JP2018512348A - Winding spindle - Google Patents

Abstract

The present invention relates to a winding spindle for winding a yarn in a winding machine. For this purpose, the take-up spindle has a long projecting chuck (3) for accommodating a plurality of packages, which chuck is supported by a hollow support (11) and consists of a multi-part drive shaft (7). ), And the rear bearing shaft (7.2) is connected to the driving device. The front bearing shaft (7.1) connected to the rear bearing shaft is connected to the chuck (3) and supported by the hollow support via the support portion (8.1). At this time, a plurality of buffer rings (13.1, 13.2) act between the support portion and the hollow support. In order to be able to buffer the critical winding speed of the chuck uniformly and strongly, according to the invention, each of the buffering rings comprises an inner sleeve (19) and an outer sleeve ( 18), and the inner sleeve and the outer sleeve are elastically coupled to each other by the rubber element (20).

Description

  The present invention relates to a winding spindle for winding a yarn into a plurality of packages in a winding machine described in the premise of claim 1.

  When a synthetic yarn is produced in a melt spinning process, a plurality of yarns at one spinning position are wound together in a package in parallel. For this purpose, a winder having one winding unit for each yarn is used, which winder has a winding spindle supported on one side in parallel to the winding unit. Since such a winding spindle is arranged to protrude from the spindle support, a package wound around the winding spindle can be removed from the free end of the winding spindle after completion. . Such a winding spindle is known, for example, from German Offenlegungsschrift 19548142 (DE 195 48 142 A1).

  This known winding spindle has a chuck, and a tightening peripheral wall having a clamping device for accommodating a winding tube is arranged around the chuck. The chuck is formed in a hollow cylindrical shape, and has a hub coupled to a drive shaft in one longitudinal portion. The drive shaft is formed of a plurality of parts, and is formed by a rear bearing shaft and a front bearing shaft. At this time, the rear bearing shaft can be connected to the drive device, and the front bearing shaft is , Coupled to the chuck hub. The weight of the chuck is received via the support portion of the front bearing shaft, and this support portion is formed inside the hollow support. The hollow support is fixed to the spindle support so as to protrude in the same manner. At this time, the free end of the hollow support enters the inside of the chuck.

  A consideration when designing such a winding spindle is that a very high yarn travel speed in the range of 2000 to 6000 m / min must be realized when winding the yarn. Based on the complex structure of the winding spindle, several critical natural vibrations must be taken into account that, when overlapped with the excitation frequency, cause an undesirable increase in resonance. This so-called critical winding speed can determine the end of the operating range of the winding spindle in relation to the respective resonance excess. It is therefore common to buffer the vibration characteristics of the winding spindle in order to influence the operating range and to expand the operating range.

  For this purpose, the known take-up spindle is provided with two bearing sleeves arranged in a telescopic manner, both bearing sleeves being isolated from each other and against the hollow support via a plurality of buffer rings. Has been. At this time, an O-ring is used as the buffer ring, and the O-ring has a drawback that the buffer material and the buffer cross section have a relatively rough tolerance. Therefore, in order to avoid the disadvantageous incompressibility of the O-ring, the receiving groove needs to have a correspondingly large tolerance. However, this adversely affects the buffering characteristics of the O-ring. The material of the O-ring is basically designed for the sealing function and not designed for buffering and spring elasticity. Furthermore, double bearing bushes require a relatively large mounting space, which reduces the strength of the hollow support.

  The object of the present invention is thus to make it possible to realize a winding spindle of this type with a very long protruding chuck for a relatively high winding speed, despite the limited outer diameter. Is to form.

  Another object of the present invention is to provide a winding spindle in which the chuck can be used over a plurality of critical winding speeds.

  An object of the present invention is that each of the shock-absorbing rings is formed by an inner sleeve and an outer sleeve that surrounds the inner sleeve with a space therebetween, and the inner sleeve and the outer sleeve are elastically coupled to each other by a rubber element. It is solved by being.

  Preferred developments of the invention are defined by the features and combinations of features of the respective dependent claims.

