US2830431A - Strand twisting machine - Google Patents

Description

April 15, 1958 N. E. KLEIN STRAIID TWISTING MACHINE;

6 Sheets-Sheet 1 Filed March 22. 1954 NOR MA N E. KLEIN INVENTOR.

ATTORN EY April 1958 N. E. KLEIN 2,830,431

STRAND TWISTING MACHINE Filed March 22. 1954 6 Sheets-Sheet 2 FIG.'2'

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NORMAN E. KLEIN Q INVENTOR.

. BY 4/; flit/1% ATTORNEY Ap 15, 1958 N. E. KLEIN 2,830,431

STRAND TWISTING MACHINE Filed larch 22. 1954 6 s'ne ts-sneet 3 a I a Q Q 4&3: Q m i a a a I L J\ \Q R a Q \3 a v 3 M i a 3 a #1 a Q N \sn 4 N w u w a a Q In N N M x I l v 2 s i b u. Q

2 LL N NORMANE.KLEIN J; INVENTOR. N

ATTORNEY A ril 15, 1958 r N. E. KLEIN 2,330,431

STRAND TWISTING MACHINE Filed March 22. 1954 6 Sheets$heet 4 82 77 1 I 30 l I Hill I |1| I I I 30 1 u;

I i x /37 26 NORMAN E.KLE|N If! /.r/ /3 INVENTOR.

FIGQII- BY Wfiifw ATTORNEY April 15, 1958 N. E. KLEIN STRAND TWISTING MACHINE 6 Sheets-Sheet 6 Filed March 22, 1954 NORMAN E. KLEIN INVENTOR. BY W,

ATTORNEY age.

United States Patent STRAND TWISTING MACHINE Norman E. Klein, Pendleton, S. C., assignor to Deering Milliken Research Corporation, Pendleton, S. C., a corpor'ation'of Delaware Application March 22, 1954, semi No. 417,619 44 Claims. (Cl. 57-5852 The invention relates to a strand twisting machine and more particularly to a machine of the type that imparts two turns of twist in the strand for each revolution of .the twisting spindle. The machine of my invention is further characterized in that it is capable of plying two or more strands together during the twisting operation to form a multiple twisted strand or cord.

Twisting machines of this general class may be classified as either of the inflow or the outflow type. In the latter type the yarn. or strand in which twist is to be inserted is carried in the form of a supply package by a spindle support and is fed therefrom outwardly through a balloon and finally wound in twisted form onto a take-up package externally of the balloon generatrix. This form of machine has many limitations principally because the supply package platform will not readily accommodate a plurality of supply packages of s'uflicient size to make a combined twisting and plying action practical.

The inflow type of machine is particularly suited for combined twisting and plying operations in that a large number of strands from individual packages carried by a creel may be drawn in combined form axially into the balloon and again fed axially into .the interior thereof and wound on suitable take-up means to form a pack- It is with particular attention to improvements in this form of twisting machine that the present invention is directed.

More specifically, although not particularly limited thereto, the twisting machine of my invention is adapted" to produce a twisted, multiple strand or'cord suitable for use in the manufacture of pneumatic rubber .tire casings or as reinforcing elements in the V type rubber belts or backing cords in the manufacture of textile floor coverings and the like. The twister by virtue of the combination of a number of improved elements is capable of handling flexible strands of a variety of materials such as cotton, rayon, nylon, or other synthetic materials or combinations of any of these materials to form a compact closely wound package of size and shape that is acceptable in the trade.

The improved twisting machine of my invention is also adapted to produce twisted cord of a wide range of sizes, namely, from 2,000 to 50,000 denier, and wind such cord to form a firm compact headless package of weight considerably heavier than heretofore produced and that will not slough off at the ends and generally will withstand rougher handling than similarly shaped packages made on prior art machines.

Briefly, the twisting machine with which the improved results are obtained makes provision for combining a plurality of strands or ends of yarn as may be drawn from individual packages carried by a creel and feeding these combined strands axially into .the tubular shaft of the twister spindle. The-spindle shaft is mounted for rotation at high speed and carries a flyer in combination with a yarn storagedevice adjacent the shaft. An orifice through the wall of the tubular spindle shaft that terminates on the yarn receiving surface of the yarn storage 2,830,431 Patented Apr. 15, 1958 device provides an opening through which the combined strands may emerge. The combined strands make contact with the surface of the yarn storage device in wraparound fashion and then proceed alongthe surface of the flyer and when .the spindle shaft is rotated form a balloon about a support floatingly carried by the end of the spindle shaft. This baloon extends between the flyer and an apex guide mounted on the floating frame support and positioned on the extended axis of the spindle.

The combined strands or cord, now having a double twist inserted therein-for each revolution of the spindle,

- are drawn inwardly from the apex guide by a capstan arrangement carried by the end of the floating frame and driven at constant speed from the rotating spindle. The floating frame also carries a take-up package support in the; form of a rotatable mandrel or sleeve mounted with its axis of, rotation parallel to the axis of rotation of the spindle and adapted to receive a winding core.

The twisted strands or cord are advanced from the capstan through a precision wind traverse mechanism onto the winding core. The traverse mechanism is driven in timed relation with respect to the winding core and ar-' ranged to produce a headless package having a close precision wind. The winding core is driven from 'the spindle by means producing a constant operational torque so that, as the winding builds up, the tension in the twisted strands'or cord is gradually decreased. The close precision wind together with the controlled winding tension produces a much higher density and better shaped package than those produced on prior art machines.

The machine of my invention also presents many structural improvements such as the arrangement of the elements driven by the spindle and mounted on the floating: frame in such manner that the center of gravity of the frame and supported parts is lower than the axis of rotation of the spindle with respect to theframe so that the frame is automatically stabilized against rotation. The apex guide structure which provides means for leading the cord into the capstan advancing means is hingedly carried on the floating support frame thereby. providing ready access to the take-up mechanism and permits doffing a completed package and the replacement of an empty winding core without disassembling any part of the machine or having to rethread the machine.

Other structural improvements relate to the coacting arrangement of parts permitting the incorporation of yarn or cord storage control to-provide balloon shape control as set forth in my co-pending application Serial Number 220,665, filed April 12, 1951, for Textile Plying or Twisting Device, which control prior to the invention of said application was unobtainable on infeed two-for-one spindle systems.

