US2171607A - Manufacture of golf balls or the like - Google Patents

Description

P 1939- c. R. SIBLEY 2,171,607

MANUFACTURE OF GOLF BALLS OR THE LIKE Filed Jan. 28, 1935 3 Sheets-Sheet l Sept 5, 1939. c. R. SIBLEY MANUFACTURE OF GOLF BALLS OR THE LIKE Filed Jan. 28, 1955 3 Sheets-Sheet 2 Sept. 5, 1939. c. R. SlBL-EY 2,171,507

MANUFACTURE OF GOLF BALLS OR THE LIKE Filed Jan. 28, 1955 5 Sheets-Sheet s Figfi w/ w Patented Sept. 5, 1939 UNITED STATES MANUFACTURE OF GOLF BALLS OR THE LIKE Charles R. Sibley, Marblehead, Mass, assignor to Sibley-Pym Corporation, Lynn, Mass, a corporation of Massachusetts Application January 28, 1935, Serial No. 3,773

25 Claims.

This invention relates to the manufacture of cores for golf balls and other wound articles. In one aspect it consists in a novel process of producing a resilient core by a continuous Winding cycle in which thread is laid in different parts of the ball in great circle fashion and in basket weave fashion, In another aspect it consists in a novel machine for carrying out the process of my invention.

In the manufacture of golf balls it has been found that cores may be wound at a high rate of speed when the thread is laid in great circle fashion, that is to say, in courses which correspond substantially to the full or meridian diameter of the core. A number of successful commercial machines operate in this manner. the thread being laid on one full diameter or great circle of the core for one or two turns, and then the axis of rotation of the core being slightl3 shifted so that .the next turns of thread are laid upon another great circle slightly displaced from the preceding turns. The great circle process of Winding is not only advantageous from thestandpoint of high speed of winding but it also lends itself .to winding at relatively high tension, since the thread is thus delivered symmetrically with respect to the core positioning elements and substantially in the plane of maximum driving traction upon the core.

While great circle winding is advantageous in the respects noted, certain manufacturers of golf balls prefer coresin which the elastic thread is laid, at least in the surface windings of the core, in basket weave fashion, that is to say, with I substantial spaces between adjacent turns of the thread. In that style of winding the consecutive turns are spaced from each other and need not all be laid in great circle fashion but may be displaced laterally so as to form turns on the core which are less than the full diameter thereof. The basket weave winding gives to the surface of the core a rougher and more open texture and presents interstices into which the plastic material of the shell may enter in the molding operation. I A somewhat better bond is, therefore, secured between a basket wound core and the molded shell. This appears so desirable that many manufacturers divide the winding opera" tion into two distinct steps, some going so far as to take the partially wound core from a great circle winding machine and present it to a second winding machine for completing or topping the core with thread laid in basket weave fashion. This procedure, of course, adds greatly to the expense of manufacture and necessitates the extra operations of fastening off the end of the great circle wound thread and fastening in the end of the basket Weave wound thread.

I have discovered a process whereby the complete core may be wound by a continuous winding cycle without interruption and from a continuous elastic thread laid first in great circle fashion and then in basket weave fashion. The process of my invention is characterized by rotating a core continuously first at a high rate of speed in a manner for great circle winding, and then at a lower rate of speed in a manner for basket weave Winding, meanwhile delivering elastic thread continuously to the core. In winding the inner portion of the core, I preferably engage the same by members rotatable in fixed axial position, and under these conditions the axis of rotation of the core is shifted gradually and the thread laid in great circle fashion. When the desired predetermined diameter of core has been reached, I impart an additional axial movement to one of the members whichrotate and position the core, thus abruptly shifting the axis of rotation of the core between turns so that the thread is wound thereon in basket weave fashion. I

Various mechanisms may be employed for carrying out the process of my invention. For purposes of illustration I have herein disclosed a machine in which the core is first rotated and positioned by three members rotatable in fixed axial position, one of said members being adapted to be automatically oscillated in axial movement when it is desired to lay the elastic thread in basket weave fashion. It will be understood that the specific winding machine herein selected for illustration is merely for the purpose of exemplifying one manner in which the process of my invention may be carried out, and that my invention contemplates the continuous winding first in great circle fashion and then in basket weave fashion, or vice versa, by any mechanism suitable fo these two functions.

