DE2252644A1 - SPINDLE ARRANGEMENT FOR A SPINNING MACHINE - Google Patents

Description

Applicant: Whitin Machine Works, Inc., PO Box 1889, Charlotte, North Carolina, USA

Spindle arrangement for a pre-cutting press

The invention relates to a spindle arrangement for a roving machine, especially for a wing spinning machine.

Spinning machines generally contain a number of identically designed stations, in which the drafting system delivered tape is fixed and twisted in wing spinning machines and wound there on a reel. The wing device is usually arranged on a spindle shaft. One that limits the working speed of a spinning machine The factor is the speed of the spindle arrangement. Although it is common practice to precisely balance the flights! Facilities and carry out the assigned spindle shafts, vibrations of the spindle assembly occur at higher speeds. Such vibrations can lead to fatigue and the failure of certain parts, which increases costs cannot be compensated for by the increased speed. The reason for these vibrations is, in certain cases, the result

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ORIGINAL INSPECTED

a state of resonance in the spindle assembly when a driving force corresponds approximately to a natural frequency of the arrangement.

In a known spindle machine of this type, the spindle arrangement contains a relatively long spindle shaft, which carries the wing device at the upper end. The shaft has radial bearings that are separated from one another in the axial direction stored. The bearing closest to the wing is arranged in a stable support tube so that it can be displaced along the axis to allow the spindle shaft relative to the main frame, while the other bearing is fixedly provided on the main frame is. With this arrangement, the unsupported length of the spindle shaft must be at least as long as the displacement distance of the carrier when the carrier is in its lowest position. Because of the limited shaft bearings, the leeway and the associated geometries, the stiffness of these links is limited. Therefore, at a resonance state the oscillation amplitude become too large.

Furthermore, such a resonance can occur at speeds that are slightly greater than or equal to the highest speeds such machines are. The production speed is therefore limited in known machines that below a critical speed must be worked.

It is therefore the object of the invention to provide an elastic support device for the individual locker arrangements of a Specify spinning machine through which the spindle assembly vibrates too much even at relatively high spindle speeds be avoided. According to the invention, the rate of deflection or the rigidity of the support device is selected so that that the natural frequency of the spindle assembly is considerable is less than the frequency rate of variable forces exerted on the spindle assembly when a drive is on economically expedient speeds takes place.

In the preferred embodiment, the support means includes an elastic bushing in the radial direction

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attack at a base end of a support tube. Deformation of the socket enables the upper free end of the support tube to be pivoted laterally. A spindle shaft held in a bearing at one end in the radial direction extends up through the support tube, where it is in
a radial bearing is mounted in the free end of the support tube. The elastic bushing supports the spindle shaft by resisting deflection of the support tube. In this preferred embodiment, the length of the support tube serves as a lever for the bushing in order to reduce its deflection or spring constant and to ensure a more linear and predictable deflection for small displacements of the lockers, such as He.

In particular, a device is provided in order to exert an adjustable preload on the elastic bushing of the support device and to achieve optimum rigidity. The adjusting device can consist of an adjustable nut
consist, which is arranged at one end of the socket to compress the socket in a support arm.

According to a further feature of the invention is a
Stabilization unit provided to increase the stability of the spindle arrangement by damping secondary vibrations,
which result from the relative softness of the support device. The stabilizing unit contains a friction pad, which
surrounds the spindle shaft and dampens its vibrations by frictional engagement with the surfaces attached to the frame of the machine.

The invention is to be explained in more detail with the aid of the drawing. Show it:

Fig. 1 shows a partially sectioned wing spinning machine with a spindle arrangement according to the invention?

Fig. 2 is a perspective view of the axle beam
in a spindle arrangement according to the invention, of which
Wearer the top has broken away;

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Fig. 3 is a sectional view taken along line 3-3 in Fig. 2; and

4 shows an enlarged partial section through a spindle arrangement according to the invention with a rather elastic support device.

Fig. 1 shows a wing spinning machine 10, the one station a roving machine. A support arm 11 holds in place vertically arranged support tube 12, as will be explained in more detail later shall be. The support tube 12 supports a spool 13 and a spindle shaft 14. A wing 16 is at the top the vane shaft 14 is arranged. A roving machine usually includes a number of such wing spinning machines 10, the are arranged in one or more rows.