The details of my winding machine whereby the abovementioned advantages are achieved will now be described in connection with the accompanying drawings in which:

Figure 1 is a perspective view of the twisting machine of my invention with certain parts thereof broken away to bring other parts into view;

Figure 2 is a fragmentary end view of the twisting machine showing parts of the cord guide structure in the dofling position;

Figure 3 is a fragmentary view of the drive mechanism for the cord take-up package;

Figure 4 is a fragmentary longitudinal sectional view through the spindle and floating support frame of the twisting machine;

Figure 5 is a fragmentary sectional view of the flyer, arrangement taken along the line V-V of Figure 4',

- Figure 6 is a fragmentary view partially schematic showing the driving arrangement for the cord traverse mechanism;

Figure 7 is a fragmentary sectional view taken longitudinally through the take-up package driving roll;

Figure 8 is a fragmentary view, partially schematic,

illustrating the cord compensator arrangement used in,

connection with the cord traverse mechanism;

Figure 9 is an enlarged fragmentary view of the mounting arrangement of one of the gears in the traverse mechanism;

Figure 10 is an enlarged fragmentary view showing details of the mechanism for adjusting the rate of change in driving torque to the driving roll for the cord package;

bearings 16 and 17 for receiving a tubular spindle shaft 18 having, as more particularly shown in Figure 4, an a! bore 19 extending inwardly from the lefthand end ereof.

A motor 11 mounted on the frame 10 is coupled in driving relation through a pair of V belts 13 to a pair of split pulleys 15 adjustably mounted on the shaft 18 between the bearings 16 and 17. The motor 11 is preferably of a constant speed type and the desired spindle shaft speed is obtained by adjusting the spacing of the split pulleys 15 as is'well known in the art.

Disposed intermediate the ends ofthe spindle 18 is a flyer 20 carried by a flyer hub 21. The fiyer hub 21, as more clearly shown in Figures 4 and 5, has a two-step wrap-around cord storage device in which the first step presents a cylindrical surface 22 that is eccentric with respect to the axis of the spindle and a second cylindrical surface 23 axially displaced from the first surface but having a point of mergence with the first surface and a radius of curvature greater than the first surface but disposed in eccentric relation with the axis of the spindle. The manner in which the wrap-around surfaces of the cord storage device serves to control the tension in the cord balloon is fully covered in my co-pending applica- Figure 4 and which is disposed within the cup-shaped flyer 20, has a sleeve 26 mounted thereon by means of low- friction bearings 28 and 29. The sleeve 26 has a flange 30 thereon disposed intermediate its 'ends to which is secured an annular plate 32 which forms the inner end support for a support frame generally indicated at 34. The floating support frame 34 also includes an outer plate 36 generally of C shape as more clearly illustrated in Figure 2. Plates 32' and 36 are held in fixed spaced relation with respect to each other by two channelshaped connecting members 38 and 39.

An ofi-set bracket 40 suitably mounted on the inner plate 32 serves as a fixed mount for an axle 42 extending in a direction generally parallel to the axis of rotation of the spindle 18. Axle 42 carries a pair of low friction bearings 44 and 45 on which a cylindrical rotatable mandrel or sleeve 46 is mounted. Sleeve 46 also carries an integral gear 48 disposed at one end thereof for a purpose which will be more fully described hereinafter. A collar 49 is disposed adjacent the gear portion 48 on the sleeve 46 and coacts with a flanged annular cap member 50 that is screw threaded to the opposite end of the sleeve for retaining a winding core 52 on the sleeve. It will thus be seen that the cap may be readily removed to permit' the placing of a winding core on the sleeve and replaced with its flange engaging the end of the winding core to. prevent it turning with respect to the sleeve during a winding operation as will be more fully explained hereinafter.

In order to hold the sleeve 46 against rotation during the removal and replacement of the flange cap 50, a suitable locking device is provided in the form of a bell crank 54 mounted for rocking movement about a pin 56 carried by a U-shaped bracket 58 mounted on the support plate 32. The horizontal arm portion of bell crank.

54 as viewed in Figure 4 is provided with a plurality of tapered downwardly projecting teeth 60. A coil tension spring 62 connected between the upper end of the bell crank 54 and the support plate 32 normally maintains the teeth out of registration with the teeth of the gear 48 integrally formed on the sleeve 46. A handle 64 projecting from the upper end of bell crank 54 provides a ready means for rocking the bell crank 54 about its pivot pin 56 in a clockwise direction as viewed in Figure 4 to bring the teeth 60 into engagement with the teeth of the gear 48 in order to lock the gear and consequently the sleeve 46 against rotation.

The sleeve 46 is adapted to be driven by a friction driving roll 66 making surface contact with the package as the cord is wound on the winding core 52. The driving roll 66 as more clearly shown in Figures 3 and 4 is journaled adjacent the ends of a'pair of swing arms 68 and 69. The swing arms 68 and 69 are preferably joined and rigidly maintained in spaced relation by a tubular yoke 70 which in turn is mounted for limited rotative movement about a shaft 72 rotatively journaled at its ends in the back plate-32 and the front plate 36. A plurality of springs 74, as more clearly shown in Figures 3 and 4, encircle the yoke 70 and have one end each in tension producing engagement with a tie rod 76 carried by the arms 68 and 69 and their respective other ends engaging a tie bar 78 connecting back plate 32 and front plate 36. It will thus be seen that the springs 74 acting in concert will urge the arms 68 and 69 together with the drive roll 66 in a counterclockwise direction as shown in Figure 3 toward the winding core 52.

During the dotting operation it is desirable to latch the driving roll 66 in a position out of engagement with the cord package. For this purpose as shown in Figure 2, I provide a spring biased latch bolt 75 mounted on the end plate 36 and having a rounded end piercing the plate and extending a short distance therebeyond in the path of movement of swing arm 69. Swing arm 69 is provided with a bored cavity 77 in alignment with the rounded end of the latch bolt 75 and into which the bolt is caused to extend when the swing arm is brought into registration therewith. Thus by withdrawing latch bolt 75 from its normal position to one that will permit clearance of the swing arm 69, the latter arm may be swung in a counterclockwise direction, as viewed in Figure 2, until the bolt and recess 77 are in alignment. By releasing the bolt it will enter the recess and hold the swing arm 69 in latched position and the driving roll 66 out of contact with the package. After-package removal and the replacement of a new winding core on the sleeve 46, the bolt 75 can be withdrawn to release the arm 69 and allow the driving roll 66 to again assume a driving position with respect to the formation of another precision wound package.

The driving roll 66 is driven through a gear train from the spindle 18. This gear train starts with a pinion 80 formed on the end of the spindle 18 which meshes with a speed reducing stud gear 82 mounted on a stub shaft 79 with bearings to the back plate 32. The outer end of this stub shaft carries a twist gear 81 which is meshed with a second reducing gear 84 fixedly mounted on the shaft 72. Twist gear 81 is preferably interchange able with gears of different size in order to obtain, within predetermined limits, the amount of twist desired. The specific structural arrangement whereby the desired gear change may be expeditiously made will be more fully described hereinafter. The shaft 72 also carries a smaller gear 85 adjacent the gear 84 and is in mesh with a pinion gear idler 86 in turn meshing with a second idler pinion 88, both of which idler gears are carried by the swinging arm 68. The idler pinion 88 makes final engagement with the gear 90 coupled to the drive roll 66 through a clutch mechanism as more clearly illustrated in Figure 7. It will thus be seen that, since the gear 84 rotates about the same axis as the swing arms 68 and 69, the final drive gear 90 is always in driving engagement through the idler gears 86 and 88 for all positions of the driving roll 66.

