enable the co-ordinates of each of the n double screw-chains to be discovered. The mechanical property of these double chains is to be found in the following statement : If any mass-chain have n degrees of freedom, then in general n screw- chains can always be found (but not more than n), such that if the mass-chain receive an impulsive wrench from any one of these screw-chains, it will immediately commence to move by twisting about the same screw-chain. In the case where the mass-chain reduces to a single rigid body, free or constrained, the n screw-chains to which we have just been conducted reduce to what we have called the n principal screws of inertia. In the case, still more specialized, of a rigid body only free to rotate around a point, the theorem degenerates to the well-known property of the principal axes. We may thus regard the n principal chains now found as the generalization of the familiar property of the principal axes for any system anyhow con strained. Considerable simplification is introduced into the equations when, instead of choosing the chains of reference arbitrarily, we select the n principal screw-chains for this purpose ; we then have the very simple results, 0, = (11) x ; 2 = (22) 2 ; ... 6 n = (nn) a n . This gives a method of finding the impulsive screw-chain corresponding to any instantaneous screw-chain. It is only necessary to multiply the co ordinates of the instantaneous screw-chain i, a 2 by the constant factors (11), (12), &c., in order to find the co-ordinates of the impulsive screw-chain. The general type of homography here indicated has to be somewhat specialized for the case of impulsive screw-chains and instantaneous screw- chains. The n double screw-chains are generally quite unconnected we might, indeed, have exhibited the relation between the two homographic 357] THE THEORY OF SCREW-CHAINS. 395 systems of screw-chains by choosing n screws quite arbitrarily as the double screws of the two systems, and then appropriating to them n factors (11), (22), (33), &c., also chosen arbitrarily. In the case of impulsive and instant aneous chains, the n double chains are connected together by the relation that each pair of them are reciprocal, so that the whole group of n chains form what may be called a set of co-reciprocals. To establish this we may employ some methods other than those previously used. Let us take a set of w-co-reciprocal chains, and let the co-ordinates of any other two chains, 6 and < of the same system, be 1> ... 6 n and fa, ...fa,,. Let 2p 1} *2p 2 , &c., 2p n be certain constant parameters appropriated to the screws of reference. 2pj is, for example, the work done by a twist of unit amplitude on the first screw-chain of reference against a wrench of unit intensity on the same chain. The work done by a twist O l against a wrench fa on this chain is 2p 1 1 fa. As the chains of reference are co-reciprocal, the twist on 6 l does no work against the wrenches fa 2 , < 3 , ... &c. ; hence the total work done by a twist on 6 against the wrench on </> is and hence if 6 and < be reciprocal, The quantities p 1 , . . . p n are linear magnitudes, and they bear to screw-chains the same relation which the pitches bear to screws. If we use the word pitch to signify half the work done by a unit twist on a screw-chain against the unit wrench on the screw-chain, then we have for the pitch p 6 of the chain 6 the expression The kinetic energy of the mass-chain, when animated by a twist velocity of given amount, depends on the instantaneous screw-chain about which the system is twisting. It is proportional to a certain quadratic function of the n co-ordinates of the instantaneous screw. By suitable choice of the screw- chains of reference it is possible, in an infinite number of ways, to exhibit this function as the sum of n squares. It follows from the theory of linear transformations that it is generally possible to make one selection of the screw-chains of reference which, besides giving the energy function the required form, will also exhibit p e as the sum of n squares. This latter condition means that the screw-chains of reference are co-reciprocal. It only remains to show that the n screw-chains of reference thus ascertained must be the n principal screw-chains to which we were previously conducted. We may show this most conveniently by the aid of Lagrange s equations of motion in generalized co-ordinates ( 86). 396 THE THEORY OF SCREWS. [357- Let #j , . . . 6 n represent the co-ordinates of the impulsive screw-chain, and let !,... a n be the co-ordinates of the corresponding instantaneous screw- chain, reference being made to the screw-chains of reference just found. Lagrange s equations have the form A ( dT .\ -dT- p dt \ddj cfaj where T is the kinetic energy, and where PiSc^ denotes the work done against the forces by a twist of amplitude BO.I. If Q" denote the intensity of the impulsive wrench, then its component on the first screw of reference is f "0 1} and the work done is 2p 1 "0 l &a l , while, since the chains are co-reciprocal, the work done by Sttj against the components of &" on the other chains of reference is zero, we therefore have JV*%$r r fc We have also T=M(u 1 2 d 1 *+...+u n *d n 2 ), when u lt ... u n are certain constants. We have, therefore, from Lagrange s equation, whence, integrating during the small time t, during which the impulsive force acts, in which d is the actual twist velocity about the screw-chain, so that d l = dx l , each being merely the expression for the component of that twist velocity about the screw-chain. We hence obtain lt ... n , proportional respectively to Pi " Pn u 2 If we make = (11), &c., we have the previous result, PI n = (nn)a n . 358. Conjugate screw-chains of Inertia. From the results just obtained, which relate of course only to the chains of reference, we can deduce a very remarkable property connecting instantaneous chains, and impulsive chains in general. Let a. and ft be two instantaneous chains, and let and $ be the two corresponding impulsive chains, then when OL 359] THE THEORY OF SCREW-CHAINS. 397 is reciprocal to </>, ft will be reciprocal to 6. This, it will be observed, is a generalization of a property of which much use has been previousl)<jfcnade ( 81). The proof is as follows. The co-ordinates of the instantaneous chains are &.-.. The co-ordinates of the corresponding impulsive chains are Pi Pn and V& Ujfin Pi Pn If the chain a be reciprocal to the impulsive chain which produces /3, then we have <!& + ... + u n 2 nl3 n = ; but this being symmetrical in a and /3 is precisely the same as the condition that the impulsive chain corresponding to a. shall be reciprocal to /9. Following the analogy of our previous language we may describe two screw-chains so related as conjugate screw-chains of Inertia. 359. Harmonic screw-chains. We make one more application of the theory of screw-chains to the discussion of a kinetical problem. Let us suppose that we have any material system with n degrees of freedom in a position of stable equilibrium under the action of a conservative system of forces. If the system receive a small displacement, the forces will no longer equilibrate, but the system will be exposed to the action of a wrench on a screw-chain. We thus have two corresponding sets of screw-chains, one set being the chains about which the system is displaced, the other set for the wrenches which are evoked in consequence of the displacements. By similar reasoning to that which we have already used, it can be shown that these two corresponding chain systems are homographic. We can therefore find n screw-chains about which, if the system be displaced, a wrench will be evoked on the same screw-chain, and (the forces having a potential) it can be shown that this set of n screw-chains are co-reciprocal. If after displacement the system be released it will continue to make small oscillations. The nature of these oscillations can be completely exhibited by the screw-chains. To a chain a, regarded as an instantaneous screw-chain, will correspond the screw as an impulsive screw-chain. To the chain a, regarded as the seat of a displacing twist, will correspond a wrench 398 THE THEORY OF SCREWS. [359 (f) which is evoked by the action of the forces. It will, of course, generally happen that the chain 6 is different from the chain <. It can however be shown that 6 and </> are not in every case distinct. There are n different screw-chains, each of which regarded as a will have the two corresponding screws 6 and < identical. Nor is it difficult to see what the effect of such a displacement must be on the small oscillations which follow. A wrench is evoked by the displacement, and since 6 and < coincide, that wrench is undistinguishable from an infinitely small impulsive wrench which will make the system commence to twist about a. We are thus led to the result that There are n screw-chains such that if the system be displaced by a twist about one of these screw-chains, and then released, it will continue for ever to twist to and fro on the same screw-chain. Following the language previously used, we may speak of these as harmonic screw-chains, and it can be shown that whatever be the small displacement of the system, and whatever be the small initial velocities with which it is started, the small oscillations are merely compounded of twist vibrations about the n harmonic screw-chains. CHAPTER XXV. THE THEORY OF PERMANENT SCREWS*. 360. Introduction. In commencing this chapter it will be convenient to recite a well-known dynamical proposition, and then to enlarge its enunciation by successive abandonment of restrictions. Suppose a rigid body free to rotate around a fixed point. There are, as is well known, three rectangular axes about any one of which the body when once set in rotation will continue to rotate uniformly so long as the application of force is withheld. These axes are known as permanent axes. The freedom of the body in this case is of a particular nature, included in the more general type known as Freedom of the Third Order. The Freedom of the Third Order is itself merely one subdivision of the class which, including the six orders of freedom, embraces every conceivable form of constraint that can be applied to a rigid body. We propose to investigate what may be called the theory of permanent screws for a body constrained in the most general manner. The movement of the body at each moment must be a twist velocity about some one screw belonging to the system of screws prescribed by the character of the constraints. In the absence of forces external to those arising from the reactions of the constraints, the movement will not, in general, persist as a twist about the same screw 6. The instantaneous screw will usually shift its position so as to occupy a series of consecutive positions in the system. It must, however, be always possible to compel the body to remain twisting about 6. For this purpose a wrench of suitable intensity on an appropriate screw 77 may have to be applied. Without sacrifice of generality we can in general arrange that 77 is one of the system of screws * Trans. Roy. Irish Acad., Vol. xxix. p. 613 (1890). 400 THE THEORY OF SCREWS. [360- which expresses the freedom of the body ( 96). It may sometimes appear that the intensity of the necessary wrench on 77 vanishes. The body in such a case requires no coercion beyond that of the original constraints to preserve 9 as the screw about which it twists, and when this is the case we shall describe as a permanent screw. This use of the word permanent does not imply that the body could remain for ever twisting about this screw, for the movement of the body to an appreciable distance will in general entail some change in its relation to the constraints. The character istic of the permanent screw is the absence of any acceleration in the body twisting about it, using the word acceleration in its widest sense. In the earlier parts of the chapter we shall discard the restrictions involved in the assumption that the material arrangement is only a single rigid body. The doctrine of screw-chains (Chap, xxiv.) enables us to extend a considerable portion of the present theory to any mass-chain whatever. Any number of material parts connected in any manner must still conform to the general law, that the instantaneous movements can always be repre sented by a twist about a certain screw-chain. In general the mass-chain will have a tendency to wander from twisting about the original screw-chain. In such cases the position of the instantaneous screw-chain cannot be maintained without the imposition of further coercion than that which the constraints supply. This additional set of forces may be applied by a restraining wrench-chain, the relation of which to the instantaneous screw- chain we shall have to consider. Sometimes it may appear that no restraining wrench-chain is necessary beyond one of those provided by the reaction of the constraints. The instantaneous screw-chain is then to be described as permanent. 361. Different properties of a Principal Axis. Another preliminary matter should be also noticed, because it exhibits the relation of the subject discussed in this chapter to some other parts of the Theory of Screws. In the ordinary theory of the rigid body there are, as is well known, two distinct properties of a principal axis which possess dynamical significance. We may think of a principal axis as the axis of a couple which, when applied impulsively to the body, will set it rotating about this axis. We may also think of the principal axis as a direction about which, if a body be once set in rotation, it will continue to rotate. The first of these properties by suitable generalization opens up the theory of principal screw-chains of inertia, which we have already explained in previous chapters. It is from the other property of the principal axis that the present investigation takes its rise. It is important to note that two quite different departments in the Theory of Screws happen to coalesce in the very special case of a rigid body rotating around a point. 362] THE THEORY OF PERMANENT SCREWS. 401 362. A Property of the Kinetic Energy of a System. It is obvious that the mere alteration of the azimuth about a fixed axis from which a rigid body is set into rotation will not affect its kinetic energy, provided the position of the axis and the angular velocity both remain un altered. A moment s reflection will show that this principle may be extended to any movement whatever of a rigid body. At each instant the body is twisting about some instantaneous screw a with a twist velocity a. Let the body be stopped in a position which we call A. Let it receive a dis placement by a twist of any amplitude about a and thus be brought to a position which we call B*. Finally, let the body be started from its new position B so as to twist again about a with the original twist velocity d, then it is plain that the kinetic energy of the body just before being stopped at the position A is the same as its kinetic energy just after it is started from the position B. Enunciated in a still more general form the same principle is as follows : Any mass-chain in movement is necessarily twisting about some screw- chain. If we arrest the movement, displace the mass-chain to an adjacent position on the same screw-chain, and then start the mass-chain to twist again on the same screw-chain, with its original twist velocity, the kinetic energy must remain the same as it was before the interruption. This principle requires that whatever be the symbols employed, the function T, which denotes the kinetic energy, must satisfy a certain identical equation. I propose to investigate this equation, and its character will perhaps be best understood by first discussing the question with co-ordinates of a perfectly general type. We shall suppose the mass-chain has n degrees of freedom. Let the co-ordinates x lt ...x n represent the position of the mass-chain, and let its instantaneous motion be indicated by x l ,...x n . Let be the initial position of the mass-chain, then in the time Bt it has reached the position , whereof the co-ordinates are x l + x^t, ... x n + x n $t. The movement from to must, like every possible movement of a system, consist of a twist about a screw-chain. This is a kinematical fact, wholly apart from whatever particular system of co-ordinates may have * We have supposed that the pitch of this displacement is the same as the pitch of a. This restriction is only introduced here because the constraints will generally forbid the body to make any other twist about the axis of a. If the body were quite free we might discard the restriction altogether as is in fact done later on ( 376). B. 26 402 THE THEORY OF SCREWS. [362, been adopted. We call this screw-chain 0, and 6 denotes the twist velocity with which the system moves round 0. Choose any n independent screw-chains, about each one of which the mass-chain is capable of twisting. Then 6 can be decomposed into n com ponents which have twist velocities 1} ... 6 n about the several screw-chains of reference ( 355). Since everything pertaining to the position or the movement of the mass-chain must necessarily admit of being expressed in terms of the co ordinates of the mass-chain, and since the quantities 1} ... O n are definitely determined by the position and movements of the mass-chain, it follows that these quantities must be given by a group of formulae which may be written "n Jn\%i y H>n j #1 > Xnj- Let the mass-chain be stopped in the position A. Let it then be dis placed to an adjacent position B defined by the following variations of the co-ordinates where 8e is a small quantity. From this new position B let the mass-chain be started into motion so that it shall have the same twist velocity as it had just before being stopped in A and about the same screw- chain. This condition requires that each of the quantities lt ... Q n shall resume its original value unaltered by the stoppage and subsequent restarting of the mass- chain from a new position. There must accordingly be an adjustment of 8x l} ... 8x n to satisfy the equations dx n Under these circumstances T has obviously not altered, so that we have also dT dT . dT .. dT Let us assume, for brevity, the symbol A, such that * _ . d d dx l dx n 363] THE THEORY OF PERMANENT SCREWS. 403 Then we obtain, by elimination of Bx l} ... 