US2901883A

US2901883A - Hydraulic fly frame drive and method

Info

Publication number: US2901883A
Application number: US620488A
Authority: US
Inventors: Edgar H Granberry
Original assignee: West Point Manufacturing Co
Current assignee: West Point Manufacturing Co
Priority date: 1956-11-05
Filing date: 1956-11-05
Publication date: 1959-09-01
Anticipated expiration: 1976-09-01
Also published as: FR1192255A; ES238389A1; CH346801A

Description

Sept. 1, 1959 E. H. GRANBERRY A 2,901,883

HYDRAULIC FLY FRAME DRIVE AND METHOD v Filednov. 5, 1956 4 sheets-sheet 1 mg mmum..nnnnuur (D Q 2" 9. o WMI ullmlllm 9 D IllllllllllllllllllllNlhlllllll EDGAR H.GRANBERRY ATTORNEYS Sept. 1, 1959 E. H. GRANBERRY HYDRAULIC FLY FRAME DRIVE AND METHOD Filed Nov. 5,v 1956 4 Sheets-Sheet 2 INVENTOR A fl' EDGAR H. GRANBERRY ATTORNEYS NN ON Sept. 1, 1959 E. H. GRANBERRY HYDRAULIC FLY FRAME DRIVE AND METHOD 4 Sheets-Sheet 3 Filed Nov. 5, 1956 www oom INVENTOR EDGAR H. GRANBERRY Sui ATTORNEY sept. 1, 1959 E. H. GRANBERRY HYDRAULIC FLY FRAME DRIVE AND METHOD 4 Sheets-Sheet 4 Filed Nov. 5, 1956 INVENTOR EVDGA R H. GRANBERRY ATTORNEYS United States Patent O HYDRAULIC FLY FRAME DRIVE AND METHOD Edgar H. 'Granberry, Shawmut, Ala., assignorto West IPoint Manufacturing Company, West Point, Ga., a corporation of Georgia -Application November '5, 1956, Serial No. 620,488

44 Claims. (Cl. 5798)' This invention relates to fly frames, also known as roving frames, which are designed to draft stock (usually sliver) by means of rolls, twist it by means of flyers, and wind it onto bobbins. The invention relates also to a method of operating fly frames.

A principal object of the invention is the provision of ahydraulically driven ily frame, wherein hydraulic power transmission means is substituted for the variable speed drive (cones) of conventional frames, and, optionally, for the-main drive and compound also.

"Hydraulic power transmission to and in the ily frame involves many advantages. For example, hydraulic driving ymakes it possible to transmit more power in the frame, lwith better control, whereby larger and more uniform packages may be wound than ever before. It is well known that cone variable speed transmissions designed for Yuse with large diameter packages, exceeding for eX- ample 6 inches, are exceedingly bulky, and the cones become progressively less sensitive (accurate) with increase in package diameter, to the point of impracticality. The variable hydraulic drive means of the present invention, distinctively, is sensitive and accurate, and effects even winding with uniform tension. This is particularly true at .large bobbin diameters, the `invention making possible accurate and uniform winding of packages 9 inches and more in diameter.

The improved variable Speed transmission, further, is capable of -precise speed control, producing accurate speeds which may be consistently repeated. Moreover, the hydraulic variable speed drive has little inertia and is capable of changing speeds almost instantaneously, these characteristics further contributing to sensitivity and accuracy. The hydraulic drive also reduces loss of speed in the variable speed transmission, and variation in the stock. Incidental advantages include the elimination of errors due to backlash, and the elimination of the well known variables inherent in cone operation, due to variations in temperaure, humidity, cleanliness and the like.

A further object of the invention is the provision of a hydraulically driven fly frame in which adjustment for different hank size ranges is greatly facilitated.

Another object of the invention is the provision of a ily frame drive system which facilitates kinking prior to dolling.

Still another Yobject -is the provision of a hydraulic 'fly frame drive which permits power movement of the bobbin carriage Itoward or to the end of a stroke while the frame is otherwise at rest. By this means, bobbins may be wound with a full or almost full first layer, regardless of the point lat which the frame was stopped for the previous doff.- A related object is the provision of a method of ily Vframe operation, involving independent movement of the .carriage while the frame is at rest.

Still another object is the provision of a hydraulic ily frame drive having a supercharging system, whereby pumps and motors may be prestressed and all possibility of lost motion eliminated. Further objects will be in part evident, and in part pointed out hereinafter.

Mice

The invention and the novel features thereof may best be made clear from the following description and` the accompanying drawings in which:

Figure l is a diagrammatic illustration 'of a conventional ily frame, wherein the cones are replaced by va simplified variable speed 'hydraulic transmission;

Figure 2 is a view of the transmission control cam, taken on the line 2 2 of Figure l;

Figure 3 is a view taken on the line 3 3 of Figure nl, illustrating the control cam driving means;

Figure 4 is a view ltaken on the line 4 4 of Figure -1, illustrating the builder motion actuating means controlling the hydraulic transmission;

Figure `5 is a diagrammatic illustration of a ily frame similar to that of Figure l, wherein a supercharged hydraulic system has been substituted for the conventional cones, and for the drive therefrom to the compound and to the lay;

Figure 6 is a view of the variable hydraulic pump control cam of Figure 5, taken on the line 6 6 of lFigure 5;

Figure 7 is a view taken on the line 7 7 of Figure 5, illustrating the builder motion cam controlling the reversing of the lay motor;

Figure 8 is a diagrammatic illustration of a 'hydraulic ily frame drive system corresponding generally to that of Figure 5, but representing an alternative arrangement and incorporating means for kinking and for driving the carriage while the remainder of the frame is at rest. This embodiment of the invention utilizes conventional builder motion elements for mechanical control of the variable speed hydraulic drive, and for reversal of the lay motor;

Figure 9 is a view on the line 9 9 of Figure 8, illustrating a builder motion cam suitable for mechanical actuation of the lay motor reversing valve;

Figure 10 is an alternative variable hydraulic pump control cam, adapted to facilitate kinking at the end of a frame cycle;

Figure 1l is a diagrammatic illustration of an alternative arrangement for mechanically actuating the lay motor reversing Valve; and

Figure l2 is a diagrammatic illustration of a ily frame having an all hydraulic drive, in which the hydraulic drive system replaces not only the cones of the frame, but also the usual compound.

