JP2018512349A - 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 winding spindle has at least one long projecting chuck (3) for accommodating a plurality of winding tubes, wherein the chuck is supported by a hollow support (11) from a plurality of parts. The drive shaft (7) can be driven, and the rear bearing shaft (7.2) is connected to the drive device. A front bearing shaft (7.1) connected to the rear bearing shaft (7.2) is coupled to the chuck (3), and a hollow cylindrical hollow support body (11) is connected to the chuck (3). It is supported by. The support part has a front rolling bearing (14.1) and a rear rolling bearing (14.2). In order to minimize the load on the bearing shaft due to the rotating bending moment, according to the invention, the front rolling bearing (14.1) is arranged close to the center of gravity (19.1) of the chuck (3). As a support bearing, the entire weight of the chuck is supported.

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 with a clamping device for receiving and fixing the 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 and particularly the weight of the wound package is received via the support portion of the front bearing shaft, and this support portion is formed inside the hollow support. The support portion is composed of a front roller bearing and a rear roller bearing, and the both roller bearings are arranged around the front bearing shaft at a distance from each other.

  On the one hand, the front roller bearing and the rear roller bearing are loaded with each other in order to receive the static load and on the other hand to guarantee the guidance of the drive shaft. Both roller bearings interact to ensure a static load on the chuck and guide the drive shaft. The chuck of such a take-up spindle has a limited outer diameter in order to accommodate a commercially available winding tube, so that the structural space and thus the bearing size of the support portion are also limited. Therefore, the load bearing capacity of the rolling bearing and the strength of the drive shaft are limited.

  At this time, it is basically known to use a rolling bearing that realizes a relatively high load resistance based on its characteristics as much as possible. For example, in a winding spindle known from DE 102009021647 (DE 10 2009 021 647 A1), the bearing shaft is constituted by two ball bearings held against each other under load. It is supported. This certainly allows an increased load capacity with the rolling bearing, however, it does not increase the strength of the drive shaft. Furthermore, the preload in the axial direction of two rolling bearings arranged at different locations requires extremely high manufacturing accuracy and extreme fitting accuracy between each other.

  Therefore, an object of the present invention is to form a winding spindle having a support portion that increases the axial strength and, in turn, the load resistance, in such a winding spindle.

  According to the present invention, this problem is solved by the fact that the front rolling bearing is arranged near the center of gravity of the chuck and supports almost the entire weight of the chuck as a support bearing.

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

  The invention is based on the recognition that the weight of the package in the chuck must be introduced into the support via a coupling point between the chuck and the front bearing shaft. Such lateral movement of weight necessarily results in a bending moment that is the product of force and travel distance. Since the weight acts to fix the space and the bearing shaft rotates, a rotational bending moment is generated that adds a rotational frequency to the bearing shaft. As a result, the greater the weight, for example, with a large number of thick packages, and the greater the travel distance determined by the spacing between the support and the shaft / hub coupling between the chuck and the bearing shaft. The greater the load, the greater the load on the bearing shaft due to the rotating bending moment. In order to minimize this load, according to the present invention, the front rolling bearing is disposed near the center of gravity of the chuck, so that the total weight of the chuck can be received almost as a single supporting bearing.

  A consideration in the position of the support bearing is that the wound package has a package center of gravity at the chuck that does not necessarily match the center of gravity of the empty chuck. Therefore, superposition of the center of gravity of the chuck and the center of gravity of the package results in a total center of gravity. During package winding, the total center of gravity moves from the center of gravity of the chuck toward the center of gravity of the package. Therefore, the support bearing is arranged near the center of gravity of the chuck in order to be able to accept the total load as much as possible. Usually, the position of the support bearing is arranged in a region between the center of gravity of the chuck and the center of gravity of the package. Depending on the length of the chuck and the number of wound packages, the position of the support bearing can be located somewhat outside the region between the center of gravity of the chuck and the center of gravity of the package. Depending on the position of the support bearing near the center of gravity of the chuck, the load on the drive shaft due to the rotational bending moment is limited to the front shaft portion of the front bearing shaft. This increases the strength of the drive shaft as a whole.

  Forming the front rolling bearing as a support bearing enables a completely new bearing concept for the chuck. For example, in a particularly preferred development of the invention, the rear rolling bearing is formed as a guide bearing, which does not apply an axial load to the support bearing. As a result, the support bearing remains unaffected in the axial direction. The function of receiving the load and the function of guiding the front bearing shaft are divided. The guide bearing remains as unloaded as possible and guides the front bearing shaft.