Although it is not essential, I prefer to rotate the spindle shaft 18 and its pinion in a counterclockwise direction as viewed in Figure 3. Since pinion 80 drives reducing gear 84 through the idler gear combination 82, 81, the reducing gear and shaft 72 on which it is fixedly mounted will also be driven in a counterclockwise direction. The'reactive force tending to resist rotation of shaft 72 operates through the gear 85 in mesh with the gear train 86, 88 and 90 carried by the swing arm 68. In consequence the swing arm 68 will have applied thereto a rotative force in the counterclockwise direction so as to assist the springs 74 in urging the driving roll 66 toward the package being wound on the core 52.

As specifically illustrated 'in Figures 1 and 2, the end plate 36 of the floating frame 34 has hingedly mounted thereon an apex guide array generally indicated at 92. This guide array includes a trumpet guide 94 rotatably mounted on one enri of a tubular support 96, the other end of which is notched as shown at 98 to provide a bifurcated portion. The bifurcated portion is adapted to receive a guide pulley 100 which may be joumaled on a pin 102 extending diametrically across the bifurcated portion. The tubular support 96 extends through and is supported by a collar 104 which is carried on the ends of three support arms 106 diverging with respect to the collar and the tubular support 96. The other ends 'of the support arms 106 are rigidly secured in equally spaced circumferential relation to a support ring 108. A pair of hinge arms 110 rigidlymounted to the support ring 108 coact with a hinge plate 112 which in turn may be bolted or otherwise secured to the end plate 36 thereby providing a hinged mount for the apex guide array. In order to provide suitable latch means for holding the apex guide array 92 in operative position, two of the arms 106 may be provided with flat latch plates 114 welded or otherwise secured in abutting relation to the ends of the arms as shown. In operative position the latch plates 114 are adapted to lie flat against the end plate 36 and are held in contact with the end plate 36 by means of coacting rotatable cam latch members 116 suitably mounted in end plate 36 and having handles 118 for actuating the cam latch portion.

As will be described more fully later the apex guide array 92 provides means for directing the cord being twisted from the cord balloon axially inwardly toward the cord takeup package. The twisted cord delivered through the apex guide trumpet 94 and tubular support 96 is adapted to be advanced at a uniform rate through the medium of a double capstan drive generally indicated at 120. The capstan drive 120 includes a capstan 122 mounted together with a gear 123 on the outer end of shaft 72. A second capstan 124 is mounted for rotation on a stub shaft 126 secured to end plate 36. The capstan 124 has a spur gear 128 either formed integrally therewith or otherwise suitably secured thereto and is driven through an idler gear 130 carried by a stub shaft 132 which idler gear in turn meshes with the gear 123 mounted on and driven by the shaft 72. It will be noted that stub shaft 126 is slightly skewed out of parallelism with respect to shaft 72 as more clearly shown in Figures 2 and 4 to provide a slight misalignment of the respective capstan surfaces thereby causing a separation of the several reaches of the cord passing between and about the capstans 122 and 124. In order to accommodate the misalignment of the gear 128 and the idlergear 130 the teeth on gear 128 are cut at an angle with respect to its axis of rotation so that it may properly mesh with the idler gear 130. Since the capstan drive 120 is driven directly from the shaft 72 which in turn is driven through gearing from the spindle 18 the cord will be advanced by the capstan drive at a substantially constant rate.

From the foregoing description it is apparent that for a given spindle speed the degree of twist imparted to the cord will depend upon the rate at which the cord is advanced by the capstan drive. Thus the speed ratio of the gear train between the spindle l8 and the capstan drive shaft 72 will determine the amount of twist being imparted to the cord. Changes in twist can thus be achieved by making appropriate changes in the gear ratio. In practice I have found it desirable to obtain these changes by the interchange of only one gear of the train and prefer gear 81 as the change gear on account of its ing a laterally extending flange 133 thereabout in the form of a support plate. The housing 131 projects through an arcuate slot 135 in the back plate 32 and is adjustably held in the desired position by means of two elongated brackets 137 of L-shaped cross section which respectively engage a marginal portion of the flange 133 on opposite sides of the housing. Suitable fastening means, such as cap screws 139, passing through the brackets 137 and making threaded engagement with the back plate 32 serve to clamp the flange into contact with the back plate.

The center of curvature of the arcuate slot 135 coincides with the axis of rotation-of the driving pinion 80 on the spindle 18 so that the housing 131 carrying shaft 79 may be swung about such axis, within the limits determined by the length of the slot 135, while maintaining the pinion 80 in driving engagement with reducing gear 82. The swing path thus provided for the shaft 79, however, is in a direction that permits positioning of the shaft at different distances from the gear 84. Consequently, twist gears 81 of different diameter may be, interchangeably mounted on the shaft 79 and brought into meshing engagement with gear 84 by adjusting the position of the housing 131 in which the shaft 79 is journaled. Once the proper adjustment for a given size gear 81 is made, the housing is securely held in position by tightening the clamping screws 139.

The twisted cord that is advanced by the capstan drive 120 is then directed by suitable guide means to be hereinafter more specifically described to a traverse mechanism generally indicated at 134 in Figures 1 and 2. The traverse mechanism 134 serves the purpose of producing a lay of cord on the winding form 52 of predetermined pattern as will be more fully described hereinafter. For a clearer understanding of the components and operations of the traverse mechanism 134 reference will be had to Figure 6. The traverse mechanism comprises a traverse arm 136, having a guide eye 138 at its upper end and through which the cord to be wound passes. The lower end of the traverse arm 136 terminates in an enlarged bifurcated portion 140 having a transverse bore 142 therethrough. A guide rod 144 having its ends secured to the end plates 32 and 36, respectively, passes through the bore 142 and provides a means for slidingly supporting the traverse arm. The traverse arm in addition to being slidably mounted on the guide rod 144 may Disposed between the two legs of the bifurcated portion and slidably mounted upon the guide rod 144 is an actuating block 146 having a boss 148 projecting from one side thereof which boss is provided with a bore 150. Within the bore 150 is retained the cylindrical shank 152 of a crescent shaped cam follower 15.4. The.

cam follower 154 is arranged to ride in a continuous reversing cam groove 156 provided in a barrel cam 158. Suitable means are provided for rotatably mounting the barrel cam 158 as for example shaft ends 160 and 162 which are respectively journaled in end plates 32 and 36. It will thus be seen that as cam 158 is rotated causing the cam follower 154 to be driven throughout the length of the cam groove 156 it causes the actuating block 146 and the traverse arm 136 to sweep back and forth along the guide rod 144.