Referring to the drawings in detail, the frame illustrated in Figure l corresponds generally to the type identilied with the Whitin Machine Works, `although it will be recognized that the invention is suitable for application to Saco-Lowell and other well known ily frame types. Power is supplied to the frame at pulley 20, mounted on the main shaft 22. Rotation of the main shaft is transmitted through its gear 24 and the diagrammatically illustrated gear train 26 `to the gear 28 mounted on spindle shaft 30. By means of

bevel gears

32 and 34, the spindle shaft 30 drives the spindles 36 and flyers 38 o-f the frame, these elements being driven in customary manner directly from the main drive, and at constant speed.

The constant speed main drive also drives the compound 40, 4this constant speed, it will be understood, representing one component of input to the compound. The mainshaft 22 also has a direct drive connection to the topy cone shaft 42, through twist change gear 44, intermediate gears 46'and the top cone shaft vgear 48. The direct drive is also transmitted through

gears

50 and 52 to thefront roll shaft 54, and thereby to the drawing rolls ofthe frame. By means of bevel gear 56 and gap gear 58, the top cone shaft drives the usual tumbler shaft 60, with which are associated the customary builder dogs 62, builder shaft 64, and builder jaws 66.

In the conventional frame, power is transmitted from the top cone shaft 42 to the center lift driving shaft 70, through a pair of cones which serve to convert the direct drive constant speed of the top cone shaft to a variable speed. The resultant variable speed of the center lift driving shaft is transmitted through its gear 72 and the diagrammatically illustrated gear train 74 to the compound 40, whereby a variable speed input component is fed into the compound. The variable speed output of the compound, representing the sum of the constant speed and the variable speed input components, is transmitted therefrom through gear train 76 and gear 78 to the bobbin shaft 80.,

Bevel gears

82 and 84 transmit the variable speed rotation of the bobbin shaft to the bobbins 86.

The variable speed rotation of the center lift driving shaft 70 is also transmitted through its bevel pinion 88 to the reverse stud bevel gear 90. The reverse stud bevel pinion 92 is adapted to drive one side or the other of the twin bevel gear 94 mounted on the center lift shaft 96, and the tumbler shaft 60 operates through conventional means not shown to periodically displace the shaft 96 in axial direction,'whereby the direction of its rotation is reversed. The center lift shaft 96 is adapted to reciprocate the bobbin carriage of the frame by means of its rack 98, the movement of the center lift shaft being transmitted through lay change gear 100, center lift intermediate gear 102, center lift intermediate pinion 104, lifting shaft gear 106,-lifting shaft 108, and the lifting shaft pinion 110. All of the fratrie elements described to this point are conventional.

In vaccordance with ay simplified embodiment of the present invention, the constant speed direct drive of the top cone shaft 42 is converted to a variable speed and transmitted to the center lift driving shaft 70, through an hydraulic variable speed transmission 120. The transmission 120 may be for example a Vickers Model TR 3, provided with the usual side control shaft 122 and control arm 124 extending therefrom. A gear 126 on the top cone shaft drives the transmission through a gear train or chain 128, engaged to ygear 130 mounted on the transmission input shaft 132. The transmission output shaft 134 carries a gear 136 drivingly engaged by gear train or chain 138 to the gear 140 mounted on the center lift driving shaft 70.

The variable output of the transmission 120 is controlled by movement of its control arm 124, and means are provided to control the movement of the control arm by means of and in coordination with the operation of the builder motion. In the exemplary embodiment, a link 142 is pivotally engaged to the outer end of control arm 124. The link 142 carries a cam following roller 144 at its opposite end, and the link is suitably guided and maintained in contact, by conventional means not shown, with the edge of disc cam 146. The cam 146 is mounted on stub shaft 148, which also carries a gear 150. The gear 150 is drivingly engaged by a tension change gear 152, mounted on a shaft 154, which also carries a rack wheel 156. A solenoid S is mounted adjacent rack Wheel 156, its arm 160 carrying at its outer end a pawl 162 adapted to engage and rotate the rack wheel 156. An actuating cam 164 is mounted on the tumbler shaft 60 and a switch 166 disposed for actuation by said cam, as shown. The switch 166 is in circuit with solenoid 15S and a source of power 168.

To prevent lost motion in the variable speed transmission 120, an hydraulic pump 170, driven by an electric motor 172, may be provided, the output side of the pump being in liiuid communication with the transmission through conduit 174. The supercharging pump 170 maintains operating pressure in the transmission at all times, even while it is at rest, so that the transmission is prestressed andrmay start without any lost motion. The actuating cam 164, as illustrated in Figure 4, may be circular exceptfor two diametrically opposed ats 180. Preferably, theswitch 166 is normally open, and disposed so that its operating armv or button engages one of the cam ats While the tumbler shaft is at rest. Periodically, as is well known, the tumbler shaft rotates 180, and

4 each rotation of the tumbler shaft 60 etfects corresponding rotation of the actuating cam 164, which serves thereby to momentarily depress the operating arm or button of switch 166, and close the switch. Each closing of switch 166 is effective to retract the arm 160 of solenoid 158 (see Figure 3), whereby its pawl 162 correspondingly displaces or indexes the rack wheel 156. Each rotary movement of rack wheel 156 is transmitted through shaft 154, tension change Igear 152, gear 150, and stub shaft 148 to the cam 146, whereby the cam 146 is correspondingly indexed. As an alternative possibility, a rotary solenoid may be utilized to index the control cam 146. In this manner, the output of the variable hydraulic drive means, specifically the hydraulic transmission, is controlled by electrical means actuated by the builder motion.