8x n , and 8e, AT, AA, dT dT df n dfn = 0. dx l " dx 1t Such is the general condition which must be satisfied by the kinetic energy of any material arrangement whatever. But the equation is so complicated when expressed in ordinary rectangular co-ordinates that there is but little inducement to discuss it. 363. The Identical Equation in Screw-chain Co-ordinates. The Theory of Screw-chains exhibits this equation in a form of special simplicity. For, suppose that then the equation of the last article reduces to We thus have the following theorem : If the co-ordinates, #/ , ... O n , of a mass-chain be n twists about n screiv- chains, belonging to the system of screw-chains which express the freedom of the mass-chain, and if Oi, ... O n be the twist velocities of the mass-chain about these same screw-chains, then the kinetic energy T satisfies the equation A dT v i ~jm~> f Un ja~ f ~ a PJ au n I have thought it instructive to exhibit the origin of this equation as a special deduction from the case of co-ordinates of the general type. For a brief demonstration the following simple argument suffices : If the mass-chain be displaced through S0/, ... S0 n while the velocities are unaltered, the change of kinetic energy is If the change of the position be due to a small twist Se around the screw- chain with co-ordinates l} ... 6 n , then 262 404 THE THEORY OF SCREWS. [363- but from the physical property of the kinetic energy already cited, it appears that this kind of displacement cannot change the kinetic energy, whence A dT , dT _ " n ~ 364. The Converse Theorem. Let us take the general case where the co-ordinates are oc l ,...x n and x l , ... x n . Suppose that cb 2 , ... x n are all zero, then x^ is the velocity of the mass-chain. We shall also take x z , ... x n to be zero, so that we only consider the position of the mass-chain defined by x l . Think now of the two positions for which ^ = and x 1 = x 1 respectively. Whatever be the character of the constraints it must be possible for the mass-chain to pass from the position X-L = to the position x l #/ by a twist about a screw-chain. The magnitude Xi is thus correlated to the position of the mass-chain on a screw-chain about which it twists. If the co-ordinates are of such a kind that the identical equation which T must necessarily satisfy has the form . dT . dT _ Xl dxJ~ Xn dx n ~ then for the particular displacement corresponding to the first co-ordinate, # 2 , ... x n are all zero, and and as T must involve x^ in the second degree, we have T = Hx* where H is independent of #/ Let #j be the twist velocity about the screw-chain corresponding to the first co-ordinate, then, of course, A being a constant, T = Ae*, whence A 6f = Hxf, VZtfj = A/774, and by integration and adjustment of units and origins & . We thus see that while the displacement corresponding to the first co-ordinate must always be a twist about a screw-chain, whatever be the actual nature of the metric element chosen for the co-ordinate, yet that when the identical equation assumes the form 366] THE THEORY OF PERMANENT SCREWS. 405 the metric element must be essentially the amplitude of the twist about the screw-chain. We have thus proved the following theorem : The co-ordinates must be twists about n screw-chains of reference whenever the identical equation, satisfied by T, assumes the form 6 dT . a dT_ 9l " ffn ~ 365. Transformation of the Vanishing Emanant. Suppose that the position and movement of a mass-chain were represented by the co-ordinates #/, #</, n ; #i> @2, - &n when referred to one set of n screws of reference, and by </>/, (f> 2 } ... <,/; </>!, < 2 , </> when referred to another set of screws of reference. Then of course these sets of co-ordinates must be linearly connected. We may write 4 - (11) ft .-.. + (!)*, , = (nl) </... + (>,)<,;. Then, by differentiation 4 -(ii) ^... Thus the two sets of variables are co-gredients, and by the theory of linear transformations we must have dT , dT dT : dT The expression on either side of the equation is of course known in algebra as an emanant ( 261). We could have foreseen this result from the fact that whatever set of n independent screw-chains belonging to the system was chosen, the identical equation must in each case assume the standard form. 366. The General Equations of Motion with Screw- chain Co-ordinates. The screw-chain co-ordinates of a mass-chain with n degrees of freedom are #/, ... d n ; the co-ordinates of the velocities are 1} ... 0*. Let 77 be the wrench-chain which acts on the system. Let the components of the wrench- chain, when resolved on the screw-chains of reference, have for intensities Vi > W- Let p l , ... p n be the pitches of the chains of reference, by which is meant that 2p t is the work done on that screw-chain by a twist of unit amplitude against a wrench of unit intensity on the same screw-chain. Then the screw-chains of reference being supposed to be co-reciprocal, we have, 406 THE THEORY OF SCREWS. [366- irom Lagrange s equations, d (dT\ dT ~ = ^W.T?] . dt \d0J dd, w - dt\de These equations admit of a transformation by the aid of the identity e^- f dT -o *ap" n de n - Differentiating this equation by & lt we find but dT * _ , ** = Q _ _ , dt \dej ~ J dd? 2 de.de, n de, de n * de^ei + n de~de~f whence, by substitution AfdT.} = 0fT d * T dT dt\dej ~ l de^" n Hence when screw-chain co-ordinates are employed Lagrange s equations may be written in the form ifT d T d T * 367. Generalization of the Eulerian Equations. The equations just written can be further simplified by appropriate choice of the screw-chains of reference. We have already assumed the screw-chains of reference to be co-reciprocal. If, however, we select that particular group which forms the principal screw-chains of inertia ( 357), then every pair are conjugate screw-chains of inertia besides being reciprocal. In this case T takes the form 368] THE THEORY OF PERMANENT SCREWS. 407 Neglecting the small quantities 6-^ ... &c. we have -r = 0, &C. d6.de, Introducing these values we obtain dT These may be regarded as the generalization for any material arrangement whatever of the well-known Eulerian equations for the rotation of a rigid body around a fixed point. If there are no external forces then i\" , . . . rj n " are all zero, and the equations of movement assume the simple form AT 368. The Restraining Wrench-chain. If a mass-chain be twisting about an instantaneous screw-chain 0, the mass-chain will, in general, presently forsake 6 and gradually adopt one instantaneous screw-chain after another. It is however possible, by the application of a suitable wrench-chain, to compel the mass-chain to continue twisting about the same screw 6 with unchanged twist velocity. We now proceed to the discovery of this restraining wrench-chain when no other external forces act on the mass- chain. As all the accelerations of 6 must vanish, the co-ordinates of the wrench- chain required are obtained by imposing the conditions 1 = 0; a = 0,...0 n =0. We therefore infer from the general equations of 366, that if IJ L ", . . . r) n " are the co-ordinates of the restraining wrench-chain we must have 1 dT 1 dT 408 THE THEORY OF SCREWS. [368- whcnce we deduce the following theorem : If the position of a mass-chain be referred to co-reciprocal screw-chains of reference, then 1 dT 1 dT Pi dffi p n d6n are the co-ordinates of the restraining wrench- chain which would coerce the mass-chain into continuing to twist about the same screw-chain 6*. 369. Physical meaning of the Vanishing Emanant. We may verify this theorem by the following method of viewing the subject. It must be possible to coerce the system to twist about 6 by the imposition of special constraints. The reactions of these constraints will constitute, in fact, the restraining wrench-chain. It is, however, a character istic feature that, as the system is, ex hypothesi, still at liberty to twist about 6, the reaction of any constraints which are consistent with this freedom must lie on a screw-chain reciprocal to 0. The condition that two screw-chains, 6 and rj, shall be reciprocal ( 354) s but this is clearly satisfied if for i) 1} ... we substitute l^dT^ 1 dT piW p n d0 n ] for the equation then becomes dT i. fl dT n i ddr" n de~r which, when multiplied by 0, reduces to the known identity e dT ^ dT o *ap"- + *n?--?.- We thus obtain a physical meaning of this equation. It is no more than an expression of the fact that the restraining wrench-chain must be reciprocal to the instantaneous screw-chain. 370. A displacement without change of Energy. It should also be noticed that provided the twist velocities remain un altered the kinetic energy will be unchanged by any small displacement of the mass-chain arising from a twist on any screw-chain reciprocal to the restraining screw-chain. * A particular case of this, or what is equivalent thereto, is given in Williamson and Tarleton s Dynamics, 2nd ed., p. 432. 372] THE THEORY OF PERMANENT SCREWS. 409 For, if 6-^, ... d,i be the co-ordinates of the displacement, the change in Tis ^.+ +0 ~ which may be written O dT- i0 L<W-. but this will be zero if, and only if, the screw-chain #/, ... n be reciprocal to the screw-chain ^ dT ^dT^ p l ddj " p n dQn 371. The Accelerating Screw-chain. When the mass-chain has forsaken the instantaneous screw-chain 6, and is twisting about another instantaneous screw-chain <, there must be a twist velocity about some screw-chain p, which, when compounded with the twist velocity about 6, gives the twist velocity about </>. When < and are indefinitely close, then p is the accelerating screw-chain. Taking the n principal screw-chains of inertia as the screws of reference and assuming that external forces are absent, we have ,i dT 11 = dl 7 ,if 20 - a u n u n It is plain that the co-ordinates of the accelerating screw-chain are 1 , ... n , whence we have the following theorem: If a mass-chain be twisting around a screw-chain 6, and if external forces are absent, the co-ordinates of the corresponding accelerating screw-chain are proportional to I dT I dT 372. Another Proof. It is known from the theory of screw-chains (357) that if a quiescent mass-chain receive an impulsive wrench-chain with co-ordinates 11 2 11 2 til U-n TT^ 1 " pn> P\ Pn the mass-chain commences to twist about the screw-chain, of which the co-ordinates are pi, Pn- 410 THE THEORY OF SCREWS. [372- Jf, by imposition of a restraining wrench-chain, the mass-chain continues to twist about the same screw-chain 6, the restraining wrench-chain has neutralized the acceleration. It follows that the restraining wrench-chain, regarded as impulsive, must have generated an instantaneous twist velocity on the accelerating screw-chain, equal and opposite to the acceleration that would otherwise have taken place. The co-ordinates of this impulsive wrench-chain are proportional to dT 1 dT Pl d0 l " " Pnd0 n " The corresponding instantaneous screw-chain is obtained by multiplying these expressions severally by and thus we find, as before, for the co-ordinates of the accelerating screw- chain 373. Accelerating Screw-chain and instantaneous Screw-chain. We have, from the expressions already given, . dT rlT M(utf& + ...+ utfjj = e, JL + . . . e n j* , . But the right-hand side is the emanant which we know to be zero, whence This shows that 1} ... 6 n , and lf ... d n are on conjugate screw-chains of inertia, and hence we deduce the following theorem : Whenever a mass-chain is moving without the action of external forces, other than from constraints restricting the freedom, the instantaneous screw- chain and the accelerating screw-chain are conjugate screw-chains of inertia. 374. Permanent Screw-chains. Reverting to the general system of equations ( 366) we shall now in vestigate the condition that 6 may be a permanent screw-chain. It is obvious that if 0J, ... n are all zero, then dT dT_ d0 i " " d0 n must each be zero. If, conversely, the differential coefficients just written are all zero, then the quantities j , ... n must each also vanish. 375] THE THEORY OF PERMANENT SCREWS. 411 This is obviously true unless it were possible for the determinant dd? d*T to become zero. Remembering that T is a homogeneous function of the quantities l) ... n in the second degree, the evanescence of the determinant just written would indicate that T admitted of expression by means of n 1 square terms, such as This vanishes if = 0, &c.; each of these is a linear equation in lt ... n , and consequently a real system of values for 6^ ... n must satisfy these equations, and render T zero. It would thus appear that a real motion of the mass-chain would have to be compatible with a state of zero kinetic energy. This is, of course, im possible ; it therefore follows that the determinant must not vanish, and consequently we have the following theorem : If the screw-chains of reference be co-reciprocal, then the necessary and the sufficient conditions for 6 to be a permanent screw are that its co-ordinates l , 2 , ... n shall satisfy the equations dT =o- ^=o dOl d0 n There are n of these equations, but they are not independent. The cmanant identity shows that if n 1 of them be satisfied, the co-ordinates so found must, in general, satisfy the last equation also. 375. Conditions of a permanent Screw-chain. As the quantities #/, . . . tl are small, we may generally expand T in powers, as follows : T=T + 1 T 1 +...0 n T n The equation therefore becomes dT 412 THE THEORY OF SCREWS. [375, and as #/, a , &c., are indefinitely small, this reduces to 2*1 = 0, where 2\ is a homogeneous function of lt 2 , ... B n in the second degree. For the study of the permanent screws we have, therefore, n equations of the second degree in the co-ordinates of the instantaneous screw-chain, and any screw-chain will be permanent if its co-ordinates render the several differential coefficients zero. We may write the necessary conditions that have to be fulfilled, as follows : Let us denote the several differential coefficients of T with respect to the variables by I, II, III, &c. Then the emanant identity is 1 i + 2 n + 3 ni + ...=o, and we may develop any single expression, such as III, in the following form : III = III! A 2 + III 22 2 2 + III^s 2 + 2111,-M + . . . 2III M 4 . As the emanant is to vanish identically, we must have the coefficients of the several terms, such as Of, Q?Q. ly A0Ai & c -> all zero, the result being three types of equation In = 0, I-B+ II 12 = 0, I 23 +II 1 3 + IIIi 2 = > 1122 = 0, II U + I 12 =0, &C., 11133 = 0, II B + III B = > &C. f IV^ = 0, &c., &c. &c. Of the first of these classes of equations, I n = 0, there are n, of the second A e^ +u- A n(n-l)(n-2) . w(n+l)(n+2) there are n (n - 1), and of the third, ^^ , in all, - i ^ 5 . 1 . L . o 1 . Z 376. Another identical equation. Let T be the kinetic energy of a perfectly free rigid body twisting for the moment around a screw 6. It is obvious that T will be a function of the six co-ordinates, #/, . . . # 6 , which express the position of the body, and also of 0j, ... 6> the co-ordinates of the twist velocity, T=f(0 l ,...0. t ft, ...A). We may now make a further application of the principle employed in 302. The kinetic energy will be unaltered if the motion of the body be arrested, and if, after having received a displacement by a twist of amplitude e about a screw of any pitch on the same axis as the instantaneous screw, the body be again set in motion about the original screw with the original twist velocity. This obvious property is now to be stated analytically. 376] THE THEORY OF PERMANENT SCREWS. 413 It has been shown in 265 that if lt 2 , ... 6 are the co-ordinates of a screw of zero pitch, then the co-ordinates of a screw of pitch p x on the same axis are respectively * p x dR A p x dR * p x dR "l~l ---- - ~ , t/2 "1 -- -- T~ , . . . t/u T -- ~ - . ^ d0 1 4p 2 d0 2 4>p 6 d0 G In these expressions p x denotes an arbitrary pitch, while R is the function es + fa ... + 6 2 + 2 (12) eA + 2 (23) e,e 3 , &c., where (12) is the cosine of the angle between the first and second screws of reference, and similarly for (23), &c. The principle just stated asserts that T must remain unchanged if we substitute for #/, #2 , & c - the expressions We thus obtain the formula p^dR^dT , A p,dRy^ = Q ^dejde, 4>p 6 deJ d0 6 As this must be true for every value of p x , we must have, besides the vanishing ernanant, the condition ^dR dT^ 1^?^ =0 p l dO, dffi p 6 d0 6 d0 6 ~ It is plain that this is equivalent to the statement that the screw whose co-ordinates are l^dR T_dR ^dR ~Pi d0\ P* d0 2 p* d6 6 must be reciprocal to the screw defined by the co-ordinates I dT_ l^dT^ \dT Pl d0 l " p,d0:r " p 6 d0 6 " The former denotes a screw of infinite pitch parallel to and hence it follows that the restraining screw must be perpendicular to 6. Remember ing also that the restraining screw is reciprocal to 0, it follows that the restraining screw must intersect 0. We thus obtain the following result : If be the screw about which a free rigid body is twisting, then to check the tendency of the body to depart from twisting about a restraining wrench on a screw which intersect* at right angles must in general be applied. 414 THE THEORY OF SCREWS. [377, 377. Different Screws on the same axis. Let the body be displaced from a standard position to another position denned by the co-ordinates #/, 2 , . . . 6 , and let it then be set in rotation about a screw of zero pitch with a twist velocity whose co-ordinates are lt 2 , ... 6 . Let the kinetic energy of the body in this condition be T. Suppose that in addition to the rotation about 6 the body of mass M also received a velocity v of translation parallel to 0. Then the kinetic energy of the body would be T , where It is obvious that the position of the body, i.e. the co-ordinates $/, 0.f, ... e , can have no concern in ^Mv 2 , whence dT dT , a , = -J0-, , and similar equations. at/i CtC/! But a body rotating about with an angular velocity and translated parallel to with the velocity v is really rotating about a screw on the same axis as and with a pitch v -f- p. As v may have any value we obtain the following theorem : All instantaneous screws lying on the same axis have the same restraining screw. 378. Co-ordinates of the Restraining Wrench for a free rigid body. Suppose the body to have a standard position from which we displace it by small twists #/, . . . 6 around the six principal screws of inertia. While the body is in its new position it receives a twist velocity of which the co-ordinates relatively to the six principal screws of inertia are lt ... 6 . To compute the kinetic energy we proceed as follows : Let a point lie initially at oc, y, z, then, by the placing of the body at the starting position the point is moved to X, Y, Z, where X = a (0, - 2 ) + y (0 5 f + 6 ) - z (0 3 f + 0/) + x, Y = b (0 3 f - 0/) + z (0, + 2 ) - x (0, + U ) + y, Z = c (0 r ; - 6 ) + x (0, + 0/) - y (0/ + a ) + z, in which a, b, c are the radii of gyration on the principal axes. The six principal screws of inertia lie, of course, two by two on each of the three principal axes, with pitches + a, a on the first, + b, b on the second, and + c, c on the third. In consequence of the twist velocity with the components #1,... 6 , each point X, Y, Z receives a velocity of which the components are 378] THE THEORY OF PERMANENT SCREWS. 