The cam 158 is arranged to be driven in timed relation with respect to the winding core 52 and to this end gear 48 disposedon the end of mandrel 46 is utilized to drive a suitable gear train disposed between the mandrel and the cam. This gear train includes an idler gear, 164 journaled on a stub shaft 166 mounted on the back plate 32 which is driven by the gear 48 and in turn drives a gainer gear assembly generally indicated at 168. The

gainer gear assembly 168 is in driving engagement with an idler gear 170 rotatively mounted on a stub shaft 172 and in turnmeshes with the gear 174 mounted on the shaft end 160 which shaft is fixed t0 the cam 158.

The gainer gear assembly is interposed in this drive to provide a small continuous rate of advance of the cam 158 and consequently the traverse arm 136 so as to obtain an accurate processional displacement of adjacent turns of the cord. This is of particular importance in the building of a precision wind headless package wherein high density is desired. In this particular instance I prefer to use a rapid traverse producing approximately apparent that the degree of advance desired can be obtained by a selection of the proper gear ratio of the planetary gear system used to advance the ring gear 186. By

making appropriate gear changes the relative rotation two turns per length of package or what is known in the trade as a .two wind. Thus unless the rate of traverse is increased by a given increment during each excursion of the traverse arm 136, the cord will hill or pile up. The size of the increment will, of course, depend upon the size of cord and the closeness of the wind desired. If a close wind of maximum density is desired, the small increase in the rateof traverse will be just enough to constantly advance the traverse arm by an amount slightly greater than the diameter of the cord being wound on the winding core.

More specifically, the gainer gear assembly 168 comprises a main gear 176 journaled by means of low friction bearings 178 and 180 onto a stub shaft 182 se- 7 cured to the back plate 32. The gear 176 has an offset of the ring gear 186 with respect to the gear 176 may be obtained. In practice I have found it desirable to make changes in the gear ratio by using gears 190 of different diameter. To avoid making changes in the diameter of the mating idler gear 192, the latter gear is mounted on a swing arm 191 as more clearlyshown in Figure 9. Arm 191 is mounted for swinging movement about stub shaft 199 rotatably carrying the gears 194 and 195. The stub shaft 201 carrying gears 192 and 193 is mounted on the arm 191 intermediate its ends at a position such that pinion 193 will always be in mesh with gear 194 for all positions of the arm. Thus, arm 191 may be swung either toward or away from shaft 182 so as to accommodate the meshing engagement of gear 192 with pinions 190 of different size. Once the swing arm 191 is adjusted for a given size pinion 190, it may be held in clamped position against the cover 188 by a clamping plate 203 releasably secured to the cover by screws 205.

It is conceivable that in addition to varying the relative rate of change between these gears by merely changing the gear ratio it is also possible to change the direction of rotation of the final gear in the planetary system, namely pinion 202, so as to retard the rate of movement of the ring gear 186 with respect to the gear 176.

It should also be understood that the mounting of the planetary gears 190, 192,193, 194, 195, 196, 197 and 198 on stub shafts that are greatly extended, as shown in Figure 6, is merely for the purpose of illustration. In actual practice I mount these gears on stub shafts of much shorter hub section 184 which serves as a hearing about which a composite internal, external gear 186 is adapted to rotate. A circular cover plate 188 is disposed adjacent the hub section 184 and in addition to providing a closure for the ring gear 186 also serves as a support for numerous stub shafts on which a plurality of gears are mounted. These gears are arranged in a planetary gear extends inwardly beyond the cover plate 188.and carries a driving pinion 202 which engages the internal teeth of the ring gear 186. It will thus be seen that, as the main gear 176 is rotated carrying cover plate 188 therealong, all gears carried by the cover plate will be rotated in planetary fashion about the pinion 190 which is held stationary. The planetary gears, however, being in mesh with the stationary pinion 190 will have imparted therelength so that the entire planetary gear train will occupy a position closely adjacent the cover plate 188.

From the foregoing description the advantages of disposing the rotational axis of the winding core parallel with the rotational axis of the spindle are apparent. This arrangement permits the formation of a larger package for a given balloon diameter and also facilitates dofling a completed package and the replacement of an empty winding core. However, in order to wind a precision package within the limited space of the balloon generatrix, special consideration must be given to the cord guide means leading from the capstan drive 120 to the traverse mechanism 134. Movement of the traverse arm 136 back and forth lengthwise of the package constitutes a movement that is alternately toward and away from the'capstan drive 120 which advances the cord at a constant speed. Consequently the tension in the cord will oppose traverse movement away from the capstan and aid such movement in a direction toward the capstan. In fact, the length of the cord path would be changed at each traverse movement. These difficulties are overcome through the use of a compensator actuated by the traverse arm 136 to provide a cord path of constant length between the capstan and traverse arm for all positions of the traverse arm; the effect being equivalent to the control yarn guide-focal point systems wherein the distance from the package surface to said guide was infinite.

This compensator comprises a flexible belt or cord of suitable material 204 having an attachment lug 206 at one ent thereof which is secured to the enlarged portion 140 of the traverse arm 136. The belt 204 is threaded about two idler pulleys 208 and 210 fixedly mounted on-the back end plate 32 and then proceeds to pass about a movable pulley 212 and has its other end fastened to an eyelet 214 anchored to the-end plate 32.

The movablepulley 212 is mounted in a clevis 216 attachedto one end of a relatively stilf spring 218 the other end of which is secured to a clevis 220. The clevis 220 carries a pulley 222 similar to pulley 212. The twisted cord is directed from the capstan drive 120 to an idler pulley 230 mounted in convenient manner on the front plate 36 from whence it proceeds in loop form about the movable pulley 222 and then in succession about two idler pulleys 232 and 234 each mounted on the front plate 36 and finally about an idler pulley 236 mounted on the enlarged portion 140 of the traverse arm 136. From the idler pulley 236 the twisted cord is directed through the guide eye 138 in the traverse arm 136 as more clearly shown in Figure 6. Again with reference to Figure 8 the symmetry of the path that the twisted cord takes in traveling from the idler pulley 230 to the idler pulley 236 with respect to the path defined by the belt 204 will be noted. This particular arrangement providesa path of constant length for the twisted cord to the traverse arm 136 irrespective of the position of the traverse arm. Thus as the traverse arm oscillates back and forth, a corresponding movement is imparted to the pulley 222 but in a'direction opposite to that of the traverse arm so as to compensate for any change in position of the traverse arm 136 with respect to the linear distance from the capstan drive 120.