In the accompanying drawings Fig. 1 is a view in side elevation of a machine adapted for carrying out my novel process;

Fig. 2 is a view in perspective of the machine as seen from the rear, with the motor parts omitted;

Fig. 3 is a fragmentary View of the core positioning and rotating parts of the machine;

Fig. 4 is a view in side elevation, partly in section and on an enlarged scale, of the rear part of the machine;

Fig. 5 is a view in elevation and on a still larger scale showing a great-circle-wound core in its position in the machine; and

Fig. 6 is a similar view of a basket-Weave wound core.

The machine herein illustrated is in some aspects based upon that disclosed in United States Letters Patent No. 2,033,356 granted March 10, 1936, and for details of construction not herein shown reference may be had to that application.

the cylindrical end of a square shaft [2, and a driven roll it. The square shaft I2 is mounted for horizontal reciprocation,inbearings formed in the panel ll and the driven roll I5 is fast to the forward end of a rotary shaft 39 journaled in bearings provided in the panel l l. The driven roll i5 is concave in contourand the roll I3 is herein shown as being straight sided. Over the two rolls is stretched an endless flexible apron l6, which may be of suitable rubber composition and which serves both to provide a cradle for holding the core 28 and to impart rotation thereto in the winding operation. The apron or band l3 also rotates the roll l3 at all times, both while reciprocating axially and while rotating on a fixed axis.

The core 28 isheld firmly in place upon the apron i6 and its supporting rolls by a detector disk l'l having a'convex rim and being mounted for free rotation upon a stud projecting from the end of an arm is. The arm extends transversely across the front of the panel If and is secured at its other end to the forward end of the horizontal shaft at which is journaled in the panel H. To the rear end of the shaft 20 is secured a transverse arm 2i which extends across the rear face of the panel ll and carries an adjustable weight 22. The arm 2| projects forwardly at its free end in an extension 85, which will presentl'y be referred to. The weight 22 insures firm engagement of the detector disk I! upon the core 28 throughout the winding operation.

Elastic thread 25 to be wound upon the core is supplied from a reel or spool 26 rotatably mounted in a yoke-shaped bracket 21 supported above thepanel H. Thread 25 is led from the supply spool 26 "to tension mechanism, not herein shown since it forms no part of the present invention, and then over a guide roll 29 to the core 28, as shown in Fig. 3. As the core 28 is rotated and thread 25 supplied thereto, the detector disk I! reacts with the last wound turns of thread to displace the core and cause it to remain always spherical in shape, the threadbeing laid upon the core in great circle fashion. Traction for rotating the core is supplied directly by the flexible apron 23 which cradles the core, as shown in Figs. 5- and 6, although the core is actually supported in position by the driven roll I5 and the idle roll l3.

The machine is driven by a motor 30 supported upontherear portion of the frame I0 and provided with a shaft 3i carrying a universal joint 32 at its outer end. The forward end of the universal joint 32 is connected to the rear end of a shaft 33, best shown in Fig. 4, which is jourdriven roller i5, and interposed between these two aligned shafts 33' and 39 is a short intermediate shaft 36 journaled in ball bearings 31 and supported at its rear end by a smaller set of ball bearings which are received within a sleeve 43 keyed to the forward end of the shaft 33".

