CN107406214B

CN107406214B - Winding machine

Info

Publication number: CN107406214B
Application number: CN201680015485.9A
Authority: CN
Inventors: H·瓦尔特曼; K·谢弗
Original assignee: Oerlikon Textile GmbH and Co KG
Current assignee: Oerlikon Textile GmbH and Co KG
Priority date: 2015-03-14
Filing date: 2016-03-10
Publication date: 2020-08-18
Anticipated expiration: 2036-03-10
Also published as: CN107406214A; DE112016001204A5; JP7060380B2; WO2016146464A1; JP2018507833A

Abstract

The invention relates to a winding machine for winding a thread group to form a plurality of bobbins. For this purpose, the winding machine has a winding spindle (3.1, 3.2) with a projecting clamping chuck (12) for receiving a plurality of bobbin tubes (7), which can be driven by a multi-part drive shaft (16) mounted in a hollow support (20). A rear bearing shaft (16.2) is coupled to the drive, a front bearing shaft (16.1) connected to the rear bearing shaft is coupled to the clamping chuck and mounted in the hollow support by damping bearings (25.1, 25.2). In order to allow strong damping without structurally weakening the clamping chuck, an additional damping device is provided between the front bearing shaft and the hollow support, which additional damping device is arranged in an axially offset manner outside the bearing.

Description

Winding machine

Technical Field

The invention relates to a winding machine for winding a thread group to form a plurality of bobbins.

Background

In the production of synthetic threads in a melt spinning process, the threads of a spinning station are wound together in parallel to form bobbins. For this purpose, known winding machines are used, which in each case have one winding station for each thread, wherein the winding stations extend in a parallel manner along the winding spindles. The winding spindle is arranged to project on the spindle support so that a bobbin wound on the circumference of the winding spindle when completed can be removed from the free end. It is now desirable to produce as many threads as possible in one spinning station, so that a plurality of bobbins must be wound in parallel side by side in one winding machine and a winding spindle projecting in a particularly extended manner is required.

However, the basic design of winding spindles of this type takes into account the very high running speeds of the thread in the range from 2000 to 6000 m/min to be achieved during winding. Furthermore, due to the complex design of the winding spindles, a plurality of critical resonance frequencies, which can cause resonance when matched to the excitation frequency, are also to be taken into account. These so-called critical winding speeds can be exaggerated in terms of the permitted resonance to determine the end points of the operating range of the winding spindles. It is therefore common to reduce the vibration behavior of the winding spindles or to damp the vibrations of the winding spindles in order to influence or enlarge the operating range, respectively.

A winding machine of the generic type with a winding spindle is known from DE 19548142 a 1. The winding spindle has a chuck, on the circumference of which clamping devices for receiving a winding tube are arranged. The chuck is configured to be hollow cylindrical toward the driving side and is connected to the driving shaft through a hub. The drive shaft is formed in several parts and is realized by a rear bearing shaft and a front bearing shaft. The rear bearing shaft is embodied so as to be connectable by its free end to the drive. The front bearing shaft is connected to the hub of the chuck by a free end. For mounting the drive shaft, a hollow support projects into the open end of the chuck, wherein a seat for the front bearing shaft is formed in the interior of the hollow support. The bearing of the front bearing shaft has two roller bearings which are arranged between the bearing shaft and the inner bearing sleeve. The inner bearing sleeve is insert-fitted into the outer bearing sleeve, wherein a plurality of rubber elements are provided for damping between the two bearing sleeves. Furthermore, an additional damping element is arranged between the outer bearing sleeve and the hollow support. Here an O-ring is used as the damping element.

Due to the use of two bearing sleeves which are nested one inside the other, the installation space required by the known winding spindles is increased, so that only with relatively large chuck diameters relatively large lengths can be achieved. On the other hand, O-rings used as damping elements have the disadvantage that the damping cross section is specified with relatively coarse tolerances. The receiving grooves in these bearing sleeves must therefore be provided with correspondingly large tolerances in order to avoid an undesirable lack of compressibility. However, this has a negative effect on the damping behavior of the rubber element. Moreover, the receiving grooves affect the production of the components of the winding spindle.