The coupling spring 218 between the pulleys 212 and 222 serves the purpose of compensating for any irregularities in the wind occurring at the end of traverse stroke.

I have discovered that in the formation of-a headless package of the type here under consideration that it is desirable to vary the tension in the cord as the winding progresses. More specifically, it is more desirable to start the wind with a relatively high tension and gradually decrease the tension as the package grows in size. duction in tension as the package builds up represents some loss in density but has the advantage of producing a better shaped package. A high level tension throughout the wind will cause considerable deformation in package shape particularly at the ends making it difiicult to wind and to handle after it is wound. The deformation may even be so severe that it interferes with the winding mechanism making it impossible to wind a normal size package.

The desired result is accomplished by the provision of a variable torque coupling in the drive between the spindle and the driving roll 66. This variable torque coupling is more clearly shown in Figure 7. The driving roll 66 preferably comprises a metal shaft 238 covered with a resilient material 240, such as rubber or the like, so as to provide the necessary frictional contact with the surface of the package to drive the same but without causing injury by abrasion to the cord. The shaft 238 is preferably mounted in low friction bearings 242 and 244, respectively, carried by swing arms 68 and 69. The left hand end of shaft 238 terminates in a flange portion 246 so as to provide a plane circular surface of considerable area which serves as a clutch face and is adapted to coact with one of the plane sides of the gear 90. The latter gear is mounted for rotation on a low friction bearing 248 carried by a pressure control rod 250, in this instance extending through a coaxial bore 252 within the shaft 238. A closure cap member 254 is provided for the outer side of the bearing 244 and is secured to the swing arm 69 and has an axial passage 256 therethrough which is in alignment with the bore 252, so as to permit the pressure control rod 250 to extend therethrough. The closure cap member 254 is also provided with a multiple tooth spiral cam portion 258 which is adapted to coact with a movable spiral cam member. 260 having cam teeth of complementary form with respect to the stationary cam portion. A compression spring 262 encircling the right-hand end of the rod 250 This reand disposed between cammember 260 and a nut 264 on the end of the rod 250 hold the two cam surfaces in engagement and provide pressure between the contacting faces of gear and the flange portion 246 of the shaft 238. The movable cam member 260 is provided with a radially extending actuating lever 266, the end of which is pivotally connected to one end of a connecting link 268. The other end of the connecting link 268, as shown more clearly in Figure 10, is secured to a pin 270 mounted on an elongated plate 267 slideable in a recessed guide 269 disposed in the outer end plate 36. Suitable means such as a clamping bar 271 extending across the plate 267 'and fastened to the end plate 36 by screws 273 permit adjustment of the pivot position.

With particular reference to Figures 2 and 7 it will be noted that pin 270 which pivotally secures one end of the connecting link 268 to the end plate 36 is disposed laterally from the axis of rotation of the shaft 72 about which the swing arms 68 and 69 are adapted to turn a distance of substantially equal to the length of the lever arm 266. The actuating link 268 also approximates in length the radius of the are described by the center of the friction roll 66 as it is moved downwardly with increasing package diameter. During a downward movement of the drive roll, the cam portion 258 rotates in a counterclockwise direction with respect to the cam portion260 as viewed in Figure 2 thereby causing the coacting cam portions to be moved axially toward each other which increases the effective length of compression spring 262 and consequently decreases the coupling pressure between the side face of gear 90 and the flange 264. The driving torque applied to the roll 66 will therefore be continuously decreased as the package increases in size causing the tension of the wind to decrease accordingly. It will, of course, be understood that the relative meshing position of the cam portions 258 and 260 can be adjusted by loosening the screws 273 and sliding the pin 270 to the desired pivot position but this adjustment need only be made at the start of an initial winding operation. It will also be understood that the rate at which the tension in spring 262 is caused to change with movement of the driving roll 66 from one position to another can be varied by adjusting the position of the pivot pin 270 with respect to the shaft 72. Movement of the pin 270 toward the shaft 72 will decrease the rate of change in tension whereas moving the pin away from the shaft will increase the rate of change. If the torque delivered by this slip clutch arrangement is not sufiicient at the outset, the pressure between the gear 90 and the flange 246 may be increased by taking up the nut 264. Should the torque be too great, it may be decreased by backing ofi the nut 264.

The operation of my twisting and plying machine in connection with the production of a closely wound cord package is as follows:

In threading the machine preparatory to plying, twisting and winding a plurality of yarn ends Y as more particularly shown in Figure 1 are withdrawn fromindividual cones or packages P-carried by a pin type magazine creel generally indicated at 272. The separate yarn ends Y are drawn through respective eyelet guides 274 that are mounted on an upright support 276. As the individual yarn ends Y emerge from the eyelet guides 274, each end is directed through a suitable tension device 278 which may be of the twin disc type and carried by the upright support 276. From the individual tension devices 278 the yarn ends Y are directed through a roller guide 280 from which theyproceed in generally parallel relation to a multiple eyelet separator guide 282 mounted on a bracket 284 carried by the platform 12 of the twister frame. From the eyelet guide 282' the yarn ends are directed to a compression trumpet 286 which also for convenience may be mounted on the bracket 284.

Entry of the combinedyarn ends Y into the spindle a threading tool is again used to bring the combinedends through the trumpet guide 94, through the bore in support tube 96 and about theguide pulley 100 carried at the inner end. of the support tube. From the pulley 100 the combined yarn ends are drawn forward, passed through a pigtail guide 288 carried by the outsideend plate 36 and are passed aboutthe capstan guide 120. I prefer to make five or six passes about the double capstan to insure a positivevdrive of the cord through the machine. From the capstan drive 120 the group of yarn ends are successively threaded about the guide pulleys 230, 222, 232, 234 and 236 which'pulleys define the compensator path. From pulley 236 the yarn ends are threaded through the eyelet guide 138 in the traverse arm 136 and then onto a winding core 52 which has been placed upon the. sleeve '46. The combined yarn ends are then secured about the winding core 52 in such manner that, when the sleeve and core are driven, normal cord takeup will occur. The swing arms 68 and 69 which have previously been latched to dofling position to the outer end plate 36 are now released so as to allow the drive roll 66 to swing upwardly into contact with the winding core 52.

The electric driving motor ll'for the spindle may be placed into operation and controlled by means of either of two start-stop switches 290 and 292 located at different positions as more clearly shown in Figure. 1. By actuating either switch 290 or 292 the spindle is placed into operation and continues to operate at a constant speed covering the combined yarn ends Y to balloon about the frame 34 and be drawn through the machine by the capstan 120. In order to protect the operator from the rotating cord in the balloon a cagelike guard 294 supported by a pair of brackets 296 mounted on the frame is provided as more clearly shown in Figures 1 and 2. For convenience of access to the machine the forward part of the guard 294, which is generally of conical shape, is separable and movable from the cylindrical part. The conical portion is preferably hinged as shown at 298 to the cylindrical portion thereby permitting it to be swung into and out of operative position.