A suitable control cam 146 is illustrated in Figure 2, the direction of rotation being indicated by the arrow 182. The cam is shown in starting position, at which the cam following roller 144 rests on the highest point thereof. As will be understood, the corresponding position of the transmission control arm 124 effects the speed output requisite at the beginning of a cycle of operation, this being the highest spoed transmitted to the variable speed part `of the frame, and corresponding to Winding of the initial layer on the bobbins. On the first reversal of the frame carriage, the tumbler shaft by means of its actuating cam 164 causes, in the manner described above, the cam 146 to be indexed a few degrees. The cam being substantially helical or spiral, the link 142 is thereby permitted to move slightly inwardly toward the cam, displacing the control arm 124 of the transmission and slightly reducing its output speed. In this manner, operation of the builder motion to effect reversal of the carriage direction is operable simultaneously to alter the output speed of the variable speed transmission. The reduction in speed so effected is substantially instantaneous, and controlled with extreme accuracy by the contour of the cam. The helical form of the cam may extend through 270 of its periphery, this extent corresponding to the programmed number of layers, that is to a complete winding cycle. During doing, the cam may be returned to initial starting position, either manually or automatically.

It will be noted that variable speed programming of the frame may be altered with facility, this involving merely replacement of the cam 146 with a similar cam of appropriate contour. Also, the cam 146 is indexed through the tension change gear 152, which may be readily replaced as in conventional frames, and for the same purpose. The embodiment illustrated in Figures l to 4 may be incorporated into present frames with minimum expense, involving merely replacement of the con transmission, and the mechanism for the control thereof.

While an electrical control for the variable speed drive has been illustrated, it will be understood that mechanical or other means may be utilized as Well.

Another embodiment of the invention is illustrated in Figures 5 to 7. In this embodiment, the conventional mechanical variable speed drive mechanism and carriage reversing mechanism is substantially entirely replaced by hydraulic means. As in the previous embodiment, direct constant speed drive is applied to the frame at pulley 20, and transmitted in customary manner to the spindles 36, the compound 40, the front roll shaft 54, and the builder motion. In this embodiment, gear 126 on the top cone shaft 42 is engaged -in driving relationship byv chain 128 to a gear 200, which drives a variable output hydraulic pump 202. The pump 202' may be, for example, a Vickers Model PV-2003, and is provided with the usual control plunger 204. As in the previous embodiment, the control plunger 204 is engaged by the edge of disc cam 146, which thereby controls the output of the pump. The disc cam may be indexed precisely in the manner described in connection ywith the `previous embodiment.

In operation, the output of pump 202 -is conveyed through conduit 206 to a four-way reversing valve 208, and then through either conduit 210 or conduit 212 to the xed hydraulic motor 214. The motor 214, which may be, for example, Va Vickers Model M12-2003, is adapted to rotate at a speed proportional to the volume of hydraulic fluid passed therethrough. As shown, the hydraulic motor 214'is drivingly engagedto the lay change gear 100 of the frame, which in turn is drivingly engaged, through conventional gearing already described or other arrangement, to the carriage drive rack, wherebyit may drive and reciprocate the carriage. In place of motor 214, a hydraulic cylinder may be utilized to reciprocate the rack 98 or otherwise `drive the bobbin carriage.

From hydraulic motor 214 aud the reversing valve 208, the variable oil ilow is conveyed through conduit 216 `to a xed hydraulic motor 218, which corresponds in type to the motor 214. The motor 218 in this embodiment supplies, through gear 72 and gear train 74, 'the variable speed input component to the compound 40, whereby the bobbins are driven at a variable speed representing the sum of the fixed and variable speed input components to the compound. From motor 218, the oil ow may return to the pump 202, or to a sump. In this manner, a variable oil ow is derived from the constant speed main drive of the frame, and utilized serially to provide variable speed drives for the bobbin carriage and for the compound.

The reversing valve 208 may be alternated between its two operative positions by a solenoid 220, operated by a switch 222 in series with the solenoid and with a power source 224. The switch 222 may be actuated by a cam 226 mounted on the tumbler shaft 60. As shown in Figure 7, the cam 226 may be circular, and provided with a single iiat 228, adapted to be aligned with the actuating arm `or button of the switch 222 in one of the two -rest positions of the tumbler shaft. As will be understood, in the cam position shown, the switch 222 may be open whereby the valve 208 will be disposed in one of its two operative positions by spring pressure or otherwise. Rotation of the tumbler shaft 60 through 180 then, will close the switch, causing the solenoid 220 to displace the reversing valve 208 to its other operative position, and such relationship will persist until the tumbler shaft again rotates 180.

In this embodiment the conventional builder motion is utilized to control the variable output of pump 202, and thereby the speed of the

hydraulic driving motors

214 and 218, and also to elfect reversal of the oil liow through motor 214, both operations being electrically actuated in simple manner. While in converting present machines it will rusually be convenient to use the builder motion already provided, it will be recognized that in the Figure 5 embodiment of the invention only sufcient power is required to operate the two switches 166 and '222. It is possible, accordingly, lto greatly reduce the size of the builder motion, and to incorporate it into a small control box at any convenient location on the frame. The builder motion, for example, may be built into a small gear box including the indexing mechanism for the cam 146. I-t will be further understood, accordingly, that the term builder motion as used in this speciiication and the accompanying claims, is intended to include not only conventional mechanical builder motions, but similar programming mechanisms also, that is to include any device eiective to control the direction, rate and extent of travel of the bobbin carriage.

The Figure 5 embodiment includes a distinct supercharging system, including a separate hydraulic pump 230 powered by an electric motor 232. The supercharging pump 230 may draw oil from a sump 234 through a strainer 236, and provides oil at working pressure, for example 250 lbs. p.s.i., to both sides of the variable pump 202 and Amotors .'214 and 218. AIn this way, the vvariable pump and the hydraulic motors of the variable speed drive may be prestressed while the frame is not operating, and start up without any lost motion, thereby maintaining the accuracy of the variable speed drive through successive operations. In the circuit illustrated, supercharging pressure may be transmitted from the pump 230 to the input of variable pump 202 through conduit 238, and thro-ugh conduit 240, check valve 242 and conduit 244 to the output side of pump 202, and to one side of motor 214. The super-charging pressure may also be transmitted through conduit 246 to the outlet side of motor-v218, and through bypass conduit 248 and check valve 250 to conduit 216, and thereby to the infeed side of motor 218 and to the other side of motor 214. When the frame-is in operation, the oil flow 'may bypass *the supercharging pump 230, the output `of motor v218 vpassing `throughcond-uits 246 and 240directly into conduit 238, and thereby back .tothe variable pump 202.