415 a (6, - 0.) + Y(0 r , + e G )-Z (0 3 + 4 ), 6 (B, -0J + Z (0! + 2 ) - X (e r> + 6 ), c (A - 0) + X (A + 4 ) - I 7 (9, + 4). Before substitution for X, Y, Z it will be convenient to use certain abbre viations, 0i 2 = 1 ; &i 2 = pi ; 0i + 0. 2 = \i , BI + 2 = &)] , /]//}/ /} A Q i Q \ Q \ Q "3 #4 = e 2 , 3 (7 4 = p 2 , "3 + #4 = A-2- U 3 + (7 4 = <W 2 , $> # = e 3 ; 5 $ 6 = p 3 ; #5 + #/ = X 3 , 5 + fi = <w s - With these substitutions in v 2 the square of the velocity of the element we readily obtain after integration and a few reductions and taking the total mass as unity, 2 c 2 ) . 2 (i)i bc^p^cos X 2 <w 3 &)j (c 2 a 2 ) > 3 &)i XsO^a^ (a 2 6 2 ), whence we easily find 7/TT If T;/ , ... rj s " be the co-ordinates of the restraining wrench, then, as shown in 368, "= 1^ T P*d0r whence we deduce the following fundamental expressions for the co ordinates of the restraining wrench : pMi" = acp 3 w 2 + abp 2 w s + (6 2 c 2 ) &) 2 &) 3 , PM-i = + acp 3 (o. 2 abp 2 co 3 + (b" c 2 ) &&gt; 2 &&gt; 3 , PMs" = abpico 3 + cbpsWi + (c 2 a 2 ) w^w^ PPl" = + abpitos cbpsW! + (c 2 a 2 ) o) s o) l , PS^S" = bcpzW! + acpiO) 2 + (a 2 6 2 ) w^w*, Pets" = + fop^ acpi(o 2 + (a 2 6 2 ) As usual, we here write for symmetry p l= = + a; p., = -a; p 3 = + b; We verify at once that Pw"0 1 + ... but this is of course known otherwise to be true, because the restraining screw must be reciprocal to the instantaneous screw. 416 THE THEORY OF SCREWS. [378- These equations enable us to study the correspondence between each instantaneous screw 6 and the corresponding restraining screw 77. It is to be noted that this correspondence is not of the homographic, or one-to-one type, such as we meet with in the study of the Principal Screws of Inertia, and in other parts of the Theory of Screws. The correspondence now to be considered has a different character. 379. Limitation to the position of the Restraining Screw. If a particular screw 6 be given, then no doubt, a corresponding screw r) is given definitely, but the converse is not true. If 77 be selected arbitrarily there will not in general be any possible 6. If, however, there be any one 0, then every screw on the same axis as 6 will also correspond to the same 77. From the equations in the last article we can eliminate the six quantities, 6 l , . . . (i ; we can also write ??/ = i)"^, . . . rj n " = tj"r) n where 77" is the intensity of the restraining wrench and ^,,..1)^ the co-ordinates of the screw on which it acts. We have a (%" + V ) = 2abp 2 a) 3 2ac/> 3 <w 2 , 2 c 2 r) 1 + 7; 2 , p. 2 p 3 whence = 6 c , a 7?! 7/2 C0 2 W 3 and from the two similar equations we obtain, by addition, b- j^ 77! + 7/ 2 c 2 a 2 773 + 774 a 2 6 2 % + 77,; _ a % ^2 b *73 - *?4 c 775-776 It might at first have been supposed that any screw might be the possible residence of a restraining wrench, provided the corresponding instantaneous screw were fitly chosen. It should however be remembered that to each restraining screw corresponds a singly infinite number of possible instan taneous screws. As the choice of an instantaneous screw has five degrees of infinity, it was to be presumed that the restraining screws could only have four degrees of infinity, i.e. that the co-ordinates of a restraining screw must satisfy some equation, or, in other words, that they must belong to a screw system of the fifth order, as we have now shown them to do. 380. A verification. We confirm the expression for the co-ordinates of 77 in the following manner. It has been shown ( 376) that so long as retains the same direction and situation, its pitch is immaterial so far as 77 is concerned. This might have been inferred from the consideration that a rigid body twisting about a screw has no tendency to depart from the screw in so far as its velocity of translation is concerned. It is the rotation which necessitates the restrain ing wrench if the motion is to be preserved about the same instantaneous 381] THE THEORY OF PERMANENT SCREWS. 417 screw. We ought, therefore, to find that the expressions for the co-ordinates of ?) remained unaltered if we substituted for 1} ... 6 , the co-ordinates of any other screw on the same straight line as 6. These are ( 47) 04), 04 - y (0 3 where H is arbitrary. Introducing these into the values for rj^, it becomes - aca) 2 (ft + -- a) 3 } + abw. A U% + -?- j + (& 2 - c 2 ) &&gt; 2 &&gt; 3 , y C .. / \ / from which .H" disappears, and the required result is proved. The restraining screw is always reciprocal to the instantaneous screw, and, consequently, if e be the angle between the two screws, and d their distance apart, (Pi + Pe) cos e - d sin e = 0. We have seen that this must be true for every value of p g , whence cos e = ; d = ; i.e. the two screws must intersect at right angles as we have otherwise shown in 376. This also appears from the formulae Vi + W = 26p 2 &&gt; 3 2c/9 3 &&gt; 2 , 1)3" + -n" = 2c/o 8 a>i - 2a/> 1 o> 3 , multiplying respectively by &&gt;,, &&gt; 2 , eo s , and adding, we get til + 17s) (01 + #2) + (% + ^4> (03 + 4 ) + (^75 + 17) (05 + 6 ) = 0, which proves that rj and ^ are rectangular ; but we already know that they are reciprocal, and therefore they intersect at right angles. 381. A Particular Case. The expressions for the restraining wrenches can be illustrated by taking as a particular case an instantaneous screw which passes through the centre of gravity. B. 27 418 THE THEORY OF SCREWS. [381- The equations to the axis of the screw are ap l + 3/0)3 zo) 2 _ bp 2 + za>i #a) 3 _ c/3 3 + xa) 2 yw^ 0>1 &&gt;2 W 3 If x, y, z are all simultaneously zero, then ap 1= bp 1 = cp3 ft)! ft> 2 0> 3 and these are, accordingly, the conditions that the instantaneous screw passes through the centre of gravity. With these substitutions the co-ordinates become p l7)l " = (6 2 - c 2 ) ft> 2 ft> 3 ; Pals" = (c 2 - a 2 ) 30i ; PM*" = (a 2 - & 2 ) iw 2 , PM 9 " = (& - c 2 ) &&gt; 2 a>3 ; PM" = (c 2 - a 2 ) u,^ ; jp^" = (a 2 - 6 2 ) &) 1 a) 2 ; remembering that ^ = + a ; p 2 = - a, &c., we have % " + V =0; 7 7 / + 7 74 // = 0; V+W-0; but these are the conditions that the pitch of 77 shall be infinite ; in other words the restraining wrench is a couple, as should obviously be the case. From the equations already given, we can find the co-ordinates of the instantaneous screw in terms of those of the restraining screw. We have __ ~ 2 (6 2 - c 2 ) (c 2 - a 2 ) (a 2 - 6 2 ) ,-j-f O TT . JJ and O>i = tl - 77 -fj: ] f>2 = = ti T~, T, 77V j ^3 " ~~7 77 /7\ a (r} 1 7/2 ) (773 ^4 j C ^7/5 f] 6 ) If we make then we have 3 "* - . _ G " 2pT "2o6c In these expressions, /> fl is the pitch of 6, and is, of course, an indeterminate quantity. 382. Remark on the General Case. If the freedom of a body be restricted, then any screw will be permanent, provided its restraining screw belong to the reciprocal system. For the body 383] THE THEORY OF PERMANENT SCREWS. 419 will not depart from the original instantaneous screw except by an accelera tion. This must be on a screw which stands to the restraining screw in the relation of instantaneous to impulsive, but in the case supposed these two screws are reciprocal, therefore they cannot be so related, and therefore there is no acceleration. There is little to be said as to the restraining wrench when the freedom is of the first order. Of course, in this case, as every movement of the body can only be a twist about the screw which prescribes its freedom, the restraining wrench is provided by the reactions of the constraints. It is only where the body has liberty to abandon its original instantaneous screw that the theory of the restraining wrench becomes significant. 383. Two Degrees of Freedom. If a rigid body has two degrees of freedom, then it is free to twist about every screw on a certain cylindroid. If the body be set initially in motion by a twist velocity about some one screw on the surface, then, in general, it will not remain twisting about this screw. A movement will take place by which the instantaneous axis gradually comes into coincidence with other screws on the cylindroid. If we impose a suitable restraining wrench i), then of course can be maintained as the instantaneous screw; 77 is reciprocal to 6. It may be compounded with any reactions of the constraints of the system. Thus, given 6, there is an entire screw system of the fifth order, consisting of all possible screws reciprocal to 0, any one screw of which may be taken as the restrainer. Of this system there is one, but only one, which lies on the cylindroid itself. There are many advantages in taking it as the restraining wrench, and it entails no sacrifice of generality ; we there fore have the following statement : To each screw on the cylindroid, regarded as an instantaneous screw, will correspond one screw, also on the cylindroid, as a restraining screw. The position of this restraining screw is at once indicated by the property that it must be reciprocal to the instantaneous screw. If we employ the circular representation for the screws on the cylindroid (fig. 42), and if be the pole of the axis of pitch, then it is known that the extremities of any chord, such as IR drawn through 0, will correspond to two re ciprocal screws ( 58). If therefore / be the instantaneous screw, R must be the restraining screw. If a body free to twist about all the screws on the cylindroid be set in motion by a twist velocity about /. it will be possible, by a suitable wrench 27-2 4 20 THE THEORY OF SCREWS. [383- applied on the screw corresponding to R, to prohibit the body from changing its instantaneous screw. Let be the pole of the axis of inertia, then, if I A be a chord drawn through , the points / and A correspond to a pair of conjugate screws of inertia ( 135). It further appears that A is the instantaneous screw corre sponding to an impulsive wrench on R ( 140). Therefore the effect of the wrench on R when applied to control the body twisting about 7 is to com pound its movement with a nascent twist velocity about A. Therefore A must be the accelerating screw corresponding to /. We thus see that Of two conjugate screws of inertia, for a rigid body with two degrees of freedom, either is the accelerator for a body animated by a twist velocity about the other. 384. Calculation of T. In the case of freedom of the second order we are enabled to obtain the form of T, from the fact that the emanant vanishes, that is, If we assume that T is a homogeneous function of the second degree in 0i and 2 , the solution of this equation must be T = M 2 + zseA + Me, 2 + H (6>;0 2 - o&y + (0/0 2 - #/ e,) (A0, + M), in which L, S, M, H, A are constants. If we further suppose that 0, and #./ are so small that their squares may be neglected, then the term multiplied by H may be discarded, and we have T = M 2 whence Thus, for the co-ordinates of the restraining screw, supposing the screws of reference to be reciprocal, we have from which it is evident that which is, of course, merely expressing the fact that 77 and 9 are reciprocal. 385. Another method. It may be useful to show how the form of T, just obtained, can be derived from direct calculation. I merely set down here the steps of the work and the final result. THE THEORY OF PERMANENT SCREWS. 421 Let us take any two screws on the cylindroid a and ft, and let their co ordinates, when referred to the absolute screws of inertia, be ls ... 6 , and &, ... /8. Then any other screw on the cylindroid, about which the body has been displaced by a twist, by components #/ on a. and 2 on ft will have, for co ordinates, ^ *MV...%tf*M . and the screw about which the body is twisting, with a twi^t velocity 0, will have, for co-ordinates, It readily appears that, so far as the terms involving #/and #./are concerned, the kinetic energy is the expression where A = + be (! + 2 ) [( 3 - 6 ) (& - &) - (3 - 4> (A - &)] + (6 2 - c 2 ) (a, + 04) (a, + a 6 ) (A + & + ca (a g + 4 ) [(a, - a.,) (& - /3 6 ) - ( 5 - 6 ) (A - A)] + (c 2 - a 2 ) ( B + 6 ) (! + 2 ) (/3 S + a6 (a s + 6 ) [(a, - 4 ) (A - &) - ( ai - a 2 ) (/3 3 - /3 4 )] + (a 2 - 6 2 ) (! + a a ) ( 3 + 4 ) (A = + be (& + /8 8 ) [( 5 - 6 ) 09, - A) - (a, - 4 ) (A - - (Z> 2 - c 2 ) (a : + a, ca 3 + ! - 2 / B - / 6 - 5 - - (c 2 - a 2 ) ( 3 + 4 ) (/S B - a,) (A - /3 2 ) - (i - - (a 2 - 6 2 ) (a, + .) (A + A) (A + A). 386. The Permanent Screw. We now write the equations of motion for a body which has two degrees of freedom, and is unacted upon by any force, the screws of reference being the two principal screws of inertia. We have, from the general equations (367) M" 2/3 ^^ = 422 THE THEORY OF SCREWS. Introducing the value just obtained for T, [386- There must be one screw on the cylindroid, for which This screw will have the accelerations ^ and 2 , both zero, and thus we have the following theorem : If a rigid body has two degrees of freedom, then, among the screws about which it is at liberty to twist, there is one, and in general only one, which has the property of a permanent screw. The existence of a single permanent screw in the case of freedom of the second order seems a noteworthy point. The analogy here ceases between the permanent screws and the principal screws of inertia. Of the latter there are two on the cylindroid ( 84). 387. Geometrical Investigation. Let N (fig. 43) be the critical point on the circle which corresponds to the permanent screw ( 50). Let P be a screw 0, the twist velocity about Oi Fig. 43. which is 0. Let u e be a linear parameter appropriate to the screw 6, such that Mu g 2 6 2 is the kinetic energy. Let O x and 2 be the two screws of reference on the cylindroid and for convenience let the chord 00 Z be unity. Let the point Q correspond to another screw <f>, then from 57 Ptolemy s theorem gives PQ6(f> = 2 <l $102- Now let < be the adjacent screw about which the body is twisting in a time 8t after it was twisting about 6. 388] THE THEORY OF PERMANENT SCREWS. 423 Then 01 = @i + OiOt, <j>2 ~ $2 + d z ot, whence which is, accordingly, the rate at which P will change its position. If we substitute for 0j and 6 2 their values already found in the last article, we obtain for the velocity of P the expression N being the position of the permanent screw, let p be the length of the chord P^, then the expression just written assumes the form where k is a constant. This expression illustrates the character of the screw corresponding to N. If p be zero, then the expression for this velocity vanishes. This means that P has no tendency to abandon N ; in other words, that the screw correspond ing to N is permanent. 388. Another method. It is worth while to investigate the question from another point of view. Let us think of any cylindroid 8 placed quite arbitrarily with respect to the position of the rigid body. A certain restraining screw i) will corre spond to each screw 6 on S. As 6 moves over the cylindroid, so must the corresponding screw 17 describe some other ruled surface S . The two surfaces, S and 8 , will thus have two corresponding systems of screws, whereof every two correspondents are reciprocal. One screw can be dis covered on S , which is reciprocal, not alone to its corresponding 6, but to all the screws on the cylindroid. A wrench on this ij can be provided by the reactions of the constraints, and, consequently, the constraints will, in this case, arrest the tendency of the body to depart from 6 as the instantaneous screw. It follows that this particular 6 is the permanent screw. The actual calculation of the relations between 77 and the cylindroid is as follows : A set of forces applied to a rigid system has components X, T, Z at a point, and three corresponding moments F, G, H in the rectangular planes of reference. 424 THE THEORY OF SCREWS. [388 Let p be the pitch of the screw on which the wrench thus represented lies, and let a, y, z be the co-ordinates of any point on this screw. Then, in the plane of Z the moments of the forces are xY yX, and if to this be added pX, the whole must equal H. Thus we have the three equations, so well known in statics, F=pX+yZ -zY, G=pY+zX-xZ, H=pZ + xY -yX. The centrifugal acceleration on a point P is, of course, co 2 PH, where o> is the angular velocity, and PH the perpendicular let fall on the axis. The three components of this force are X y Y , Z , where X = ft> 2 sin 6 (x sin y cos 0}, Y = ft) 2 cos 6 (y cos 6 x sin 0), Z = ft) 2 0-rasin 2(9), and the three moments are F , G , H , where F = to 2 sin 9 (yz sin + xz cos 6 Zmy cos 6), G = ft) 2 cos 6 ( yz sin 6 xz cos 6 + Zmx sin 0), H = to 2 1(2/ 2 - 2 ) sin cos 6 + xy cos 20}. We are now to integrate these expressions over the entire mass, and we employ the following abbreviations ( 324) : jxdm = Mx jydm = My ; $zdm = Mz ; jxydm = M1 3 2 ; fxzdm = Ml.? ; jyzdm = Ml? ; X = fX dm , Y=fY dm; Z = jZ dm; F = fF dm; G=fG dm; H=JH dm; then, omitting the factor Ma?, we have X= + (a? sin 6 y cos 6) sin 0, Y= (x sin 6 7/ cos 6) cos 0, Z = Z Q m sin 20 ; F = + sin (I, 2 sin + I* cos 0) - 2my sin cos 0, G = - cos (^ sin (9 + , 2 cos 0) + 2mx sin cos 0, #= (/>i 2 - p*} sin cos + r- cos 20. We can easily verify that 388] THE THEORY OF PERMANENT SCREWS. 425 We now examine the points on the cylindroid intersected by the axis of the screw F=pX+yZ -zY, G=pY+zX-xZ, H=pZ + xY-yX. We write the equations of the cylindroid in the form x R cos <f> ; y = R sin < ; z = m sin2</>; then, eliminating p and R, and making V = FX+GY+HZ, we find, after a few reductions, tan 3 ^(YV-GU) + tan 2 <f> (X V - FU + 2mX U) This cubic corresponds, of course, to the three generators of the cylindroid which the ray intersects. If we put then the cubic becomes, by eliminating m, The factor Ftan^ + Z simply means that the restraining screw cuts the instantaneous screw at right angles. The two other screws in which 77 intersects the cylindroid are given by the equation (XYV-XGU) tan 2 + (XYV- FUY) = 0. These two screws are of equal pitch, and the value of the pitch is Pl (XYV-XGU)+p 2 (FUY-XYV} U(FY-GX) where p^ and p. 2 are the pitches of the two principal screws on the cylindroid. After a few reductions the expression becomes V (I* - x opl ) sin + (I* + y opa ) cos 6 U x Q sin y cos 6 This is the pitch of the two equal pitch screws on the cylindroid which rj intersects. If 77 is to be reciprocal to the cylindroid, then, of course, the pitch of 77 itself should be equal and opposite in value to this expression. Hence the permanent screw on the cylindroid is given by (li* - XopJ sin 6 + (7 2 2 + y p 2 ) cos 6 = 0. 426 THE THEORY OF SCREWS. [388- We notice here the somewhat remarkable circumstance, that if /! 2 - ajojpi = 0> and I? + y*P* = 0, then all the screws on the cylindroid are permanent screws. It hence appears that if two screws on a cylindroid are permanent, then every screw on the cylindroid is permanent. 