  The invention stands out because the mounting space is independent of the respective rubber element and is determined only by the diameter of the inner and outer sleeves. Therefore, the spring characteristic of the rubber element between the inner sleeve and the outer sleeve can be formed with a preset shock-absorbing characteristic already before installation. In this way, in particular, it is possible to mount a shock-absorbing ring having a preset preload. Furthermore, the shock-absorbing ring can be combined directly with the support, so that structural weakening due to the receiving groove or due to an additional support part can be avoided.

  Depending on the mounting situation of the support part and the structural configuration, the buffer ring is formed such that the width of the inner sleeve is smaller than, equal to, or larger than the width of the outer sleeve. This configuration can positively affect the mobility of the inner sleeve relative to the outer sleeve and the mobility of the outer sleeve relative to the inner sleeve.

  In order to limit the number of buffer rings required to cushion the support, in a preferred development of the invention, the width of the inner sleeve and / or the width of the outer sleeve is at least 10 mm.

  According to a preferred development of the invention, the support part of the front bearing shaft is preferably formed inside the bearing bush, and in the end regions located on opposite sides of the bearing bush, the buffer ring At least two buffer rings are held, each of which is supported by the inner bushing on the bearing bush and supported by the outer race on the hollow support. If comprised in this way, isolation | separation between a buffer body and a support part is possible. However, the position of the buffer ring in the bearing bush is not limited to the end of the bearing bush. The position of the buffer ring in the bearing bush is determined by mechanical dynamic calculations and design.

  In order to realize a very long protruding chuck, in a preferred development of the invention, an additional offset is arranged between the front bearing shaft and the hollow support, which is axially offset outside the support. A shock-absorbing bearing is provided, which at this time has a significantly smaller radial strength than the shock-absorbing ring of the support. If comprised in this way, a load will not be received substantially depending on a buffer bearing. Due to the flexibility of the shock-absorbing bearing, vibrations that occur exclusively when resonance occurs are directly buffered between the rotating bearing shaft and the fixed hollow support.

  In order to obtain as high an effective buffering effect as possible, in a particularly preferred development of the invention, the buffering bearing is in one shaft part at the end of the support and the front bearing shaft connected to the chuck. It is arranged between the parts. At this time, the positioning of the buffer bearing in the vicinity of the coupling position with respect to the chuck exhibits a high buffering action both at the critical winding speed in the lower range and at the critical winding speed in the upper range.

  The shock-absorbing bearing is preferably formed of a rolling bearing and a shock-absorbing ring, and this shock-absorbing ring is directly supported by the outer race of the rolling bearing. When configured in this way, the rolling bearing forms a pivot point for the buffer ring that extends from the rotating bearing shaft.

  For the case where the mounting space between the bearing shaft and the fixed hollow support is extremely limited, in a variant of the invention that is preferably used, the two rolling rings are correspondingly arranged in the rolling bearing. The two shock-absorbing rings are arranged beside the roller bearing and are supported by the outer race of the roller bearing via a single collar sleeve. If comprised in this way, it will become possible to position a buffer ring near a rolling bearing.

  In yet another embodiment, the rear bearing shaft support is buffered against the hollow support by a plurality of buffer rings of the buffer ring. If comprised in this way, the vibration load generate | occur | produced from the drive side and the driven side can be buffered suitably.

  The winding machine according to the invention is distinguished by the fact that a plurality of winding units can be formed on the projecting winding spindle. Due to the pre-set effective damping characteristics, it is possible to achieve a length-to-diameter ratio of the take-up spindle which is at least 60% higher than the take-up spindle known in the prior art.

  Next, a winding spindle according to the present invention will be described in detail with reference to the accompanying drawings.

1 is a cross-sectional view schematically showing a first embodiment of a winding spindle according to the present invention. It is sectional drawing which shows schematically the buffer ring of embodiment shown in FIG. It is sectional drawing which shows another embodiment of a buffer ring roughly. It is sectional drawing which shows schematically another embodiment of the winding spindle which concerns on this invention. It is a diagram which shows roughly the characteristic line course of the dynamic characteristic value of a winding spindle. It is a figure showing another embodiment of a buffer bearing roughly. It is a figure showing roughly the winding machine concerning the present invention.