  The support bearing is therefore preferably formed as a cylindrical roller bearing, according to a preferred development of the invention, in order to be able to accept high loads.

  Since the position of the total center of gravity changes during operation, the rotational bending moment at the location of the support bearing cannot be completely eliminated. Thus, in a particularly preferred development of the invention, the inner race of the cylindrical roller bearing is held around the increased shaft step on the front bearing shaft. Due to the increased shaft step in the front bearing shaft, the design strength (Gestaltfestigkeit) of the front bearing shaft can be increased significantly and preferably. In particular, this makes it possible to greatly reduce the risk of so-called “Passungsrost”. Due to the corresponding design of the shaft step at the outer diameter and the transition radius, a high notch stress can be advantageously avoided, resulting in improved strength of the front bearing shaft.

  In a preferred development of the invention in which the bearing shaft can be guided preferably by means of a guide bearing configuration, the guide bearing is formed by two spindle bearings arranged side by side, said spindle bearing being The front combination is held around the front bearing shaft. If comprised in this way, since both axial direction force and radial direction force can be received, a bearing shaft will be guided reliably. Furthermore, this makes it possible to avoid the formation of an internal moment load in the double bearing.

  According to a preferred embodiment of the present invention, the support bearing and the guide bearing are arranged inside the bearing bush, and at this time, a plurality of buffer rings supported by the hollow support body are held around the bearing bush. Has been. If comprised in this way, especially the inclination of the outer race in a support bearing is avoided. Since the support portion is elastically supported with respect to the hollow support via the buffer ring, the bearing shaft can perform relative movement for the purpose of buffering with respect to the hollow support.

  In order to obtain a substantially pre-determined elasticity between the support and the hollow support after installation, irrespective of manufacturing errors, the buffer ring is preferably provided by an inner sleeve and an outer sleeve surrounding the inner sleeve. In this case, the rubber element is disposed between the inner sleeve and the outer sleeve. In this way, the spring characteristic of the rubber element between the inner sleeve and the outer sleeve can be formed with a pre-determined cushioning characteristic already before installation.

  In particular, in a long projecting chuck, an additional buffer bearing is provided in order to strongly buffer the vibration generated when the critical winding speed passes, and this buffer bearing is provided on the front bearing shaft. In the front shaft portion, the shaft portion is displaced in the axial direction with respect to the support bearing and is disposed between the front bearing shaft and the hollow support. At this time, the shock-absorbing bearing may be formed to be particularly soft, whereby the vibration generated when the resonance passes between the rotating bearing shaft and the fixed hollow support body can be buffered.

  At this time, the shock-absorbing bearing is preferably arranged on another shaft step portion of the bearing shaft which is increased between the support bearing and the end of the front bearing shaft which is coupled to the chuck.

  The shock-absorbing bearing is preferably formed by a rolling bearing and a shock-absorbing ring that is supported directly on the outer race of the rolling bearing. The rolling bearing thus forms a pivot point for introducing relative movement into the buffer ring, which extends from the rotating bearing shaft. The rotation of the bearing shaft remains largely unaffected.

  In order to increase the stability, the rolling bearing may be formed by two spindle bearings arranged side by side, both spindle bearings being held around the front bearing shaft in a rear combination. With such a configuration, a relatively high tilting moment can be received.

  In order to improve the stability of the chuck on the one hand and, on the other hand, to achieve as parallel guidance as possible during winding into the package, in a particularly preferred development of the invention, the chuck has its open position. The end portion is supported by a saddle bearing, and the position of the support bearing in the hollow support is moved toward one end of the chuck. The saddle bearing exerts an additional force component at the chuck, which affects the load distribution at the chuck. In order to keep the main load on the support bearing as it is, the position of the support bearing is moved toward the free end of the chuck.

  In order to enhance the buffering action, the saddle bearing is preferably formed by a rolling bearing and a buffering ring that act between the chuck and the hollow support. The dampening ring can preferably be formed with spring strength and dampening strength that allows movement of the chuck relative to the hollow support during full package loading.

  Further, the support portion of the rear bearing shaft is formed inside the bearing bush. At this time, the bearing bush is elastically supported with respect to the hollow support using a plurality of buffer rings. ing. If comprised in this way, the vibration load suitably generate | occur | produced from the drive side and the driven side can be buffered.

