Patent GB-1095248-A (GB)
Title: Thread winding machine
IPC: B65H54/40
Filed: 1965-01-14
Abstract: 1,095,248. Winding packages; stop motions; thread tensioning. SOCIETE D'ETUDES ET DE RECHERCHFS DE MATERIEL TEXTILES (SERMATEX). Jan. 14, 1965 [Jan. 16, 1964], No. 1619/65. Headings D1D and D1J. A thread winding machine is so constructed that the main drive shaft drives the package spindle at a constant angular velocity or rotates the package via a friction drive roll in a manner ensuring constant peripheral velocity of the package, there being a rotatable thread traversing device, the spindles of which is coupled to the package spindle such that rotation of one assures the rotation of the other. Constant Peripheral Velocity. In Fig. 1 the package 4 is mounted on a rotatable spindle 6. A drive roller 8 is carried by a support 9, biased by a spring or counterweight, presses the roller 8 against the package 4. The shaft 7 is the main drive shaft and is coupled by a belt 11, to a pulley on the shaft of the roller 8. A belt 12 also transmits power from the shaft 7 to a drum 14 around which the thread 1 passes before being delivered to the thread guide 2. When the package 4 is required to rotate at constant angular velocity the belt 11 is removed so that the drive roller 8 is on longer effective. When the driving of bobbin 4 at a constant peripheral speed can not be satisfactorily produced by roller 8 alone this action may be aided by an additional drive to the shaft 6 via a slipping clutch as described below. Constant Angular Velocity The main drive shaft 7 carries a pinion (16) Fig. 7 (not shown), the pinion (16) meshing with an intermediate pinion (18) that drives a pinion (17) rigid with the spindle 5, (see Fig. 1) of a grooved cam 3 that traverses a thread guide 2. The pinion (17) meshes with drive means coupled to the spindle 6 of the package 4 so that rotation of the shaft 5 causes the spindle 6 to rotate at constant angular velocity. When the package 4 is to be driven by the roller 8, the intermediate pinion (18) is swung away from the pinions (16, 17) on the shafts 7, 5 so that the gear train in Fig. 7 is no longer operative. Under these conditions the belt drive 11 again couples the shaft 7 to the drive roller 8. Conical Bobbins The drive roll 8 is carried by a mounting 22 that can be swung about a bolt 23 to adjust the angular setting of the drive roller 8 should it be desired that a conical bobbin be wound, see Fig. 1. The spindle 6 of the package 4 is carried in a mounting 31 that can pivot about the axis of a pin 32 and be secured in any desired setting by bolts 33, to facilitate the winding of conical packages. The gear train between the spindles 5 and 6 includes a belt drive 26 that is close to the pin 32 so that the pivotal setting of the spindle 6 does not interfere with the drive from spindle 5 to spindle 6. Altering radio between angular speed of package and rate of thread traverse In Fig. 7 (not shown) the idler pinion (24) is mounted on an adjustable arm (28) so that said pinion can be replaced by a different pinion giving a different rate of rotation between the spindles 5 and 6. Presser Roller A presser roller 45, Figs. 1 and 2 is carried by a housing 44 that pivots about the spindle 5 of the cam 3. This pivotal movement is used to stop the machine when the package reaches a predetermined diameter and the mechanisms associated therewith are also used to stop the machine should the thread break or the tension therein exceed a predetermined magnitude. Stop Motions All of the stop motions described hereinafter serve, on operation, to disengage a clutch serving to turn the main drive shaft 7. Clutch Between a common shaft (58), Fig. 8 (not shown), and each main shaft 7 (one shaft 7 for each bobbin) there is a clutch comprising a disc (59) rigid with shaft (58) and a plate (60) mounted on a shaft 7 so as to rotate therewith but be slidable thereon. A spring (61) urges the plate (60) against the disc (59) to receive a drive therefrom, this drive being maintained when no counter pressure is exerted by a clutch disengaging abutment (62). The abutment (62) is moveable by means of a lever (63) mounted on a pivot (64). A spring (65) acts on the lever (63) with a force large enough to counteract the effect of the spring (61) but is prevented from doing so so long as a lever (66) is held in a lowered clutchengaging position by the locking mechanism described hereinafter. Locking Mechanism The lever 66, Fig. 1, is coupled to a vertically moveable slider 69 carrying a finger 70 that can become latched behind a ramp 71 carried by a catch 72. The catch 72 pivots counterclockwise about an axis 73 by spring or counterweight means (not shown). The stop motions to be described acts on this catch 72 to rock it clockwise and thus release the