JP6761809B2 - Winding spindle - Google Patents

Description

The present invention relates to a take-up spindle that winds a yarn into a plurality of packages in a take-up machine according to the premise of claim 1.

When producing synthetic yarns in the melt spinning process, multiple yarns at one spinning position are wound together in parallel into the package. For this purpose, a take-up machine having one take-up unit for each thread is used, and this take-up machine has a take-up spindle supported on one side in parallel with the take-up unit. Since such a take-up spindle is arranged so as to project to the spindle support, the package wound around the take-up spindle can be removed from the free end of the take-up spindle after completion. .. Such take-up spindles are known, for example, from German Patent Application Publication No. 19548142 (DE 195 48 142 A1).

This known take-up spindle has a chuck, and a tightening peripheral wall equipped with a clamping device for accommodating 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 from 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 in particular the weight of the wound package, is received via a support on the front bearing shaft, which is formed inside the hollow support. The support portion is composed of a front rolling bearing and a rear rolling bearing, and both rolling bearings are arranged around the front bearing shaft at intervals from each other.

On the one hand, in order to receive a static load, and on the other hand, in order to guarantee the guidance of the drive shaft, the front rolling bearing and the rear rolling bearing are mutually loaded. Both rolling bearings interact with each other to ensure the static load of the chuck and the guidance of the drive shaft. Since the outer diameter of such a take-up spindle chuck is limited to accommodate a commercially available winding tube, the structural space and thus the bearing size of the support portion are also limited. Therefore, the load 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 capacity based on its characteristics as much as possible. For example, in a take-up spindle known based on German Patent Application Publication No. 10209021647 (DE 10 2009 021 647 A1), the bearing shafts are held by two ball bearings loaded against each other. It is supported. This certainly allows for the increased load capacity of the rolling bearings, however, it does not increase the strength of the drive shaft. Further, the axial preload of the two rolling bearings located at different locations requires extremely high manufacturing accuracy and extreme mating accuracy with each other.

Therefore, an object of the present invention is to form a take-up spindle having a support portion for increasing the shaft strength and thus the load capacity in such a type of take-up spindle.

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

A preferred development of the present invention is defined by the features and combinations of features of each dependent claim.

The present invention is based on the recognition that the weight of the package in the chuck must be introduced into the support via the coupling point between the chuck and the front bearing shaft. Such lateral movement of weight inevitably produces a bending moment, which is the product of force and distance traveled. Since the weight acts on the space fixation and the bearing shaft rotates, a rotational bending moment that adds a rotational frequency to the bearing shaft is generated. As a result, the greater the weight, for example with a large number of thick packages, and the greater the distance traveled, as determined by the distance between the support and the shaft / hub joint between the chuck and the bearing shaft. The greater the load on the bearing shaft due to the rotational bending moment. In order to minimize this load, according to the present invention, the front rolling bearing is located near the center of gravity of the chuck, which allows it to substantially receive the total weight of the chuck as one support bearing.

A consideration in the position of the support bearings is that the wound package has a package center of gravity in the chuck that does not necessarily match the center of gravity of the empty chuck. Therefore, the 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 the winding of the package, 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 bearings are located near the center of gravity of the chuck so that it can receive the total load as much as possible. The position of the support bearing is usually located in the region between the center of gravity of the chuck and the center of gravity of the package. It is also possible that the position of the support bearing is located somewhat outside the region between the center of gravity of the chuck and the center of gravity of the package, in relation to the length of the chuck and the number of wound packages. Due to 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. As a result, the strength of the drive shaft is increased as a whole.

Forming the front rolling bearing as a support bearing allows for a completely new bearing concept for the chuck. For example, in a particularly preferred development of the present invention, the rear rolling bearing is formed as a guide bearing, which does not apply an axial load to the support bearing. This leaves the support bearing unloaded in the axial direction. The function of receiving the load and the function of guiding the bearing shaft on the front side are separated. The guide bearing remains unloaded as much as possible and guides the front bearing shaft.

Therefore, according to a preferred development of the present invention, the support bearing is preferably formed as a cylindrical roller bearing in order to be able to receive a high load.

Since the position of the total center of gravity changes during operation, the rotational bending moment at the support bearing cannot be completely eliminated. Thus, in a particularly preferred evolution 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 steps in the front bearing shaft, the design strength (Gestaltfestigkeit) of the front bearing shaft can be suitably significantly increased. In particular, this can significantly reduce the risk of so-called Passungsrost. Appropriate design of the shaft steps in the outer diameter and transition radii allows the high notch stress to be suitably avoided, resulting in improved strength of the front bearing shaft.