The support arm 11 is rigidly attached to a frame rail 17. The frame rail 17 can be common to all wing spinning machines the entire roving machine be provided. The rail 17 is arranged on a running frame, not shown, so that the rail 17 is reciprocable relative to a stationary frame member 15 of the machine. Like on As can best be seen from FIGS. 3 and 4, the support arm 11 has a cylindrical bore 19 which extends in a vertical direction Direction extends through its unsupported outer end. At the lower end, the cylindrical bore 19 ends in a Shoulder 21 which extends radially inward to a smaller cylindrical bore 22 so that the bore 19 is a Counterbore to this smaller bore 22 forms.

The support tube 12 is in the support arm 11 by elastic means in the form of an elastic socket 31, which is arranged in the bore 19. The carrier tube 12 expediently has the shape of an elongated cylindrical Tube with a generally uniform wall thickness. The carrier tube 12 has a groove 26 at its lower end the outer surface. Adjacent to the upper end is the support tube 12 provided with a radial shoulder 27. A sleeve bearing

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28 sits with a snug fit in the upper end of the support tube 12 and abuts against the radial shoulder 27.

The top of the support arm 11 has an end face 33, which runs perpendicular to the bore 19 - A pressure disk 34 arranged on this end face 33 supports a spool gear 36. The spool gear 36 is on the outside of the support tube 12 supported by a sleeve bearing 37 which is seated in the spool gear with a snug fit. The column gear 36 is driven by a larger gear 38, which is driven by a drive of the machine, not shown will. The larger gear 38 is displaced in the vertical direction together with the rail 17. The coil 13 is in is supported in the axial direction on the spool gear 36 and is mounted radially on the outside of the support tube 12. A Pin 39 on the spool gear 36 protrudes into a radial slot 41 on the base of the spool 12 and transmits the rotary motion of the gear 36 onto the spool 12.

The spindle shaft 14 is rotatable about a vertical axis in a bearing 46 at the lower end and in the bearing sleeve 28 of the carrier stored. The lower bearing 46 includes a lower end wall 47 which supports the shaft 14 in the axial direction carries, while the upper part of the bearing 84 supports the shaft radially. This bearing 46 is in a bore 48 a step arm 49 attached. The step arm 49 is rigidly attached to the frame member 17 by a step rail 51 which is provided together with the step arms for the other stations of the machine.

The spindle shaft 14 has a portion 53 with a reduced Diameter. The wing 16 has a hub projection 57 with an inner bore 58 that closely matches the diameter of the Part 53 of the spindle shaft is adapted. A diametrical slot 59 is provided at the upper end of part 53 of the spindle shaft, through which a transverse pin 61 protrudes through the hub 57 to rotate the vane 16 along with the spindle shaft 14 and allow the vane to be removed from the shaft by hand

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ORlQINAL INSPECTED

can be. The spindle shaft 14 is driven by a drive device driven, which engages a drive gear 71, which is connected to a spindle gear 72 on the spindle shaft 14 in Engagement is.

In operation, for example, the tape drawn from a stretching station through a radial opening 66 in the upper end 67 of the hub 57 down through a tubular arm 68 of the wing 16 and through an eyelet 69 of a pressing finger 70 led. The tape is wound on the reel 13 when the reel gear 36 is rotated. The ribbon is twisted at the same time by the rotation of the spindle shaft 14 and the blade 16 in a manner known per se. While this operation moves the rail 17 up and down in a cyclical manner to allow the belt along its entire length the spool 13 is wound up. Therefore, the distance between the bearings 28 and 46, which make up the spindle assembly, changes support in the radial direction. Fig. 1 shows the lowermost layer of the support tube 12, with most of the Spindle shaft 14 is cantilevered over the support tube.

As shown in Figs. 3 and 4, the support tube 12 is elastic in the support arm 11 by the elastic Bush 31 supported. The socket 31 can be made of an elastically deformable material such as rubber or other elastomers exist. Preferably, the bushing is made of Buna N rubber with a durometer hardness of about 60. The bushing 31 is preferably a cylindrical sleeve with a groove 71 running along the outer circumference. In the free state is the inner diameter the bushing 31 is approximately equal to the diameter of the groove 26 on the support tube 12. In a corresponding manner, the free The outer diameter of the bushing 31 is approximately equal to the diameter of the bore 19 in the support arm 11.