  In FIG. 1, a part of a first embodiment of a winding spindle is schematically shown in cross-section. The winding spindle 2 is held on the spindle support 1 by a hollow support 11. In the spindle support 1, the winding spindle 2 has a long protruding chuck 3, and the chuck 3 is formed in a hollow cylindrical shape at both ends. The free end of the chuck 3 is not shown in FIG. 1 since there are no members important to the invention. Usually, the free end of the chuck 3 is closed by a cover.

  The open end of the chuck 3 located on the opposite side facing the spindle support 1 serves to accommodate the drive shaft 7, which is connected to the hub of the chuck 3 by a shaft / hub coupling 15. 6.

  Based on the static load on the chuck 3 that increases with increasing package weight and the dynamic load that increases at the same time due to the unbalance of the package, the drive shaft 7 is a front bearing shaft. 7.1 and a rear bearing shaft 7.2, which are connected to each other via a coupling 9. In this case, a coupling that transmits only the torsional moment but not the bending moment is preferably used. At this time, the coupling 9 has at least a means for buffering the torsion in order to block the front bearing shaft 7.1 from the rear bearing shaft 7.2.

  The front bearing shaft 7.1 is rotatably supported in the hollow support 11 via a front support portion 8.1. For this purpose, the free end of the hollow support 11 enters the inside of the chuck 3. The end of the chuck 3 facing the spindle support 1 surrounds the projecting hollow support 11 with a gap, so that the chuck 3 is relatively positioned relative to the fixed hollow support 11. Can rotate.

  Inside the hollow support 11, a front support part 8.1 of the front bearing shaft 7.1 is arranged. The front support part 8.1 is formed by two rolling bearings 16.1, 16.2 in the present embodiment, and the both rolling bearings are held around the front bearing shaft 7.1 by the inner race. It is supported on the bearing bush 12.1 by an outer race.

  In order to be able to accept a static bearing load on the one hand and on the other hand to avoid contact of the chuck 3 around the hollow support 11 when the critical winding speed is exceeded, the bearing bushing 12.1 A plurality of buffer rings are provided around the periphery. In this embodiment, two buffer rings 13.1, 13.2 are provided, both buffer rings being arranged in the end region of the bearing bush 12.1. At this time, in particular, one of the buffer rings 13.2 is positioned between the front bearing shaft 7.1 and the chuck 3 in the vicinity of the shaft / hub coupling portion 15. For this purpose, the bearing bush 12.1 protrudes beyond the rolling bearing 16.2 so that the shock-absorbing ring 13.2 is displaced in the axial direction with respect to the rolling bearing 16.2.

  The structure of the buffer rings 13.1, 13.2 is the same. To further illustrate this structure, reference is additionally made to FIG.

  FIG. 2 shows a cross-sectional view of one embodiment of the shock-absorbing rings 13.1, 13.2. The buffer ring 13.1 or 13.2 has an inner sleeve 19 and an outer sleeve 18 surrounding the inner sleeve 19 at a distance. A rubber element 20 is disposed between the inner sleeve 19 and the outer sleeve 18. The rubber element 20 is fixedly coupled to the inner sleeve 19 and the outer sleeve 18 to form a rubber spring. As a result, the inner sleeve 19 and the outer sleeve 18 can move relative to each other. Since the inner sleeve 19 and the outer sleeve 18 are preferably made of metal, the rubber element can be fixed between the inner sleeve and the outer sleeve by vulcanization. The rubber element 20 acting as a rubber spring can then be adapted to the mounting location from the material and with respect to the material properties, and can also be adapted to the respective operating conditions occurring at the mounting location. Furthermore, since the outer sleeve 18 and the inner sleeve 19 can be accurately manufactured with a narrow manufacturing error range, unacceptable deformation is preferably avoided when mounting the buffer rings 13.1, 13.2. On the contrary, a small tolerance is within a certain range due to the movability of the outer sleeve 18 and the inner sleeve 19 within the mounting space without adversely affecting the spring cushioning characteristics of the rubber element 20. Can be compensated.

  As shown in FIG. 1, the buffer rings 13.1, 13.2 are each supported around the bearing bush 12.1 via the inner sleeve 19. The outer sleeves 18 of the shock-absorbing rings 13.1, 13.2 are directly supported by the position-fixed hollow support 11. During operation, the relative movement between the front bearing shaft 7.1 excited via the chuck 3 can be introduced directly into the buffer rings 13.1, 13.2 via the bearing shaft 7.1. it can. Based on the various resonances, the relative movement between the bearing shaft 7.1 and the hollow support 11 varies. However, with the preferred configuration of the buffer rings 13.1, 13.2, any type of relative movement is received and buffered in the buffer rings 13.1, 13.2.