389. Three Degrees of Freedom. Let us now specially consider the case of a rigid body which has freedom of the third order. On account of the evanescence of the emanant we have *dT * dT , dT _ *W 4 * W 4 *W? It is well known that if U, V, W be three conies whose equations submit to the condition those conies must have three common intersections. It therefore follows that the three equations must have three common screws. These are, of course, the permanent screws, and, accordingly, we have the theorem : A rigid system which has freedom of the third order has, in general, three permanent screws. There will be a special convenience in taking these three screws as the screws of reference. We shall use the plane representation of the three- system, and the equations of the conies will be AJA + BAOi + CAO^O, or 7=0, AAo s + BAOi + cAo, = o, F=O, AAh + BA^ + cAe^o, w=o-, but, as e l u + e 2 v+0 3 w = o, identically, we must have ^ = 0; A, = Q; A 3 = 0; (7 1= 0; C 2 =0; B 3 =0; and also A : + B 2 + C 3 = 0. For symmetry we may write 390] THE THEORY OF PERMANENT SCREWS. 427 We thus find that when T is referred to the three permanent screws of the system, its expression must be T= aB* + 60 2 2 + c0 3 2 + ZfdA + %ff$A + %h0A + (ji-v) 010 A + (v-\) 0M + (X - A*) S A- Let 77" be the intensity of any wrench acting on a screw 77 belonging to the system, and let 2-or lr , represent the virtual coefficient between 77 and the first of the three screws of reference. Then, substituting for T in Lagrange s equations, we have + ah + h 2 + g 3 -(p-v) eA = -n-^7?", If 77 be the restraining screw, then an appropriate wrench ?/ should be capable of annihilating the acceleration, i. e. of rendering 0j = ; 2 = ; S = ; whence the position of 77, and the intensity 77" are indicated by the equations (V - We can now exhibit the nature of the correspondence between 77 and 0, for If we make H=$i$A+n"> and omit the dots over lt &c., we have + w 32 77 3 ) - H (a - 7), 03 Oia*?! + ^ 32 i?2 +p 3 r ns) =H(@- a). We may reduce them to two homogeneous forms, viz. where L = - M=; N = \ d^ * ^772 ^773 390. Geometrical Construction for the Permanent Screws. We see that 77 must lie on the polar of the point lt 2 , 3 with respect to the pitch conic ( 201) or the locus of all the screws for which 428 THE THEORY OF SCREWS. [390, We also see that 77 must lie on the polar of the point a#i, /3# 2 > 7$s with regard to the same conic. We thus obtain a geometrical construction by which we discover the restraining screw when the instantaneous screw is given. Two homographic systems are first to be conceived. A point of the first system, of which the co-ordinates are 8 1} # 2 > &s, has as its correspondent a point in the second system, with co-ordinates a0 1} /30 2 , j0 3 . The three double points of the homography correspond, of course, to the permanent screws. To find the restraining screw ?? corresponding to a given instantaneous screw 0, we join to its homographic correspondent, and the pole of this ray, with respect to the pitch conic, is the position of 17. The pole of the same ray, with regard to the conic of inertia ( 211), is the accelerator. It seems hardly possible to have a more complete geo metrical picture of the relation between 77 and 9 than that which these theorems afford. 391. Calculation of Permanent Screws in a Three-system. When a three-system is given which expresses the freedom of a body we have seen how in the plane representation the knowledge of a conic (the conic of inertia) will give the instantaneous screw corresponding to any given impulsive screw. A conic is however specified completely by five data. The rigid body has nine co-ordinates. It therefore follows that there is a quadruply infinite system of rigid bodies which with respect to a given three-system will have the same conic of inertia. If in that three-system a be the instantaneous screw corresponding to 77 as the impulsive screw for any one body of the quadruply infinite system, then will 77 and a stand in the same relation to each other for every body of the system. The point in question may be illustrated by taking the case of a four- system. The screws of such a system are represented by the points in space, and the equation obtained by equating the kinetic energy to zero indicates a quadric. For the specification of the quadric nine data are necessary. This is just the number of co-ordinates required for the specification of a rigid body. If therefore the inertia quadric in the space representation be assumed arbitrarily, then every instantaneous screw corresponding to a given impulsive screw will be determined; in this case there is only a finite number of rigid bodies and not an infinite system for which the correspond ence subsists. We thus note that there is a special character about the freedom of the fourth order which we may state more generally as follows. To establish a chiastic homography ( 292) in an n-system requires (n l)(n + 2)/2 data. 391] THE THEORY OF PERMANENT SCREWS. 429 If the restraints are such that the number of degrees of freedom is less than four, then an infinite number of rigid bodies can be designed, such that the impulsive screws and their corresponding instantaneous screws shall be represented by a given chiastic homography. If n exceed four then it will not in general be possible to design a rigid body such that its corre sponding impulsive screws and instantaneous screws shall agree with a given chiastic homography. If, however, n 4 then it is always possible to design one but only one rigid body so that its pairs of corresponding impulsive screws and instantaneous screws shall be represented by a given chiastic homography. Returning to the three-system we may remark that, having settled the inertia conic in the plane representation we are not at liberty to choose three arbitrary points as representing the three permanent screws. For if these three points were to be chosen quite arbitrarily, then six relations among the co-ordinates of the rigid body would be given, and the conic of inertia would require five more conditions. Hence the co-ordinates of the rigid body would have in general to satisfy eleven conditions which, of course, is not generally possible, as there are only nine such co-ordinates. It is therefore plain that when the conic of inertia has been chosen at least two other conditions must necessarily be fulfilled by the three points which are to represent the permanent screw. This fact is not brought out by the method of 389 in which, having chosen the three permanent screws arbitrarily, we have then written down the general equation of a conic as the inertia conic. This conic should certainly fulfil at least two con ditions which the equations as there given do not indicate. We therefore calculate directly the expression for the kinetic energy of a body in the position #/, # 2 , 3 twisting about a screw with twist velocities #1, 6 2 , 6 3 when the screws of reference are the three principal screws of the three-system with pitches a, b, c, and when a? , y , z , If, 1 2 2 , 1 3 2 , pf, p 2 * } p/ are the nine co-ordinates ( 324) of the rigid body relative to these axes. It is easily shown that we have for the kinetic energy the mass M of the body multiplied into the following expression where squares and higher powers of #/, # 2 > QS are omitted : i (a 2 ^ 2 + W + c 2 3 2 + p*0* + p*ej + p 3 *0 3 *) + 0A (c -b)x + 0A (a -c)y + 0A (b - a) z. + 0A(p* 2 - p>? + uc - ab) + 0A (V - cz ) - 6 A (4 2 430 THE THEORY OF SCREWS. + 0A (Pi 2 - p 3 2 + ba - be) + 0A (/> 2 2 - pi +cb- GO) + 0A (I? - fyo) - 3 0i (li 2 [391- + 0* + 01 The coefficients of #/, # 2 , 0s respectively each equated to zero will give three conies 7=0, F= 0, Tf = 0. These conies have three common points which are of course the three permanent screws. If we introduce a new quantity O we can write the three equations (I/ - + (l*-ax*)0 2 + (ab - p-> + H) 3 = 0. The elimination of ft between each pair of these equations will produce the three equations U = Q, V0, W = 0. If therefore we eliminate 1} 2 , 3 from the three equations just written the resulting determinant gives a cubic for H. The solution of this cubic will give three values for fl which substituted in the three equations will enable the corresponding values of 0i > 0zy 0s to be found. We thus express the co-ordinates of the three per manent screws in terms of the nine co-ordinates of the rigid body and their determination is complete. It may be noted that the same permanent screws will be found for any one of the systems of rigid bodies whose co-ordinates are whatever h may be. 392. Case of Two Degrees of Freedom. We have already shown that there is a single permanent screw in every case where the rigid body has two degrees of freedom. We can demonstrate this in a different manner as a deduction from the case of the three- system. Consider a cylindroid in a three-system, that is of course a straight line in the plane representation ( 200). Let this line be AB (tig. 44). If the movements of the body be limited to twists about the screws on the cylindroid, there may be reactions about the screw which corresponds to the pole P of this ray with respect to the pitch conic, in addition to the reactions of the three-system. 393] THE THEORY OF PERMANENT SCREWS. 431 The permanent screw on this cylindroid will be one whereof the restrain ing screw coincides with P. In gene.ral, the points corresponding homo- Fig. 44. graphically to the points on the ray AB will form a ray CD. The inter section 0, regarded as on CD, will be the correspondent of some point X on AB. The restraining screw corresponding to X will therefore lie at P, and will be provided by the constraints. Accordingly, X is a permanent screw on the cylindroid, and it is obvious from the construction that there can be no other screw of the same character. We can also deduce the expression for T in the two-system from the expression of the more general type in the three-system ; for we have T= T + o - v) o; e A +(v-\) o;d A + (*-/*) # 3 0A. Consider any screw on the cylindroid defined by substituting, we obtain (0, 8 - 2 3 ) [(X - ft) P0 2 + (\-v) Q9 3 ], which we already know to be the form of the function in the case of the two- system ( 384). 393. Freedom of the Fourth Order. The permanent screws in the case of a rigid body which has freedom of the fourth order may be investigated in the following manner: If a screw be permanent, the corresponding restraining screw 77 must be provided by the reactions of the constraints. All the reactions in a case of freedom of the fourth order lie on the screws of a cylindroid. On a given cylindroid three possible 77 screws can be found. For, if we substitute a l + \^ 1 , 2 + X/3 2 , &c., for T/!, 7/2, &c., in the equation { c-a [ b 7? 3 - 7/4 432 THE THEORY OF SCREWS. [393-397 we obtain a cubic for X. The three roots of this cubic correspond to three 77 screws. Take the 6 corresponding to one of the 77 screws, then, of course, 6 will not, in general, belong to the four-system. We can, however, assign to Q any pitch we like, and as it intersects 77 at right angles, it must cut two other screws of equal pitch on the cylindroid ( 22). Give to 6 a pitch equal and opposite to that of the two latter screws, then 6 is reciprocal to the cylindroid, and therefore it belongs to the four-system. We thus have a permanent screw of the system, and accordingly we obtain the following result : In the case of a rigid body with freedom of the fourth order there are, in general, three, and only three, permanent screws. 394. Freedom of the Fifth and Sixth Orders. When a rigid body has freedom of the fifth order, the screws about which the body can be twisted are all reciprocal to a single screw p. In general, p does not lie on the system prescribed by the equation which the co-ordinates of all possible 77 screws have to satisfy. It is therefore, in general, not possible that the reaction of the constraints can provide an 77. There are, however, three screws in any five-system which possess the property of permanent screws without however making any demand on the reaction of the constraints. The existence of these screws is thus demonstrated : Through the centre of inertia of the body draw the three principal axes, then, on each of these axes one screw can always be found which is reciprocal to p. Each of these will belong to the five-system, and it is obvious from the property of the principal axes, that if the body be set twisting about one of these screws it will have no tendency to depart therefrom. A body which has freedom of the sixth order is perfectly free. Any screw on one of the principal axes through the centre of inertia is a permanent screw, and, consequently, there is in this case a triply infinite number of permanent screws. 395. Summary. The results obtained show that for a rigid body with the several degrees of freedom the permanent screws are as follows : No. of Permanent Screws Freedom I 1 II. 1 Ill . 3 IV. . 3 V. 3 VI Triply infinite CHAPTER XXVI. AN INTRODUCTION TO THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 396. Introduction. The Theory of Screws in non-Euclidian space is a natural growth from some remarkable researches of Clifford* in further development of the Theory of Riemann, Cayley, Klein and Lindemann. I here give the in vestigation sufficiently far to demonstrate two fundamental principles ( 42 7> 434) which conduct the theory to a definite stage at which it seems convenient to bring this volume to a conclusion. I have thought it better to develop from the beginning the non- Euclidian geometry so far as we shall at present require it. It is thus hoped to make it intelligible to readers who have had no previous acquaintance with this subjectf. I give it as I have worked it out for my own instruction*. It is indeed characteristic of this fascinating theory that it may be surveyed from many different points of view. 397. Preliminary notions. Let #!, # 2 , x 3 , x t be four numerical magnitudes of any description. We may regard these as the co-ordinates of an object. Let y lt y 2 , y 3t y 4 be the co-ordinates of another object, then we premise that the two objects will be identical if, and only if 1 ^2 3 4 ?/l ~ #2 ~ 2/3 ~ 2/4 All possible objects may be regarded as constituting a content. "Preliminary Sketch of Biquaternions," Proceedings of the London Mathematical Society, Vol. iv. 381395 (1873). See also "On the Theory of Screws in a Space of Constant Positive Curvature," Mathematical Papers, p. 402 (1876). Clifford s Theory was much extended by the labours of Buchheim and others ; see the Bibliographical notes. t We are fortunately now able to refer English readers to a Treatise in which the Theory of non-Euclidian space and allied subjects is presented in a comprehensive manner. Whitehead, Universal Algebra, Cambridge, 1898. Trans. Roy. Irish Acad., Vol. xxvm. p. 159 (1881), and Vol. xxix. p. 123 (1887). B - 28 434 THE THEORY OF SCREWS. [397- All objects whose co-ordinates satisfy one linear homogeneous equation we shall speak of as an extent. All objects whose co-ordinates satisfy two linear homogeneous equations we shall speak of as a range. It must be noticed that the content, with its objects, ranges, and extents, have no necessary connexion with space. It is only for the sake of studying the content with facility that we correlate its several objects with the points of space. 398. The Intervene. In ordinary space the most important function of the co-ordinates of a pair of points is that which expresses their distance apart. We desire to create that function of a pair of objects which shall be homologous with the distance function of a pair of points in ordinary space. The nature of this function is to be determined solely by the attributes which we desire it to possess. We shall take the most fundamental pro perties of distance in ordinary space. We shall then re-enunciate these properties in generalized language, and show how they suffice to determine a particular function of a pair of objects. This we shall call the Intervene between the Two Objects. Let P, Q, R be three collinear points in ordinary space, Q lying between the other two ; then we have, of course, as a primary notion of distance, PQ + QR = PR. In general, the distance between two points is not zero, unless the points are coincident. An exception arises when the straight line joining the points passes through either of the two circular points at infinity. In this case, however, the distance between every pair of points on the straight line is zero. These statements involve the second property of distance. In ordinary geometry we find on every straight line one point which is at an infinite distance from every other point on the line. We call this the point at infinity. Sound geometry teaches us that this single point is properly to be regarded as a pair of points brought into coincidence by the assumptions made in Euclid s doctrine of parallelism. The existence of a pair of infinite points on a straight line is the third property which, by suitable generalization, will determine an important feature in the range. The fourth property of ordinary space is that which asserts that a point at infinity on a straight line is also at infinity on every other straight line passing through it. This obvious property is equivalent to a significant law of intervene which is vital in the theory. If we might venture to enunciate it in an epigrammatic fashion, we would say that there is no short cut to infinity. THE THEORY OF SCREWS TN NON-EUCLIDIAN SPACE. 435 The fifth property of common space which we desire to generalize is one which is especially obscured by the conventional coincidence of the two points at infinity on every straight line. We prefer, therefore, to adduce the analogous, but more perfect, theorem relative to two plane pencils of homographic rays in ordinary space, which is thus stated. If the two rays to the circular points at infinity in one pencil have as their correspondents the two rays to the circular points in the other pencil, then it is easily shown that the angle between any two rays equals that between their two correspondents. We now write the five correlative properties which the intervene is to possess. They may be regarded as the axioms in the Theory of the Content. Other axioms will be added subsequently. 399. First Group of Axioms of the Content. (I) If three objects, P, Q, R on a range be ordered in ascending para meter ( 400), then the intervenes PQ, QR, PR are to be so determined that (II) The intervene between two objects cannot be zero unless the objects are coincident, or unless the intervene between every pair of objects on the same range is also zero. (III) Of the objects on a range, two either distinct or coincident are at infinity, i.e. have each an infinite intervene with all the remainder. (IV) An infinite object on any range has an infinite intervene from every object of the content. (V) If the several objects on one range correspond one-to-one with the several objects on another, and if the two objects at infinity on one range have as their correspondents the two objects at infinity on the other, then the intervene between any two objects on the one range is equal to that between their correspondents on the other. 