A further embodiment of the invention is illustrated in Figures I8 and 9, wherein, as in the previous embodiment, the conventional mechanical direct and constant speed drive to the spindles, compound, drawing rolls and builder motion is retained. This embodiment is distinguished` by the provision of hydraulic means facilitating kinking of the stock above the ilyers immediately priorl to dofling, and .providing for driving the bobbin carriage toward 'or to the end of a stroke while the frame vis -otherwise at rest. Further, in this embodiment, the variable speed control cam and reversing valve for the lay motor are mechanically actuated by the builder motion.

As in the previous case, the power input to pulley 20 and main shaft y22 is transmitted directly to the spindles, the compound, the draft rolls and the building motion tumbler shaft, and by means of gear 200 to the Variable output hydraulic pump 202, which is accordingly powered by the direct drive. The variable output iiow 4of pump 202 is conveyed through

hydraulic motors

214 and 218 in series, although in this case the oil llow passes rs't through conduit 216 to themotor 218, and from motor 218 through conduit 260 to the reversing valve 208. vOn leaving the reversing Valve, the oil flow is lreturned directly to the pump `202 through conduit 262. In this manner, .as in the previous case, the constant speed mainY drive `is converted by variable pump 202 to a variable oil ow, which flows successively through

motors

218 and 214, delivering `a variable speed tothe compound and to the carriage drive. For independent control of the vspeeds of motors 214 and 2.18, a portion of the variable oil flow may be bypassed around motor 214 through conduit 252 and variable lthrottle valve 254. The operation of the throttle valve may be controlled by a disc cam 256, indexed in unison with the control cam 146, conveniently by means of a xed yconnection 258. Such independentv control and means therefor are disclosed and claimed in my copending application Serial No. 620,406, led on even date herewith.

In this embodiment the conventional builder motion is used to drive the Variable pump control cam 146 directly and mechanically. The movement of tumbling shaft 60 is transmitted in conventional manner through the tenf sion change gear 264 to the Winding shaft 266, and the periodic movement of the winding shaft is eiective through` its gear 268 to displace the rack 270, usually associated with the cone belt. The rack 270 actuates 'the builder shaft 64 through the twist change gear 272 4in conventional manner, and in this case is utilized to rotate the .gears 274 and 276, which may be mounted on a common shaft 278. The gear 276 may be engaged in driving relationship to a gear 280, which corresponds to the rack wheel 156 of previous embodiments, and is operative to index'the cam 146 through the gear 152.

The action of the builder motion is also utilized tol mechanically actuate the four way reversing valve 208. For this purpose, a. .reversing cam 282 may be -ixedto 7 the tumbler shaft 60, and a rigid link 284 provided between the reversing valve and the reversing cam. Conventional means may be provided to guide the link 284, and the assembly is desirably biased toward the reversing cam, yas by spring 286. The reversing cam 282 may be shaped as illustrated in Figure 9. In the position shown, the link 2874 is displaced a maximum distance from the cam axis, and the valve 208 Would be displaced, against the actionfof spring l286, to the position opposite to that illustrated in Figure 8. Rotation of the reversing cam through 180 would permit the link 284 to move inwardly against the cam llat 28S, permitting the spring 286 to displace the Valve 208 and the link 284, to the relative relationship illustrated in Figure 8.

VTo facilitate kinking of the stock above the yers, for the purpose of doing, an auxiliary circuit may be prow'ded to bypass the output of pump 202, thereby etlectively deactivating the variable speed drive. This circuit includes the branch 290 leading from the conduit 216', at a point adjacent the outlet of pump 202, to the valve 292, which is normally closed. A branch line 294 leads from the valve 292 to the return conduit 262. A manually operated lever 296 may be provided adjacent valve 292, pivotally mounted and adapted to move the valve to open position. As shown, movement of the operating lever to the left will displace the valve 292 to the left against the action of the spring 298, whereby the valve passage -300 opens the conduit 290 to the conduit 294. In this position, the valve 292 permits the output of pump 202 to circulate through

conduits

290, 294 and 262, whereby the

motors

214 and 218 are bypassed. As will be understood, the operating lever 296 may be manipulated as described somewhat before .the frame comes to a stop at the end of a cycle, thereby terminating the variaole vspeed drive to the bobbin carriage and to the cornpound. This allows the roving to kink or bunch up on top of the flyers so as to provide slack for removing the flyers prior to dofling. In conventional frames, it is customary to raise the bottom cone and thus disengage the cone pulley, to effect the same result.

An alternative arrangement for kinking at the end of a cycle is illustrated in Figure 10. As there shown, the disc cam 146 corresponds to the control cam 146 described -in connection with Figure l through the 270 segment corresponding to the winding cycle. That is, the periphery of the cam descends in a spiral from starting point 340 to point 342, which represents the end of the winding cycle. Beyond point 342, the cam 146 descends to `a, low point 344, adapted to position the control plunger 204 of pump 202 at a position corresponding to zero delivery. Near the end of a cycle, then, the variable pump control plunger may contact the cam 146 at or near its point 342, and the cam may then be indexed mechanically or manually to bring the pump plunger into contact with point 344, whereby delivery of oil by pump 202 and through the

motors

214 and 218 will be terminated, before the frame comes to a full stop. Running of the frame for about two or three revolutions of the bobbins after terminating the oil delivery will cause the sliver to kink above the flyers in precisely the same way as may be eiected by the operation of valve 292 to bypass the pump. When the frame is reset for the next cycle, the special cam 146 may be reset to starting position, manually or otherwise. Deactivation of the variable speed hydraulic drive for kinking may also be eiected in the present invention by the interposition of clutch means between