  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. By increasing the shaft strength of the drive shaft and the high load resistance of the support portion, the number of packages wound at the same time can be increased and the length of the chuck protruding from the take-up spindle can be increased.

  Next, a winding spindle according to the present invention will be described in detail with respect to some embodiments 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 support part of the front side of embodiment shown in FIG. It is sectional drawing which shows schematically another embodiment of the winding spindle which concerns on this invention. It is sectional drawing which shows schematically another embodiment of the winding spindle which concerns on this invention. 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.

  For reasons of manufacturing technology, the drive shaft 7 is divided into two shaft parts and is formed by a front bearing shaft 7.1 and a rear bearing shaft 7.2. Both bearing shafts 7.1, 7.2 are fixedly connected to each other via a shrinkage bushing 35.

  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 open 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 relative to the fixed hollow support 11. Can be rotated.

  Inside the hollow cylindrical hollow support 11, a front support part 8.1 of the front bearing shaft 7.1 is arranged. In order to describe the front support 8.1, reference is additionally made to FIG. In FIG. 2, a part of the embodiment shown in FIG. Unless specifically referred to one of the drawings, the following description is for both drawings.

  The front support part 8.1 is formed by a front rolling bearing 14.1 and a rear rolling bearing 14.2 arranged at an axial interval. The front rolling bearing 14.1 is arranged near the center of gravity 19.1 of the chuck 3 and is a pure support bearing. The center of gravity 19.1 relates to an empty chuck 3 that does not have a wound package. Accommodation of the wound package in the chuck 3 results in a package center of gravity 19.2 that does not coincide with the position of the center of gravity 19.1 of the empty chuck 3. Therefore, it is necessary to consider the total center of gravity (Gesammtschwerpunkt) generated by the superposition of the center of gravity 19.1 and the package center of gravity 19.2. For example, the total center of gravity is located at the center of gravity 19.1 of the empty chuck 3 at the start of package winding and can then move toward the package center of gravity 19.2 as winding proceeds.

  In order for the total load consisting of the weight of the chuck 3 and the package mass of the wound package to be able to act on the support bearing 14.1, the support bearing 14.1 has a center of gravity 19. 1 and a bearing plane 34 located between the package center of gravity 19.2. The support bearing 14.1 is therefore arranged in the immediate vicinity of the center of gravity 19.1 of the chuck 3.

  The support bearing 14.1 is formed as a cylindrical roller bearing 16. This cylindrical roller bearing 16 is an inner race 16.1 and is arranged on the increased shaft step 18.1 of the front bearing shaft 7.1. At this time, the shaft step portion 18.1 extends over the entire width of the cylindrical roller bearing 16. Transition portions of the shaft step portion 18.1 to the shaft stem (Wellenschaft) 33 of the front bearing shaft 7.1 are rounded on both sides of the cylindrical roller bearing 16. The outer race 16.2 of the cylindrical roller bearing 16 is supported by a bearing bush 12.1 extending parallel to the front bearing shaft 7.1.

  The rear rolling bearing 14.2 is formed as a guide bearing for guiding the front bearing shaft 7.1. The guide bearing 14.2 is formed in this embodiment by two spindle bearings 17.1, 17.2, which are loaded against each other. The spindle bearings 17.1, 17.2 are loaded against each other in a front combination (X-Anodrnung). At this time, the spindle bearings 17.1, 17.2 are arranged directly side by side and are held by the increased shaft step 18.2. A shaft step 18.2 that thickens the bearing shaft 7.1 extends over the width of both spindle bearings 17.1, 17.2. At this time, similarly, one rounded portion is provided in each transition region to the shaft stem 33. The spindle bearings 17.1, 17.2 are supported on the bearing bush 12.1 by their outer races.

  A plurality of buffer rings are provided around the bearing bush 12.1 in order to buffer the vibrations that occur during passage of the critical winding speed and in particular to avoid contact of the chuck 3 around the hollow support 11. It has been. In the present embodiment, two buffer rings 13 are provided, and both buffer rings 13 are respectively disposed on the bearing bush 12.1 and elastically support the bearing bush 12.1 with respect to the hollow support 11. . At this time, in particular, one of the buffer rings 13 is positioned in the vicinity of the shaft / hub coupling portion 15. For this purpose, the bearing bush 12.1 protrudes beyond the support bearing 14.1, so that the buffer ring 13 is displaced in the axial direction with respect to the support bearing 14.1.