  The preferred properties of the shock-absorbing ring are also used to block the rear support part 8.2 of the rear bearing shaft 7.2 from the hollow support 11. Similarly, in the present embodiment, the rear support portion 8.2 is formed by two rolling bearings 17.1, 17.2, and the both rolling bearings include the rear bearing shaft 7.2 and the bearing bush 12. .2 is held between. Around the bearing bush 12.2, two further buffer rings 14.1, 14.2 are arranged. Both buffer rings 14.1, 14.2 are supported by the portion of the hollow support 11 that is held directly on the spindle support 1. At this time, the rear support portion 7.2 is formed at the end of the hollow support 11. At this time, the driving end of the rear bearing shaft 7.2 protrudes out of the hollow support 11, and at this time, the driving end is formed as a coupling end 10. Therefore, the spindle drive device can be directly connected to the drive shaft 7 via the coupling end 10.

  The chuck 3 has a clamping device 4 and fastening means 5 around it for accommodating and fixing the winding tube. The clamping device 4 and the fastening means 5 are generally known in the prior art and will not be further described here. The clamping device 4 and the tightening means 5 may be configured as in the embodiment described in, for example, International Publication No. 2011/086142 (WO 2011/086142 A1). Therefore, we shall refer to the cited publications here.

  The size important for accommodating the winding tube is determined by the nominal diameter D of the tightening wall 5. The nominal diameter D of the tightening peripheral wall 5 is usually the same as the inner diameter of the wound tube, taking into account radial play in the range of 0.5 mm to 1 mm. In connection with the manufacturing process, the inner diameter of the winding tube is preset invariably, so that the tightening peripheral wall 5 of the winding spindle 2 cannot be arbitrarily configured with respect to the outer diameter. The length that can be used to accommodate the winding tube is indicated in FIG. 1 by the nominal length L of the clamping wall 5. Therefore, the nominal length L is the dimension of the protruding length of the chuck 3. The longer the nominal length L of the chuck 3, the greater the number of winding tubes that are simultaneously held around it to accommodate the package.

The use of a buffer ring inside the winding spindle 2 shown in FIG. 1 allows a wide variety of structural forms of the buffer ring in relation to the attachment point and each pivot point used for buffering. FIGS. 2 and 3 show a wide variety of construction forms of the shock-absorbing ring which can be used, for example, as shock-absorbing rings 13.1, 13.2 or as shock-absorbing rings 14.1, 14.2. In the structural form shown in FIG. 2, the inner sleeve 19 is configured with a smaller width than the outer sleeve 18. In FIG. 2, the width of the inner sleeve 19 is indicated by b _I , and the width of the outer sleeve 18 is indicated by the symbol b _A. Therefore, the relationship b _I <b _A is established, and at this time, the rubber element 20 has the width of the inner sleeve 19 at the maximum.

On the other hand, the structure of the buffer ring shown in FIG. 3 has an outer sleeve 18 with a smaller width than the inner sleeve 19. Here, the relationship b _I > b _A is established, and at this time, the rubber element 20 has the width of the outer sleeve 18 at the maximum. As a result, the mobility between the sleeves 18, 19 can be influenced in consideration of the elastic coupling via the rubber element 20. However, the minimum width of the inner sleeve 19 or the outer sleeve 18 is limited based on the static load to be transmitted between the chuck 3 and the hollow support 11. In order to guarantee the functionality of the winding spindle, the width of the inner sleeve or outer sleeve is a minimum of 10 mm, depending on the type of construction. However, at this time, large widths of the inner sleeve 19 and the outer sleeve 18 are avoided in order to maintain the concentration of the pivot point where the motion is introduced. For example, a buffer ring having an inner sleeve width or an outer sleeve width of 50 mm at the maximum is used as the buffer ring inside the winding spindle 2. In the mounting situation, it is possible to use a relatively wide sleeve in order to fix the buffer ring with a stopper. The mobility is assured by the other sleeve, in which case it is possible in principle, that is to say that both sleeves, ie the inner sleeve and the outer sleeve, have equal widths.