In a preferred development of the invention in which the bearing shaft can be suitably guided by the configuration of the guide bearing, the guide bearing is formed by two spindle bearings arranged side by side, the spindle bearing , It is held around the front bearing shaft in front combination. With such a configuration, both the axial force and the radial force can be received, so that the bearing shaft is reliably guided. Further, this makes it possible to avoid the formation of an internal moment load in the double bearing.

The support bearing and the guide bearing are arranged inside the bearing bush according to a preferred development of the present invention, at which time a plurality of buffer rings supported by the hollow support are held around the bearing bush. Has been done. With such a configuration, tilting of the outer race, in particular, in the support bearing is avoided. Since the support portion is elastically supported by the hollow support via the buffer ring, the bearing shaft can perform a relative motion for the purpose of cushioning with respect to the hollow support.

After mounting, the cushioning ring is preferably provided by an inner sleeve and an outer sleeve that surrounds the inner sleeve in order to obtain near-predetermined elasticity between the support and the hollow support independent of manufacturing error. It is formed, at which time a rubber element is arranged so as to be surrounded between the inner sleeve and the outer sleeve. In this way, the spring properties of the rubber element between the inner sleeve and the outer sleeve can be formed with pre-determined cushioning properties already prior to mounting.

In particular, in a chuck that protrudes long, an additional buffer bearing is provided in order to strongly buffer the vibration generated when the critical winding speed is passed, and this buffer bearing is provided on the front bearing shaft. In the shaft portion on the front side of the above, the bearing shaft on the front side and the hollow support are arranged so as to be displaced in the axial direction with respect to the support bearing. At this time, the buffer bearing may be formed particularly softly, whereby the vibration generated during the passage of resonance between the rotating bearing shaft and the position-fixed hollow support can be buffered.

At this time, the buffer bearing is preferably arranged in another shaft step portion where the bearing shaft is increased, between the support bearing and the end portion of the front bearing shaft coupled to the chuck.

The buffer bearing is preferably formed by a rolling bearing and a buffer ring directly supported by the outer race of the rolling bearing. The rolling bearing therefore forms a pivoting point in the buffer ring that extends from the rotating bearing shaft to introduce relative motion. The rotation of the bearing shaft remains largely unaffected.

For added stability, the rolling bearings may be formed by two spindle bearings arranged side by side with each other, both spindle bearings being held around the front bearing shaft in a back combination. With such a configuration, a relatively high tilting moment can be received.

In a particularly preferred evolution of the invention, in order to improve the stability of the chuck on the one hand and to achieve as parallel guidance as possible during winding into the package, the chuck is opened. It is supported by a collar bearing at the end, and the position of the support bearing in the hollow support is moved towards one end of the chuck. The collar bearings act on an additional force component in the chuck, which affects the load distribution in the chuck. In order to leave the main load in the support bearing intact, the position of the support bearing is moved towards the free end of the chuck.

In order to enhance the cushioning action, the collar bearing is preferably formed by a rolling bearing and a cushioning ring acting between the chuck and the hollow support. The cushioning ring can preferably be formed with spring strength and cushioning strength such that the chuck can move relative to the hollow support under full package load.

Further, the support portion of the bearing shaft on the rear side is formed inside the bearing bush, and at this time, the bearing bush is elastically supported with respect to the hollow support by using a plurality of cushioning rings. ing. With such a configuration, it is possible to buffer the vibration load preferably generated from the driving side and the driven side.

The winder according to the present invention is particularly outstanding because it can form a plurality of winding units on the protruding winding spindle. By increasing the axial strength of the drive shaft and the high load capacity of the support portion, the number of packages wound at the same time can be increased, and the protruding length of the chuck in the take-up spindle can be extended.

Next, the take-up spindle according to the present invention will be described in detail for some embodiments with reference to the accompanying drawings.

It is sectional drawing which shows 1st Embodiment of the winding spindle which concerns on this invention. FIG. 5 is a cross-sectional view schematically showing a support portion on the front side of the embodiment shown in FIG. It is sectional drawing which shows roughly another embodiment of the winding spindle which concerns on this invention. It is sectional drawing which shows still another Embodiment of the winding spindle which concerns on this invention. It is a figure which shows schematicly the winder which concerns on this invention.

