JP6856538B2 - Winding spindle - Google Patents

Description

The present invention relates to a take-up spindle for winding a yarn into a plurality of packages, which is described in the premise of claim 1.

A take-up spindle of this type is known from Japanese Patent Application Publication No. 2261709 (DE 2 261 709 A1).

Known take-up spindles are used in take-up machines to wind multiple yarns in parallel on a package. Therefore, the take-up spindle is arranged so as to project from the spindle support, and the projecting portion of the take-up spindle is formed as a chuck for accommodating and fixing the winding tube. The chuck is formed in a hollow cylindrical shape and is coupled to a drive shaft located inside the take-up spindle via a hub. The drive shaft is rotatably supported in a hollow cylindrical hollow support, at which time the hollow support has entered the inside of the chuck.

The drive shaft may have a relatively large length to couple the drive devices located on the spindle support, as a correspondingly long protruding chuck is required to accommodate multiple packages. is necessary. It should be noted at this time that the chuck lowers as the package weight increases, which creates a bending load on the drive shaft. The drive shaft is formed from multiple parts so that it can follow the descent of the chuck, at which time the front bearing shaft is coupled to the chuck and the rear bearing shaft is coupled to the drive. There is. An intermediate shaft is provided between the rear bearing shaft and the front bearing shaft, and the intermediate shaft is coupled to both bearing shafts via a flexible soft coupling. Such a coupling is directly coupled to the shaft end by press coupling. However, such press coupling, which is usually formed by shrink fitting, impairs the strength of the drive shaft, depending on the joint diameter. Further, in order to drive the chuck, an extremely high rotation speed, which can be 16000 rpm or more, must be transmitted at the start of winding. Therefore, a very accurate support of the drive shaft is required, and such support requires axial orientation in the case of a multi-part configuration, despite the coupling.

Another drawback of take-up spindles known in the art is that in the case of chucks that project very long, mounting is extremely cumbersome or nearly impossible.

Therefore, an object of the present invention is to provide a take-up spindle of this type, in particular, in which a chuck having an extremely long protrusion can be easily attached and can be reliably driven in operation. ..

According to the present invention, this problem is solved by fixing the front coupling and / or the rear coupling to the shaft ends of the bearing shaft and the intermediate shaft by a plurality of clamp elements.

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

The present invention is freed from the condition that the clamp coupling is only suitable for small torques that fluctuate slightly, at which time the contact pressure per unit area applied to the shaft is extremely non-uniform. It is evaluated as a thing. However, it has been found that torque transmission at the coupling points between the shaft portions of the drive shaft is possible without loss even at full load of the chuck with the wound package. A special advantage of the take-up spindle according to the present invention is that the axial fixation is variable around the shaft end, and thus the intermediate shaft can be accurately associated with the bearing shaft.

Further, the chuck can be lowered under the load of the entire package without forced deformation in the drive shaft. The descent can preferably be absorbed by angular deformation in the coupling, where the clamps at the shaft ends of the bearing shaft and intermediate shaft allow the shaft to grow. This allows the drive shaft to be made significantly thicker, avoiding high rotational bending moments on the bearings and the resulting quasi-load (Blindlast).

In particular, in order to obtain a uniform contact pressure per unit area over the entire circumference of the shaft end, in a preferred embodiment of the invention, each clamp element is formed from two half-shell shaped clamp portions. The clamp portions confine the fitting holes between them and are screwed to each other. The diameter of the shaft end and the fitting hole of the clamp portion may be aligned with each other so as to produce a so-called screwable press seat. Such a split clamp coupling between the coupling and the shaft end has therefore been found to be particularly good.

To be able to compensate for the descent caused by the chuck, especially at the total package weight in the chuck, the clamp elements of one of the couplings, corresponding to the shaft end, are at least axially and They are coupled to each other by laterally elastic coupling means. As the bending elastic coupling means, for example, a shaft tube element or an occlusal element can be used.

Individual resonances cannot be avoided due to the high speed increase during operation of such take-up spindles, which can range from 1400 rpm to 16000 rpm. However, such a critical take-up speed gives rise to the enhanced vibration characteristics of the chuck, which acts directly on the drive shaft. Therefore, in a preferred embodiment of the present invention, the intermediate shaft is elastically supported by a plurality of buffer bearings with respect to the hollow support. With this configuration, vibration transmission, in particular, can also be avoided via the coupling. Since the intermediate shaft is held with almost no lateral force and no bending moment, the buffer bearing works almost only at resonance. In addition, very stable guidance of the intermediate shaft within the hollow support is achieved.