400. Determination of the Function expressing the Intervene between Two Objects on a Given Range. Let x l , x 2 , x s , x 4 , and y 1} y z , y s , y 4 be the co-ordinates of the objects by which the range is determined. Then each remaining object is constituted by giving an appropriate value to p in the system, Let A. and /* be the two values of p which produce the pair of objects of which the intervene is required. It is plain that the intervene, whatever it be, must be a function of x lt x 2 , # 3 , # 4 and y j} y 2 , y s> y t , and also of X and /z. So far as objects on the same range are concerned, we may treat the co- 28-2 436 THE THEORY OF SCREWS. [400 ordinates of the originating objects as constant, and regard the intervene simply as a function of X, and /*, which we shall denote by/(X, yu,). The form of this function will be gradually evolved, as we endow it with the attributes we desire it to possess. The first step will be to take a third object on the same range for which the parameter shall be v, where X, p, v are arranged in order of magnitude. Then, as we wish the intervene to possess the property specified in Axiom I., we have By the absence of /u from the right-hand side, we conclude that /j, must disappear identically from the left-hand side. This must be the case whatever X and v may be. Hence, no term in which /A enters can have X as a factor. It follows that f(\, p) must be simply the difference of two parts, one being a function of X, and the other the same function of p. Accordingly, we write, The first step in the determination of the intervene function has thus been taken. But the form of (f> is still quite arbitrary. The rank of the objects in a range may be concisely defined by the magnitudes of their corresponding values of p. Three objects are said to be ordered when the corresponding values of p are arranged in ascending or descend ing magnitude. Let P, Q, Q be three ordered objects, then it is generally impossible that the intervenes PQ and PQ shall be equal ; for, suppose them to be so, then PQ + QQ = PQ by Axiom I.; but, by hypothesis, PQ = PQ , and hence QQ = 0. But, from Axiom Tl., it follows that (Q and Q being different) this cannot be true, unless in the very peculiar case in which the intervene between every pair of objects on the range is zero. Omitting this exception, to which we shall subsequently return, we see that PQ and PQ cannot be equal so long as Q and Q are distinct. We hence draw the important conclusion that there is for each object P but a single object Q, which is at a stated intervene therefrom. Fixing our attention on some definite value B (what value it does not matter) of the intervene, we can, from each object X, have an ordered equi- intervene object /j, determined. Each X will define one yu,. Each p will correspond to one X. The values of X with the correlated values of /u, form two homographic systems. The relation between X and yu depends, of course, 400] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 437 upon the specific value of 8, but must be such that, when one of the quantities is given, the other shall be determined by a linear equation. It is therefore assumed that X and //, must be related by the equation where the ratios of the coefficients A, B, C, D shall depend, to some extent, upon 8. If X and // be a given pair of parameters belonging to objects at the required intervene, then by which the disposable coefficients in the homographic equation are reduced to two. The converse of Axiom II., though generally true, is not universally so. It will, of course, generally happen that when two objects coincide their intervene is zero. But on every range two objects can be found, each of which is truly to be regarded as two coincident objects of which the intervene is not zero. Let us, for instance, make X = yu, in the above equation ; then we have This equation has, of course, two roots, each of which points out an object of critical significance on the range. We shall denote these objects by and . Each of them consists of a pair of objects which, though actually coincident, have the intervene 8. The fundamental property of and is thus demonstrated. Let X be any object on the range ; then (Axiom I.) XO + 8 = XO; and as 8 is not zero, we have XO = infinity. Therefore every object on the range is at an infinite intervene from 0. A similar remark may be made with respect to ; and hence we learn that the two objects, and , are at infinity. We assume, in Axiom in., that there are not to be more than two objects on the range at infinity : these are, of course, and . We must, therefore, be conducted to the same two objects at infinity, whatever be the value of the intervene 8, from which we started.* We thus see that while the original coefficients A , B, C, D do undoubtedly contain 8, yet that 8 does not affect the equation A\* + (B + C) X + D = 0. * My attention was kindly directed to this point in a letter from Mr F. J. M Aulay. 438 THE THE011Y OF SCEEWS. [400 It follows that D -T- A and (B + C) -=- A must both be independent of 8. We may therefore make and thus the homographic equation becomes where A is the only quantity which involves 8. The equation can receive a much simpler form by taking the infinite objects as the two originating objects from which the range was determined. In this case the equation must have as roots X = and X = x, and therefore 4=0; D = 0, hence the homographic equation reduces to B\ + C/* = ; since B -=- C is a function of the intervene 8, we may say, conversely, that We have, however, already learned that the intervene is to have the form Now we find that it can also be expressed, with perfect generality, in the form It follows that these two expressions must be equal, so that In this equation the particular value of B does not appear, nor is it even implied. The formula must therefore represent an identical result true for all values of X and all values of /it. We may, therefore, differentiate the formula with respect both to \ and to fji, and thus we obtain 400] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 439 whence we deduce X < (>) = /*</> (/A As X and p are perfectly independent, this equation can only subsist by assuming for < a form such that \<j> (\) = H, where H is independent of X. Whence we obtain </> = f, and, by integration, (X) = H log X + constant. The intervene is now readily determined, for <j> (X) - </> O) = H log X - H log p, = H log - . f We therefore obtain the following important theorem which is the well- known* basis of the mensuration of non-Euclidian space : Let #1, # 8 , #g, # 4 , and y lt y a , y s , y* be the two objects at infinity on a range, and let a^ + X^i, # 2 + Xy 2 , x 3 + \y 3 , x + ^y, and x l + /u# 1} x 2 + /j,y 2 , oc 3 + ^y 3 , i + py* be any two other objects on the range, then their intervene will be expressed by H (log X - log fi) t where H is a constant depending upon the adopted units of measurement. It will be useful to obtain the expression for the intervene in a rather more general manner by taking the equation in X and /A, for objects at the intervene 8, as Let X and X" be the two roots of this equation when //. is made equal to X. It follows that what we have just written may be expressed thus: X^ + X (0 - IX - IX") + fi (- 6 - ^X - IX") + X X" = 0. For, if X = p, this is satisfied by either X or X", while 6 disappears. 6 is, of course, a function of the intervene, and it is only through 6 that the inter vene comes into the equation. By solving for 9, we find * Professor George Bruce Halsted remarks in Science, N. S., Vol. x., No. 251, pages 545557, October 20, 1899, that "Koberto Bonola has just given in the Bolletirw di Bibliografia e Storia della Scienze Matematiche (1899) au exceedingly rich and valuable Bibliografia sui Fondamenti, della Geometria in relazione alia Geometria non-Euclidea in which he gives 353 titles." 440 THE THEORY OF SCREWS. [400, The intervene itself is F (&), where F expresses some function; and, accordingly, When we substitute in this expression the value of 6 given above, we have an identity which is quite independent of the particular 8. We must, there fore, determine the functions so that this equation shall remain true for all values of X, and all values of p. The formulae must therefore be true when differentiated d6_ __(/*-X )OA-X") d6 = (X-X )(X"-X) dx t-x) 2 d^ (/i-x) 2 whence, or (X - X )(X - X") < (X) = O - X )(/A - X") f (/*), which has the form Considering the complete independence of both X and /JL, this equation re quires that each of its members be independent alike of X and /*. We shall denote them by H (X X") where H is a constant, whence (X - X )(X - X") (j> (\) = H(\ r - X"), JUV -v x-x V whence, integrating and denoting the arbitrary constant by C, (f>(\)=H [log (X - X ) - log (X - X")] + G ; similarly, and, finally, we have for the intervene, or (X) </> (^), the expression, This expression discloses the intervene as the logarithm of a certain an- harmonic ratio. We may here note how a difficulty must be removed which is very likely to occur to one who is approaching the non-Euclidian geometry for the 401] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 441 first time. No doubt we find the intervene to be the logarithm of an an- harmonic ratio of four quantities, but these quantities are not distances nor are they quantities homologous with the intervene. They are simply numerical. The four numbers, X, jj,, X , X" are merely introduced to define four objects, one of them being, and the others are obtained by replacing X by //,, X , X", respectively. All we assert is, that if we choose to call the two objects defined by X and X" the objects at infinity, and that if we desire the intervene between the objects X and /j, to possess the properties that we have already specified, then the only function possible will be the logarithm of the anharmonic ratio of these four numbers. The word anharmonic is ordinarily applied in describing a certain function of four collinear points. In the more general sense, in which we are at this moment using the word, it does not relate to any geometrical or spacial relation whatever ; it is a purely arithmetical function of four abstract numbers. We may also observe that the relation between 6 and the intervene 8 is given by the equation 8 P H , 1 /i i/v \ \ "It* ~ x )-s- and the expression of the intervene as a function of 6 ; that is, the expression F(6} is 401. Another process. We may also proceed in the following manner. Let us denote the values of X for the infinite objects on the range by pe ie and pe~ ie . If then X, fji be two parameters for two objects at an intervene , we must have (p. 439) X/i + X (e p cos 6) + fM ( e - p cos 6) + p 2 = 0. Solving for e, we have _ X/i p cos 6 (X + p,} + p z fji X The intervene 8 must be some function of e, whence 442 THE THEORY OF SCREWS. [401- whence dF de _ dF p? - 2//, cos + p* * ( J de d\ ~ de ~ (fi - X) 2 dF de _ dF A, 2 - 2X cos + p 2 * (/ * ~~fadiM~Te ~(/a - \) 2 ~ (X 2 - 2X cos + p 2 ) < (A,) = (fj? - 2/4 cos + p*) < (^) = p sin suppose. Hence we have . ,. x , / p sin 6 \ </> (X) = tan- 1 - a - , \p cos \J and thus we get for the intervene with a suitable unit o, . / psin 8 \ ( p sin 6 \ 8 = tan- ] ^ - -tan" 1 -* -^ -1. \p cos 6 \/ \p cos V p/ 402. On the Infinite Objects in an Extent. On each range of the extent there will be two objects at infinity, by the aid of which the intervene between every two other objects on that range is to be ascertained. We are now to study the distribution of these infinite objects over the extent. Taking any range and one of its infinite objects, 0, construct any other range in the same extent containing as an object. This second range will also have two infinite objects. Is to be one of them? Here we add another attribute to our, as yet, immature conception of the intervene. In Euclidian space we cannot arrive at infinity except we take an infinitely long journey. This is because the point at infinity on one straight line is also the point at infinity on any other straight line passing through it. Were this not the case, then a finite journey to infinity could be taken by travelling along the two sides of a triangle in preference to the direct route vid the third side. To develop the analogy between the conception of intervene and that of Euclidian distance, we therefore assume (in Axiom IV.) that an infinite object has an infinite intervene with every other object of the content. In consequence of this we have the general result, that If be an infinite object on one range, then it is an infinite object on every one of the ranges diverging from 0. The necessity for this assumption is made clear by the following con sideration : Suppose that were an infinite object on one range containing the object A, but were not an infinite object on another range OB, diverging also from 0; then, although the direct intervene OA is infinite, yet the intervenes from A to 5 and from B to would be both finite. The only escape is by the assumption we have just italicised. Otherwise infinity could be reached by two journeys, each of finite intervene. 403 J THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 443 Take any infinite object 0. Construct a series of ranges in the extent, each containing 0. Each of these ranges will have another infinite object, Oi, 2 , 3 , &c. The values x lt # 2 , x 3 , which define O lt 2 , 3 , &c., must fulfil some general condition, which we may express thus : Form a range through O l and 2 . There must be two infinite objects on this range, and of course all other objects thereon will be defined by a linear equation L = in x ly x 2 , x 3 . Every object satisfying the condition/^, x z , x 3 ) = is infinite, and there fore all the values of x 1} x 2 , x s common to the two equations L = and /(#!, a? 2 , # 3 ) = must denote infinite objects. But we have already seen that there are only two infinite objects on one range ; therefore there can be only two systems of values common to the two equations. In other words, f(%i, x 2 , x 3 ) must be an algebraical function of the second degree. There can be no infinite object except those so conditioned ; for, suppose that S were one, then any range through S would have two objects in common with /, and thus there would be three infinite objects on one range, which is contrary to Axiom in. Hence we deduce the following important result : All the infinite objects in an extent lie on a range of the second degree. We thus see that every range in an extent will have two objects in common with the infinite range of the second order. These are, of course, the two infinite objects on the range. 403. On the Periodic Term in the Complete Expression of the Intervene. We have found for the intervene the general expression H (log X - log p). We may, however, write instead of X, (cos 2n7r + i sin 27r) X, where n is any integer ; but this equals e 2inir \ ; hence, log X = Zimr + log X ; and, consequently, the intervene is indeterminate to the extent of any number of integral multiples of The expression just written is the intervene between any object and the same object, if we proceed round the entire circumference of the range. We may call it, in brief, the circuit of the range. 444 THE THEORY OF SCREWS. [403, The intervene between the objects X and X is iHir. Nor is this inconsistent with the fact that \ = zero denotes two coincident objects, as does also X= infinity. In each of these cases the coincident objects are at infinity, and the intervene between two objects which coalesce into one of the objects at infinity has an indeterminate value, and may thus, of course, be iH-rr, as well as anything else. 404. Intervenes on Different Ranges in a Content. Let us suppose any two ranges whatever. There are an infinite number of objects on one range, and an infinite number on the other. The well- known analogies of homographic systems on rays in space lead us to inquire whether the several objects on the two ranges can be correlated homo- graphically. Each object in either system is to correspond definitely with a single object in the other system. We determine an object on a range by its appropriate X. Let the corresponding object on the other range be defined by X . The necessary conditions of homography demand that for each X there shall be one X , and vice versa. Compliance with this is assured when X and X are related by an equation of the form PXX + Q\ + R\ + 8 = 0. Let \i, X 2 , X 3 , X 4 be any four values of X, and let X/> X,/, X*/, X/ be the cor responding four values of X , then, by substitution in the equation just written, and elimination of P, Q, R, S, it follows that Xi Xs Xj X 4 A! Xs A-2 X4 X^ \s Xj X 4 X 2 X 3 Xj X 4 We now introduce the following important definition : By the expression, anharmonic ratio of four objects on a range, is meant the anharmonic ratio of the four values of the numerical parameter by which the objects are indicated. We are thus enabled to enunciate the following theorem : When the objects on two ranges are ordered homographically, the an harmonic ratio of any four objects on one range equals the anharmonic ratio of their four correspondents on the other. Three pairs of correspondents can be chosen arbitrarily, and then the equation last given will indicate the relation between every other X and its corresponding X . Among the different homographic systems there is one of special im portance. It is that in which the intervene between any two objects in 404] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 445 one range equals that between their correspondents in the other. But this homography is only possible when a critical condition is fulfilled. In the first place, an infinite object on one range must have, as its correspondent, an infinite object on the other. For if X be an infinite object on one range, it has an infinite intervene with every other object on that range (Axiom iv.) ; therefore X , the correspondent of X, must have an infinite intervene with every other object on the second range. If, then, X and Y are the infinite objects on one range, and X and Y the infinite objects on the other, and if A and B be two arbitrary objects on the first range, and A and B their correspondents on the other; then, using the accustomed notation for anharmonic ratio, But, if H be the factor (p. 440) for the second range, which H is for the first, we have, since the intervenes are equal, H log (ABXY) = H log (A B X Y ) ; and, since the anharmonic ratios are equal, we obtain H=H . If, then, it be possible to order two homographic systems of objects, so that the intervene between any two is equal to that between their correspondents, we must have H and H equal ; and conversely, when H and H are equal, then equi-intervene homography is possible. We have therefore assumed Axiom v. ( 399) which we have now seen to be equivalent to the assumption that the metric constant H is to be the same for every range of the content. Nor is there anything in Axiom V. which constitutes it a merely gratuitous or fantastic assumption. Its propriety will be admitted when we reduce our generalized conceptions to Euclidian space. It is an obvious notion that any two straight lines in space can have their several points so correlated that the distance between a pair on one line is the same as that between their correspondents on the other. In fact, this merely amounts to the statement that a straight line marked in any way can be conveyed, marks and all, into a different situation, or that a foot-rule will not change the length of its inches because it is carried about in its owner s pocket. In a similar, but more general manner, we desire to have it possible, on any two ranges, to mark out systems of corresponding objects, such that the intervene between each pair of objects shall be equal to that between their correspondents. We have shown in this Article that such an arrangement is possible, when, and only when, the property v. is postulated. We may speak of such a pair of ranges as equally graduated. 