FIG. 1 schematically shows a part of the first embodiment of the take-up spindle in a cross-sectional view. The take-up spindle 2 is held by the hollow support 11 on the spindle support 1. In the spindle support 1, the take-up spindle 2 has a chuck 3 that projects long, 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 because there are no members important to the present invention. Normally, the free end of the chuck 3 is closed by a cover.

An open end of the chuck 3 located on the opposite side of the chuck 3 toward the spindle support 1 acts to accommodate the drive shaft 7, which is the hub of the chuck 3 by the shaft / hub coupling portion 15. It is combined with 6.

For manufacturing technical reasons, the drive shaft 7 is divided into two shaft portions, and is formed by a front bearing shaft 7.1 and a rear bearing shaft 7.2. Both bearing shafts 7.1 and 7.2 are immovably coupled to each other via a shrink bush 35.

The bearing shaft 7.1 on the front side is rotatably supported in the hollow support 11 via the support portion 8.1 on the front side. Therefore, the free end of the hollow support 11 has entered the inside of the chuck 3. Since the open end of the chuck 3 facing the spindle support 1 surrounds the protruding hollow support 11 at intervals, the chuck 3 is relative to the position-fixed hollow support 11. Can be rotated.

Inside the hollow cylindrical hollow support 11, a support portion 8.1 on the front side of the bearing shaft 7.1 on the front side is arranged. Additional reference is made to FIG. 2 to illustrate the front support section 8.1. In FIG. 2, the support portion 8.1 on the front side is shown by enlarging a part of the embodiment shown in FIG. Unless one of the drawings is specifically referred to, the description below is for both drawings.

The front support portion 8.1 is formed by a front rolling bearing 14.1 and a rear rolling bearing 14.2 arranged at axial intervals. The rolling bearing 14.1 on the front side is a pure support bearing that is arranged near the center of gravity 19.1 of the chuck 3. Center of gravity 19.1 relates to an empty chuck 3 that does not have a wound package. The accommodation of the wound package in the chuck 3 creates a package center of gravity 19.2, and the position of the package center of gravity 19.2 does not coincide with the position of the empty chuck 3 center of gravity 19.1. Therefore, it is necessary to consider the total center of gravity (Gesammtschwerpunkt) caused 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 towards the package center of gravity 19.2 as winding progresses.

In order to allow a total load consisting of the weight of the chuck 3 and the package mass of the wound package to act on the support bearing 14.1, the support bearing 14.1 is set to the center of gravity of the chuck 3 19. It is arranged on the bearing plane 34 located between 1 and the center of gravity of the package 19.2. Therefore, the support bearing 14.1 is 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. The cylindrical roller bearing 16 is arranged in the increased shaft step portion 18.1 of the bearing shaft 7.1 on the front side in the inner race 16.1. At this time, the shaft step portion 18.1 extends over the entire width of the cylindrical roller bearing 16. The transition portion of the shaft step portion 18.1 to the shaft stem (Wellenschaft) 33 of the bearing shaft 7.1 on the front side is formed round 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 bearing shaft 7.1 on the front side.

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 by two spindle bearings 17.1, 17.2 loaded against each other in this embodiment. The spindle bearings 17.1 and 17.2 are loaded against each other in a frontal combination (X-Anodrnung). At this time, the spindle bearings 17.1 and 17.2 are arranged directly side by side and are held by the increased shaft step portion 18.2. The shaft step portion 18.2 that thickens the bearing shaft 7.1 extends over the widths of both spindle bearings 17.1, 17.2. At this time, similarly, one rounded portion is provided in each of the transition regions to the shaft stem 33. The spindle bearings 17.1 and 17.2 are supported by the bearing bush 12.1 in the outer race.

A plurality of buffer rings are provided around the bearing bush 12.1 in order to buffer the vibration generated when passing through the critical winding speed, and in particular to avoid contact of the chuck 3 around the hollow support 11. Has been done. In this embodiment, two buffer rings 13 are provided, and both buffer rings 13 are arranged 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 near the shaft / hub coupling portion 15. Therefore, since the bearing bush 12.1 projects beyond the support bearing 14.1, the buffer ring 13 is arranged so as to be offset from the support bearing 14.1 in the axial direction.