The 'motor""30" may rotate at relatively high speed, for example 3500B. P. M.', and the shaft 33,-according-ly, is rotated always at this rate of speed. The intermediate shaft 36 'may be driven at the full motor speeddirectly from the shaft 33 or it may be driven through reducing gear mechanism at a much slowerrate of speed, for example 600 R. P. M. The machine is so organized as to drive the intermediate shaft 36 at high speed while the core 28 is being wound in great circle fashion, and to drive the intermediate shaft 316 at low speed through the reducing gear mechanism when the core 28 is being wound in basket weave fashion.

The driving mechanism between the shafts 33 and 33 will now be described. As already stated, the shaft 33 carries at its forward end a sleeve or collar d3 which is .keyed thereon. Keyed to the sleeve 63 for longitudinal movement thereon is a clutch member 42 having concave clutch surfaces upon both faces. 'The outer face of the clutch member 62 is arranged to cooperate with a clutch cone 44 fast upon the rear end of the shaft 36. The rear face of the clutch member 42 is arrangedto cooperate. with a clutch cone ll which is fast with a pinion 43 upon a sleeve journaled to rotate freely upon the shaft 33. Accordingly, when the clutch member 32 is shifted toward the rear, as shown in Fig. 4, it engages with the clutch cone H and acts to drive the pinion lilat the speed of the shaft 33. While so engaged, the clutch cone 44 is free so that there is no direct driving connection between the shafts 33 and 36.

The pinion ll! is arrangedto mesh at all times with a large gear 5i! fast upon a shaft journaled to rotate freely in bearings 51 carried by an adjustable bracket 53 which is bolted to the bracket 35 of the frame. On the same shaft with the gear Ellis a smaller gear 52. which meshes at all times with a gear 5 fast upon the rear end of a horizontal shaft 35 journaled in bearings 56 formed in the bracket 38 and carrying at its forward end another gear 51. The gear 51 is arranged to mesh with a pinion 33 which is keyed together with a clutch cone 66 upon a sleeve 59 arranged to rotate freely upon the shaft 36. The clutch cone 66 is arranged to cooperate with asliding clutch member 6| keyed to the shaft 36 for longitudinal movement thereon and arranged to transmit rotation of the pinion 58 to the shaft 38. when moved rearwardly, as shown in Fig. 4.

The clutch members 42 and 6| are arranged to be shifted simultaneously by shipping mechanism which will now be described. The clutch member 32 is circumferentially grooved to receive a shipper shoe 62 and the clutch member 6i is correspondingly groovedto receive a shipper shoe 63. These shoes extend circumferentially in the grooves of the clutch members. and are connected by a yoke-shaped carrier 64 which is supported in position between the arms of a forked shipper lever 65 pivotally mounted upon a fulcrum pin 36 in the bracket 38. At its lower end the shipper lever 65 is connected through an adjustable link 63 to a downwardly extending arm 69 loose to a transverse shaft Ill journaled in the machine frame. The shaft 16 also carries a forwardly extending handle H, by which the operator may control the position of the shipper lever 65 in certain respects. A tension spring fi secured to the lower end of the shipper lever tends always to swing the lever in a counterclockwise direction, as seen in Fig. 1, and to shift the clutch members 42 and 61 into the position shown in Fig. 4, that is to say, to render the reducing gear mechanism effective. Under these conditions it will be seen that the shaft 36 is driven at reduced speed by the clutch cone 60,

this in turn being rotated by the gear train 7 585I-54-52- 50-40. The gear train in turn is rotated by the clutch cone 4| set in motion by the clutch member 62. On the contrary, when the shipper lever 65 is rocked in a clockwise direction against the tension of the spring 72, the clutch cones t2 and 6?) are disengaged and the shaft 3'5 is rotated directly at high speed by the engagement of the clutch member 42 with the clutch cone M.