446 THE THEORY OF SCREWS. [404- The conception of rigidity involves the notion that it shall be possible to displace a system of points such that the distance between every pair of points in their original position equals that between the same pair after the displacement. We desire to have corresponding notions in the present Theory, which will only be possible when we have taken such a special view of the nature of the intervene as is implied in Axiom v. 405. Another Investigation of the possibility of equally Gradu ated Ranges. The importance of the subject in the last Article is so great in the present Theory that I here give it from a different point of view. Taking the infinite objects on a range as the originating objects, we have on the first range for the intervene between the objects X and a, H (log X - log a) ; arid for the second range for the intervene between ju, and ft, we have Regarding a and (3 as fixed, and X and ^ as defining a pair of correlative objects, we get, as the relation between X and /n for equally graduated ranges, whence the relation between X and //, is thus given : IT H When this is the case, there are several values of X corresponding to one value of p., which may be thus found : Let m be any integer ; then, in the usual manner, x f p\*( H . . H \ - TS cos 2w ff if + * sm *m ~fr ^ ; a \I3J \ H ff J and therefore fl_ H or fl_ \ H ! 2H 406] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 447 or H 1 . 4P &c. &c. &c. We see that the correspondence between X and //. cannot be of the homo- graphic character, unless H = H . The necessity for this condition may be otherwise demonstrated by considering the subject in the following manner: The intervene between any two objects on one range is, of course, ambiguous, to the extent of any integral number of the circuits on that range. Let G and C be the circuits, and let 8 be an intervene between two objects on the second range. If we try to determine two objects, a and X, on the first range that shall have an intervene 8, we must also have another object X , such that its intervene from a is B + C . Similarly, there must be another object X" with the intervene S + 2C", &c. It is therefore impossible to have a single object at the intervene S + raC" from a, unless it happened that C=C , or that H = H . Thus, again, are we led to the conclusion that ranges cannot be equally graduated unless their circuits are the same. The circuits on every range in the content being now taken to be equal, we can assume for the circuit any value we please. There are great advan tages in so choosing our units that the circuit shall be TT ; but we have as its expression, whence we deduce 406. On the Infinite Objects in the Content. Certain objects in the content are infinite, and it is proposed to determine the conditions imposed on x lt x^, # 3 , x 4 when they indicate one of these. If an object be infinite, then every range through that object will have one other infinite object. Let these be 1} 2 , &c. These several objects will conform with the condition, Every infinite object in the content must satisfy this equation ; and, conversely, every object so circumstanced is infinite. 448 THE THEORY OF SCREWS. [406- Two linear equations in # 1} a? 2 , # 3 , x 4 determine a range, and the simul taneous solution of these equations with gives the infinite objects on that range but there can only be two and hence we have the following important theorem : The co-ordinates a; 1} # 2 , x 3 , x 4 of the infinite objects in a content satisfy an homogeneous equation of the second degree. We denote this equation by 407. The Departure. Let the ranges x^ x 2 , 0, be formed when the parameter x 1 -r x 2 has every possible value, then the entire group of ranges produced in this way is called a star. In ordinary geometry the most important function of a pair of rays in a pencil is that which expresses their inclination. We have now to create, for our generalized conceptions, a function of two ranges in a star which shall be homologous with the notion of ordinary angular magnitude. We shall call this function the Departure. Its form is to be determined by the properties that we wish it to possess. In the investigation of the departure between two ranges, we shall follow steps parallel to those which determined the intervene between two objects. If OP, OQ, OR be three rays in an ordinary plane diverging from 0, then In general the angle between two rays is not zero unless the rays are coin cident ; but this statement ceases to be true when the vertex of the pencil is at infinity. In this case, however, the angle between every pair of rays in the pencil is zero. Every plane pencil has two rays (i.e. those to the circular points at infinity), which make an infinite angle with every other ray. 408. Second Group of Axioms of the Content. We desire to construct a departure function which shall possess the following properties : (VI) If three ranges, P, Q, R, in a star, be ordered in ascending parameter, and if the departure between two ranges, for example, P and Q, be expressed by PQ, then PQ + QR = PR. 410] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 449 (VII) The departure between two ranges cannot be zero unless the ranges are coincident, or unless the departure between every pair of ranges in that star is also zero. (VIII) Of the ranges in a star, two (distinct or coincident) are at infinity, i.e. have each an infinite departure from all the remainder. (IX) An infinite range has an infinite departure, not only with every range in its star, but with every range in the extent. (X) If the several ranges in one star correspond one to one with the several ranges in another, and if the two infinite ranges in one star have as their correspondents the infinite ranges in the other; then the departure between any two ranges in one star is equal to that between the two corre sponding ranges in the other. 409. The Form of the Departure Function. The analogy of these several axioms to those which have guided us to the discovery of the intervene, shows that the investigation for the function of departure will be conducted precisely as that of the intervene has been ; accordingly, we need not repeat the several steps of the investigation, but enunciate the general result, as follows : Let ac 1} x. 2 , and y 1} y z be the co-ordinates of any two ranges in a star, and let \i, \2, and //, 1} /i 2 be the co-ordinates of the two infinite ranges in that star. Then the departure between (x l , # 2 ) and (y 1} y 2 ) is Aa - y a X 410. On the Arrangement of the Infinite Ranges. Every star in the extent will have two infinite ranges, and we have now to see how these several infinite ranges in the extent can be compendiously organized into a whole. To aid in this we have assumed Axiom ix., the effect of which is to render the following statement true. Let several objects on a range, 0, be the vertices of a corresponding number of stars. If be an infinite range in any one of the stars, then it is so in every one. Let a lt Oz, a s be any three ranges in an extent. Then every range in the same extent can be expressed by #!! + # 2 a 2 -f x 3 a 3 , where # lt x 2 , x 3 are the three co-ordinates of the range. It is required to determine the relation between x 1} # 2 , x 3 if this range be infinite. B. 29 450 THE THEORY OF SCREWS. An object L will be defined by an equation of the form, where L ly L 2 , L 3 are numerical, L 3 x 3 = 0, for any two sets of values, x lt x z , x 3 , which satisfy this equation, will deter mine a pair of ranges which have the required object in common. Let the relation between the co-ordinates of an infinite range be /Oi, a? 2 , s ) = 0; then the infinite ranges in the star, whose vertex is the object L, will be defined by co-ordinates obtained from the simultaneous solution of = 0, But there can only be two such ranges ; and, accordingly, the latter of these equations must be of the second degree. We hence deduce the following important result : The infinite ranges in an extent may be represented by the different groups of values of the co-ordinates x ly x z , x 3 which satisfy one homogeneous equation of the second degree. Remembering that the existence of zero intervene between every pair of objects on a range is a consequence of the coincidence of the two objects of infinite intervene on that range, we have the following result : The range through, two consecutive objects of infinite intervene is a range of zero intervene. And, similarly, we have the following : The object common to two consecutive ranges of infinite departure is the vertex of a star of zero departure. 411. Relations between Departure and Intervene. With reference to the theory of Departure, we thus see that there is a system of critical ranges, and a system of critical objects in each extent. Every critical range has an infinite departure from every other range. Every critical object is the vertex of a star of which the departure between every pair of ranges is zero. It will be remembered that in the theory of the intervene we were conducted to the knowledge that every extent contained a system of objects and ranges, critical with regard to the intervene. Each critical object had an infinite intervene with every other object in the extent. Each critical range possessed the property that the intervene between any two objects thereon is zero. There are, thus, objects and ranges critical with repect to the intervene. There are also objects and ranges critical with respect to the departure. But nothing that we have 412] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 451 hitherto assumed will entitle us to draw any inference as to the connexion, much less as to the actual identity, between the critical systems related to intervene, and those related to departure. We have already assumed five properties for the intervene, and five like properties for the departure. These are, in fact, the axioms by which alone the functions of intervene and of departure could be constructed. But another axiom of quite a distinct type has now to be introduced. There are objects of infinite intervene, and objects of zero departure. There are ranges of infinite departure, and ranges of zero intervene. A range generally contains two objects of infinite intervene, and two of zero departure. A star generally contains two ranges of infinite departure, and two ranges of zero intervene. On a range of zero intervene the two objects of infinite intervene coalesce, and their intervene from other objects on the range becomes indeterminate. In a star of zero departure the two ranges of infinite departure coalesce, and their departure from other ranges in the same star becomes indeterminate. We have thus the following state ment : On a range of zero intervene, the intervene between every pair of objects is zero, except where one particular object is involved, in which case the intervene is indeterminate. In a star of zero departure, the departure between every pair of ranges is zero, except where one particular range is involved, in which case the departure is indeterminate. The new axiom to be now introduced will be formed as the others have been by generalization from the conceptions of ordinary geometry. In that geometry we have two different aspects in which the phenomenon of paral lelism may be presented. Two non-coincident lines are parallel when the ansle between them is zero, or when their intersection is at an infinite o distance. Without entering into any statement about parallel lines, we may simply say, that when two different straight lines are inclined at the angle zero, their point of intersection is at infinity. Generalizing this proposition, we assume the following axiom or property, which we desire that our systems of measurement shall possess. 412. The Eleventh Axiom of the Content. This axiom, which is the first to bring together the notions of intervene and of departure, is thus stated : (xi) If two ranges in the same extent have zero departure, their common object will be at infinity, and conversely. The vertex of every star of zero departure will thus be at infinity, and hence we deduce the important result that all the objects of infinite inter- 292 452 THE THEORY OF SCREWS. [412, vene are also objects of zero departure, and conversely. Thus we see that the two systems of critical objects in the extent coalesce into a single system in consequence of the assumption in Axiom xi. Each consecutive pair of critical objects determine a range, which is a range of infinite departure as well as of zero intervene. The expression infinite objects will then denote objects which possess the double property of having, in general, an infinite intervene from other objects in the extent, and of being also the vertices of stars of zero departure. The expression infinite ranges will denote ranges which possess the double property of having, in general, an infinite departure with all other ranges, and which consist of objects, the intervene between any pair of which is, in general, zero. There is still one more point to be decided. The measurement of depar ture, like that of intervene, is expressed by the product of a numerical factor with the logarithm of an anharmonic ratio. This factor is H for the intervene. Let us call it H for the departure. What is to be the relation between H and H l Here the analogy of geometry is illusory; for, owing to the coincidence between the points of infinity on a straight line, H has to be made infinite in ordinary geometry, while H must be finite. But in the present more general theory H is finite, and we have found much convenience *t derived from making it equal to -= , for then the entire circuit of any range z ft is TT. We now stipulate that H is also to be ^ . The circuit of a star it will then be TT also. With this assumption the theory of the metrics of an extent admits of a remarkable development. Let x, y, z be any three objects. Let a, b. c denote the intervenes between y and z, z and x, x and y, respectively. Let the departure between the ranges from x to y and x to z be denoted by A, from y to z and y to # be denoted by B, and from z to x and z to y be denoted by C. Then, sin A _ sin B _ sin G sin a sin b sin c cos a = cos b cos c 4- sin b sin c cos A, cos b = cos c cos a + sin c sin a cos B, cos c = cos a cos b + sin a sin b cos C. Thus the formulae of spherical trigonometry are generally applicable through out the extent*. * I learned this astonishing theorem from Professor Heath s very interesting paper, Phil. Trans. Part n. 1884. 413] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 453 413. Representation of Objects by Points in Space. The several objects in a content are each completely specified when the four numbers, x lt x 2 , x 3 , # 4 , corresponding to each are known. It is only the ratios of these numbers that are significant. We may hence take them to be the four quadriplanar co-ordinates of a point in space. We are thus led to the construction of a system of one-to-one correspondence between the several points of an Euclidian space, and the several objects of a content. The following propositions are evident : One object in a content has for its correspondent one point in space, and one point in space corresponds to one object in the content. The several objects on a range correspond one to one with the several points on a straight line. The several objects in an extent correspond one to one with the several points in a plane. Since the objects at infinity are obtained by taking values of x l} x z , x 3 , x t , which satisfy a quadric equation, we find that The several objects at infinity in the content correspond with the several points of a quadric surface. This surface we shall call the infinite quadric. The following theorem in quadriplanar co-ordinates is the foundation of the metrics of the objects in the content by the points in space. If # 1; #2, s, \ and y 1} y 2 , y*, y* be the quadriplanar co-ordinates of two points P and Q respectively, and if 1} 2 , 3 , 4 be any other four points on the ray PQ whose co-ordinates are respectively i, #2+^42/2, %3 + \y 3 , #4 + ^42/4, then, we have the following identity Remembering the definition of the anharmonic ratio of four objects on a range ( 404), we obtain the following theorem : The anharmonic ratio of four objects on a range equals the anharmonic ratio of their four corresponding points on a straight line. 454 THE THEORY OF SCREWS. [413- We hence deduce the following important result, that The intervene between any two objects is proportional to the logarithm of the anharmonic ratio in which the straight line joining the corresponding points is divided by the infinite quadric. We similarly find that The departure between any two ranges in the same extent is proportional to the logarithms of the anharmonic ratio of the pencil formed by their two corresponding straight lines, and the two tangents in the same plane from their intersection to the infinite quadric. 414. Poles and Polars. The point # 1} x z , x 3 , x 4 has for its polar, with regard to the infinite quadric, the plane, dU dU dU dU A X 1 3 h X 2 -j h X. A -j h # 4 -7 = 0. dxi dx 2 dx 3 dxi Thus we see that an object corresponding to the point will have a polar extent corresponding to the polar of that point with regard to the infinite quadric. The following property of poles and polars follows almost imme diately. 