The cushioning ring 13 is configured in the same manner and has an inner sleeve 13.2 and an outer sleeve 13.1 that surrounds the inner sleeve 13.2 at intervals. 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 immobilely coupled 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, which acts as a rubber spring, can be adapted to the mounting location with respect to material and spring properties. Further, since the outer sleeve 13.1 and the inner sleeve 13.2 can be accurately manufactured within a narrow manufacturing error range, unacceptable deformation during mounting of the buffer ring 13 is preferably avoided. Conversely, slight manufacturing errors within the mounting space will not adversely affect the spring cushioning properties of the rubber element 13.3, while the outer sleeve 13.1 and inner sleeve 13.2 are mobile. Can be compensated to some extent.

As can be seen from the illustration of FIG. 1, the buffer ring 13 is also used to shield the rear support portion 8.2 of the rear bearing shaft 7.2 from the hollow support 11. In the present embodiment, the rear support portion 8.2 is formed by two rolling bearings 20.1 and 20.2, and the double rolling bearings 20.1 and 20.2 are formed by the rear bearing shaft 7. It is held between 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 within a hollow cylindrical portion of the hollow support 11 that is directly held by the spindle support 1. At this time, the rear support portion 8.2 is formed at the end portion of the hollow support 11. The bearing shaft 7.2 on the rear side projects to the outside of the hollow support 11 at the drive end portion, and at this time, the drive end portion is formed as the coupling end portion 10. Therefore, the spindle drive device can be directly connected to the drive shaft 7 via the coupling end portion 10.

To accommodate and secure the winding tube, the chuck 3 has a clamping device 4 and a tightening peripheral wall 5 around it. Since the clamp device 4 and the tightening peripheral wall 5 are common in the prior art, further description is omitted here. The clamp device 4 and the tightening peripheral wall 5 may be configured, for example, as in the embodiment described in WO 2011/086142 (WO 2011/086142 A1). Therefore, here we refer to the cited publications.

During operation, a plurality of winding tubes are pressed back and forth around the tightening peripheral wall 5 and fixed by a clamping device 4. At each of the winding tubes, the thread is wound into a package. Therefore, the chuck 3 is driven via the drive shaft 7 so that a substantially constant peripheral speed is obtained for winding the thread. 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 run in a rotation 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 provided with 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 the alternate long and short dash line in FIG. 1 and is indicated by reference numeral 34. The support bearing 14.1 is arranged on the bearing plane 34. The introduction of the full weight is performed via the shaft / hub coupling portion 15 between the chuck 3 and the bearing shaft 7.1 on the front side. 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 into the free end portion of the bearing shaft 7.1 on the front side via the shaft / hub coupling portion 15. Such a take-up spindle has a plurality of critical natural frequencies based on its complex structure, and these critical natural frequencies may cause resonance when overlapped with the excitation frequency. Therefore, the support portion 8.1 is buffered with respect to the hollow support 11 via the buffer ring 13. Such a so-called critical take-up rate can determine the end of the operating range of the take-up spindle in relation to an acceptable resonance overrise (Resonanzueberhoehung). Therefore, it is necessary to strengthen the cushioning action of the bearing shaft on the front side in order to affect the operating range and expand the operating range. Therefore, FIG. 3 schematically shows another embodiment of the take-up spindle according to the present invention in a cross-sectional view.

The form of the take-up spindle in FIG. 3 is almost the same as the above-described embodiment shown in FIG. 1 in its structure. Therefore, only the differences are described here, and the other points are described above. Shall refer to.

To ensure a reliable drive of the chuck 3, the drive shaft 7 is based on the static load of the chuck 3 that increases with increasing package weight and the dynamic load due to the imbalance of the package that increases at the same time. Also in this embodiment, it is formed by the front bearing shaft 7.1 and the rear bearing shaft 7.2. The bearing shaft 7.1 on the front side is coupled to the bearing shaft 7.2 on the rear side via a coupling 9. The coupling 9 preferably has a buffering means, which can transmit only the torsional moment but not the bending moment, and can buffer the torsional vibration.