From DE 10037201 a 1a winding machine with a winding spindle is known, in which the chuck is driven by a one-piece drive shaft which is mounted a number of times in a hollow support. Here, a sleeve packet arranged on the outer or inner diameter of the hollow support is provided as the damping device. The sleeves are movable relative to each other within the sleeve pack to counteract vibrations of the hollow support by internal friction. This type of vibration compensator also requires considerable additional mounting space, which comes at the expense of the strength or large diameter of the chuck. However, the diameter of the chuck is predetermined by the winding tube and cannot be freely selected.

Disclosure of Invention

The object of the present invention is now to construct a winder of the generic type which, despite the limited outer diameter, still has a very large number of projecting chucks for high winding speeds.

A further object of the present invention is to provide a winding machine with winding spindles whose chucks can be used across a plurality of critical speeds.

According to the invention, this object is achieved in that an additional damping device is provided between the front bearing shaft and the hollow support, which additional damping device is arranged axially offset outside the bearing.

The invention is based on the following principle, namely: damping can be particularly effective only at locations where the hinge points acting on the damping means can perform a mutual relative movement. To this end, the vibration of the front bearing shaft coupled to the chuck is damped directly using the mounting space between the front bearing shaft and the hollow support. A further advantage of the invention is that no considerable additional installation space is required for integrating the damping device between the bearing shaft and the hollow support. No additional radial installation space is required.

In order to obtain a highly effective damping action, the improvement of the invention is particularly advantageous in that the damping means are arranged on the shaft portion of the front bearing shaft between the abutment and the end connected to the chuck. Here, the damping means is positioned near the chuck connection point, which shows a high damping both in the case of critical winding speeds in a relatively low range and in the case of critical winding speeds in a relatively high range.

In order to be able to drive the chuck by the drive shaft without considerable frictional losses, it is preferred to implement the improvement of the invention in which the damping means are formed by a damping bearing held on the circumference of the front bearing shaft. It is important here that the damping bearing remains almost free of any stress imposed by its own weight and the weight of the chuck. The damping bearing is only active when transmitting resonance.

The damping bearing is preferably formed by at least one roller bearing and a further damping element supported on the outer ring of the roller bearing. In this regard, the roller bearing forms a hinge point for the damping element, which hinge point originates from the swivel bearing shaft.

Preferably, the damping element is formed by a damping ring having an inner sleeve and an outer sleeve surrounding the inner sleeve in a spaced apart manner therefrom, the inner sleeve and the outer sleeve being resiliently interconnected by a rubber element. The installation space is thus independent of the respective rubber element and depends only on the diameter of the inner sleeve and the outer sleeve. The spring properties of the rubber element between the inner and outer sleeve can thus be configured to have predetermined damping properties before the rubber element is mounted.

The damping ring may be configured in such a manner that the width of the inner sleeve is smaller than, equal to, or larger than the width of the outer sleeve, depending on the installation position. The mobility of the sleeves relative to each other can thus be influenced in particular.

In order to achieve a reliable guidance of the damping element in the hollow support relative to the front bearing shaft, the roller bearing is formed by two spindle bearings held side by side in an O-shaped arrangement on the front bearing shaft. The damping bearing thus has no influence on the adjacent abutment of the front bearing shaft.

In order to obtain a damping effect which is as predetermined as possible at each position of the drive shaft, it is further provided that: the bearing of the front bearing shaft is formed by two roller bearing units arranged spaced apart from one another, which are arranged in a bearing bush and which is held in the hollow support by means of a plurality of damping rings. It is thus possible to obtain an additional damping adjusted for the damping bearing, which in particular results in a comparatively large operating range over the entire range of winding speeds.

Further configured to: the rear bearing shaft mount is damped relative to the hollow support by a plurality of damping rings. Thus, it is possible to advantageously damp the vibration stress generated in the drive train from the drive side as well as from the exit side.

Drawings

The winding spindle according to the invention will be described in more detail below by means of several exemplary embodiments with reference to the accompanying drawings.

In the figure:

FIG. 1 schematically illustrates a side view of an exemplary embodiment of a winder;

fig. 2 schematically shows a cross-sectional view of one of the winding spindles of the exemplary embodiment of fig. 1;

FIG. 3 schematically illustrates a cross-sectional view of a damping ring;

FIG. 4 schematically illustrates a cross-sectional view of another exemplary embodiment of a damping ring;

FIG. 5 schematically illustrates another exemplary embodiment of a damping bearing;

fig. 6 shows a diagram of the curve progression of the dynamic primary indicator with respect to the L/D ratio and the winding speed.