7T The intervene from an object to any object in its polar extent is equal to -^ . We have hitherto spoken of the departure between a pair of ranges which have a common object: we now introduce the notion of the departure between a pair of extents by the following definition : The departure between a pair of extents is equal to the intervene between their poles. 415. On the Homographic Transformation of the Content. In our further study of the theory of the content we shall employ, instead of the objects themselves, their corresponding points in ordinary space. All the phenomena of the content can be completely investigated in this way. Objects, ranges, and extents, we are to replace by points, straight lines, and planes. Intervenes are to be measured, not, indeed, as distances, but as logarithms of certain anharmonic ratios obtained by ordinary distance measurement. Departures are to be measured, not, indeed, as angles, but as logarithms of anharmonic ratios of certain pencils obtained by ordinary angular measurement. I now suppose the several objects of a content to be ordered in two homographic systems, A and B. Each object, X, in the content, regarded as belonging to the system A, will have another object, Y, corresponding thereto in the system B. The correspondence is to be simply of the one-to- 416J THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 455 one type. Each object in one system has one correspondent in the other system. But if X be regarded as belonging to the system B, its correspondent in A will not be Y, but some other object, Y . To investigate this correspondence we shall represent the objects by their correlated points in space. We take x l} x 2 , x 3 , x 4 as the co-ordinates of a point corresponding to as, and y l} y 2 , y 3 , y 4 as the co-ordinates of the point corresponding to y. We are then to have an unique correspondence between as and y, and we proceed to study the conditions necessary if this be complied with. 416. Deduction of the Equations of Transformation. All the points in a plane L, taken as x points, must have as their correspondents the points also of a plane ; for, suppose that the corre spondents formed a surface of the nth degree, then three planes will have three surfaces of the nth degree as their correspondents, and all their n 3 intersections regarded as points in the second system will have but the single intersection of the three planes as their correspondent in the first system. But unless n = 1 this does not accord with the assumption that the correspondence is to be universally of the one-to-one type. Hence we see that to a plane of the first system must correspond a plane of the second system, and vice versa. Let the plane in the second system be AM + A. 2 y, + A 3 y, + A 4 y t = 0. If we seek its corresponding plane in the first system, we must substitute for y 1} 7/2, 2/s> 2/4 the corresponding functions of x ly x. 2> x 3 , # 4 . Now, unless these are homogeneous linear expressions, we shall not find that this remains a plane. Hence we see that the relations between X 1) x 2 ,x 3 ,x 4 and y\,y<i>y*,yi must be of the following type where (11), (12), &c., are constants : TA = (11K + (12) * 2 + (13) * 3 + (14) * 4 , 7/ 2 = (21) x, + (22) x z + (23) x s + (24) a> 4 , y , = (31 K + (32) x, + (33)^3 + (34) # 4 , /4 = (41 X + (42)^ 2 + (43)^ 3 + (44) x 4 . Such are the equations expressing the general homographic transformation of the objects of a content. From the general theory, however, we now proceed to specialize one particular kind of homographic transformation. It is suggested by the notion of a displacement in ordinary space. The displacement of a rigid system is only equivalent to a homographic trans formation of all its points, conducted under the condition that the distance between every pair of points shall remain unaltered (see p. 2). In our extended conceptions we now study the possible homographic transformations of a 456 THE THEORY OF SCREWS. [416, content, conducted subject to the condition that the intervene between every pair of objects shall equal that between their correspondents. 417. On the Character of a Homographic Transformation which Conserves Intervene. In all investigations of this nature the behaviour of the infinite objects is especially instructive. In the present case it is easily shown that every object infinite before the transformation must be infinite afterwards when moved to . For, let X be any object which is not infinite before the transformation, nor afterwards, when it becomes X . Then, by hypothesis, the intervene OX is equal to O X ; but OX is infinite, therefore O X must be also infinite, so that either or X is infinite ; but, by hypothesis, X is finite, therefore must be infinite, so that in a homographic transformation which conserves intervene, each object infinite before the transformation remains infinite afterwards. It follows that in the space representation each point, representing an infinite object, and therefore lying on the infinite quadric U=Q must, after transformation, be moved to a position which will also lie on the infinite quadric. Hence we obtain the following important result : In the space representation of a homographic transformation which con serves intervene, the infinite quadric U=Q is merely displaced on itself. A homographic transformation of the points in space will not, in general, permit any quadric to remain unchanged. A certain specialization of the constants will be necessary. They must, in fact, satisfy a single condition, for which we shall presently find the expression. Let cc lt oc 2 , x 3 , # 4 be the quadriplanar co-ordinates of a point, and let us transform these to a new tetrahedron of which the vertices shall have as their co-ordinates with respect to the original tetrahedron 1 . rr /y> "I ) *2 ) X 3 > " 4 > v" <r" r" <r" *Tl i a 2 ^3 > "^l > If then X l} X 2 , X 3 , X 4 be the four co-ordinates of the point referred to the new tetrahedron + Xi X* + x^"X s + 417] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 457 For these equations must be linear and if X z , X 3 , X^ are all zero then #i> 2, 3, #4 become a;/, # 2 , x 3 , x as they ought to do, and similarly for the others, whence we get X,= vCo OC*> OCn Otif? vu- (KA oc* We may write this result thus Let us now suppose that the vertices of this new tetrahedron are the double points of a homography defined by the equations 2h = (11) x, + (12) x, + (13) x, + (14) x 4t y, = (21) x, + (22) x 2 + (23) 8 + (24) a? 4 , y 3 = (31) ^ + (32) ^ 2 + (33) x t + (34) # 4 , y 4 = (41) ^ + (42) a; 2 + (43) x a + (44) ar 4 . We have to solve the biquadratic (11) -p (12) (13) (14) =0. (21) (22) -p (23) (24) (31) (32) (33) -p (34) (41) (42) (43) (44) -p Let the roots be p l} p^, p 3 , p t . Then we have Pl x{ = (11) / + (12) / + (13) a?, + (14) ar 4 , p a a7 2 = (21) a?/ + (22) # 2 + (23) x, + (24) a?/, /9^ 3 = (31 ) a?/ + (32) a? s + (33) ar, + (34) ar/, P!^ = (41) a;/ + (42) a?/ + (43) <c, + (44) a-/, with similar equations for a;/ , a;/", a^"", a;/ , &c. 458 THE THEORY OF SCREWS. [417 We thus get Hpipipsp+Xi = or H Pl X^ 11 12 13 14 21 22 23 24 31 32 33 34 41 42 43 44 2/1 y* 2/3 2/4 X-i Xn Xv XA But these determinants are the co-ordinates of y referred to the new tetrahedron, and omitting needless factors We thus obtain the following theorem. Let x ly x 2 , x 3 , #4 be the co-ordinates of a point with respect to any arbitrary tetrahedron of reference. Let T/J, y. 2 , t/ 3 , y be the co-ordinates of the corresponding point in a homographic system defined by the equations y l = (11) x l + (12) x z + (13) x 3 + (14) x, y z = (21) as, + (22) x, + (23) x, + (24) * 4 , y z = (31) x, + (32) x 2 + (33) x, + (34) x,, 7/ 4 = (41) x, + (42) x, + (43) x, + (44) x.. If we transform the tetrahedron of reference to the four double points of the homography, and if X 1} X 2 , X 3 , X^ be the co-ordinates of any point with regard to this new tetrahedron then the co-ordinates of its homographic correspondent are =0. where p 1} p 2 , p 3 , p 4 are the four roots of the equation, (11) -p (12) (13) (14) (21) (22) -p (23) (24) (31) (32) (33) -p (34) (41) (42) (43) (44) -p 417] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 459 In general there are four, but only four double points, i.e. points which remain unaltered by the transformation. If however two of the roots of the biquadratic equation be equal, then every point on the ray connecting the two corresponding double points possesses the property of a double point. For if p 1 = p 2 , then YI : Y 2 :: X 1 : X 2 , and hence the point whose co-ordinates are X,, Z a , 0, 0, being transformed into F 1; F 2 , 0, remains unchanged. Let us now suppose that a certain quadric surface is to remain unaltered by the homographic transformation. At this point it seems necessary to choose the particular character of the quadric surface in the further developments to which we now proceed. The theory of any non-Euclidian geometry will of course depend on whether the surface adopted as the infinite be an ellipsoid or a double sheeted hyperboloid with no real generators or a single sheeted hyperboloid with real generators. We shall suppose the infinite, in the present theory, to be a single sheeted hyperboloid. The homographic transformation which we shall consider will transform any generator of the surface into another generator of the same system, for if it transformed the generator into one of the other system, then the two rays would intersect, which is a special case that shall not be here further considered. Let three rays R 1} R 2 , R s be generators of the first system on the hyperboloid. After the transformation these rays will be transferred to three other positions jR/, R 2 , R 3 belonging to the same system. Let S 1} 83 be two rays of the second system. Then the intersection of R lt RI, R 2 , R 2 &c., with Si give two systems of homographic points. The two double points of these systems on Si give two points through which two rays of the first system must pass both before and after the transformation. Two similar points can also be found on S 2 . These two pairs of Double points on Si and $ 2 will fix a pair of generators of the first system which are unaltered by the transformation. 460 THE THEORY OF SCREWS. [417, In like manner we find two rays of the second system which are unaltered. The four intersections of these rays must be the four double points of the system. We can also prove in another way that in the homographic transforma tion which preserves intervene, the four double points must, in general, lie on the fundamental quadric. For, suppose that one of the double points P was not on the quadric. Draw the tangent cone from P. The conic of contact will remain unaltered by the transformation. Therefore two points 1 and 0. 2 on that conic will be unaltered (p. 2). So will R the intersection of the tangents to the conic at Oj and 2 . The four double points will therefore be P, R, O l and 2 . But PR cuts the quadric in two other points which cannot change. Hence PR will consist entirely of double points, and therefore the discri minant of the equation in p would have to vanish, which does not generally happen. Of course, even in this case, there are still four double points on the quadric, i.e. O ly 0. 2 and the two points in which PR cuts the quadric. We may therefore generally assume that two pairs of opposite edges of the tetrahedron of double points are generators of the fundamental quadric, the latter must accordingly have for its equation with the essential condition Every point on any quadric of this family will remain upon that quadric notwithstanding the transformation. Nor need we feel surprised, when in the attempt to arrange a homographic transformation which shall leave a single quadric unaltered, it appeared that if this was accomplished, then each member of a family of quadrics would be in the same predicament. Here again the resort to ordinary geometry makes this clear. In the displacement of a rigid system in ordinary space one ray remains unchanged, and so does every circular cylinder of which this ray is the axis. Thus we see that there is a whole family of cylinders which remain unchanged ; and if U be one of these cylinders, and V another, then all the cylinders of the type U+XV are unaltered, the plane at infinity being of course merely an extreme member of the series. More generally these cylinders may be regarded as a special case of a system of cones with a common vertex ; and more generally still we may say that a family of quadrics remains unchanged. 418] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 461 Reverting, then, to a space of which the several points correspond to the objects of a content, we find, that for every homographic transformation which corresponds to a displacement in ordinary geometry a singly infinite family of quadrics is to remain unchanged, and the infinite quadric itself is to form one member of this family. Let us now suppose a range in the content submitted to this description of homographic transformation. Let P, Q be two objects on the range, and let X, Y be the two infinite objects thereon. This range will be transformed to a new position, and the objects will now be P , Q , X , Y . Since infinite objects must remain infinite, it follows that X and Y must be infinite, as well as X and Y. Also, since homographic transformation does not alter anharmonic ratio, we have (PQXY) = (P Q X Y }; whence, by Axiom v., we see that the intervene from P to Q equals the intervene from P to Q ; in other words, that all intervenes remain unchanged by this homographic transformation. Every homographic transformation which possesses these properties must satisfy a special condition in the coefficients. This may be found from the determinantal equation for p (p. 458), for then the following symmetric function of the four roots p lt p. 2 , p :i , p 4 must vanish : (Pi Pz ~ Pap*) (pip 3 - p 2 pi) (pip* - p 2 p s ). 418. The Geometrical Meaning of this Symmetric Function. We may write the family of quadrics thus : JVXs+ : xr t x-.a, All these quadrics have two common generators of each kind : , = 0, ^ 3 = fZ 1 = 0, X, = and and For the rays ^ = 0, X a = Q, and X 1 = 0, Z 4 = 0, are both contained in the plane X 1; and therefore intersect, and, accordingly, belong to the opposed system of generators. The geometrical meaning of the equation PiPz Psp* can be also shown. The tetrahedron formed by the intersection of the two pairs of generators just referred to remains unaltered by the transformation. Any point on the edge, X l = 0, X 3 = 0, of which the co-ordinates are 0, *, 0, Z 4 , 462 THE THEORY OF SCREWS. will be transformed to 0, p 2 X z , 0, p 4 X 4 . The question may be illustrated by Figure 45. [418 Fig. 45. Let 1, 2, 3, 4 be the four corners of the tetrahedron. Let the transfor mation convey P to P and Q to Q . As P varies along the ray, so will P vary, and the two will describe homographic systems, of which 2 and 4 are the double points. In a similar way, Q and Q will trace out homographic systems on the ray 1 3. We shall write the points on 2 4, in the order, 2, 4, P, P . Through 2, the generator of the surface 2 3 can be drawn (1 2 is not a generator), and through 4 the generator 4 1 can be drawn (4 3 is not a generator) ; thus we have, for the corresponding order on 1 3. 3, 1, Q, Q . Points. Points. Co-ordinates. 20100 40001 P X 2 X P o P*X 2 p,X The anharmonic ratio of the first set is that of 0, ,, second Co-ordinates. 3 1 1 i Q I/ ar; Q i piXS p 3 Z 3 Z/ V 3 ^3-^-3 , 0, y-,, -yvJ Aj ^ A! but since then the anharmonic ratios are equal. 418] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 463 The theorem can otherwise be shown by drawing Figure 46. Fig. 46. 1 4 and 3 2 are to be generators of the infinite quadric. This will show that 4 (and not 2) is the correspondent to 1, and that 2 (and not 4) is the correspondent to 3, and thus the statement of anharmonic equality, (1 QQ 3) = (4 PP 2), becomes perfectly definite. 1 2 and 3 4 are, of course, not generators; they are two conjugate polars of the infinite quadric. We can now see the reason of the anharmonic equality. Let PQ be a generator of the infinite quadric, as is clearly possible, for 1, 3 and 2, 4 are both generators of the opposite system. Then, since a generator of the infinite quadric must remain thereon after the displacement, it will follow that P Q , to which PQ is displaced, must also be a generator ; and thus we have four generators, 4 1, PQ, P Q , 2 3, on a hyperboloid of one system intersecting the two generators of another, and by the well-known property of the surface, We also see why the infinite quadric is only one of a family which remains unaltered. For, if PQ be a generator of any quadric through the tetrahedron, 1, 2, 3, 4; then, since P and Q are conveyed to P and Q , and since the anharmonic equality holds, it follows that P Q will also be a generator of the quadric, i.e. a generator of the quadric will remain thereon after the displacement. It is a remarkable fact that, when the linear transformation is given, the infinite quadric is not definitely settled. We have seen how, in the first place, the linear transformation must fulfil a fundamental condition; but when that condition is obeyed, then a whole family of quadrics present themselves, any one of which is equally eligible for the infinite. 464 THE THEORY OF SCREWS. [419, 419. On the Intervene through which each Object is Conveyed. Given an object, X 1} X 2 , X s , X 4 , find the intervene through which it is conveyed by the transformation, when is the infinite quadric. In this equation substitute for X l} X l + 6Y 1> &c.; and, remembering that Y l = p^X-L, &c., we have, (X, + pjx,) (X, or 6- (p 1 p 2 X l X 2 + \p 3 p 4 X 3 X 4 ) + 6 (p^X^X^ + p 2 X l X 2 + Xp 3 X 3 X 4 + \p 4 X s X 4 ) + X,X 2 + \X 3 X 4 = 0. We simplify this by introducing Pi 02 = PS Pl, and writing \X 3 X t -=- XX Z = (f>, whence the equation becomes ffifrpi (1 + 0) + 6 [ Pl + p. 2 + </> ( Pa + p,)] + (1 + </>) = ; hence if 8 be the intervene, we have, cos 8 = 2 V/hp. 1 + < or, if we restore its value to <f>, cos g _ 1 ^1^2 (pi + p 2 H_(p 3 + p 4 V^L/o \j . . . ^^ ^^ H Pt + P2 = Pi + P*, then cosS = ^il: i.e. all objects are translated through equal intervenes. This is the case which we shall subsequently consider under the title of the vector, as this remarkable conception of Clifford s is called. In this case, as and also, p l p 2 = p 3 p^ } we must have PI = p s , and p 2 = p 4 , or Pi = p t , and p a = p a . In either case the equation for p will become a perfect square. 420] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 465 In general let X 1 = 0, then cos 8 = p3 tjgi whence we find that all objects in the extent Z a are displaced through equal intervenes. This intervene can be readily determined for whence or 8 = The intervene through which every object on X 2 is conveyed has the same value. We could have also proved otherwise that objects on X 1 and X^ are all displaced through equal intervenes, for the locus of objects so displaced is a quadric of the form XtXt+XX^Tj-t), and, of course, for a special value of the distance this quadric becomes simply ^JT.