gears

126 and 200, and declutching the pump 202 near the end of the cycle. Y It is essential in ordinary fly trame operation to terminate a cycle with the carriage in a position intermediate the extremes of its possible travel. This follows from the shaping of packages with cone ends, and the termination of winding approximately at the middle of the outer layer. During the rest period for dong, the frame is reset lto starting condition, and winding on the new bobbins necessarily begins with the carriage in the same position at which the previous cycle was terminated. The inintial layer of roving on the new bobbins, accordingly, is a half or partial layer starting near the center of the bobbins and extending to one end thereof. The next roving layer is necessarily uneven, since it is partially on the first layer and partially on the bare wood. This introduces diversity in tension through the initial layers which is not equalized until several layers have been wound upon the bobbins. Usually, because of this inherent condition, the tension on the first two or three layers is made excessively tight, whereby the roving constituting these layers is unduly stretched with respect to the roving in the outer layers of the package. This undesirable non-uniformity may be eliminated by initiating winding at or near an end of the bobbin rather than in the middle, and means are provided in the present invention to move the bobbin canriage to or toward an end of its travel in either direction, while the remainder of the frame is `at rest.

In the embodiment of Figure 8, the supercharge system and its pump 230 are utilized for traversing or resetting the canriage. As previously indicated the super-v charge pump remains operative While the frame is at rest during doing. At such times, of course, the direct drive to the frame is deactivated, and there is no input to the variable hydraulic pump 202. The supercharge pump furnishes Working pressure to the inlet side of pump 202 through conduit `302. The same conduit conveys working pressure through conduit 262 and normally open valve 306 to the reversing valve 20S, and thence to one side of motor 214. Working pressure is transmitted also through

conduits

240 and 310 and check valve 312 to conduit 216', and thereby to the outlet side of pump 202 and to the inlet of motor 218. From conduit310, a branch conduit 314 Ileads through check Valve 316 and conduit 260 to the outlet side of motor 218, and also to the reversing valve 208, and thereby to the other side of motor 214.

The normally open Valve 306 has two positions, its normal position providing communication between connected sections of conduit 262, as shown. In its other position, the valve by means of its passage 322 is adapted to connect conduit 262 with the return line 324, which empties into the sump 234. As indicated in Figure 8, the valve 306 may be normally maintained in the position illustrated as by a spring 326, and disposed for operation to opposite position by the operating lever 296.

VJhen the operating lever is displaced to the right as shown in Figure 8, the valve 306 is moved against the action of spring 326 to connect conduit 262 with return line 324. This permits a iiow of oil through the lay motor 214, while the motor 218 and the pump 202 are at rest. The oil path is from the supercharge pump 230 through conduit 240, branch 314, check valve 316, reversing valve 208 (and, of course,

conduits

210 and 212 and motor 214), conduit 262, valve 306 (in particular the passage 322 thereof), and through conduit 324- back to the sump 234. As will be apparent, the position of the reversing valve is immaterial, and the supercharge pump will drive the bobbin carriage in the direction determined by the position of the reversing Valve to or toward the end of its travel. The movement of the carriage may be terminated by return of the operating lever 296 to central inoperative position, or stop means may be provided 0n the frame or carriage to deactivate the hydraulic circuit just described at or near the end of the carriage stroke. In other words, an interlocking arrangement may insure that the carriage is not run beyond the end of its stroke, and such interlocking arrangement may be mechanical or electrical and associated with operating lever 296, or hydraulic, or otherwise. In this manner the bobbin carriage may be reset during the doing period, and winding on the new bobbins begun at an end thereof, with the attendant advantages indicated. If desired, to expedite subsequent operations or for other reason, the carriage may be reset to a position near an end of its travel, to permit initiation of Winding with a partial layer representing a small fraction of a full layer.

Figure l1 illustrates an alternative arrangement for mechanical actuation of the reversing valve for the lay motor 214. In this Figure, an eccentric 330 is mounted on the tumbler shaft 60, and a rotary reversing valve 332 establishes alternative communication between

conduits

260 and 262, on the one hand, with the conduits 21) and 212 leading to the motor 214, on the other hand. A bifurcated actuating arm 334 extending from the valve body may enclose the eccentric 3311. In the position illustrated, conduit 260 communicates with conduit 212, and conduit 262 with conduit 210. The eccentric 330 and the valve actuating arm 334 are so dimensioned and disposed that 180 rotation of the tumbler shaft 60 and the eccentric 330 will rotate the actuating arm 334 and the valve body to bring conduit 264i into communication with conduit 210, and conduit 262 into communication with 212, thereby reversing the direction of iiow through the lay motor. As will be evident, the valve body may be otherwise engaged to the eccentric, or other mechanical arrangement may be provided to reverse the oil ow through motor 214 in accordance with operation of the builder motion. For example, the valve 288 may be substituted by a mechanically actuated snap-action valve, adapted to be tripped by means of cams mounted on the blocks or nuts of the builder motion. This would permit the reversing valve to be mounted on the bobbin carriage, being tripped at each end of the carriage stroke by engagement with a cam.

In Figure l2 is illustrated a ily frame having a lcornpletely hydraulic drive, that is a drive system in which both constant and variable speed inputs are effected hydraulically. In this embodiment, the conventional cornpound is eliminated, and replaced by a simple plumbing tting such as a T.

As illustrated, an electric motor 358 drives a xed hydraulic pump 352 at constant speed, whereby a constant flow of oil is pumped thereby through conduit 354. The hydraulic pump 352 is necessarily of` considerable capacity, and may be for example a Vickers Model PV- 2008. Conduit 354 carries the constant oil flow to a ixed hydraulic motor 356, which may be a Vickers Model MF-2008, and the oil flow passes through the motor 356 to the conduit 358. The motor 356, as will be recognized, pro-vides the constant speed main drive for the frame, driving a gear 368 which is drivingly engaged to a gear 362, the latter being mounted on the main shaft 22 in place of the customary drive pulley. The constant speed drive is transmitted by gear train 26 to the spindles 36 and yers 38, and through twist change gear 44 and intermediate gearing to the top cone shaft 42, and to the front roll shaft 54.