  In order to realize a very thin and long projecting chuck 3, FIG. 4 shows another embodiment of the winding spindle according to the invention. In FIG. 4, the drive end of the winding spindle 2 is shown in cross-section.

  The embodiment shown in FIG. 4 is substantially the same as the embodiment shown in FIG. 1, so only the differences will be described here, and the above description will be referred to for other points.

  In the embodiment shown in FIG. 4, an additional buffer means formed as a buffer bearing 21 is arranged on the drive shaft 7. The shock-absorbing bearing 21 is arranged on the shaft portion of the front bearing shaft 7.1 so as to be shifted in the axial direction outside the front support portion 8.1. The buffer bearing 21 is disposed corresponding to the shaft end of the front bearing shaft 7.1 and is held near the shaft / hub coupling portion 15. At this time, the buffer bearing 21 extends between the bearing shaft 7.1 on the front side and the free end portion from which the hollow support 11 protrudes. The buffer bearing 21 has a rolling bearing 21.1 and a buffer ring 21.2 in this embodiment. The rolling bearing 21.1 is held around the front bearing shaft 7.1 in the inner race, and holds the buffer ring 21.2 in the outer race. With this configuration, the buffer ring 21.2 can be disposed between the front bearing shaft 7.1 and the fixed hollow body 11 without preventing the drive shaft 7 from rotating. it can. The buffer ring 21.2 is configured as in the structural form shown in FIGS. However, at this time, the rubber element 20 of the buffer ring 21.2 has a significantly smaller radial strength in order to achieve a soft coupling of the buffer bearing 21. The buffer bearing 21 is positioned so that a load is not applied to the buffer bearing 21 substantially and the buffer bearing 21 is effective only when resonance occurs. Since the buffer bearing 21 is located in the immediate vicinity of the coupling portion between the drive shaft 7 and the chuck 3, it is possible to realize a very effective buffer function that operates over the entire speed range during winding of the yarn. it can.

The influence of the shock-absorbing bearing 21, in particular the influence and use of the shock-absorbing rings 13.1, 13.2 in the region of the front support 8.1 can be indicated in particular by the dynamic characteristic values of the winding spindle 2. This dynamic characteristic value is denoted here by the symbol K. For example, it is known that at the start of an empty winding spindle, the operating range is guided through a plurality of critical winding speeds and is limited by the upper mixed critical winding speed (mischkritische Spulgeschwindigkeit). Resonant excess vibrations occurring in the chuck 3 can no longer be suppressed by existing buffering measures, so that a relatively high winding speed above the critical winding speed is no longer feasible. The dynamic characteristic value of the winding spindle is simplified and represented by the following formula:
K = (v _{spul, max} / 10 ⁵ m / min.) × (L / D) ²
In this equation, the maximum winding speed is indicated by v _{spul, max,} where the maximum winding speed in a winder known in the prior art is the same as the critical winding speed v _kritisch . The symbol D indicates the nominal diameter of the chuck as already described for FIG. The symbol L indicates the nominal length of the chuck that accommodates the wound tube.

  The dynamic characteristic value K then takes into account, in particular, the damping action and vibration characteristics of the chuck, in addition to the complex rotor dynamic correlation. In today's universal designs of such winding spindles, the dynamic characteristic value K is in the range of values 8-10. In this case, the dynamic characteristic value K is related to the maximum allowable winding speed (which is the same as the critical winding speed limiting the winding range in relation to the ratio (L / D) between the nominal length and the nominal diameter ( v) to decide.