Detailed Description

An exemplary embodiment of a winding machine according to the present invention is schematically illustrated in fig. 1. The winding machine has two largely projecting winding spindles 3.1 and 3.2, the two winding spindles 3.1 and 3.2 being arranged on a winding tower 2, which winding tower 2 is mounted so as to be rotatable in the machine frame 1. Four winding stations 4.1 to 4.4 extend along the winding spindles 3.1 and 3.2, in which four bobbins 6 are wound in parallel. For this purpose, the winding spindles 3.1 and 3.2 are each coupled to a spindle motor 5.1 and 5.2.

The number of winding stations is exemplary. In principle, winding machines of this type have a plurality of winding stations in order to simultaneously wind a plurality of bobbins.

The winding stations 4.1 to 4.4 are assigned a contact pressure roller 9 and a traverse 8, wherein the traverse 8 for each winding station 4.1 to 4.4 has a thread guide which guides in each case one thread in a reciprocating manner. The contact pressure roller 9 is held on a movable roller support 11. The thread penetration is in each case routed by a top thread guide 10, which top thread guide 10 forms the penetration into the winding station.

A plurality of winding tubes 7 engage side by side on the winding spindles 3.1 and 3.2 in order to receive the bobbins 6. For this purpose, each winding spindle 3.1 and 3.2 has a chuck, which is explained in more detail below with reference to fig. 2. Fig. 2 schematically shows a partial view of a cross section of the winding spindle 3.1 or 3.2.

As shown in the illustration in fig. 2, the circumferential chuck 12 of the winding spindle 3.1 has a snap-in sleeve 14, which snap-in sleeve 14 interacts with the clamping device 13 in order to catch a winding tube which is push-fitted onto the circumference of the snap-in sleeve 14. The tube located on the circumference of the snap sleeve 14 is not shown in the illustration of fig. 2.

The chuck 12 is connected to the drive shaft 16 in a rotationally fixed manner. In this exemplary embodiment, the drive shaft 16 is formed by a front bearing shaft 16.1 and a rear bearing shaft 16.2 interconnected by a torsionally rigid coupling 18. The coupling 18 thus preferably has means for torsional damping.

The front bearing shaft 16.1 is connected in a rotationally fixed manner to the hub 15 of the chuck 12 by means of a hub connection 24.

The front bearing shaft 16.1 and the rear bearing shaft 16.2 are each mounted for rotation in the hollow support 20 by a front bearing seat 17.1 and a rear bearing seat 17.2. A hollow support 20 is fastened to the winding tower 2 and projects with protruding ends into the interior of the chuck 12, which is hollow cylindrical on either side of the hub 15. Thereby forming a small space between the circumference of the hollow support 20 and the chuck 12.

The rear bearing 17.2 of the rear bearing shaft 16.2 is constructed in that part of the hollow support 20 which is fastened to the winding tower 2. The rear bearing shaft 16.2 is mounted so as to be rotatable in two roller bearings 27.1 and 27.2. The roller bearings 27.1 and 27.2 are arranged in the bearing bush 21.2. The bearing bush 21.2 is held in the interior of the hollow support 20 by a plurality of damping elements in the form of damping rings 28.1 and 28.2.

The rear bearing 17.2 is configured on one end of the hollow support 20. In the rear abutment 17.2, the rear bearing shaft 16.2 projects outside the hollow support 20 by a drive end, which is configured as a coupling end 19. In this connection, the spindle drive 5.1 or 5.2 is coupled directly to the drive shaft 16 via this coupling end 19.

The front bearing seat 17.1 of the front bearing shaft 16.1 is configured in a protruding part of the hollow support 20. In this exemplary embodiment, the front carrier 17.1 has two roller bearing units 26.1 and 26.2. The roller bearing units 26.1 and 26.2 are arranged in the bearing bush 21.1. The bearing bush 21.1 is supported relative to the hollow support 20 by a plurality of damping elements in the form of a plurality of damping rings 25.1 and 25.2.