  The buffer ring 13 is configured identically and has an inner sleeve 13.2 and an outer sleeve 13.1 surrounding the inner sleeve 13.2 at a distance. A rubber element 13.3 is arranged between the inner sleeve 13.2 and the outer sleeve 13.1. The rubber element 13.3 is fixedly connected to the inner sleeve 13.2 and the outer sleeve 13.1 to form a rubber spring. This allows the inner sleeve 13.2 and the outer sleeve 13.1 to move relative to each other. Since the inner sleeve 13.2 and the outer sleeve 13.1 are preferably made of metal, the rubber element 13.3 is fixed between the inner sleeve 13.2 and the outer sleeve 13.1 by vulcanization. ing. The rubber element 13.3 acting as a rubber spring can be adapted to the mounting location in terms of material and spring properties. Furthermore, since the outer sleeve 13.1 and the inner sleeve 13.2 can be accurately manufactured with a narrow manufacturing error range, unacceptable deformation when mounting the buffer ring 13 is preferably avoided. On the other hand, a slight manufacturing error inside the mounting space does not adversely affect the spring cushioning characteristics of the rubber element 13.3, and the movability of the outer sleeve 13.1 and the inner sleeve 13.2. Can compensate within a certain range.

  As can be seen from the illustration in FIG. 1, the buffer ring 13 is also used for blocking the rear support portion 8.2 of the rear bearing shaft 7.2 from the hollow support body 11. The rear support portion 8.2 is formed by two rolling bearings 20.1 and 20.2 in this embodiment, and the two rolling bearings 20.1 and 20.2 are formed on the rear bearing shaft 7. 2 and the bearing bush 12.2. Two buffer rings 13 are arranged around the bearing bush 12.2. These buffer rings 13 are supported in a hollow cylindrical portion of the hollow support 11 that is held directly on the spindle support 1. At this time, the rear support portion 8.2 is formed at the end of the hollow support 11. The rear bearing shaft 7.2 protrudes outside the hollow support 11 at the drive end, and at this time, the drive end is formed as a coupling end 10. Accordingly, the spindle drive device can be directly connected to the drive shaft 7 via the coupling end 10.

  In order to receive and fix the winding tube, the chuck 3 has a clamping device 4 and a tightening peripheral wall 5 around it. Since the clamping device 4 and the tightening peripheral wall 5 are common in the prior art, further explanation is omitted here. The clamping device 4 and the tightening peripheral wall 5 may be configured, for example, in the embodiment described in International Publication No. 2011/086142 (WO 2011/086142 A1). Therefore, we shall refer to the cited publications here.

  At the time of operation, a plurality of wound tubes are pressed and fitted around the tightening peripheral wall 5 and fixed by the clamp device 4. In each of the winding tubes, the yarn is wound into a package. For this purpose, the chuck 3 is driven via the drive shaft 7 so as to obtain a substantially constant peripheral speed for winding the yarn. The winding speed at which the yarn is wound is in the range of 2000 m / min to 6000 m / min depending on the manufacturing process. In relation to the respective diameter of the package, the chuck must perform a rotational speed range of about 2000 rpm to 22000 rpm. The load generated in the chuck during winding is almost received by the support bearing 14.1. The load is generated by the weight of the chuck 3 including the clamping device 4 and the tightening peripheral wall 5 and the package held around the tightening peripheral wall 5. At this time, the center of gravity 19.1 is located near the bearing plane of the chuck 3, and this bearing plane is indicated by a one-dot chain line in FIG. The support bearing 14.1 is arranged in the bearing plane 34. The total weight is introduced via a shaft / hub coupling 15 between the chuck 3 and the front bearing shaft 7.1. In order to increase the strength of the shaft portion on the front side of the bearing shaft 7.1, another shaft step portion 18.3 for thickening the drive shaft is provided. The shaft step portion 18.3 extends to the shaft / hub coupling portion 15.

  The load and vibration of the chuck 3 are introduced to the free end portion of the front bearing shaft 7.1 through the shaft / hub coupling portion 15. Such a winding spindle has a plurality of critical natural frequencies based on its complex structure, and these critical natural frequencies may cause resonance when they overlap with the excitation frequency. Therefore, the support portion 8.1 is buffered with respect to the hollow support body 11 via the buffer ring 13. Such a so-called critical winding speed can determine the end of the operating range of the winding spindle in relation to an acceptable resonance excess. Therefore, in order to influence the operating range and to expand the operating range, it is necessary to strengthen the buffering action of the front bearing shaft. To that end, FIG. 3 shows a schematic sectional view of another embodiment of the winding spindle according to the invention.