  To that end, FIG. 5 is a diagram showing the relationship between the maximum allowable winding speed and the length / diameter ratio L / D of the chuck. In FIG. 5, the maximum allowable winding speed is entered for each ratio value L / D. In this embodiment, the curve for the characteristic value K = 9 forms the normal range of a winding spindle known in the prior art. In the winding spindle according to the invention, this range can be greatly expanded. In the winding spindle according to the invention, a typical value of the characteristic value K is K = 23. The expansion of the operating range in the diagram is indicated by the curve with the value K = 23. In particular, this makes it possible to reliably realize a significantly longer chuck in a state where the nominal diameter D of the chuck remains unchanged. For example, in the melt spinning method, it is known to wind a so-called POY yarn around a package at a winding speed of, for example, 3000 m / min. The conventional winding spindle was limited by the value L / D = 16 with respect to the length-diameter ratio, as can be seen from the diagram of FIG. In the winding spindle according to the invention, it is now possible to use chucks with length-diameter ratios up to L / D = 27. Thus, a much longer chuck can be operated at the same nominal diameter D. For example, even at a relatively high winding speed of 6000 m / min, the length-diameter ratio is further increased from L / D = 12 to L / D = 20. Therefore, the winding spindle according to the present invention has a special feature that the number of winding tubes that can be accommodated, and hence the realization of the winding unit in one winding machine, can be almost doubled compared to a general-purpose winding spindle. Offer a great advantage. The length-to-diameter ratio of the chuck is increased by at least 60% in the winder according to the present invention. The use and positioning of the dampening ring, as well as the matching of the structural types, has a surprisingly important effect in order to influence the operating area of the winding spindle. In the winding spindle that forms the basis of the calculation, a shock-absorbing bearing is additionally incorporated in the front bearing shaft 7.1. The diagram therefore serves to show a possible dynamic improvement of the winding spindle according to the invention.

  For the case where the mounting space between the front bearing shaft 7.1 and the hollow support 11 has an insufficient mounting height when the buffer bearing 21 is inserted, FIG. One embodiment of a possible buffer bearing 21 is schematically shown in cross-section. In the embodiment shown in FIG. 6, a rolling bearing 21.1 is arranged around the front bearing shaft 7.1. In this embodiment, the rolling bearing 21.1 is formed by two spindle bearings 23.1, 23.2, and both spindle bearings 23.1, 23.2 are held in a rear combination. As a result, the support part 8.1 of the front bearing shaft 7.1 is completely unaffected and a reliable guide and positioning of the buffer ring 21.2 is ensured. Two collar sleeves 22.1 and 22.2 are supported on the outer race of the spindle bearings 23.1 and 23.2. Each one collar end on the outside of 23.2 supports one buffer ring 21.2, 21.2 '. The buffer rings 21.2, 21.2 'are configured identically to the embodiment described above on the buffer ring. Therefore, the structural height of the shock-absorbing bearing 21 can be greatly reduced, so that the weakening of the drive shaft 7 and the weakening of the hollow support 11 inside the winding spindle can be avoided.

  FIG. 7 schematically shows an embodiment of a winder according to the present invention. The winding machine has two winding spindles 2.1 and 2.2 that protrude long, and both winding spindles 2.1 and 2.2 are held by a spindle support 1. The spindle support 1 is formed as a winding turret that is rotatably supported by the machine frame 24. The winding spindles 2.1, 2.2 are configured as in one of the embodiments shown in FIG. 1 or FIG.

  In the present embodiment, four winding units 25.1 to 25.4 extend along the winding spindles 2.1 and 2.2, and in these winding units 25.1 to 25.4, Packages 27 are wound in parallel with each other. For this purpose, two spindle motors 26.1, 26.2 are respectively arranged correspondingly to the winding spindles 2.1, 2.2. The number of winding units is determined according to the manufacturing process, whether it is necessary to wind up the weaving yarn or the industrial yarn. The number of winding units is an example in the present embodiment, and in the illustrated variation, it can be used when winding industrial yarn or carpet yarn.

  In the winding units 25.1 to 25.4, the pressure roller 30 and the traverse device 29 are arranged correspondingly. At this time, the traverse device 29 is Each has yarn guide means for reciprocating one of the plurality of yarns. The pressure roller 30 is held by a movable roller support 32. Yarn entry is guided through one head yarn guide 31 that forms the entry portion of the winding units 25.1 to 25.4.

  In order to accommodate a plurality of packages 27, a plurality of winding tubes 28 are fastened side by side on the winding spindles 2.1, 2.2. For this purpose, the take-up spindles 2.1, 2.2 have long protruding chucks, as described in the above-described embodiment shown in FIGS. The effective length L and the nominal diameter D of the chuck are clearly shown in the example of the winding spindle 2.2 shown in FIG.