In the present embodiment of the take-up spindle 2 according to the present invention, an additional cushioning means formed as a buffer bearing 21 is correspondingly arranged on the drive shaft 7. The buffer bearing 21 is arranged on the shaft portion of the front bearing shaft 7.1 on the outside of the front support portion 8.1 so as to be axially offset from the support bearing 14.1. The buffer bearing 21 is arranged corresponding to the shaft end portion of the bearing shaft 7.1 on the front side, 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 protruding free end portion of the hollow support 11. The cushioning bearing 21 has a rolling bearing 21.1 and a cushioning ring 21.2 in the present embodiment. The rolling bearing 21.1 is formed by a double spindle bearing 22.1.22.2. The spindle bearings 22.1, 2.2.2 are loaded against each other by a so-called back combination (O-Anordnung). As a result, a preload can be generated between the spindle bearings 22.1, 2.2.2, and this preload greatly extends the bearing life. A cushioning ring 21.2 is held around the spindle bearings 22.1, 2.2. The buffer ring 21.2 is the same as the buffer ring 13 of the embodiment shown in FIG. 1 in its structure. Therefore, the description described above shall be referred to.

The buffer ring 21.2 has a significantly smaller radial strength than the buffer ring 13, which allows a soft bond of the buffer bearing 21 to the hollow support 11. As a result, the buffer bearing 21 is effective only when resonance occurs around the bearing shaft 7.1.

The spindle bearings 22.1, 2.2 of the buffer bearing 21 are arranged around another increased shaft step portion 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 joint portion 15. At this time, since the maximum rotational bending moment is generated at the shaft / hub coupling portion 15, it is desired to thicken the bearing shaft 7.1 until the shaft / hub coupling portion 15 is reached.

The take-up spindle according to the present invention is outstanding because a chuck that projects extremely long can be realized, particularly in a state where the nominal diameter of the chuck does not change. Due to the increased load capacity of the front support and the increased strength of the drive shaft, larger packages if the chuck lengths are equal, or more packages if the package weights are equal. , Can be wound around the chuck. Therefore, the take-up spindle according to the present invention is particularly suitable for winding one thread group in parallel to a plurality of packages.

FIG. 4 schematically shows another embodiment of the take-up spindle according to the present invention in cross-sectional view. Since the embodiment of the take-up spindle shown in FIG. 4 is almost the same as the embodiment shown in FIG. 3 in its structure, only the differences will be described here, and the other points will be described above. The description shall be referred to.

In the embodiment of the take-up spindle according to the present invention shown in FIG. 4, an additional collar bearing 36 is formed at the open end of the chuck, which is arranged corresponding to the spindle support 1. Therefore, the chuck 3 has an annular collar 37 which is an enlarged diameter portion at an open end portion. At this time, the collar bearing 36 is formed by a rolling bearing 36.1 and a 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 by an annular collar 37 of the chuck 3. Similarly in the present embodiment, the buffer ring 36.2 is formed by two metal sleeves sandwiching a rubber element.

The flange bearing 36 improves the stability of the chuck 3 especially when the package is wound. Further, the cushioning ring 36.2 has a property of allowing the chuck 3 to descend with respect to the hollow support 11 even when a load is applied to the chuck 3 by the wound package, and on the other hand, a property of guaranteeing a cushioning action. are doing. By the flange bearing 36, an additional force component that affects the load distribution in the chuck 3 acts on the chuck 3. This involves a load transfer (Lastverschiebung) that 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 toward 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 portion of the bearing bush 12.1. From the direct comparison of the take-up spindle with the embodiment shown in FIG. 3, the position change of the support bearing 14.1 based on the collar bearing 36 can be recognized. All other members are formed identically in the embodiments shown in FIGS. 3 and 4 of the take-up spindle.

FIG. 5 schematically shows another embodiment of the winder according to the present invention. The take-up machine has two take-up spindles 2.1 and 2.2 that project long, and both take-up spindles 2.1 and 2.2 are held by the spindle support 1 and each of them. It has one protruding chuck 3. The spindle support 1 is formed as a take-up turret rotatably supported by the machine frame 24. The take-up spindles 2.1 and 2.2 are configured as one of the embodiments shown in FIG. 1 or FIG.

In this embodiment, four winding units 25.1 to 25.4 extend along the winding spindles 2.1 and 2.2, and four winding units 25.1 to 25.4 extend from these winding units 25.1 to 25.4. The packages 27 are wound in parallel with each other. Two spindle motors 26, 1, 6.2 are correspondingly arranged on the take-up spindles 2.1 and 2.2. The number of winding units is determined according to the manufacturing process, whether to wind the weaving yarn or the industrial yarn. The number of winding units is an example in this embodiment, and in the illustrated variation, it can be used when winding industrial yarn or carpet yarn.