  The embodiment of the take-up spindle in FIG. 3 is substantially identical in structure to the above-described embodiment shown in FIG. 1, so only the differences will be described here, and the rest described above. Shall be referred to.

  In order to ensure reliable driving of the chuck 3 based on the static load of 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, Also in this embodiment, it is formed by the front bearing shaft 7.1 and the rear bearing shaft 7.2. The front bearing shaft 7.1 is coupled to the rear bearing shaft 7.2 via a coupling 9. The coupling 9 preferably has damping means, which can transmit only the torsional moment but not the bending moment, and can buffer the torsional vibration.

  In this embodiment of the winding spindle 2 according to the present invention, an additional buffer means formed as a buffer bearing 21 is arranged correspondingly to the drive shaft 7. The shock-absorbing bearing 21 is arranged on the shaft portion of the front bearing shaft 7.1 outside the front support portion 8.1 and is shifted in the axial direction with respect to the support bearing 14.1. 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 formed by double spindle bearings 22.1, 22.2. The spindle bearings 22.1 and 22.2 are loaded against each other in a so-called rear combination (O-Anordnung). As a result, a preload can be generated between the spindle bearings 22.1 and 22.2, and this preload significantly increases the service life of the bearing. A buffer ring 21.2 is held around the spindle bearings 22.1 and 22.2. The buffer ring 21.2 is identical in structure to the buffer ring 13 of the embodiment shown in FIG. Therefore, reference is made to the description given above.

  The buffer ring 21.2 has a significantly smaller radial strength compared to the buffer ring 13, whereby a soft coupling of the buffer bearing 21 to the hollow support 11 can be obtained. Thereby, the buffer bearing 21 is effective only when resonance occurs around the bearing shaft 7.1.

  The spindle bearings 22.1, 22.2 of the shock-absorbing bearing 21 are arranged on another increased shaft step 18.3 around the bearing shaft 7.1. The shaft step portion 18.3 that thickens the bearing shaft 7.1 extends to the shaft / hub coupling portion 15. At this time, since the maximum rotational bending moment is generated in the shaft / hub coupling portion 15, it is desired to make the bearing shaft 7.1 thick until it reaches the shaft / hub coupling portion 15.

  The winding spindle according to the invention is distinguished by the fact that a very long protruding chuck can be realized, in particular in the state where the nominal diameter of the chuck remains unchanged. Due to the increased load bearing capacity of the front support and the increased strength of the drive shaft, a larger diameter package can be used if the chuck lengths are equal, or more packages if the package weights are equal. It can be wound around the chuck. Therefore, the winding spindle according to the present invention is particularly suitable for winding one yarn group in parallel into a plurality of packages.

  FIG. 4 shows a schematic cross-sectional view of another embodiment of the winding spindle according to the invention. The embodiment of the winding spindle shown in FIG. 4 is substantially the same in structure as the embodiment shown in FIG. 3, so only the differences will be described here and the other points will be described above. Reference should be made to the description.

  In the embodiment of the winding spindle according to the invention shown in FIG. 4, an additional saddle bearing 36 is formed at the open end of the chuck which is arranged corresponding to the spindle support 1. For this purpose, the chuck 3 has an annular collar 37 that is an enlarged diameter portion at the open end. At this time, the flange bearing 36 is formed by the rolling bearing 36.1 and the buffer ring 36.2. The rolling bearing 36.1 is arranged around the hollow support 11. The rolling bearing 36.1 is surrounded by a buffer ring 36.2 supported on an annular collar 37 of the chuck 3. Similarly, in the present embodiment, the buffer ring 36.2 is formed by two metal sleeves that sandwich the rubber element therebetween.