The buffer bearing is preferably held in the end region of the intermediate shaft, each of which is formed from one rolling bearing and a sleeve buffer ring. The rotation of the intermediate shaft remains unaffected, and only the relative motion in the intermediate shaft is introduced directly through the rolling bearings into each of the correspondingly arranged sleeve buffer rings.

The rolling bearing of the buffer bearing is preferably formed by two spindle bearings arranged side by side with each other, and the spindle bearings are held around an intermediate shaft in a back combination. This, on the one hand, enhances stability for guiding the intermediate shaft, and on the other hand, the cushioning bearing remains unaffected by the adjacent support of the front bearing shaft.

The front support of the front bearing shaft is located inside the bearing bush according to a preferred development of the present invention, with a plurality of sleeves supported by a hollow support around the bearing bush. A buffer ring is supported. With such a configuration, tilting of the rolling bearing is particularly avoided. Since the support portion is elastically supported by the hollow support via the sleeve cushioning ring, the bearing shaft can perform a relative motion with respect to the hollow support for the purpose of cushioning.

In yet another embodiment, a bearing shaft support on the rear side is formed inside the bearing bush, where the bearing bush is elastically relative to the hollow support using a plurality of sleeve buffer rings. It is supported. With such a configuration, it is possible to suitably buffer the vibration load generated from both the driving side and the driven side.

After installation, the sleeve buffer ring is preferably an inner sleeve and an outer sleeve that surrounds the inner sleeve in order to obtain near-predetermined elasticity and cushioning of the intermediate shaft and support, independent of manufacturing error. Is formed by. At this time, the rubber element is sandwiched between the inner sleeve and the outer sleeve. The spring elastic properties of the rubber element between the inner sleeve and the outer sleeve can be formed with a predetermined cushioning property already prior to mounting, and can be adapted to the mounting location and mounting conditions.

The take-up machine according to the present invention is particularly outstanding because it can form a plurality of take-up units on the protruding take-up spindle. A multi-part drive shaft and its coupling can provide a particularly long protruding chuck, which can significantly increase the number of packages wound around the chuck.

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

It is a vertical cross-sectional view which shows 1st Embodiment of the winding spindle which concerns on this invention. FIGS. 2.1 and 2.2 are views of one of the drive shaft couplings of the embodiment shown in FIG. 1 viewed from different directions. It is a vertical sectional view schematically showing another embodiment of the winding spindle which concerns on this invention. It is a figure which shows a part of the embodiment shown in FIG. 3 schematically. 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. The shaft / hub coupling portion 15 is formed between the hub 6 and the thick shaft step portion 18 of the bearing shaft 7.1 on the front side.

The drive shaft 7 is formed of a front bearing shaft 7.1, an intermediate shaft 7.2, and a rear bearing shaft 7.3. The front bearing shaft 7.1 is coupled to the intermediate shaft 7.2 via a front coupling 9.1. The rear bearing shaft 7.2 is non-rotatably coupled to the intermediate shaft 7.1 via the rear coupling 9.2.

To illustrate couplings 9.1 and 9.2, one of the couplings, here coupling 9.1, is viewed from different directions in FIGS. 2.1 and 2.2. Is additionally referred to. FIG. 2.1 schematically shows the coupling 9.1 in a side view, and FIG. 2.2 shows the coupling 9.1 schematically in a cross-sectional view. Unless one of the drawings is specifically referred to, the description below is for both drawings.

The coupling 9.1 has clamp elements 26, 1, 6.2 at both ends, respectively. These clamp elements 26.1, 6.2 are coupled to the shaft end portion 30.1 of the front bearing shaft 7.1 and the shaft end portion 30.2 of the intermediate shaft 7.2 via a clamp coupling. There is. The clamp elements 26.1,6.2 sandwich the coupling means 28 in between, and the coupling means 28 is immovably coupled to the clamp elements 26.1,6.2 and axially and laterally. It is formed elastically in the direction. However, on the rotating axis, since the coupling means 28 is formed to have torsional rigidity, torque transmission of torsional rigidity is performed between the shafts 7.2 and 7.1. As the coupling means 28, for example, a shaft tube element or a Klauen element can be used.