As heretofore explained the floating frame 34 is stabilized'against rotation by virtue of mounting the various elements carried thereby in such manner to produce a center of gravity which is below the axis of rotation of the spindle 18. If for some reason the frame 34 should be placed into rotation during the operation of the machine, I have provided a safety device in the form of a lever 300 mounted for pivotal movement about a pin 302 secured to the upper connecting frame member 38. Duringnormal operation of the spindle at which time the frame 34 remains stable the lever 300 is adapted to be folded substantially flush with the upper surface of the channel member 38. However, shouldthe frame 34 be thrown into rotation, both centrifugal force and gravity acting upon the lever 300 will cause it to pivot about its support pin 302 in a direction generally outwardly from the spindle 18. In this-extended position the lever 300 will engage a trip lever 304 which actuates a safety switch 306 connecting in the motor control circuit, cutting off energy to the driving motor 11. Actuation of the switch 306 by its lever 304 as a result of an engagement with the lever 300 causes the power to be disconnected from the motor and brings the machine to a stop. When the difiicultyhas been corrected, actuating lever 304 is again reset to its closed switch position and safety lever 300 is also folded downwardly into itsflush position with its channel member 38.

As the individual plies or strands of yarn Y are advanced beyond the compression trumpet 286 through the axial bore 19 and the orifice 24 of the spindle 18, it is both plied and twisted to form cord by the rotative action of flyer 20 throwing the cord in balloonlike mantension and causing the balloon to contract.

ner about floating frame 34. It is to be understood that yarn ends Y route through the spindle and apex guide in such manner as to produce two complete twists in said yarns for each revolution of the spindle whorl and fiyer. The rate of advance of the cord into the machine is maintained substantially constant being controlled by the capstan drive 120 which is positively driven from the spindle 18. Tension within the balloon is automatically controlled to maintain the desired balloon dimensions by action of the cord on the storage device surfaces 22 and 23. In emerging from the orifice 24 the cord does not move directly radially outwardly to the periphery thereon during rotation. in the balloon.

The manner in which the yarn storage device functions to control the balloon geometry is best illustrated as follows: i

Assuming that the input tension has increased which may arise in the aggregate or any one or more of a number of factors, such as the unwinding friction from the packages P, the incremental effect will be transmitted through tension devices 278, the compression trumpet 286 or the like up to the capstan which is drawing the cord at a constant rate, in turn increasing the balloon The contracting balloon offers less air friction, upsetting the force equilibrium previously set up by the air drag at the particular circumferential velocity of the cord versus that contributed by the lever arm function of the storage step thus allowing the yarn in the balloon to speed up, thereby decreasing the amount of lag or wraparound on the yarn storage surface. Decreasing the amount of wrap-around also decreases the tension, thus allowing the balloon to regain 'its normal size and configuration.

If the input tension should decrease, the cord balloon would tend to increase in size thereby causing more air drag and a resultant increase in wraparound about the yarn storage device surface. The increase in wraparound is accompanied by a corresponding increase in tension, which again tends to bring the balloon dimensions down to the required size. Thus the cord storage device acts as a regulator, feeding the required amount of cord into the balloon to maintain its geometry substantially constant.

The particular dimension of the cord storage surfaces 22 and 23 is dependent to a degree upon the range in denier of the cord to be handled by the machine. For a particular storage surface geometry the amount of wrap-around is dependent upon the cord material, density, spindle speed, the initial tension control setting into the balloon and degree of twist being imparted. The twist shows its effect through density change of the cord which in turn affects the air drag to centrifugal force ratios establishing the particular balloon shape. For a morecomplete description of the structure and theory action. The cord guiding means from the capstan drive 120 provides a constant length path to the cord, winding traverse mechanism making possible a high speed traverse for building a headless package of high density.

In practice I have found that it is practical to wind ZS-pound packages of multiple ply twisted cord of different'denier and fibrous material. An accurate and close lay of the wind, resulting in high package density, is made possible by use of the precision drive for the traverse arm 136 incorporating a gainer gear mechanism. Good package shape without end bulges or surface distortions is achieved by winding the initial turns'on the winding core under high tension and gradually decreasing the winding tension as the package increases. This at the same time creates a firmer package than would be possible if a constant tension had been employed throughout. The gradual decrease in winding tension is achieved by use of the variable torque coupling to the package driving roll 66. 4 I

The improved high density precision wound headless cord package can also be formed at a relatively higher cord speed than those formed on machines of the prior art. In practice I have obtained excellent results by operating the spindle at 5,000 R. P. M. and advancing the twisted cord to the takeup package at a rate of .150 yards per minute.

While I have shown and described a specific machine for plying, twisting and winding a plurality of strands of flexible fibrous material, it is to be understood that the same is for the purpose of illustration and not by way of limitation and that numerous changes and modifications can be made by those skilled in the art without departing from the spirit and scope of the appended claims.

I claim:

1. A strand twisting machine comprising a rotatable spindle, a strand tension control device secured to said spindle and having a strand receiving surface thereon,

said spindle having an orifice in the wall thereof terminating adjacent the surface of said strand tension control device and an axial passage leading from one end thereof into communication with said orifice, a supporting frame fioatingly mounted on said spindle and stabilized against rotation therewith, a strand take-up device mounted on said frame including arotatable mandrel for supporting a winding core, means for driving said mandrel from said spindle, strand guide means carried by said frame and positioned on the extended axis of said spindle to cause a flexible strand that is advanced therethrough from the axial passage and orifice of said spindle to balloon about said frame and put twist therein when the spindle is rotated, means carried by said frame and driven from said spindle for advancing said strand through said guide means, and a second guide means including a strand traverse mechanism driven in timed relation with said mandrel for directing said twisted strand from said strand advancing means toward said winding core and cause it to be wound thereon to form a package.

2. The twisting machine of claim 1 wherein the mandrel is driven from the spindle through a controlled torque coupling for applying a substantially constant operational torque on said mandrel and thereby control the tension on the strand as it is wound on the core.

3. The twistingmechanism of claim 1 wherein the means for driving said mandrel comprises a driving roll driven from said spindle and mounted on a hinged support carried by said frame and biased toward said mandrel so that the surface of the driving roll is in driving engagement with the surface of the package being wound on the winding core.

4. The twisting machine of claim 3 wherein the driving roll is driven from the spindle through a gear train interposed between the spindle and roll, the gear train including a controlled variable torque coupling to con- 14 trol the tension on the strand as it is wound on the core.