Within chuck 12, the free end of hollow support 20 extends just short of hub 15. A further damping device 22 is arranged on the circumference of the drive shaft 16 between the hollow support 20 and the drive shaft 16 in the shaft portion between the bearing 17.1 of the front bearing shaft 16.1 and the hub 15. In this exemplary embodiment, the damping device 22 is formed by a damping bearing 23. The damping bearing 23 has a roller bearing 23.1 held on the circumference of the front bearing shaft 16.1 and a damping ring 23.2 arranged between the outer ring of the roller bearing 23.1 and the hollow support 20. The roller bearing 23.1 is held on the circumference of the front bearing shaft by an inner ring. The outer ring of the roller bearing 23.1 serves to support the damping element 23.2. The damping device 22 can thus be arranged between the front support shaft 16.1 and the fixed hollow support 20 without hindering the rotation of the drive shaft 16.

In addition to fig. 2, reference is also made to fig. 3 in order to illustrate the damping ring 23.2. A sectional view of the damping ring 23.2 is schematically shown in fig. 3. The damping ring 23.2 is formed by an outer sleeve 30 and an inner sleeve 31. A rubber element 32 is arranged between the inner sleeve 31 and the outer sleeve 30. The rubber element 22 is fixedly connected to the inner sleeve 31 and the outer sleeve 30 and forms a rubber spring. The inner sleeve 31 and the outer sleeve 30 can thus be moved relative to each other. The inner sleeve 31 and the outer sleeve 30 are preferably formed of metal so that the rubber element can be secured between the inner and outer sleeves by vulcanization.

As shown in the illustration of fig. 2, the inner sleeve of the damping ring 23.2 is supported on the circumference of the roller bearing 23.1. The outer sleeve of the damping ring 23.2 bears on the inner diameter of the hollow support 20.

Due to the location of the damping bearing 22 in close proximity to the connection between the drive shaft 16 and the chuck 12, very effective damping is achieved, which is effective over the entire speed range when winding the wire. In principle, the position of the damping bearing 22 depends on the layout of the winding spindles. Thus, the chuck 12 must be lowered parallel to itself. In order to keep the rotational related flexural stresses as low as possible, the hub connection between the drive shaft 16 and the chuck 12 is positioned as close as possible to the damping bearing 22. The influence of the damping bearing 22 and the application of the damping rings 25.1 and 25.2 in the region of the front abutment 17.1 can be represented in particular by a dynamic indicator K. It is therefore known that when starting an empty winding spindle, the operating range is defined by the upper mixing critical winding speed, since the resonance amplification occurring on the chuck can no longer be controlled by the existing damping measures. In simplified form, the dynamic indicator of the winding spindle is the result of the following formula:

K＝v_{winding, maximum}/10⁵Meter/min x (L/D)²

In this equation, the maximum winding speed is represented by v_{Winding, maximum}Define, wherein the maximum winding speed in the case of the winding machines known in the prior art is equal to the critical winding speed v_{Critical point of}. Reference character D represents the nominal diameter of the chuck, which is substantially equal to the inner diameter of the convolute duct. Reference L indicates the nominal length of the chuck for receiving the convolute duct.

In fig. 1 and 2, the length L and the nominal diameter D of one of the chucks is identified using the example of the winding spindle 3.1. The length L and the nominal diameter D form the relevant parameters when using a winding spindle.

Thus, in addition to the complex rotor dynamics dependence, the dynamic indicator K takes into account in particular the damping measures and the vibration behavior of the chuck. In the case of the basic design of winding spindles of this type, which is common today, the dynamic indicator K is between the values 8 and 10. Here, a dynamic indicator K depending on the nominal length to nominal diameter ratio (L/D) of the chucks determines a maximum allowable winding speed (v) equal to a critical winding speed defining a winding range.

To this end, in a diagrammatic view, the maximum allowable winding speed is plotted in fig. 6 against the length to diameter ratio L/D of the chuck. Here, the allowable critical winding speed is plotted for each ratio L/D. In this exemplary embodiment, the curve progression of the indicator K with the value K-9 forms the general operating range of winding spindles known from the prior art.