A crimping roller 30 and a twill swing device 29 are arranged correspondingly to the winding units 25.1 to 25.4, and at this time, the twill swing device 29 is arranged with respect to each winding unit 25.1 to 25.4. Each of the thread guide means for reciprocating one of the plurality of threads is provided. The crimping roller 30 is held by a movable roller support 32. The thread run-in is guided via each one head thread guide 31 forming the run-in portion of the winding unit 25.1 to 25.4.

The take-up machine according to the present invention is suitable for winding a plurality of freshly extruded yarns into a package in parallel as one yarn group for all conventional melt spinning processes. For example, synthetic yarns produced in a POY melt spinning process, an FDY melt spinning process, or an IDY melting spinning process can be simultaneously wound into a package in one yarn group having a plurality of yarns. However, the winder is also suitable for winding multiple crimped threads into a package due to the BCF process.

Claims (13)

A take-up spindle that winds a thread into a plurality of packages in a take-up machine and has at least one long protruding chuck (3) that accommodates the package, and the chuck (3) is a hollow support. body (11) supported within, it can be driven by the front bearing axis (7.1) and behind the bearing axis (7.2) and a drive shaft comprising a plurality of portions having (7), the rear side of the bearing axis (7.2) are possible coupled to the drive device, the rear side of the bearing shaft (7.2) coupled to said front bearing axis (7.1), the chuck (3 ) Is non-rotatably coupled to the front side bearing shaft (7.1), and the front side rolling bearing (14.1) and the rear side rolling bearing (14) with respect to the hollow support (11). In the take-up spindle rotatably supported by .2), the front rolling bearing (14.1) is configured as a support bearing, and the center of gravity (19.1) of the chuck (3). A take-up spindle, characterized in that it is located between the and the package center of gravity (19.2) . The rear rolling bearing (14.2) is formed as a guide bearing, and the guide bearing (14.2) does not apply an axial load to the support bearing (14.1). The take-up 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). Claim that the inner race (16.1) of the cylindrical roller bearing (16) is held around an enlarged shaft step portion (18.1) in the front bearing shaft (7.1). The take-up spindle according to 3. The rear rolling bearing (14.2) is formed by two spindle bearings (17.1, 17.2) arranged side by side with each other, and the spindle bearing (17.1, 17.2). Is the take-up spindle according to any one of claims 2 to 4, which is held around the front bearing shaft (7.1) in a frontal combination. The support bearing (14.1) and the rear rolling bearing (14.2) are arranged inside the bearing bush (12.1), and the bearing bush (12.1) is surrounded by the bearing bush (12.1). The take-up spindle according to any one of claims 1 to 5, wherein a plurality of buffer rings (13) supported by the hollow support (11) are held. Each of the plurality of cushioning rings (13) is formed of an inner sleeve (13.2) and an outer sleeve (13.1) that surrounds the inner sleeve (13.2) at intervals. The take-up spindle according to claim 6, wherein the sleeve (13.2) and the outer sleeve (13.1) are elastically coupled to each other by 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 axially displaced forward with respect to the support bearing (14.1). The take-up spindle according to any one of claims 1 to 7, which is arranged between the bearing shaft (7.1) on the front side and the hollow support (11). The buffer bearing (21) has an increased diameter between the support bearing (14.1) and the end of the front bearing shaft (7.1) coupled to the chuck (3). The take-up spindle according to claim 8, which is arranged in a shaft step portion (18.3). The chuck (3), at the end towards the drive device of the chuck, which is supported by the rolling bearings disposed annular collar formed to the end portion (37) (36.1), wherein The take-up spindle according to any one of items 1 to 9. Said rolling bearing (36.1), the hollow support are arranged around the (11), the chuck (3) is surrounded depending on supported cushion ring (36.2), claim 10. The take-up spindle according to 10. A support portion (8.2) for supporting the bearing shaft (7.2) on the rear side is formed inside the bearing bush (12.2), and the bearing bush (12.2) has two support portions (12.2). A buffer ring (13) is held, each of which is supported by the bearing bush (12.2) in an inner race (13.2) and said in an outer race (13.1). The take-up spindle according to any one of claims 1 to 11, which is supported by a hollow support (11). A take-up machine for winding a plurality of threads into a package provided with two take-up spindles (2.1, 2.2) held by a spindle support (1), wherein the take-up spindle (2. A winder, characterized in that at least one of 1, 2.2) is formed as described in claims 1 to 12.

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