A variable speed may be derived from the constant speed drive precisely in the manner illustrated in the embodiment of Figure 5, and described in connection therewith. That is, a variable hydraulic pump 202 may be driven from the top cone shaft, the output of the variable pump being controlled by a control cam 146, which is indexed automatically in accordance with the operation of the builder motion. The variable output of pump 202 is carried by conduit 296 to the reversing valve 268, and passes through the lay motor 214, the direction of the oil flow through the lay motor being automatically reversed in the manner previously described by the reversing valve, the operation of which is controlled electrically in this case, by the builder motion. The oil flow, after leaving the lay motor 214, is conducted `through conduit 216 to the hydraulic motor 218.

Before it reaches the hydraulic motor 218, the variable oil flow passing through conduit 216 is combined with the constant oil flow passing through conduit 358, at junction 362, and the combined oil ows pass-through and drives the bobbin motor 218. The output of motor 218 is transmitted by means of gear 364 and gear train 366 to the gear 78 mounted on the bobbin shaft 80, and thereby to the bobbins. yIt will be recognized that the speed of motor 218 and resultant bobbin speed accordingly represent a combination of the constant speed component of the main drive of the frame plus the variable speed component derived from pump 282, the latter corresponding to the speed of the lay motor 214. The combination of the two oil iiows, then, serves the function of the usual compound, which in the present invention is replaced by a simple plumbing fitting such as a T at the junction 362.

The motor 350 may also drive a supercharge pump 370, adapted to maintain working pressure throughout the system while the frame is at rest. If a single electric motor 351) is used, suitable provision may be made to declutch the pump 352 or to bypass its output while the frame is at rest, the pump 370 remaining active during such periods. Alternatively, a separate motor may be provided for the supercharge pump 371). In the Figure l2 embodiment, supercharging pressure is supplied through

conduits

372 and 374 and check valve 376, and conduit 354 to the inlet of motor 356, and to the outlet of pump 352. The supercharging pressure is transmitted also through

conduits

372 and 378 and check valve 380 to the outlet side of motor 356 and to the inlet side of motor 218. A branch 382 leads from conduit 378 to the inlet of variable pump 282, this branch constituting the normal feed line for pump 202, and another branch conduit 384 transmits supercharging pressure through check valve 386 to the outlet side of pump 202, and to one side of motor 214. Conduit 383 communicates with conduit 372, and carries supercharging pressure to conduit 390, which leads to the outlet of motor 218 and' to the inlet of pump 352, and through conduit 392 and check valve 394 to the other side of the lay motor 214. The supercharging system described, then, provides access of supercharging pressure to both sides of all hydraulic pumps and motors of the system, prestressing these elements, whereby the frame may remain at rest for short or extended periods of time and then start up without lost motion.

The completely hydraulic drive system illustrated in Figure 12, obviously, can be adapted for kinking, and for resetting the carriage while the frame is at rest, in a manner corresponding to that described in connection with Figure 8. lIt will thus be seen that there has been provided by this invention an article and method in which the various objects hereinbefore set forth, together with many practical advantages, are successfully achieved. As various possible embodiments may be made of the novel features of the above invention, all Without departing from the scope thereof, it is to be understood that all matter hereinbefore set forth or shown in the accompanying drawings is to be interpreted as illustrative, and not in a limiting sense.

I claim:

1. In a fly frame including drawing rolls, flyers, bobbin rotating means, a traversing bobbin carriage and a builder motion, variable hydraulic drive means engaged to said carriage and to said bobbin rotating means in driving relationship, and means actuated by said builder motion controlling the output of said hydraulic drive means. 2. In a fly frame including drawing rolls, flyers, bobbin rotating means, a traversing bobbin carriage and a builder motion, means engaging said drawing rolls, flyers and builder motion in direct driving relationship, variable hydraulic drive means powered by said direct drive means engaged to said carriage and to said bobbin rotating means in driving relationship, and means actuated by said builder motion controlling the output of said hydraulic drive means.

3. 'In a y frame including drawing rolls, flyers, bobbin rotating. means, a traversing bobbin carriage and a builder motion, means engaging said drawing rolls, flyers and builder motion in direct driving relationship, said.- direct drive means being engaged also to said bobbin rotating means through a compound, variable hydraulic drive means engaged to said carriage and to said compound in drivingrelationship, and means actuated by said builder motion controlling the output of said hydraulic drive means.

4. -In ally frame includingzdrawing rolls, ilyers, bobbin rotating means, a traversing bobbin carriage and a builder motion, means engaging said drawing rolls, flyers and builder motion in direct driving relationship, said direct drive means being engaged also to said bobbin rotating means through a compound, variable hydraulic drive means powered by said direct drive means engaged to said carriage and to said compound in driving relationship, and means actuated by said builder motion controlling the output of said hydraulic drive means.

5.. In a ily frame including drawing rolls, flyers, bobbin rotating means, a traversing bobbin carriage and a builder motion, means engaging saidfdrawing rolls, flyers and builder motion in direct driving relationship, said direct drive means being engaged also to said bobbin rotating means through av compound, variable hydraulic drive means powered by said direct drive means engaged to said carriage and to said compound in driving relationship, a cam controlling the output of said hydraulic drive means, and means for indexing said cam in accordance with the Operation of said builder motion.

6. .A ily frame as delined in claim 5, wherein said cam indexing means includes a tension change gear.

7. In a ily frame including drawing rolls, flyers, bobbin yrotating means, a traversing bobbin carriage and a builder motion, means engaging said drawing rolls,iflyers and builder motion in direct driving relationship, said direct drive means being engaged also to said bobbin rotating means through a compound, a variable speed hydraulic transmission powered by said direct drive engaged to said carriage and to said compound in driving relationship, and means actuated by said builder motion controlling the output of said hydraulic transmission.