The clamp elements 26.1, 6.2 are formed in the same manner, respectively. For example, FIGS. 2.1 and 2.2 show a clamp element 26.1 formed from two half-shell shaped clamp portions 27.1, 7.2. The clamp portions 27.1, 7.2 have confined the fitting hole 25 between them. At this time, the fitting hole 25 is formed at the shaft end portion 30 of the bearing shaft 7.1 on the front side so that a kind of screw-coupled press seat is generated in the screw-coupled state of the clamp portions 27.1, 7.2. It is adjusted to the outer diameter of 1. As a result, a substantially uniform contact pressure per unit area can be generated over the entire circumference of the bearing shaft 7.1 on the front side. The screw connection of the clamp portions 27.1, 7.2 is performed by two screw means 29 located on opposite sides of each other. The clamp portion 27.1 or 27.2 of one of the clamp portions 27.1, 7.2 is immovably coupled to, for example, the coupling means 28, which is an occlusal element.

As shown in FIG. 2.1, the clamp element 26.2 located on the opposite side also has two half-shell type clamp portions 27, 1, 7.2, and both clamp elements 27. .1,27.2 are coupled to each other via screwing means 29.

As shown in FIG. 1, the couplings 9.1 and 9.2 between the bearing shaft 7.1, 7.3 and the intermediate shaft 7.2 are configured to be the same in the present embodiment. However, it should be made clear here that couplings 9.1 and 9.2 can also have different structural types of clamp coupling and coupling means, if desired. .. For example, a slit-shaped clamp element is also possible to couple the coupling to one shaft end.

The bearing shaft 7.1 on the front side is rotatably supported in the hollow support 11 having a hollow cylindrical shape via the support portion 8.1 on the front side. The hollow support 11 therefore enters the inside of the chuck 3 at the free end of the hollow cylinder. Since the end of the chuck 3 facing the spindle support 1 surrounds the protruding hollow support 11 at intervals, the chuck 3 can rotate with respect to the position-fixed hollow support 11. it can.

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. In the present embodiment, the front support portion 8.1 is formed by two rolling bearings 13.1, 13.2, and both rolling bearings 13.1, 13.2 are the bearing shafts on the front side in the race. It is held around 7.1 and is supported by the bearing bush 12.1 in its outer race.

Bearing bush 12.1 to be able to receive static bearing loads on the one hand and to avoid abutment of the chuck 3 around the hollow support 11 when passing the critical take-up speed on the other hand. A plurality of sleeve cushioning rings are provided around the. In this embodiment, two sleeve buffer rings 14.1, 14.2 are provided, and both buffer rings 14.1, 14.2 are respectively arranged in the end region of the bearing bush 12.1. .. At this time, in particular, the sleeve buffer ring 14.1 of one of the sleeve buffer rings is positioned near the shaft / hub coupling portion 15 between the front bearing shaft 7.1 and the chuck 3. Since the bearing bush 12.1 protrudes beyond the rolling bearing 13.1, the sleeve buffer ring 14.1 is arranged so as to be offset from the rolling bearing 13.1 in the axial direction.

The structures of the sleeve buffer rings 14.1 and 14.2 are the same and will be described in more detail below.

The intermediate shaft 7.2 coupled to the front bearing shaft 7.1 also extends inside the protruding portion of the hollow support 11 immovably coupled to the spindle support 1. In the hollow cylindrical portion of the hollow support 11 that is directly held by the spindle support 1, a support portion 8.2 on the rear side of the bearing shaft 7.3 on the rear side is formed. In the present embodiment, the rear support portion 8.2 is formed by two rolling bearings 16.1, 16.2, and the double rolling bearings 16.1, 16.2 are formed by the rear bearing shaft 7. It is held between 3 and the bearing bush 12.2. Two other sleeve buffer rings 17.1, 17.2 of the sleeve buffer rings are arranged around the bearing bush 12.2. The bearing shaft 7.3 on the rear side advances 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.