The arm I59 above referred to carries a downwardly extending spring blade 13 having at its lower end a hardened wear piece I4. This is arranged to cooperate with a latch block I5 adjustably secured to a latch lever 76 mounted to rock about a fulcrum pin 11 which is carried by a standard projecting from the base of the machine frame. A tension spring 18 is connected to the rear end of the latch lever I6 and tends always to rock it in a clockwise direction. The upper end of the spring I3 is secured to an eye carried by the adjustable link 58. A downwardly extending T-shaped arm 9!] is secured to the shaft '59. Its rearwardly extending branch is connected to the forward end of the latch lever it by means of a slotted link 9| and its forward end is located in line with the wear piece 74. Consequently, when the handle 'II is depressed, the arm $39 is swung in a clockwise direction and the shipper lever 65 is rocked in a clockwise direction by the link 58 against the tension of the spring it. When the wear piece 14 has been carried behind the rear upper edge of the latch block to, the latch lever snaps upwardly under the actuation of the spring 78 and the shipper lever i5 is thus latched in high speed position, that is to say, with the clutch member 42 engaged with the clutch cone it and the clutch member ti disengaged from the clutch cone 5%. Under these conditions the winding operation proceeds at high speed in great circle fashion, laying the turns of elastic thread in the manner indicated in Fig. 5.

The depression of the handle II is effected by th operator preliminarily to starting the machine and after the mechanism has been once organized to operate in this manner it continues until the latch is tripped either manually at the option of the operator or automatically when the core reached a predetermined diameter. The latch may be tripped manually at any time by iifting the handle "it, and when this occurs the latch lever it is rocked in a counterclockwise direction by the link ill It will be apparent that the slot in the link 9i permits the arm 9!! to be moved rearwardly sufficiently to cause latching engagement between the wear piece '54 and the latch block 75 without affecting the position of the latch lever or in any way preventing it from snapping upwardly in effecting the latching operation.

The latch may be tripped automatically by mechanism which will now be described. The forward end of the latch lever 16 is connected to the lower end of a long vertically-disposed link it and the latter is connected at its upper end to a forwardly-extending arm 8@ of a yoke member arranged to rock about a transverse shaft 85 which is supported by a lug extending rearwardly from the panel I I, as shown in Fig. 2. The other arm 82 of the yoke carries an adjustable stop member 83 which extends a variable distance beneath the arm 82 and in alignment with a forward extension 85 at the free end of the lever 2i. The level 2|, as already explained, carries an adjustable counterweight 22 and tends always to move downwardly to a position determined by the engagement of the detector disk I! with the core being wound. The initial position of the arm 82, and consequently of the link i9, is determined by an adjustable stop screw 841 which projects downwardly from the arm 82 and engages the portion of the machine frame which carries the fulcrum pin 8|.

From the foregoing description it will be clear that as the diameter of the core increases and the arm 59 is rocked upwardly carrying with it the arm 2%, the extension 85 of this arm will engage the stop member 83, rocking the yoke in a counterclockwise direction, lifting the link 19 and rocking the latch lever I6 downwardly at its rear end so as to disengage the latch block I5 from the wear piece I4 and thus permit the spring "52 to shift the speed reducing mechanism to its low speed condition.

Whenever the machine is shifted from high to low speed operation, mechanism for oscillating the square shaft I2 and the idle roll I3 is thrown into action. This mechanism will now be described. The shaft I2 is connected at its rear end to an oscillatory arm 92 slotted at its lower end to receive a fulcrum pin 93. The fulcrum pin is carried by an adjustable arm 94 which is slotted and clamped to the machine frame. The amplitude of movement of the arm 92 may be varied and adjusted by shifting the position of the arm 94 and the fulcrum pin 93. The oscillatory arm 92 is connected through an adjustable link 95 to the free end of a cam lever 9% which is pivotally supported at a point (not shown) behind the shaft 22, as seen in Fig. 3, and is provided with a cam roll 9? arranged to run in the track of a cam 98 loosely mounted on the forward end of the shaft 55.