5. The twisting machine of claim 4 wherein an intermediate gear of the gear train hasits axis of rotation coincident with the axis about which said hinge support is adapted to rotate and the remaining gears of the train are successively driven thereby, being rotatively mounted on said hinged support, said intermediate gear being driven in a direction to cause the normal reactive rotative force on said hinge support to operate in a direction about the hinged axis to move the driving roll toward the winding core.

6. The twisting machine of claim 4 wherein the variable torque coupling between the gear train and driving roll comprises a friction clutch having driving and driven members yieldingly urged into engagement with each other, and means controlled by the position of the driving roll with respect to said mandrel for varying the pressure between said members to control the torque transmitted by said clutch.

7. The twisting machine of claim 6 wherein the pressure between said clutih members is provided by a spring and the tension of said spring in urging said clutch members toward each other is controlled by a pair of coacting cam members, the relative position of which with respect to eachother is determined by the position of said driving roll with respect to said mandrel.

8. The twisting machine of claim 1 wherein said strand guide means comprises a trumpet guide disposed on a hinged support carried by said frame, and means releasably holding said hinged support in operative position with respect to said frame, said holding means when released permitting said support to be swung about its hinged mount to a position providing unobstructed access through the end of said frame to said mandrel for dotfing a wound package and replacing an empty winding core thereon without removal of the strand from said trumpet guide.

9. The twisting machine of claim 1 wherein said strand guide means comprises a trumpet guide disposed for free rotation on the end of a tubular member projecting from the apex end of a conical-shaped cagelike support hingedly. mounted on one end of said supporting frame, and means releasably holding said cagelike support in operative position, said holding means when released permitting said cagelike support to be rocked about its hinged mount to expose the said one end of said supporting frame and provide unobstructed access to said mandrel for dofiing wound packages and replacing empty winding cores thereon.

10. The twisting machine of claim 1 wherein the strand traverse mechanism comprises a'movable strand guiding member for directing said strand onto the winding movement along a path parallel to the axis of rotation of said winding core, means for driving said arm along said path from said mandrel, said driving means including means for continuously advancing by a predetermined increment the relative position of said guide eye circumferentially with respect to said winding core during each excursion of said traverse arm to provide a precision wind on said core.

12. The twisting machine of claim 11 wherein the means for driving the traverse arm comprises a cam follower carried by the arm and co-acting with a rotatable barrel cam, and a gear train disposed between the man-. drel and the barrel cam for imparting rotation to the cam.

13. The twisting machine of claim 12 wherein the gear train'includes a diflerential gainer gear assembly whereby the speed ratio between the mandrel and the barrel cam is increased by an increment sufficient to provide accurate processionaldisplacement of adjacent turns. a

14. The twisting machine of claim .13 wherein the differential gainer gear assembly includes a spur gear pair, one of which gears having both internal and external teeth, and means coupling said spur gears together in driving relation comprising a speed reducing planetary gear cluster, the first gear of which is in mesh with the internal teeth of said one spur gear and the last gear of which mates with a stationary sun gear.

15. The twisting machine of claim 1 wherein the traverse mechanism comprises a movable strand guiding member, and means operative in response to movement of said strand guiding member for directing the strand to said guiding member, saidstrand directing means being operative independently of force reactions in the running strand.

16. The twisting machine of claim 1 wherein the traverse mechanism comprises a movable strand guiding member, a linear compensator operable in response to the traversing movement of said guiding member to provide a strand path of constant length from the strand balloon to the guiding member during the traversing movement of the member.

17. The twisting machine of claim 16 wherein the compensator comprises a movable guide element mounted for reciprocating movement along a path generally parallel to the traverse path of said guiding member, means driving said movable guide element from said guiding member in directions opposite to the directions of movement of said member, and stationary guiding elements for directing the moving strand through said movable guide element and toward said member, said stationary guiding elements being so positioned with respect to said movable guide element and said member that the linear path of travel of the strand to said member remains constant in length for all positions of traverse of the member. 7

18. The twisting machine of claim 16 wherein the compensator comprises a cable one'end of which is attached to said guiding member and its other end secured to said frame, stationary pulley guides disposed on one side of said frame between said member and the fixed end.

of said cable about which said cable is adapted to pass,

a a movable pulley engaging a bite of said cable adjacent its fixed end, stationary strand guiding pulleys disposed on the opposite side of said frame in complementary position with respect to said stationary cable pulley guide and a second movable pulley coupled and movable with said first movable pulley adapted to engage a bite of said strand, said second movable pulley and said stationary strand guiding pulleys providing a path of fixed length to said guiding member for all positions of traverse of said guiding member.

19. The twisting machine of claim 1 wherein the means for advancing said strand comprises a pair of capstan members mountedfor rotative movement and in spaced relation with respect to each .other and having strand receiving surfaces disposed to receive a plurality of wraps of the strand thereabout, and means for driving each of said members in timed relation with the spindle to advance the strand into the machine at a rate proportional to the rotating speed of the spindle.

20. The twisting machine of claim 19 wherein the axes of rotation of said capstan members are disposed in parallel planes but skewed with respect to'each other to provide a processional displacement axially of ing frame are arranged to provide a center of mass of the frame and its supported parts that is below the axis of rotation of said spindle to stabilize the frame against rotation.

22. In a strand twisting machine of the type wherein twist is inserted in a strand by causing it to advance axially into a tubular rotating spindle, out through an orifice in the spindle and balloon about a floating support frame carried by one end of the spindle, the improvement comprising a rotatable mandrel carried by said frame for receiving a winding core, a friction driving roll adapted to make driving engagement with said winding core and the surface of the package as the strand is wound about the core, and means for driving said driving roll from the spindle through a controlled torque coupling for applying a substantially constant operational torque on the package being wound on the core to thereby control the tension of the strand as it is being wound thereon 23. The improvement in a strand twistingmachine according to claim 22 wherein the driving roll is carried by a pair of swing arms mounted on a rotatable shaft journaled in the floating frame support, means for biasing said swing arms to urge said driving roll into engagement with the surface of the package being wound on said winding core, and a gear train between the spindle and driving roll whereby the roll is driven from the spindle.

24. The improvement in a strand twisting machine according to claim 23 wherein the rotatable shaft on which the swing arms are mounted is driven by an intermediate gear of said gear train, and means driven by said rotatable shaft for positively advancing the strand.

applying member for yieldingly urging the engageable members toward each other, and cam means actuated by a change of position of said drive roller with respect to the rotational axis of the winding core to change the position of said pressure applying member to accordingly control the torque transmitted by said clutch.