-O. If X l = 0, and X 3 = 0, then cos 8 becomes indeterminate ; but this is as it should be, because all objects on X l and X 3 are at infinity. 420. The Orthogonal Transformation*. The formulae y, = (21) Xl + (22) x, + (23) x 3 + (24) x ti 7/3 = (31) x, + (32) # 2 + (33) x, + (34) a? 4 , 2/4 = (41 ) x, + (42) x z + (43) ^ + (44) x 4 , denote the general type of transformation. The transformation is said to be orthogonal if when x lt &c., are solved in terms of y lt &c. we obtain as follows: _ X, = (11) yi + (21) y, + (31) y, + (41) y 4 , ^ 2 = (12) y, + (22) y a + (32) y, + (42) y 4> ^3 = (13) yi + (23) y a + (33) y s + (43) y 4 , ** = (14) y x + (24) y a + (34) y, + (44) y 4 . This is employed in Professor Heath s memoir, cited on p. 452. B " 30 466 THE THEORY OF SCREWS. [420- From the first formulae the equation for p is, as before, 417 (11) -p (12) (13) (14) (21) (22) -p (23) (24) (31) (32) (33) -p (34) (41) (42) (43) (44) -p From the second, the equation for p must be =0. <">-$ (12) (13) (14) (21) (22) -1 (23) (24) (31) (32) (33) -1 (34) (41) (42) (43) (44)- 1 P = 0; but we may interchange rows and columns in a determinant so that the last may be written, = 0; (11)- (12) (13) (14) p (21) (22) -1 (23) (24) P (31) (32) (33) - 1 (34) P (41) (42) (43) (44)- 1 P whence we see that the equation for p must be unaltered, if for p we sub stitute - . It must therefore be a reciprocal equation of the type p 4 + 4Ap* + GBp 2 + 4<Ap +1=0, and the roots are of the form , 1 ]_. and as this transformation fulfils the fundamental condition ( 417). 421. Quadrics unaltered by the Orthogonal Transformation. The special facilities of the orthogonal transformation in the present subject arise from the circumstance that it is the nature of this transforma tion to leave unaltered a certain family of quadrics. This is as we have 422] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 467 seen the necessary characteristic of the homographic transformation which preserves intervene. The infinite quadric which the transformation fails to derange can be written at once, for we have x* + x? + # 3 2 + # 4 2 = yi 2 + / 2 2 + y? + y? = 0. It is also easily seen that the expression is unchanged by the orthogonal transformation. We thus have the following quadric, which remains unaltered : + (24K] ^ or, writing it otherwise, If this be denoted by U, and x? + x + x + # 4 2 by H, then, more generally, U AH is unaltered by the transformation. We now investigate the intervene 6, through which every object on V-MI = Q is conveyed by the transformation. If we substitute x 1 + \y 1 &c. for x l &c. in the infinite quadric we have and, accordingly, the intervene 6, through which an object is conveyed by the orthogonal transformation is defined by the equation cos ^ = n ; hence the locus of objects moved through the intervene is simply u - n cos e = o. 422. Proof that U and H have Four Common Generators. The equation in p has four roots of the type These correspond to the vertices of the tetrahedron (fig. 47). Symmetry shows that the conjugate polars as distinguished from the generators will be the ray joining the vertices corresponding to and p , * 302 468 THE THEORY OF SCREWS. [422- and that joining p Fig. 47. Let a 1} 2 , 3 , 4 and /3 1} /9 2 , /3 3) /3 4 be the co-ordinates of the corners at p and p". If we substitute a : + X,^, a 2 4- X/3 2 . . . &c., for x 1} x 2 &c. in fl = 0, 2\ (a, J3, + a 2 /3 2 + a 3 /3 3 + 4 /3 4 ) = 0. Let us make the same substitution in U, we have, in general, = (11) (a, + X&) + (12) (a, + \/3 2 ) + (13) (a, + X&) + (14) (a 4 + X/3 4 ) = p otj + Xp"/3i ; whence, remembering that + \p"/3 2 ) + &c., and as a and /S are both on O, we have, U=\(p+ p") ( ai /3 x + 2 /9 2 + a 3 yS 3 + a 4/ S 4 ) ; but since the line joining p and p" is a generator of O, the last factor must vanish, and the line is therefore also a generator of U. It is thus proved that U has four generators in common with fl. 423. Verification of the Invariance of Intervene. As an exercise in the use of the orthogonal system of co-ordinates, we may note the following proposition : Let #!, x. 2 , x 3 , # 4 , and #/, a? 2 , x 3 , #/, be two objects which are conveyed by the transformation to y lt y 2 , y a , 7/ 4 , and y/, y a , y 3 , y 4 , respectively, it is desired to show that the intervene between the two original points is equal to that between the transformed. The expressions for the cosine of the intervene are (x* + x? + x? + xff (x^ + x? + x^ + 424] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 469 and the similar one with y and y , instead of x and x . The denominators are clearly equal, and we have only to notice that as an immediate consequence of the formula? connecting the orthogonal transformation. 424. Application of the Theory of Emanants. We can demonstrate the same proposition in another manner by revert ing to the general case. Let U=0 be a function of x 1} x 2 , x 3 , # 4 . Let #/, x 2 , x 3 , x 4 be a system of variables cogredient with x lt x. 2 , x 3 , # 4 , and let us substitute in U the ex pressions x l + kxi, # 2 + kx 2 , &c., for x lt x 2 . The value of U then becomes where . _ , d , d , d , d LA = Xi j -J- X.2 i ~ ~\~ Xn ~^j -p X z If U be changed into V, a function of y, by the formulae of transformation, we have, of course, U-Yt but since y l is a linear function of x l} &c., i.e. y 1 = (11) x, + (12) x 2 + (13) x 3 + (14) x., it follows that if we change x^ into x 1 + kx 1 , &c., we simply change y^ into y l + ky l . Hence we deduce, that if U be transformed by writing x 1 + kx 1 , &c., for x, then V will be similarly transformed by writing y^ + %/ for y, and, of course, as the original U and V were equal, so will the transformed U and V be equal. It further follows that as k is arbitrary, the several coefficients will also be equal, and thus we have =y l , l dy, Hence the intervene between two objects before displacement remains unaltered by that operation ; for ,dU * dx +&C rx _ (Mil and by what we have just proved, this expression will remain unaltered if y be interchanged with x. 470 THE THEORY OF SCREWS. 425. The Vector in Orthogonal Co-ordinates. Since, in general, cos 6 = pr , 12> we have for the vector ( 419) the following conditions : (11) = (22) = (33) = (44), and also, [425 and the similar equations. In fact, U can only differ from fl by a constant factor. The orthogonal equations require the following conditions + (11) . (12) - (12) . (11) + (13) . (23) + (14) . (24) = 0, + (11) . (13) - (12) . (23) - (13) . (11) + (14) . (34) = 0, + (11) . (14) - (12) . (24) - (13) . (34) - (14) . (11) = 0, + (12) . (13) + (11) . (23) - (23) . (11) + (24) . (34) = 0, + (12) . (14) + (11) . (24) - (23) . (34) - (24) . (11) = 0, + (13) . (14) + (23) . (24) + (11) . (34) - (11) . (34) = 0, h(14) 2 =l, h(24) 2 =l, + (13) 2 + (23) 2 + (11)- + (34) 2 = 1, + (14) 2 + (24) 2 + (34) 2 + (II) 2 = 1. We now introduce the notation : (!!) = ; (12) = 0; (13) = 7; (14) = 8, and the equations give us + 7 (23)+ B (24) = (i), -(23) + a (34) = -(24)- 7 (34) = + 7 +(24)(34) = + a 2 + p 2 + /3 2 + a 2 + 7 2 + (23) -(23)(34) = +(23)(24) = + 7 2 + 8- = 1 + (23) 2 + (24) 2 =l + a 2 + (34) 2 =l a 2 -l) (ii), , (iii), . (iv), (vi), (vii). 425] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 471 From (iv), From (v), by multiplication, but, from (vi), whence, we deduce, = -(24) (34). = + (23) (34); = -(23)(24)(34) 2 ; 7 S = -(23)(24); ft 2 - (34) 2 . The significance of the double sign in the value of ft will be afterwards apparent ; for the present we take From (ii) B = + (23), From (iii) 7 = - (24), while the group (vii) will be satisfied if The scheme of orthogonal transformation for the Right Vector (for so we designate the case of ft = + (34),) is as follows : + a + ft +7 + B -/3 + a. + B - 7 -7 - B + a +/3 - B +7 -ft + a If we append the condition then we have completely defined the Right Vector. We now take the other alternative, = -(34); then, from (ii), B = (23), then, from (iii), 7 = + (24). We thus have for the Left Vector, the form, + a + ft +7 + B ft + a. 8 +7 -7 +8 + a -ft - B -7 +/3 + a 472 THE THEORY OF SCREWS. [425- with, as before, the condition, a 2 + /3 2 + r + S 2 = 1- If 6 be the intervene through which the vector displaces an object then it is easily shown that cos 6 = c/. 426. Parallel Vectors. The several objects of a content are displaced by the same vector along ranges which are said to be parallel. Taking the space representation, 413, Clifford showed that all right vectors, which are parallel, intersect two generators of one system on the infinite quadric, while all left vectors, which are parallel, intersect two generators of the other system. A generator intersected by two rays from a right vector may be defined by the points whose coordinates are + < -/3, -7, -B, + & +a , -8, +7, while a generator intersected by two rays from a left vector will be defined by + <*o, - fio, ~7o> -&o, To prove the theorem, it is only necessary to show that these four points are coplanar, for then the two generators intersect, i.e. are of opposite systems. We have, then, only to show that the following determinant vanishes : 7 8 a a 70 This will be most readily shown by squaring, for with an obvious notation it then reduces to the simple form O a ] [ /?] whence we see that the original determinant is simply [ ] [/8o ] aa fl - Q - 427] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 473 which expanded, becomes (a + ftj3 + 770 + 88 V (a po py 760 + 070 = a 2 2 + # 2 /3 2 -I- a 2 /3 2 + /2 /3 2 - 7 2 7 2 - S 2 S 2 - &y<? - 7 2 S 2 = a 2 (a 2 + /3 2 ) + ^ (a /2 + /3 2 ) - 7 2 (7 2 + S 2 ) - 3 2 (7 2 + S 2 ) = (a 2 -I- /3 2 ) (a,, 2 + /3 2 ) - (7 2 + S 2 ) (7o 2 + 8 2 ) 5 but, a 2 +/3 2 + 7 2 + 8 2 = 0; whence this expression is ( a /2 + /3 2 )(a 2 +/3 2 + 7 2 +S 2 ) = 0. On the supposition that the vectors were homonymous, i.e. both right or both left, the corresponding determinant would have been a yS 7 8 n i ^ p a 6 7 o - @o 7o &o /3o a/ -^o 7o Squaring, we get, as before, but now, whence the determinant reduces to [aV] 2 +[/3 ?, a value very different from that in the former case. 427. The Composition of Vectors. Let an object x be conveyed to y by the operation of a vector, and let the object y be then conveyed to z by the operation of a second vector, which we shall first suppose to be homonymous (i.e. both right or both left) with the preceding. Then we have, from the first, supposed right yi = + #! + /&r 2 + 73.3 + 8x 4 , 2/4 = - Bx l 474 THE THEORY OF SCREWS. [427, and, from the second vector, *i = + ay, + ffy* + yy a + 8 y 4 , Substituting for y n y 2 , .Vs. y*, we obtain the following values for z lt z%, z s , z 4 . The right vector, a, ft, 7, 8, followed by the right vector, a , /? , 7 , 8 z a = + aa - pp - 77 - 65 ^ + + a/3 + /3a + 75 - 7 x 2 + ay - fid + ya +dp X 3 + + ad + Py - yp + da x 4 , z%= -ap -pa -y8 + dy x l + + aa - pp - yy - 85 a; 2 + a5 + 7 - 7(3 + Sa x 3 + - ay + pS -ya - = -a7 + /35 --ya -8/3 a; 1 + - aS - Py + 7/3 - da x. 2 + aa - pp - yy - 88 x 3 + + a/3 + /3a + 78 - dy x 4 , 5a x 1 + +ay - pd + ya +dp x 2 + - a/3 - /3a - 76 + 67 x 3 + + aa - /3/3 - yy - 55 x 4 . The right vector, a, ft , 7 , 8 , followed by the right vector, a, ft, 7, 8 != + aa - /3/3 - yy - 55 ^ + + a/3 + /3a - 78 + 87 rc 2 + + a> + /35 + 701 - S/S x 3 + + ad - fiy + 7/3 + 8a x 4 , z. 2 = - a/3 - /3a + 78 - 87 x l + + aa - /3/3 - 77 - 55 x 2 + + aS - fiy + y{? + 8a x 3 + - ay ~ /35 - ya + 5/3 x t , ~ 7* + 8/3 ^i + - a5 + fty - 7/8 - 5a J 2 + + aa - /3/3 - 77 - 55 x 3 + + a/3 + /3a - 78 + 87 x 4 , yp -8a x 1 + + ay + /36 + ya - 5/3 x. 2 + - a/i - /3a + 75 - 57 x 3 + + aa - /3/3 - 77 - 55 x . We thus learn the important truth, that when two or more homonymous vectors are compounded, the order of their application must be carefully specified. For example, if the object x be first transposed by the vector a and then by a , it attains a position different from that it would have gained if first transposed by a! and then by a. We see, however, that in either case two homonymous vectors compound into a vector homonymous with the two components. We now study two heteronymous vectors, i.e. one right and one left. The right vector, a, ft, 7, 8, followed by the left vector, a , ft , 7 , 8 z l = +aa -pp -yy -88 x 1 + + a/3 + pa + yd - dy x 2 + + ay - p8 + ya + 5/3 x 3 + +aS + py - 7/8 + 5a z 4 , + aa - /3/3 + 77 + 55 x 2 + -a8 -py - yp + da x 3 + +ay - pd -ya - dp = -a7 -/35 -7a + S/3 a; 1 + + aS - pS - yp - da x 2 + + aa + pp - yy + 55 x 3 + - a/3 + /3a - 78 - 8y x 4 , Z 4 - - a5 + 7 - 7/3 - Sa x l + - ay - pd + ya - dp x 2 + + a/3 - pa - 78 - 87 x 3 + + aa + pp 1 + yy - 55 x 4 . The left vector, a , ft , 7 , 8 , followed by the right vector, a, ft, 7, 8 ! = + aa - pp - 77 - 85 x 1 + -f a/3 7 + /3a + 78 - 87 x 2 + + 07 - /3S + ya + 8p x s + + aS + Py - yp + da x t , 2 = - ap - pa + yd - dy X 1 + + aa - pp + yy 4 58 X 2 + - ad - Py - yp + da X 3 + + ay - pd - ya - dp X 4 , Z 3= -ay -pd -ya + dp x l + + ad - py - yp - da X 2 + + aa + /3/3 - 77 + 55 X 3 + - a/3 + )3a - 76 - z 4 = - ad + Py - yp - da X-L+ - ay - pd + ya - dp x 2 + +ap - pa -yd - dy x 3 + + aa + pp + yy - 88 z 4 . 428] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 475 We thus learn the remarkable fact, that if a right (left) vector be followed by a left (right) vector, the effect produced is the same as if the order of the two vectors had been interchanged. This is not true for two right vectors or two left vectors. The theorems at which we have arrived may be thus generally enunciated : In the composition of vectors the order of two heteronymous vectors does not affect the result, but that of two homonymous vectors does affect the result. In the composition of two homonymous vectors the result is also an homony mous vector. In the composition of two heteronymous vectors the result is not a vector at all. The theorems just established constitute the first of the fundamental principles relating to the Theory of Screws in non-Euclidian Space referred to in 396. Their importance is such that it may be desirable to give a geometrical investigation. 428. Geometrical proof that two Homonymous Vectors com pound into one Homonymous Vector. Left vectors cannot disturb any right generators of the infinite quad- ric. Take two such generators, AB and A H (Fig. 48). Let AA , BB , CC be three left generators which the first vector conveys to A^Ai, -BjjB/, eft-!, and the second vector further conveys to A 2 A 2 , B,B 2 , C 2 C 2 . Let X and Y be the double points of the two homo- graphic systems defined by A, B, G and A 2 , B 2 , (7 2 . Then we have and As anharmonic ratios cannot be altered by any rigid displacement, it follows that X and Y must each occupy the same position after the second vector which they had before the first, similarly, X and Y will remain unchanged, and as the two rays, AB and A B are divided homo- lg 8 476 THE THEORY OF SCREWS. [428- graphically, it follows that XX and YY are both generators. We there fore find that after the two vectors all the right generators remain as before, and so do also two left generators, i.e. the result of the two vectors could have been attained by a single vector homonyrnous therewith. 429. Geometrical proof of the Law of Permutability of Hetero- nymous Vectors. Let AB and A B be a pair of right generators (fig. 49), and CD and C U a pair of left generators. Let the right vector convey P to Q, and Fig. 49. then let the left vector carry Q to the final position P . We shall now show that P would have been equally reached if P had gone first to R, so that intervene PR = QP , and that then R was conveyed by the vector, RB B, through a distance equal to PQ. Draw through P the transversal PRCC . Take R, so that but, because this relation holds, PQ, RP , CD, G D must all lie on the same hyperboloid. Therefore RP must intersect AL and AM, and therefore, also, (PQAA ) = (RP BB }. Hence, finally, we have for the intervenes PQ = RP and PR = QP . 430. Determination of the Two Heteronymous Vectors equi valent to any given Motor. If a right vector, a, ft, <y, B, be followed by a left vector, a, ft , 7 , 8 , then 430] THE THEORY OF SCREWS IN NON-EUCLIDIAN SPACE. 477 the result obtained is a displacement of the most general type called a motor. We now prove Clifford s great theorem that a right vector and a left vector can be determined so as to form any motor, i.e. to accomplish any required homographic transformation that conserves intervene. For, if we identify the several coefficients at the foot of p. 474 with those of 420, we obtain equations of the type (11)= ace - ftp - 77 - 88 , (21) = -a/9 -/9a + 78 -87 , (31) = - ay - 8 - ya + 8/3 , (41) = - 08 + /3y - 7/3 - 8a . These can be simply reduced to a linear form ; for multiply the first by a , and the second, third, and fourth by ft, 7 , 8 , respectively, and add, we obtain for a 2 + /3 /2 + 7 2 -f 8 2 =1. In a similar manner we obtain a number of analogous equations, which are here all brought together for convenience (11) a! - (21) ft - (31) 7 - (41) 8 = a, - (21) a - (11) ft + (41) 7 - (31) 8 = & - (31) a - (41) ft - (11) 7 + (21) 8 = 7, - (41) a + (31) ft - (21) 7 - (11) 8 = 8. + (22) a! + (12) ft - (42) 7 + (32) 8 = a, + (12) a - (22) ft - (32) 7 - (42) 8 - ft, - (32) a! - (42) ft - (12) 7 + (22) 8 = 8. + (33) a + (43) ft + (13) 7 - (23) 8 = a, + (43) a + (33) ft - (23)7 - (13)8 = & - (13) a - (23) ft - (33) 7 - (43) 8 = 7, + (23) a! + (13) ft - (43) 7 + (33) 8 = 8. + (44) a - (34) /3 + (24) 7 + (14)8 = a, + (34) a! + (44) ft + ( 14) 7 - (24) 8 = & - (24) a - (14) ft + (44) 7 - (34) 8 = 7, + (14) a! - (24) ft - (34) 7 - (44) 8 = 8. These will enable a, ft, 7, 8 and a , ft, 7 , 8 to be uniquely determined. 478 THE THEORY OF SCREWS. [431, 431. The Pitch of a Motor. Any small displacement of a rigid system in the content can be produced by a rotation (see 417) a about one line followed by a rotation ft about its conjugate polar with respect to the infinite quadric, the amplitudes of both rotations being small quantities. The two movements taken together constitute the motor. It will be necessary to set forth the conception in the theory of the motor, which is the homologue of the conception of pitch in the Theory of Screws in ordinary space. The pitch can most conveniently be expressed by the function 2ct/3 P ~a? + 0*- If either a. or ft vanish, then the pitch becomes zero. The motor then degenerates to a pure rotation about one or other of the two conjugate polars. This, of course, agrees with the ordinary conception of the pitch, which is zero whenever the general screw motion of the rigid body degrades to a pure ro