A toothed clutch is provided for engaging and disengaging the cam 98 with respect to the shaft 55. To this end the forward face of the cam is provided with teeth Ififi arranged to interlock with corresponding teeth of a member ltI keyed to the shaft I05 but free to move longitudinally thereon. The member IilI is provided with a circumferential groove to receive the pins of a horizontally moving shipper yoke I522. The shipper member I52 has a pin and slot connection with a vertically-extending arm I83 which is pivotally supported at its upper end upon the pivot shaft 8 I, already described, and has a yokeshaped portion through which passes the shaft 39. A forwardly-extending tension spring HM connected to the lower end of the arm I83 tends always to swing it forwardly and through the shipper I82 to disengage the clutch IQD-Ifil.

A self-contained clutch I66 is interposed between the shaft 36 of the driving mechanism of the machine and the shaft 39 which operates the instrumentalities of the machine handling the core. The clutch I66 is not herein shown in full detail since it corresponds to that fully disclosed in said Letters Patent No. 2,033,356. The clutch I 06 is normally disengaged and is engaged by movement of the sleeve Ii]? under the actuation of the arm Hi3, which is provided with pins I538 for connection with a groove in the sleeve I ill. When the arm I 33 is rocked rearwardly, both the clutch I06 and the clutch llllliil are engaged. Accordingly, the core being wound is set in rotation and an operative connection is established between the low speed mechanism and the connections for oscillating the square shaft I2. If the slow speed mechanism has been thrown into operation, the shaft I2 is reciprocated and osciliii latory'm'ov'ement'imparte'd to the core in addition to its'rotary'movement. If, however, the driving mechanism is operating at high speed, the shaft oscillating mechanism still remains at rest.

The arm' I03 is connected through a rod I09 to a'starting button. I05 located within convenient reach of the operator, who may start the winding operation by pushing the starting button I05 in- Wardly. and rocking the arm I03 rearwardly against the tension of the spring I04. When this occurs, the arm I04 is latched in running position by a latch, notshown, and this in turn may be tripped'whenit desired to stop the machine by depressing astopping button H0. The details of this'mechanism are not herein illustrated since they form no part of the present invention and are fully disclosed in the pending application above identified.

The machine above described has of itself me many novelfeatures of construction but it ex- 75 -weave effects to the surface of the core, The

emplifies only one suitable type of machine for carrying out the novel method of my invention, and it will be understood that widely different mechanism may be employed for carrying out the method. Bearing in mind that the illustrated machine is only one example of what might be used, the method of handling the core therein will be summarized as carried out under commercial conditions. The operator starts with a center, which may be solid rubber or a liquidfilled ball, and upon this makes a few turns of elastic thread 25. He then lifts the detector disk I! and'places the core upon the apron I6 between the rolls I3 and I5, the thread 25 running tothe core 28 from suitable tension mechanism, not herein described. Meanwhile, the motor 30 is running and the handle 'II has been depressed, disengaging the clutch member 42 from the cone 4 I and engaging it with the cone 44, so that the reducing gear mechanism is at rest and the shaft 36 is rotating at high speed. The operator now depresses the starting button I05, clutching the shaft 39 to the high speed shaft 36 and incidentally engaging the clutch I00I 0|, although, as already explained, the shaft 55 is at this time at rest. Immediately upon the engagement of'the clutch I06, the driven roll I5 revolves at 'high speed, driving the apron I6 and rotating the core 28 beneath the detector disk II. Under these conditions, the thread is laid upon the core 28 in great circle fashion, the core being gradually displaced by the reaction of the detector disk with the last wound turns of thread but the successive turns being laid close together at high speed, rapidly building up a. spherical 'core of smooth exterior. As the winding operation progresses and the diameter of the core 28 increases, the detector disk is lifted, carrying with it the arm 2|, which eventually engages the stop member 83 and trips the latch 'I4I5, permitting the spring I2 to throw the reducing gear mechanism into operation and reduce the speed of rotation of the roll I5 from approximately 3600 to 600 R. P. M.