8. A ily frame as defined in claim 7, including a supercharge pump connected to said transmission and adapted to eliminate lost motion therein.

v9. In a fly frame including drawing rolls, yers, bobbin rotating means, a traversing bobbin carriage and a builder motion, means engaging said drawing rolls, flyers and builder motion in direct driving relationship, said direct drive means beingengaged also to said-bobbin rotating means through a compound, a variable speed hydraulic transmission powered by said direct drive engaged to said carriage and to said compound in driving relationship, a cam controlling the output of said hydraulic transmission, and means for indexing said cam in accordance with the operation of said ybuilder motion.

10. In a y frame including drawing rolls, flyers, bobbin rotating means, a traversing bobbin carriage and a builder motion, means engaging said;drawing rolls, yers andk builder motion in direct driving relationship, said direct drive means being engaged also to said bobbin rotating. means through a compound, a hydraulic pump powered by said direct drive means, a first hydraulic motor engaged to said .carriage indriving relationship, a second hydraulic motor engaged to said compound in driving relationship, means conveyingthe output of said pump through saidmotors in series, and means actuated byV said builder motion Ycontrolling the speed of said motors.y

11; A fly frame as defined in claimlO, including a supercharge pump and circuit adapted ,to maintain `operating pressure and eliminatel lost motion in said pump and motors at all'times.

v12. A y frame as defined in claim 10, ywherein said 12 rst hydraulic motor, is engaged to said carriage through a lay change gear.

13. In a y frame including drawing rolls, yers, bobbin rotating means, a traversing bobbin carriage and a builder motion, means engaging said drawing rolls, yers and builder motion in direct driving relationship, said direct drive means being engaged also to said bobbin rotating means through a compound, a variable hydraulic pump powered by said direct drive means, means actuated by said builder motion controlling the output of said pump, a lirst hydraulic motor engaged to said carriage in driving relationship, a second hydraulic motor engaged to said compound in driving relationship, and means conveying the output of said pump through said motors in series.

14. A ily frame as defined in claim 13, wherein the output of said pump is conveyed iirst through said irst hydraulic motor.

15. A ily frame as defined in claim 13, wherein the output of said pump is conveyed irst through said second hydraulic motor.

16. A fly frame as delned in claim 13, wherein said means actuated by said builder motion includes a cam, and means for indexing said cam in accordance with operation of said builder motion.

17. A ily frame as delined in claim 13, wherein said means actuated by said builder motion includes a cam, a tension change gear, and means for indexing said cam through said tension change gear in accordance with operation of said builder motion.

18. A y frame as defined in claim 13, wherein said means actuated by said builder motion includes a cam, and means for mechanically indexing said cam in accordance with operation of said builder motion.

19. A fly frame as defined in claim 13, including an electrically operated valve for reversing the flow through said irst hydraulic motor, a cam driven by said builder motion, and a switch actuated by said cam controlling the operationof said reversing valve.

20. In a ily frame including drawing rolls, yers, bobbin rotating means, a traversing bobbin carriage and a builder motion, means engaging said drawing rolls, yers and builder motion in direct driving relationship, said direct drive means being engaged also to said bobbin rotating means through a compound, a variable hydraulic pump powered by said direct drive means, means actuated by said builder motion controlling the output of said pump, a lirst hydraulic motor engaged to said carriage in driving relationship, a second hydraulic motor engaged to said compound in driving relationship, means conveying the output of said pump through said motors in series, and means for reversing the direction of said rst hydraulic motor.

21. In a fly frame including drawing rolls, flyers, bobbin rotating means, a traversing bobbin carriage and a builder motion, means engaging said drawing rolls, flyers and builder motion in direct driving relationship, said direct drive means being engaged also to said bobbin rotating means through a compound, a variable hydraulic pump powered by said direct drive means, means actuated by said builder motion controlling the output of said pump, a rst hydraulic motor engaged to said carriage in driving relationship, a second hydraulic motor engaged to said compound in driving relationship, means conveying the output of said pump through said motors in series, a valve for reversing the ow through said rst hydraulic motor, and means actuated by said builder motion con-I trollingl the operation of said reversing valve.

22. In a fly frame including drawing rolls, flyers, bobbin rotating means, a traversing bobbin carriage and a builder motion, means engaging said drawing rolls, ilyers and builder motion in direct driving relationship, said direct. drive means being engaged also to said bobbin rotating means through a compound, a variable hydraulic pump poweredby said direct drive means, means actu-` ated by said builder motion .controlling the outputlof said pump, a rst khydraulic motor engaged -to said carriage in driving relationship, .a second hydraulic motor engaged to said compound in driving relationship, means conveying the output of said pump through said "motors in series, .an electrically operated valve for reversing the flow through said lirst hydraulic motor, a cam driven by said builder motion, and a switch actuated by said cam controlling the operation of said reversing valve.

23. In 'a ily frame including drawing rolls, ilyers, bobbin rotating means, a traversing bobbin carria'ge and a builder motion, means engaging said drawing rolls, flyers and builder .motion in direct driving relationship, said directdrive means being engaged also to saidbobbin rotating means through a compound, a valiablehydraulic pump powered by said direct drive means, means actuated by said builder motion controlling the output of said pump, a iirst hydraulic motor engaged to said carriage in driving relationship, a second hydraulic motor engaged to said compound in driving relationship, means conveying the output of said pump through said motors in series, a mechanically operated valve for reversing the ilow through said iirst hydraulic motor, a cam driven by said builder motion, and a mechanical linkage actuated by said cam controlling the operation of said reversing valve.

24. In a ily frame including drawing rolls, flyers, bob- .bin rotating means, a traversing bobbin carriage and a builder motion, variable hydraulic drive means engaged to said carriage and to said bobbin rotating means in driving relationship, means actuated by said builder motion controlling the output of said variable hydraulic drive means, and means for deactivating said variable hydraulic drive means for kinking prior to doiling.