  The winder according to the present invention is suitable for winding a plurality of freshly extruded yarns in parallel as a single yarn group into a package for all normal melt spinning processes. For example, a synthetic yarn produced in a POY melt spinning process, an FDY melt spinning process, or an IDY melt spinning process can be simultaneously wound on a package in one yarn group having a plurality of yarns. However, the winder is also suitable for winding a plurality of wound yarns into a package for the BCF process.

Claims (11)

  A winding spindle for winding a yarn into a plurality of packages in a winding machine, which has at least one long protruding chuck (3) for accommodating the package, the chuck (3) being a hollow support Driven by a multi-part drive shaft (7) supported by the body (11), a rear bearing shaft is connectable to the drive device, the rear bearing shaft (7.2) A front bearing shaft (7.1) coupled to the chuck (3) is connected to the chuck (3), and a support portion (8.1) of the front bearing shaft (7.1) is connected to the hollow support body. In the take-up spindle supported by a plurality of buffer rings (13.1, 13.2) with respect to (11), the buffer rings (13.1, 13.2) each have an inner sleeve (19) And spacing the inner sleeve (19) A winding, characterized in that it is formed by a surrounding outer sleeve (18), said inner sleeve (19) and said outer sleeve (18) being elastically connected to each other by means of a rubber element (20). Take spindle. The buffer ring (13.1, 13.2) has a width (b _I ) of the inner sleeve (19) smaller than or equal to a width (b _A ) of the outer sleeve (18), The winding spindle according to claim 1, wherein the winding spindle is formed to be large. The buffer ring (13.1, 13.2) is formed such that the width (b _I ) of the inner sleeve (19) and / or the width (b _A ) of the outer sleeve (18) is at least 10 mm. The winding spindle according to claim 1 or 2.   The support portion (8.1) of the front bearing shaft (7.1) is formed inside the bearing bush (12.1), and the bearing bush (12.1) is provided with the buffer ring. Two of the shock-absorbing rings (13.1, 13.2) are held, and each of the shock-absorbing rings (13.1, 13.2) is the inner race (19) and the bearing bush (12.1). The take-up spindle according to any one of claims 1 to 3, wherein the take-up spindle is supported by the outer race (18) and supported by the hollow support (11).   An additional shock-absorbing bearing (21) arranged between the front bearing shaft (7.1) and the hollow support (11) and shifted axially outside the support (8.1). ), And the buffer bearing (21) has a significantly smaller radial strength than the buffer ring (13.1, 13.2) of the support portion (8.1). The take-up spindle according to any one of claims 1 to 4, wherein:   The buffer bearing (21) is an end of the bearing shaft (7.1) coupled to the chuck (3) of the support portion (8.1) and the front bearing shaft (7.1). The take-up spindle according to claim 5, wherein the take-up spindle is disposed between the two parts.   Winding spindle according to claim 5 or 6, wherein the buffer bearing (21) is formed of at least one rolling bearing (21.1) and at least one other buffer ring (21.2).   Two shock-absorbing rings (21.2, 21.2 ′) are arranged corresponding to the rolling bearing (21.1), and the two shock-absorbing rings (21.2, 21.2 ′) Located on the side adjacent to the bearing (21.1) and supported by the outer race of the rolling bearing (21.1) via one collar sleeve (22.1, 2.2.2), respectively. The winding spindle according to claim 7.   The support portion (8.2) of the rear bearing shaft (7.2) is connected to the hollow support body (11) by a plurality of buffer rings (14.1, 14.2) of the buffer rings. The winding spindle according to claim 1, wherein the winding spindle is buffered.   The support portion (8.2) of the rear bearing shaft (7.2) is formed inside the bearing bush (12.2) and is opposite to the bearing bush (12.2). Two shock-absorbing rings (14.1, 14.2) are held in the end region located in the inner race (19), respectively. The take-up spindle according to claim 9, supported by said bearing bush (12.2) and supported by said outer race (18) on said hollow support (11).   A winding machine having two winding spindles (2.1, 2.2) held by a winding turret (1) and winding a plurality of yarns into a package, the winding spindle (2. Winding machine, characterized in that at least one of (1, 2.2) is formed as claimed in claims 1 to 10.

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