27. The improvement ina strand twisting machine according to claim 26 wherein the cam means are arranged to decrease the pressure between the engageable clutch members to decrease the driving torque of the clutch with increasing diameter of the wound package so that the strand tension is progressively decreased with the growth of the package diameter.

28. In a strand twisting machine of the type wherein twist is inserted in a strand by causing it to advance axially into a tubular rotating spindle, out through an orifice in the spindle and balloon about a floating support frame carried by one end of the spindle, and is directed into the support frame along the central axis of the rotating sprindle and wound on a package core rotatably'mounted on the floating support frame and driven from the spindle,

' v 17 last-named driving means including means for confinuously advancing by a predetermined increment the relative position of saidtraverse member circumferentially with respect to the package core to provide a wind of predetermined pattern on the core.

29 The improvement in a strand twisting machine according to claim 28 wherein the traverse member is mounted for sliding movement on a guide bar disposed parallel to the package core, a rotatable and reversing barrel cam, a cam follower coupling said traverse member to said barrel cam, said barrel cam being driven by a gear train-including the drive to said package core.

30. The improvement in a strand twisting machine according to claim 29 wherein the gear train for driving said barrel cam includes a gainer gear array for continuously advancing the traverse member by a predetermined increment circumferentially with respect to the package core during each excursion of the traverse member to provide a strand lay of predetermined pattern.

31. In a strand twisting machine of the type wherein twist is inserted in a strand by causing it to advance axially into a tubular rotating spindle, out-through an orifice in the spindle and balloon about a floating support frame carried by one end of the spindle and is directed into the support frame along the central axisof the rotating spindle and wound on a package core rotatably mounted on the floating support frame and driven from the spindle, the improvement comprising a traverse arm for directing the strand to the package core, means for traversing said arm, and a strand guide travel compensator actuated by said arm to maintain the strandapproach path to said traverse arm of constant length throughout the cyclic operation of the traverse arm.

32. The improvement in a strand twisting machine according to claim 31 wherein the strand guide compensator includes a plurality of stationary strand guiding pulleys and a movable guiding pulley arranged to define, an approach path for the twisted strand to said traverse arm, and means actuated by the traversing movement of said arm to move said movable pulley in the opposite direction and in distance and amount to compensate against any tendency of a change in length of the strand path occasioned by the traversing movement of said arm.

33. The improvement in a strand twisting machine according to claim 32 wherein the movable strand guiding pulley is actuated by a cable attached at one end to said traverse arm and at the other end to the support frame, said cable being guided by a plurality of stationary pulleys and a movable .pulley arranged in complementary relation with respect to said strand guiding pulleys, said movable pulleys being mechanically coupled so that the tension in the moving strand provides a balanced force system for all positions of the movable pulleys as determined by the position of the traverse arm.

34. In a flexible strand-handling machine, a rotatable mandrel to receive a winding core, means for driving said mandrel, and means for directing a strand at a predetermined linear rate to said winding core to be wound thereon, said mandrel driving means comprising a driven friction roll disposed for swinging movement toward and away from said mandrel, means for biasing said friction roll toward said mandrel so that the surface of the roll is in driving engagement with the surface of the package being wound on the winding core, and a controlled torque coupling to apply a substantially constant operational torque on said mandrel.

35. The machine of claim 34 wherein the friction roll is driven through a friction clutch having driving and driven members yieldingly urged into engagement with each other, and means controlled by the positions of the friction roll with respect to said mandrel for varying the pressure between said members to control the torque transmitted by said clutch.

36. The machine of claim 35 wherein the pressure 18 between the driving and driven members of said friction clutch is controlled by cam means actuated by a change of position of said driving friction roll with respect to the winding core to accordingly control the torque transmitted by said friction clutch.

37. In a flexible strand handling machine, a rotatable mandrel to receive a winding core, means for driving said mandrel including a controlled torque coupling for applying a substantially constant operational torque on said mandrel, means, includinga strand traverse member, for directing a strand at a predetermined linear rate to said winding core to be wound thereon, and means for driving said traverse member in timed relation with the winding core, said last-named driving means including means for continuously advancing by a predetermined increment the relative position of said traverse member circumferentially with respect to the winding core to provide a wind of predetermined pattern on the core.

, 38. The machine of claim 37 wherein the means for driving the traverse member includes a gear train having a differential gainer gear assembly therein whereby the speed ratio between the winding core and the traverse member is increased by an increment suflicient to provide accurate processional displacement of adjacent turns of the strand on the winding core.

39. The machine of claim 38 wherein the differential gainer gear assembly includes a spur gear pair, one of which gears having both internal and external teeth, and means coupling said spur gears together in driving relation comprising a, speed reducing planetary gear cluster, the first gear. of which is in mesh with the internal teeth of said one spur gear and the last gear of which mates with a stationary sun gear.

40. In a flexible strand handling machine, a rotatable mandrel to receive a winding core, means for driving said mandrel including a controlled torque coupling for applying a substantially constant operational torque on said mandrel, and means for directing a strand at a substantially constant predetermined linear rate to said winding core to be wound thereon, said means directing the strand to the winding core including a traverse member, and movable strand directing means operable in response to movement of said traverse member for directing the strand to said traverse member and operable independently of force reactions in the running strand.

41. The machine of claim 40 wherein the movable strand directing means comprises a linear compensator operable in response to the traversing movement of the traverse member to provide a strand path of constant length through theconstant linear rate strand directing means to the traverse member.

42. The twisting machine of claim 14 wherein the speed reducing planetary gear cluster is adjustably disposed with respect to the stationary sun gear whereby sun gears of different size may be interchangeably associated with the planetary gear cluster to obtain an increment of speed change between the mandrel and the barrel cam in direct proportion to the size of sun gear-operatively associated with the gear cluster.

43. The machine of claim 42 wherein the incremental speed change between the mandrel and the barrel cam obtained with said planetary gear cluster is dependent upon the size of the sun gear operatively associated therewith and said gear cluster is adjustably disposed for interchangeable operation with sun gears of different size.

44. The twisting machine of claim 1 wherein the means for advancing the strand are driven from the spindle through a gear train to provide a twist of predetermined amount in the strand, one of the gears in the gear train being interchangeable with gears of different size to change the gear ratio of the gear train to accordingly obtain different amounts oftwist in the strand, and means are provided for adjustably disposing at least one other gear in said train to establish an operative association of 19 1 the gears in the train for each size of interchangeable gear 2,002,590 Shinn May 28, 1935 selected. 2,022,379 Metcalfe et al Nov. 26, 1935 I 2,487,837 Uhlig NOV. 15, 1949 References Cited in the file Of this p tfli 2,505,050 Kimball 2 Apr. 25, 1950 UNITED STATES PATENTS 5 5 r i Nov. 20, 1951 723,178 Norman Mar. 17, 1903

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