The support tube 12 is assembled on a support arm 11, by first pushing the bushing 31 up to the groove 26 of the carrier tube 12 and then the carrier tube together with the Budise is pushed into the bore 19 until the end face 72

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the socket rests against the shoulder 21 of the bore 19. One with an externally threaded nut 74 is slid over the support tube 12 and threaded onto an upper portion of the bore 19 screwed. As shown in Fig. 4, the nut 74 is provided with at least one axial opening 76 for the nut to be able to lift against the elastic bushing 31 with the aid of a tool. ·

The nut 74 can be tightened against the bushing 31 until the axial compression of the bushing 31 is sufficient to be suitable to attack the support tube 12 and to support it until a desired deflection of the socket is achieved. The dressed The state of the socket 31 is shown in FIG. 4 shown. The socket 31 may be slightly deformed by the compression, 'so that the bushing can easily be pulled out of the groove 26 at its axial ends, while the central part is thereby in a radial direction Direction more strongly acts on the carrier tube 12. The vertical load on the support tube 12 is exerted by the bushing 31 supported on the upper shoulder 77 of the groove 26.

Vibration of the spindle shaft 14 and the vane 16 is transmitted via the sleeve bearing 28 and causes the support tube 12 to bend to the side. Ideally, it oscillates the support tube 12 around an imaginary point approximately in the geometric center of the socket 31. Expediently, the smaller cylindrical bore 22 in the support arm 11 and a cylindrical bore 81 in the nut 74 the same diameter, which is selected with regard to the outer diameter * of the support tube 12 in order to avoid the lateral deflection of the To limit the support tube 12. For example, if the lowermost left part of the support tube at the adjacent part of the bore 22 rests and part of the support tube rests on the socket 31 on the adjacent right part of the nut the top of the tube and bearing 28 flex about 6 mm (1/4 inch) laterally from a vertical axis that is determined by the main bore 19 of the support arm II.

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OR5GINAL. INSPECTED

22526Λ4

It can be seen that the support tube 12 on the elastic bushing 31 as a lever in the transmission of vibrational forces to the sleeve bearing 28 from the spindle shaft 14 at the upper end of the support tube 12 acts. This arrangement reduces the effective stiffness of the bushing 31 and keeps the amount of deformation that is required in the bushing for a relative minimum large deflection of the upper free end of the support tube 12 is required, so that the deflection or the caused by the bushing 31 spring constant is relatively low, which is transmitted to the sleeve bearing 28. It is can also be seen that because of the proximity of the spool gear 36 to the imaginary pivot point in the geometric center of the Bushing 31 aligns the spool gear 36 with the drive gear 38 remains, because relatively large lateral deflections of the upper end of the support tube 12, only small displacements of the pipe adjacent to the support arm 11.

A lateral deflection of the support tube 12 enables the spindle shaft 14 and the wing 16 laterally as a unit swing around the lower end of the shaft on end wall 47 of bearing 46. The inner diameter of the support tube 12 allows a margin for a lateral deflection of the shaft 14, and the shaft supporting bearings 46 and 28 have a slight Game to be able to absorb this lateral movement. The elasticity of the bushing 31 and the lifting effect due to the Length of the support tube 12 lead to a particularly soft storage the spindle shaft 14 and the vane 16. During operation, the spindle arrangement shows a behavior which is approximately analogous the dynamic behavior of a centrifugal pendulum at normal speeds between 900 and 1200 revolutions per minute. Because of the softness or the small spring rate of the resilient bushing, the spindle assembly may have a tendency to Has nutation movements similar to the precession movements of a top. One shown in Fig. 3 in cross section Stabilizer 86 dent for damping this movement.

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The stabilizing device 86 consists of a support arm 87 / a friction pad 88, a compression spring 89, a Friction disk 91 and a housing 92. The support arm 87 is attached to the support arm 11 by a bolt 18. The case 92 is attached to the support arm 87 by screws 90 (Fig. 2). The housing 92 and the spring 89 are dimensioned so that that the spring in the housing 92 is compressed against the friction disk 91 and the friction pad 88. The level of the Friction pad 88 is essentially perpendicular to the ideal vertical axis of rotation of shaft 14. The spindle shaft 14 is inserted through openings 93, 94 and 95 in housing 92, disc 91 and support arm 87. These openings are sufficiently large to allow limited lateral movement of the spindle shaft 14. A central hole 97 in the friction pad 88 is slightly larger than the diameter of the spindle shaft 14 to allow radial play, so that the friction pad 88 is not rotated by the spindle shaft. A lateral movement of the spindle shaft 14 is nevertheless obstructed by the friction pad 88 through engagement between the shaft and the wall of the bore 97. The friction pad 88 is moved radially with the shaft 14 to mechanical To convert energy through the frictional contact between the surface of the support arm 87 and the disc 91.