When the shaft 55 of the reducing gear mechanism'starts to rotate, the cam 98 at once becomes effective to oscillate the vertical arm 92 and impart .a" reciprocation to the square shaft I2 and the roll I3 carried thereby. The effect of this movement is to impart a pronounced oscillation to the core 28 in a direction transverse to its direction of rotation, with the result that the successive turns -of elastic thread are laid upon the core witha wide spacing, giving the desired basket closed'in the Letters Patent No. 2,033,356 above j id'entifiedbut is not herein shown. Upon the stopping of the machine, either automatically or by the operator, the completed core may be removed the loose end of thread fastened off and the golf 'ball completely by the application of a I molded shell, as will be well understood.

Having -thus described my invention, what I claim. as new and desire to secure by Letters Patentis:

1; Process o'f manufacturing golf balls or the like by a continuous winding cycle, characterized by the delivery of a continuous elastic thread to a core, rotating {the core at a lngh rate of formperipheral speed in laying the inner turns of thread thereon, reducing the peripheral speed of the core while maintaining it in substantially the same position, and'laying the outer turns of the same thread in basket weave fashion at the reduced winding speed.

12; Process of manufacturing golf balls or the like? bya-continuous winding cycle, characterized by the delivery of a continuous elastic thread to a core rotating first at one speed and then at a different speed, and varying the rate of axial displ'a'cementof the core simultaneously with such changes in speed.

3. Ero'cess of manufacturing golf balls or the like vby a continuous winding cycle, characterized by the delivery of an elastic thread to acore rotating continuously first at high and then at low A Speedaand'icausing pronounced axial displacements of the core to take place after subjecting the core to such change from high speed rotation.

4. Process of manufacturing golf balls or the like by a continuous winding cycle, characterized I are imparted thereto to cause a succession of more abrupt axial displacements of the core being wound.

5. Process of manufacturing golf balls or the like by. a continuous winding cycle, characterized by the delivery of a continuous elastic thread to a core rotating first at high speed under uniform conditions tending circumferentially to displace the core being Wound and then at a lower speed While a succession of circumferential impulses is imparted to the core at a predetermined rate.

'6, Process of manufacturing golf balls or the like by a continuous winding cycle, which consists in .rotatin'g'a corecontinuously, first at a high rate of speed for great'circle winding and then a't a low rate of speed for basket weave winding, and delivering elastic thread continuously to the core throughout the entire cycle.

'7; Process of manufacturing golf balls or the like by a -continuous Winding cycle, which consists in delivering an elastic thread to a core, rotating the core continuously first with a gradual shifting of its axis of rotation whereby the thread is Wound in a great circle manner and then with abrupt 'perio'dic shifting of its axis of rotation whereby the thread is wound in basket weave fashion.

8. Process of manufacturing golf balls or the like by a continuous winding cycle, characterized by the delivery of a continuous elastic thread to a core rotated at high uniform peripheral speed while its axis of rotation is gradually and uniformly displaced, the core being thereafter rotated at lower speed and having its axis of rotation intermittently displaced by external impulses occurring intermittently in opposite directions.

9. A machine for winding golf balls or the like, comprising three core-positioning members arranged to rotate in fixed axial position, and means under the control of the operator for imparting axial movement to one of said members during a portion of the Winding cycle.

10. A machine for winding golf balls or the like, comprising a pair of core-supporting rolls, and automatic mechanism for imparting axial reciprocation to one of them when the core reaches a predetermined diameter.

11. A machine for Winding golf balls or the like, comprising a pair of core-supporting rolls, means for driving one of said rolls first at one speed and then a different speed, and means for imparting an oscillating movement to one roll When such change of speed is eifected and thereafter during the slow speed rotation of the roll.

12. A machine for winding golf balls or the like by a continuous winding cycle, comprising a pair of parallel shafts having rollers located side by side for supporting a core, means for driving one of said rollers at different rates of speed, and means for axially oscillating the other roller during certain periods in the winding cycle, said means being arranged for holding the said other roll against axial movement during certain periods of the winding cycle.