The chuck 3 has a clamping device 4 and a tightening peripheral wall 5 around it for accommodating and fixing the winding tube. The clamping device 4 and the tightening peripheral wall 5 are generally known in the prior art and are therefore omitted further herein. The clamp device 4 and the tightening peripheral wall 5 may be configured based on, for example, International Publication No. 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. Therefore, since the operation of the take-up spindle 2 is performed from the front side, the free end portion of the take-up spindle 2 is called a front end portion, and the end portion fixed to the spindle support 1 is called a rear end portion. At each winding tube around the chuck 3, a thread is wound around the package. Therefore, the chuck 3 is driven via the drive shaft 7 so that a substantially constant peripheral speed for winding the yarn is generated. Inside the drive shaft 7, torque is introduced into the intermediate shaft 7.2 via the rear bearing shaft 7.3 and the rear coupling 9.2, and from this intermediate shaft 7.2 to the front coupling. It is introduced to the front bearing shaft via 9.1. The bearing shaft 7.1 on the front side transmits torque to the chuck 3 via the shaft / hub coupling portion 15. The load and vibration in the chuck 3 are introduced directly to 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 complicated structure, and these critical natural frequencies may cause resonance when they match the excitation frequency. As such, the support section 8.1 is buffered against the hollow support 11 via sleeve buffer rings 14.1, 14.2. In particular, in order to better buffer the vibration of the chuck, FIG. 3 schematically shows another embodiment of the take-up spindle according to the present invention in a vertical 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. In the embodiment of the take-up spindle 2 according to the present invention shown in FIG. 3, additional cushioning means are correspondingly arranged on the drive shaft 7. The intermediate shaft extending inside the hollow support 11 is elastically supported with respect to the hollow support 11 via one buffer bearing 19.1 and 19.2, respectively, in both end regions. For this purpose, the buffer bearings 19.1 and 19.2 are arranged on the shaft step portions 31.1 and 31.2 of the intermediate shaft 7.2, respectively.

Additional reference is made to FIG. 4 to illustrate the buffer bearings 19.1 and 19.2. FIG. 4 shows a longitudinal sectional view of the cushioning bearing 19.1 at the front end of the intermediate shaft 7.2. This buffer bearing 19.1 has a rolling bearing 20 and a sleeve buffer ring 21 in this embodiment. The rolling bearing 20 is formed by double spindle bearings 20.1, 20.2. The spindle bearings 201 and 20.2 are loaded against each other by a so-called back surface combination (O-Anordnung). As a result, extremely stable guidance of the intermediate shaft 7.2 is achieved. A sleeve buffer ring 21 is held around the spindle bearings 20.1, 20.2. The sleeve buffer ring 21 has an inner sleeve 22 held around the spindle bearings 20.1.2. The inner sleeve 22 is correspondingly arranged with an outer sleeve 23 that surrounds the inner sleeve 22 at intervals, and the outer sleeve 23 is supported by the hollow support 11. A rubber element 24 formed as a rubber spring is arranged between the outer sleeve 23 and the inner sleeve 22. As a result, the inner sleeve 22 and the outer sleeve 23 can move relative to each other. Since the inner sleeve 22 and the outer sleeve 23 are preferably made of metal, the rubber element 24 is fixed between the inner sleeve 22 and the outer sleeve 23 by vulcanization. The rubber element 24, which acts as a rubber spring, can be adapted to the mounting location and mounting conditions with respect to material and spring characteristics. Further, since the outer sleeve 23 and the inner sleeve 22 can be accurately manufactured within a narrow manufacturing error range, unacceptable deformation during attachment of the sleeve buffer ring 21 is preferably avoided. On the contrary, a slight manufacturing error inside the mounting space is to some extent due to the mobility of the outer sleeve 23 and the inner sleeve 22 without adversely affecting the spring cushioning properties of the rubber element 24. Can be compensated. Therefore, the buffer bearing 19.1 and the buffer bearing 19.2 formed in the same manner as in the embodiment shown in FIG. 4 are used to guide and buffer the intermediate shaft 7.2 in the hollow support 11. ..

In the embodiment shown in FIGS. 1 and 3, the sleeve buffer ring 14.1, 14.2, 17.1, 17.2 additionally arranged corresponding to the support portion 8.1, 8.2 is formed in the structure. , The same as the sleeve buffer ring 21. However, in this case, a variety of different structural forms and forms can be used to affect the mobility between the inner and outer sleeves. For example, the inner sleeve and the outer sleeve preferably have different widths. Thus, the sleeve buffer ring can be combined with a variety of different sleeves, where the rubber element has a width equal to or less than the width of the shortest winding tube.

Further, the sleeve buffer ring may be formed with various radial strengths. In particular, the sleeve cushioning ring 21 arranged corresponding to the intermediate shaft 7.2 has a significantly smaller radial strength than the sleeve cushioning rings 14.1 and 14.2 arranged corresponding to the support portion 8.1. This makes it possible to obtain a correspondingly soft joint of the intermediate shaft. On the other hand, the sleeve buffer rings 14.1 and 14.2 of the support portion 8.1 must receive the load of the chuck.