It was found that impact forces due to irregularities of the teeth of the gears, pitch errors, misalignments or the like with respect to the drive gears 71 and 72 are transmitted to the spindle shaft 14 and cause the assembly of the spindle shaft 14 and the vane 16 to vibrate. The frequency of this on the spindle shaft acting impact forces is proportional to the shaft speed. The natural frequency of the spindle shaft 14 and the blade 16 depends on the generally on the rigidity of the spindle shaft 14 and the support structure in which it is mounted, as well as on the The mass of these links and the mass of other parts of the coil and the fiber material on the spool, which can vibrate with the spindle shaft 14 and the vane 16.

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At other stations of a wing spinning machine or the like, there may be other reasons for the occurrence of vibratory forces on the spindle assembly, sometimes are more significant than those forces that are generated by the drive gears of the spindle. Reasons for Such vibration forces can be in the drive reference assigned to the coil or in an imbalance in the spindle arrangement lie. In such cases, the vibration force generally changes with either magnitude or direction a frequency that is proportional to the speed of the spindle shaft.

It has hitherto been customary to design the support arm 11 and the support tube 12 as a rigid and one-piece unit. this has so far led to an arrangement in which the spindle shaft 14 and the vane 16 vibrate undesirably strong when the Spindle 14 is driven approximately at a resonance speed, which can be, for example, 950 revolutions per minute. At such a speed of rotation, such forces acting on the spindle shaft in known arrangements are caused by resonance amplified and can cause excessive vibrations in the spindle assembly.

By contrast, the invention achieves that the resilient arrangement of the support tube 12 is a relatively causes soft mounting of the spindle shaft 14 and thereby largely the resonance frequency of the spindle arrangement known arrangements reduced. By operating the spindle assembly at a speed at which the vibrations causing forces occur with a frequency that is considerably greater than the natural frequency, these vibration forces are no longer significantly increased, so that the occurring Vibration amplitudes are still acceptable. When practical As an embodiment of the invention, a resonance state resulted for the described elastic arrangement on the spindle shaft 14 at a speed between about 100 and 200 revolutions per minute, so that the spindle with minimal vibration

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functions with a desirable speed of about 1200 revolutions could be driven per minute.

Claims

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Claims (26)