25. In a ily frame including drawing rolls, flyers, bobbin rotating means, a traversing bobbin carriage and a builder motion, variable hydraulic drive means engaged to said carriage and to said bobbin rotating means in driving relationship, means actuated by said builder motion controlling the output of said variable hydraulic drive means, and hydraulic means for driving said carriage while the frame is at rest.

26. In a fly frame including drawing rolls, ilyers, bobbin rotating means, a traversing bobbin carriage and a builder motion, means engaging said drawing rolls, ilyers and builder motion in direct driving relationship, said direct drive means being engaged also to said bobbin rotating means through a compound, a hydraulic pump powered by said direct drive means, a first hydraulic motor engaged to said carriage in driving relationship, a second hydraulic motor engaged to said compound in driving relationship, means conveying the output of said pump through said motors in series, means actuated by said builder motion controlling the speed of said motors, and means for deactivating said hydraulic pump for kinking prior to doiling.

27. In a ily frame including drawing rolls, ilyers, bobbin rotating means, a traversing bobbin carriage and a builder motion, means engaging said drawing rolls, ilyers,

and builder motion in direct driving relationship, said direct drive means being engaged also to said bobbin rotating means through a compound, a hydraulic pump powered by said direct drive means, a iirst hydraulic motor engaged to said carriage in driving relationship, a second hydraulic motor engaged to said compound in driving relationship, means conveying the output of said pump through said motors in series, means actuated by said builder motion controlling the speed of said motors, and means for deactivating said iirst and second hydraulic motors tfor kinking prior to dofing.

28. In a ily frame including drawing rolls, flyers, bobbin rotating means, a traversing bobbin carriage and a builder motion, means engaging said drawing rolls, flyers and builder motion in direct driving relationship, said direct drive means being engaged also to said bobbin rotating Vmeans through a compound, a hydraulic pump powered by said direct drive means, a iirst hydraulic motor ,engaged `to said carriage in driving relationship, a secondhydraulic motor engaged to said compound in driving relationship, means conveying the output of said pump through said motors in series, means actuated by said builder .motion controlling the speed of said motors, and hydraulic means for driving said iirst hydraulicmotor while the frame is at rest.

29. In a ily frame including drawing rolls, flyers, bobbin rotating means, a traversing bobbin carriage and a buildermotion, means engaging said drawing rolls, ilyers and builder motion in direct driving relationship, said direct drive means being engaged also to said bobbin rotating means through a compound, a hydraulic pump powered bysaid direct drive means, a iirst hydraulic motor engaged to said carriage in driving relationship, a second hydraulic motor engaged to said compound in driving relationship, means conveying the output of said pump through said motors in series, means actuated by said builder motion controlling the speed of said motors, a supercharge pump and circuit adapted to maintain operating pressure in said pump and motors at all times, and means for driving said iirst hydraulic motor by means of said supercharge pump while the frame is at rest.

30. In a ily frame including drawing rolls, illyers, bobbin rotating means, a traversing bobbin carriage and a builder motion, a iirst hydraulic motor engaging said rolls, flyers and builder motion in direct driving relationship, a hydraulic pump powered by said direct drive means, a second hydraulic motor engaged to said carriage in driving relationship, means conveying the output of said pump to said second motor, a third hydraulic motor engaging said bobbin rotating means in driving relationship, means conveying the discharge of said rst and second motors to said third motor, and means actuated by said builder motion controlling the speed of said second and third motors.

31. In a ily frame including drawing rolls, flyers, bobbin rotating means, a traversing bobbin carriage and a builder motion, a iirst hydraulic motor engaging said rolls, ilyers and builder motion in direct driving relationship, a variable hydraulic pump powered by said direct drive means, meant actuated by said builder motion controlling the output of said pump, a second hydraulic motor engaged to said carriage in driving relationship, means conveying the output of said pump to said second motor, a third hydraulic moto-r engaging said bobbin rotating means in driving relationship, and means conveying the discharge of said iirst and second motors to said third motor.

32. A ily frame as defined in claim 31, wherein said means actuated by said builder motion includes a cam and means for indexing said cam in accordance with operation of said builder motion.

33. A ily frame as defined in claim 3l, wherein said means actuated by said builder motion includes a cam, a tension change gear, and means for indexing said cam through said tension change gear in accordance with operation of said builder motion.

34. A ily frame as deiined in claim 3l, wherein said means actuated by said builder motion includes a cam and electrical means for indexing said cam in accordance with operation of said builder motion.

35. A ily frame as deiined in claim 3l, wherein said means actuated by said builder motion includes a cam and mechanical means for indexing said cam in accordance with operation of said builder motion.

36. A ily frame as defined in claim 3l, including a supercharge pump and circuit adapted to maintain operating pressure and eliminate lost motion in said pump and motors at all times.

37. A fly `frame as defined in claim 3l, wherein said second hydraulic motor is engaged to said carriage through a lay change gear.

38. A ily frame as deiined in claim 31, including means for reversing the direction of said second hydraulic motor.

39. A fly frame as defined in claim 31, including a valve for reversing the flow through said second hydraulic motor, and means actuated by said builder motion controlling the operation of said reversing valve.

40. A y frame as dened in claim 31, including means for deactivating said hydraulic pump for kinking prior to dong.

41. A y frame as dened in claim 31, including hydraulic means for driving said carriage While the frame is at rest.

42. A fly frame as dened in claim 31, including hydrauljc means for driving said second hydraulic motor While the frame is at rest.

43. A fly frame as defined in claim 31, including a supercharge pump and circuit adapted to maintain operating pressure in said pump and motors at all times, and means for driving said second hydraulic motor by means of said supercharge pump While the frame is at rest.

44. In the operation of a fly frame including drawing rolls, yers, bobbin rotating means, a traversing bobbin carriage and a builder motion, the method comprising the steps of driving the drawing rolls, flyers and builder motion at constant speeds, driving the carriage and the bobbin rotating means at variable speeds, and independently driving the carriage while the frame is at rest.

References Cited in the file of this patent UNITED STATES PATENTS 2,101,395 Kato Dec. 7, 1937 2,186,696 Harris Ian. 9, 1940 2,507,904 Heller et al May 16, 1950