FIG. 5 schematically shows one 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 32. 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 33.13 to 3.4 extend along the take-up spindles 2.1 and 2.2, and four winding units 33.1 to 3.4 in these winding units 33.1 to 3.4. The packages 35 are wound in parallel with each other. Two spindle motors 34.1 and 34.2 are arranged correspondingly to 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.

A crimping roller 37 and a twill swing device 38 are arranged correspondingly to the winding units 33.1 to 33.4, and at this time, the twill swing device 38 is arranged with respect to each winding unit 33.13 to 3.4. Each has a thread guide means for reciprocating one of the plurality of threads. The crimping roller 37 is held by a movable roller support 39. The run-in of the yarn is guided via each one head yarn guide 40 forming the run-in portion of the winding unit 33.1 to 3.4.

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 melt-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 a plurality of crimped yarns into a package due to the BCF process.

Claims (9)

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. It can be driven by a drive shaft (7) composed of a plurality of parts supported in the body (11), and the drive shaft (7) is a rear bearing shaft (7.3) and a front bearing shaft (7). The front bearing shaft (7.3) is connectable to the drive device and is coupled to the rear bearing shaft (7.3). The shaft (7.1) is non-rotatably coupled to the chuck (3), and the front bearing shaft (7.1) is connected to the rear bearing shaft (7.2) by an intermediate shaft (7.2). It is coupled to 7.3), the front bearing shaft (7.1) is coupled to the intermediate shaft (7.2) via the front coupling (9.1), and the rear side. The bearing shaft (7.3) of the above is coupled to the intermediate shaft (7.2) via the rear coupling (9.2). In the take-up spindle, the front coupling (9.) 1) and / or the rear coupling (9.2) is provided by a plurality of clamp elements (26, 1, 6.2) to the bearing shaft (7.1, 7.3) and the intermediate shaft (7.1, 7.3). It is fixed to the shaft end (30.1, 30.2) of 7.2).
Each of the clamp elements (26, 1, 6.2) is formed of two half-shell type clamp portions (27, 1, 7.2), and the clamp portions (27, 1, 7.2) are formed. Confine the fitting hole (25) between them, and the clamp portions (27, 1, 7.2) are screwed to each other, whereby the respective shaft end portions (30.1, 30) are screwed together. A take-up spindle, characterized in that a contact pressure per unit area is generated almost uniformly over the entire circumference of .2). Clamp elements (26, 1, 6.2) arranged corresponding to the shaft end (30.1, 30.2) of one of the couplings (9.1, 9.2). at least axial and lateral are coupled to one another by an elastic coupling means (28), the winding spindle of claim 1, wherein. The winding according to claim 1 or 2 , wherein the intermediate shaft (7.2) is elastically supported by a plurality of buffer bearings (19.1, 19.2) with respect to the hollow support (11). Bearing spindle. The buffer bearing (19.1, 19.2) is held in the end region of the intermediate shaft (7.2), and the buffer bearing (19.1, 19.2) is rolled one by one. The take-up spindle according to claim 3 , which is formed of a bearing (20) and a sleeve buffer ring (21). The rolling bearing (20) is formed by two spindle bearings (20.1, 20.2) arranged side by side with each other, and the spindle bearings (20.1, 20.2) are rear-combined. The take-up spindle according to claim 4 , which is held around the intermediate shaft (7.2). A support portion (8.1) for supporting the front bearing shaft (7.1) is formed inside the bearing bush (12.1), and is opposite to each other of the bearing bush (12.1). Two of the sleeve cushioning rings (14.1, 14.2) are held in the end region located in the sleeve buffer ring (14, 1, 14.2). The take-up spindle according to any one of claims 1 to 5 , which is supported by a hollow support (11). A support portion (8.2) that supports the rear bearing shaft (7.3) is formed inside the bearing bush (12.2), and is opposite to each other of the bearing bush (12.2). Two sleeve buffer rings (17.1, 17.2) are held in the end region located in the sleeve buffer ring (17, 1, 17.2), which is the hollow support (11). The take-up spindle according to any one of claims 1 to 6 , which is supported by the above. Each of the sleeve buffer rings (21, 14.1, 14.2, 17.1, 17.2) has an inner sleeve (22) and an outer sleeve (23) that surrounds the inner sleeve (22) at intervals. ), And the inner sleeve (22) and the outer sleeve (23) are elastically coupled to each other by a rubber element (24), any one of claims 4 to 7. The take-up spindle described. A take-up machine for winding a plurality of yarns into a package, comprising 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 8.

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