  The saddle bearing 36 improves the stability of the chuck 3 especially when the package is wound. Further, the buffer ring 36.2 has a characteristic that enables the hollow support 11 to be lowered even when a load is applied to the chuck 3 by the wound package, and on the other hand, a characteristic that guarantees a buffering action. doing. By the saddle bearing 36, an additional force component that affects the load distribution in the chuck 3 acts on the chuck 3. This is associated with a load shift (Lastverschiebung) which affects the position of the support bearing 14.1 on the front bearing shaft 7.1. In order to leave the main load on the support bearing 14.1, it is necessary to shift the position of the support bearing 14.1 towards the free end of the chuck 3. Therefore, in the embodiment shown in FIG. 4, the support bearing 14.1 is arranged corresponding to the end of the bearing bush 12.1. From a direct comparison of the winding spindle with the embodiment shown in FIG. 3, it is possible to recognize the change in position of the support bearing 14.1 based on the saddle bearing 36. All other members are identically formed in the embodiment shown in FIGS. 3 and 4 of the winding spindle.

  FIG. 5 schematically shows another embodiment of the winder according to the invention. The winding machine has two winding spindles 2.1, 2.2 that protrude long, and both winding spindles 2.1, 2.2 are held on a spindle support 1, It has one protruding chuck 3. 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. Two spindle motors 26.1, 26.2 are arranged corresponding to the winding spindles 2.1, 2.2. The number of winding units is determined according to the manufacturing process, whether to wind the knitting 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.

  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 (13)

  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 in the body (11), a rear bearing shaft (7.2) is connectable to the drive device, the rear bearing A front bearing shaft (7.1) coupled to the shaft (7.2) is non-rotatably coupled to the chuck (3), and the front bearing shaft (7.1) is In the take-up spindle, which is rotatably supported by a front rolling bearing (14.1) and a rear rolling bearing (14.2) with respect to the support body (11), the front rolling bearing (14 .1) is the center of gravity of the chuck (3) ( 19. A take-up spindle, arranged close to 19.1), which supports substantially the entire weight of the chuck (3) as a support bearing.   The rear rolling bearing (14.2) is formed as a guide bearing, and the guide bearing (14.2) does not apply a load in the axial direction to the support bearing (14.1). The winding spindle according to claim 1.   The take-up spindle according to claim 1 or 2, wherein the support bearing (14.1) is formed as a cylindrical roller bearing (16).   The inner race (16.1) of the cylindrical roller bearing (16) is held around an enlarged shaft step (18.1) in the front bearing shaft (7.1). 3. The winding spindle according to 3.   The guide bearing (14.2) is formed by two spindle bearings (17.1, 17.2) arranged side by side, and the spindle bearings (17.1, 17.2) Winding spindle according to any one of claims 2 to 4, wherein the winding spindle is held in combination around the front bearing shaft (7.1).   The support bearing (14.1) and the guide bearing (14.2) are arranged inside a bearing bush (12.1), and the hollow support is formed around the bearing bush (12.1). The winding spindle according to any one of claims 1 to 5, wherein a plurality of buffer rings (13) supported by (11) are held.   Each of the buffer rings (13) is formed of an inner sleeve (13.2) and an outer sleeve (13.1) surrounding the inner sleeve (13.2) at a distance, The take-up spindle according to claim 6, wherein 13.2) and said outer sleeve (13.1) are elastically coupled to each other by means of a rubber element (13.3).   In the front shaft portion (18.3) of the front bearing shaft (7.1), an additional buffer bearing (21) is displaced in the axial direction with respect to the support bearing (14.1). Winding spindle according to any one of the preceding claims, arranged between a front bearing shaft (7.1) and the hollow support (11).   The buffer bearing (21) has a diameter increased between the support bearing (14.1) and the end of the front bearing shaft (7.1) coupled to the chuck (3). 9. The winding spindle according to claim 8, which is arranged on the shaft step (18.3).   The chuck (3) is supported by a saddle bearing (36) at its open end, and the position of the support bearing (14.1) in the hollow support (11) is the position of the chuck (3). The winding spindle according to any one of claims 1 to 9, wherein the winding spindle is shifted toward the free end.   The saddle bearing (36) is formed by a rolling bearing (36.1) disposed around the hollow support (11) and a buffer ring (36.2) supported by the chuck (3). The take-up spindle according to claim 10.   A support portion (8.2) of the rear bearing shaft (7.2) is formed inside the bearing bush (12.2), and two buffer rings are provided on the bearing bush (12.2). (13) is held, and each of the buffer rings (13) is supported by the bearing bush (12.2) by the inner race (13.2) and the hollow support by the outer race (13.1). Winding spindle according to any one of the preceding claims, supported on a body (11).   A winder that has two winding spindles (2.1, 2.2) held on a spindle support (1) and winds 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 1-12.

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