finger 70 and so permit the spring (65) to rock the lever 66 upwardly and, at the same time, disengage the clutch drive to the shaft 7. Package Size. Indicating. Stop Motions As the package 4 increases in size the housing 44 rocks clockwise, Fig. 1. The housing 44 carries a scale 77 and a stop 75 settable at any desired position on said scale 77 according to the size of the package desired. As the package grows in diameter the stop 75 eventually strikes the catch 72 to cause it to move away from the finger 70. This causes the clutch drive of the shaft 77 to be broken in the manner already stated and the winding motion then stops. Thread Breakage. Stop Motion The thread 1, Fig. 1, passes from the drum 14 to a roller 80 in a manner keeping a rod 78 in an elevated setting. If the thread breaks the rod 78 pivots downwardly about pivot 79 to strike a wheel 82 at the upper end of the catch 72. This causes the catch 72 to release the finger 70 and so commit the clutch drive to the main shaft 7 to be broken and so cause the winding operations to stop. Thread Tension. Stop Motion The thread 1 passes over a roller (86) carried by a pivoted arm (85), Fig. 8 (not shown) and if the tension in the thread exceeds a predetermined value said tension rocks the arm (85) to cause a rod (87) coupled to a projection 88 on the catch 72, to rise. The resulting upward movement of the projection 88 rocks the catch 72 clockwise to release the finger 70 and so permit the clutch drive to the shaft 7 to be broken. Package Shape Fig. 2 shows a slider 36 on shanks 37, the slider 36 being reciprocated by a groove 34, on a rotating cam 3. One arm of the bell-crank lever 39 carries a thread guide 2 and the other arm carries a pivotally mounted shoe 41 guided by a slideway 42 that can be angularly adjusted, about a pivot 43, in a plane parallel to the plain containing the shanks 37. The slideway 42 has a finger 47 that extends into a cam slot of a cam 46. The shape of the slot may be of any desired configuration and the setting of the cam 46 is adjustable. The arrangement is such that if the slideway 42 is parallel to the shanks 37, then the path followed by the thread guide 2 is precisely the same length as that followed by the slider 36. If the slideway 42 is moved counter-clockwise about the pivot 43 in Fig. 2 then the length of the path travelled by the guide 2 is less than that of the slider 36 and a bobbin, having conical ends is then wound. By suitably shaping the cam 46, the angular setting of the slideway 42 is continually varied, as the housing 44 rises with increasing package diameter, to give package ends that are of curved cross-section. The cam 46 is detachable to permit the use of other cam configurations. Ribbon Winding Preventing The cam 46 may be mounted on a plate 52, Fig. 1, that is continually oscillated by a rod 56. This continual oscillation is transmitted to the slideway 42 and, as a result, the length of the path traversed by the guide 2 is varied in a manner preventing the formation of hard projections along the edge of the thread body and to prevent the appearance of uneven zones on the bobbin where overlapping of the thread turns are concentrated. Drum Drive Assisted by Slipping Clutch Drive When a constant peripheral speed of the package 4 can not be satisfactorily produced by roller 8 alone this action is aided by a slipping clutch drive acting on the package spindle. Such a drive can be effected by introducing a friction torque limiter into the boibbin driving mechanism. The torque limiter could replace the pinion (18) of the arrangement described with reference to Fig. 7 (not shown). One form of such limiter is shown in Figs.. 9 and 10 (not shown) and comprises a pair of pinions (18a and 18b) rotatable independantly of one another on the same pivot (89). A washer (19) is mounted so as to rotate with pinions (18a) and slide axially on surfaces parallel to pivot (89). This washer is urged by springs (92) against the bottom of pinion (18b). With pinion (18a) positively engaging driving pinion (16), which is mounted for rotaton with shaft 7, and pinion (18b) positively engaging pinion 17 of spindle 5, the friction existing between pinions (18a) and (18b) is determined in such a way that the velocity difference existing between that created by the axial bobbin drive and the peripheral bobbin drive is absorbed by slippage between these two pinions. When it is desired to drive the bobbin 4 only through its spindle 6, while completely removing the peripheral drive action of the roller 8, it is only necessary to replace pinions (18a) and (18b) by a single pinion (18). Instead of making pinions (18a) and (18b) removeable they may be permanently mounted and provided with any well-known blocking means which cause the two pinions to rotate in unison.