13. A machine for winding golf balls or the like, comprising a pair of parallel shafts having rollers located side by side for supporting a core, two-speed mechanism for driving one roller at either high or low speed, and mechanism for scillating the other roller arranged to be rendered inoperative while the driven roller is rotating at high speed.

14. A machine for winding golf balls or the like, comprising a high speed shaft, low speed driving mechanism, a core-turning roller associated with said shaft and said mechanism, a clutch for engaging or disengaging said shaft and roller, an idle core-supporting roll, and mechanism. for oscillating the same arranged to be thrown into or out of action as said clutch is engaged or disengaged.

15. A machine for winding golf ball cores by a continuous winding cycle, comprising cooperating core-supporting rolls, a rotary shaft carrying one roll, means for driving said shaft at two different speeds, means controlled by the diameter of the core for determining the speed of said shaft, a reciprocatory shaft for the other of said core-supporting rolls, and means for governing the period of reciprocation of said latter shaft in the winding cycle.

16. A machine for winding golf ball cores, comprising a rotary shaft carrying a core-supporting roll, a non-rotary reciprocatory shaft carrying a cooperating core supporting roll, means for driving the rotary shaft at one of two speeds depending upon the diameter of the core in process of being wound, and means for reciprocating said non-rotary shaft only during the rotation of said rotary shaft at its lower speed.

17. A machine for winding cores, having cooperating rotary core-supporting rolls, two-speed mechanism. for rotating one of said rolls at different rates of speed, and means for imparting an endwise reciprocation to one of said rolls arranged to be thrown into or out of action when the speed of said rotary roll is changed from one rate to another and having provision for varying the amplitude of such reciprocation.

18. A machine for winding golf ball cores or the like, comprising instrumentalities for positioning and rotating a core to be wound, driving mechanism for certain of said instrumentalities constructed and arranged to operate them at either of two predetermined rates of speed while the winding operation progresses continuously, and automatic means for effecting such change of speed Without interrupting the operation of the driving mechanism.

19. A machine for winding golf ball cores or the like, having means for supporting and turning the core to be wound comprising a positive 1y driven roll, a roll supported for free rotation, and means for axially reciprocating the freely rotatable roll.

20. A macl'r'ne for winding golf balls or the like, including a driven shaft having a roll fast thereon, a parallel shaft having a roll mounted for free rotation and for longitudinal reciprocation, and an endless band arranged to cradle the core to be wound between the two rolls and to rotate said freely rotatable roll while it is reciprocating,

21. A machine for winding golf balls or the like, including spaced parallel shafts, one having an inwardly concave roll and the other a cylindrical roll, an endless belt driven by said inwardly concave roll and driving said cylindrical roll and cradling the core to be wound between the two, and means for reciprocating said cylindrical roll.

22. A machine for winding golf balls or the like, including spaced horizontal shafts, one being driven and having a roll fast thereon, and the other carrying a longitudinally reciprocating roll mounted thereon for free rotation, and an endless elastic band passing about said rolls and serving both to rotate the reciprocatory roll and to exert traction on a core supported between the rolls.

23. A machine for winding golf balls or the like, comprising a driven shaft having a roll fast thereon, an adjacent shaft carrying an axially reciprocating roll mounted thereon for free rotation, a hold-down roll mounted above and between said rolls, and an endless elastic band passing about the roll on the driven shaft, driving the reciprocating roll and cradling the core to be wound beneath said hold-down roll.

24. A machine for winding golf balls or the like comprising a pair of spaced core-supporting rolls, an endless elastic apron running upon said rolls, and means for imparting to the core-engaging portion of the apron a combined longitudinal and transverse movement.

25. A machine for winding golf balls or the like, comprising a pair of spaced rolls for supporting and rotating a core to be wound, means for driving one of said rolls, a flexible band for driving the other roll from said driven roll, and means for reciprocating said other roll within the band.

CHARLES R. SIBLEY.

Images