Claims 1 / Spindle arrangement for a roving machine, in particular a wing spinning machine with a spindle shaft and a wing attached to it, with a drive device for the spindle shaft which determines a frequency of a variable force which is proportional to the speed of the spindle and This causes vibrations in the locker arrangement characterized in that the spindle shaft is elastically supported on the machine by a support device, which is a rate of deflection with respect to an effective vibrating associated with the vibrations of the spindle assembly Has mass such that the resulting natural frequency is considerably less than the frequency of the forces causing the vibrations. 2. Spindle arrangement according to claim 1, characterized in that the spindle shaft (14), which on one End carries the wing (16) cantilevered in the support means away from the end during at least part of one Operating period protrudes. 3. Spindle arrangement according to claim 2, characterized in that the support device contains a bearing which is displaceable back and forth along the spindle shaft. 4. Spindle arrangement according to claim 1, characterized in that the support means includes an elongate element which is aligned in the axial direction with the spindle shaft, that a bearing is attached to the element and supports the spindle shaft in the radial direction, and that an elastic member ( 31) supports this element at a point that is at an axial distance from this bearing. 3Ü9818 / 08 62 5. Spindle arrangement according to claim 4, characterized in that that the elastic member (31) supports the element (12) such that it can vibrate. 6. Spindle arrangement according to claim 5, characterized e i c h η e t that the element is a tube (12) arranged concentrically around the spindle shaft (14). 7. Spindle arrangement according to claim 6, characterized in that shows that a tubular coil arrangement (13) is rotatably mounted about the element (12). 8. Spindle arrangement according to claim 7, characterized in that that the coil arrangement has a gear mounted on the tube, which is immediately adjacent to the elastic member is arranged. 9. Spindle arrangement according to claim 8, characterized in that that the tubular element in axial Direction relative to the spindle shaft back and forth displaceable is. 10. Spindle arrangement according to claim 9, characterized in that the spindle shaft on which the wing opposite end is mounted radially stationary on the machine. 11. Spindle arrangement according to claim 1, characterized., that the natural frequency is at least six times smaller than the vibration frequency. 12 «spindle arrangement according to claim 1, g e k e η ηζ e i c h ne t by a support device for supporting the spindle shaft on the machine, which contains a support member with a radial bearing, mounted near one end thereof and pivoting relative to the machine adjacent the other end. 309818/0862 is mounted bar, wherein the spindle shaft is mounted in the radial bearing, and wherein the elastic device is resilient counteracts a pivoting movement of the support member and a radial deflection of the shaft. 13. Spindle arrangement according to claim 12, characterized indicates that the elastic means contains an elastic member, by the deformation of which such Support of the support member is made possible. 14. Spindle arrangement according to claim 13, characterized that the support member is a circular, concentrically arranged around the shaft tube, and that the elastic The member is a cylindrical socket which engages the outer surface of the tube. 15. Spindle assembly according to claim 14, characterized in that the elastic bushing in a rigid Support arm is arranged with a bias. 16. Spindle arrangement according to claim 14, characterized in that that the pipe is arranged in a rigid bore, so that the bore swivels the pipe limited. 17. Spindle arrangement according to claim 12, characterized in that a radially with the shaft when it vibrates movable friction member (88) frictionally engages a stationary friction surface (91) to vibrate the shaft to dampen. 18. Spindle arrangement according to one of the preceding claims, characterized in that a vibration-damping device is arranged on the spindle shaft which contains a friction member which is in a plane 309818/0862 is arranged serikreclvt to an ideal axis of the shaft, that the S; spindle shaft through an opening in this friction member extends that the friction member radially with the shaft at Vibrations is movable that a friction surface is arranged relative to the ideal axis of rotation of the shaft, and that the Friction member is in contact with the friction surface to thereby lateral oscillating movements of the spindle shaft dampen. 19 spindle arrangement according to claim 18, characterized in that it is marked Ichnet that the shaft is rotatable relative to the friction member. 20. Spindle arrangement according to claim 19, characterized that the relative rotation of the shaft with respect to the friction member by a small radial Allowing clearance between the opening and the shaft. 21. Spindle arrangement according to claim 18, characterized in that a tensioned spring is the friction member in contact with the friction surface. 22. Spindle arrangement according to claim 1, characterized in that g e identifier Inet that a first bearing is attached to the machine frame, that the axle support device includes a device on which the coil is supported, and a support tube concentric about the axis of rotation of the Spindle shaft is arranged that a second bearing on the Support arrangement is arranged in one end of the support tube that the axle support device in the direction of the axis the spindle shaft can be moved back and forth so that the spindle shaft is supported in the radial direction in the bearings, while one end protrudes in a cantilevered manner, and that a drive device for driving the spindle shaft and the vane is provided, with a support device for elastic 309818/0882 rule support of the support tube is provided at one end opposite the other end, which bends of the tube at the opposite end, allowing lateral vibrations of the spindle shaft through the support device the tube is counteracted at a rate of deflection in order to lower the natural frequency of the spindle shaft considerably than to maintain the frequency of vibratory forces exerted on the rotating spindle shaft. 23. Spindle arrangement according to claim 22, characterized in that the elastic support means includes a circular elastic bushing which engages radially on the outside of the support tube and in a bore a rigid support arm is arranged. 24. Spindle arrangement according to claim 23, characterized in that the circular bushing is designed as a hollow cylinder and has a circumferential groove. 25. Spindle arrangement according to claim 24, characterized in that an adjustable device is provided for compressing the bushing in the bore, so that the rate of deflection of the bushing is adjustable. 26. Spindle arrangement according to claim 22, characterized in that a damping device is provided counteracts the lateral deflections and movements of the spindle shaft through frictional forces. 3U98 1 8 / 0Ö62 ti Blank page