In view of the additional damping measure shown in fig. 2, it has now been successful to substantially extend the operating range of the winding spindle. Thus, for example, the value K23 is used to define the inventive range of the winding spindle according to the invention. The expansion of the operating range in the figure is illustrated by the curve with the value K-23. A substantially longer chuck can thus be operated in particular in a reliably operable manner, with a constant nominal diameter D of the chuck. It is therefore known to wind so-called POY threads to form bobbins in a melt spinning process at a winding speed of, for example, 3000 m/min. To date, winding spindles are limited to a length to diameter ratio of 16L/D. In the case of the winding spindle according to the invention, chucks with a length-to-diameter ratio of up to L/D27 can now be used. With the same nominal diameter, it is thus possible to operate substantially longer chucks. Even at higher winding speeds of 6000 m/min, the length/diameter ratio is likewise increased from L/D12 to L/D20. A particular advantage provided by the winding spindle according to the invention is therefore that the number of winding stations can be almost doubled compared with conventional winding spindles. The length to diameter ratio of the winding spindle is increased by at least 60% in the case of the winding machine according to the invention. Positioning the additional damping device outside the seat of the drive shaft represents a surprisingly significant effect in order to influence the operating range of the winding spindle. In particular, the damping ring integrated in the damping bearing may be configured to have spring damper characteristics suitable for the location of the vibrations and the occurrence of the vibrations.

It has been shown that various design modes can be used for the damping ring when using damping elements in the winding spindle shown in fig. 2, depending on the installation position and the respective hinge point used for damping. Damping rings of different construction modes (such as may be employed as damping ring 23.2 in damping bearing 23, or as damping rings 25.1 and 25.2 on bearing cartridge 21.1, or as damping rings 28.1 and 28.2 on bearing cartridge 21.2) are thus shown in fig. 3 and 4. In the case of the type of construction shown in fig. 3, the inner sleeve 31 is embodied with a smaller width with respect to the outer sleeve 30. The width of the inner sleeve 31 is here indicated as b_IAnd the width of the outer sleeve 30 is denoted b_A. Thus, having b_I＜b_AWherein the rubber member 32 has the width of the inner sleeve 31 at the maximum.

In contrast, the construction type according to fig. 4 has an outer sleeve 30 which is smaller in width than the inner sleeve 31. Here is b_I＞b_AWherein the rubber element 32 has the width of the outer sleeve 30 at maximum. The mobility between the

sleeves

30 and 31 can thus be influenced, in particular by the rubber element 32, while taking into account the elastic coupling.

In the case of an installation space between the front bearing shaft 16.1 and the hollow support 20 which does not have a sufficient installation height for the damping bearing, an exemplary embodiment of a possible damping bearing 23 is schematically illustrated in a sectional view in fig. 5. In the case of the exemplary embodiment according to fig. 5, the roller bearing 23.1 is arranged on the circumference of the front bearing shaft 16.1. In this exemplary embodiment, the roller bearing 23.1 is formed by two spindle bearings 33.1 and 33.2 held in an O-shaped arrangement. The abutment 17.1 of the front bearing shaft 16.1 thus remains completely unaffected, thus ensuring reliable guidance and positioning of the damping ring.

Two support sleeves 29.1 and 29.2 are supported on the outer ring of the roller bearing 23.1, the support sleeves 29.1 and 29.2 in each case being supported on the damping rings 23.2 and 23.2' in each case by means of a collar end which is located outside the roller bearing 23.1. The damping rings 23.2 and 23.2' are embodied identically to the above-described exemplary embodiment of the sealing ring. In this connection, the mounting height of the damping bearing 23 can be reduced considerably, so that neither the drive shaft 11 nor the hollow support 20 in the winding spindle have to be weakened.

The winding machine according to the invention is suitable for all common melt spinning processes, whereby the newly extracted threads are wound in parallel as thread groups to form bobbins. Thus, a synthetic yarn generated in POY, FDY, or IDY may be simultaneously wound in a yarn group having a plurality of yarns to form a bobbin. However, the winder is also suitable for a BCF process whereby a plurality of splice wires are wound to form a bobbin.

Claims

1. A winding machine for winding a group of threads into a plurality of bobbins, having at least one winding spindle (3.1, 3.2) with a largely protruding chuck (12) for receiving a plurality of winding tubes (7), the chuck (12) being drivable by a multipart drive shaft (16) mounted in a hollow support (20), a rear bearing shaft (16.2) being coupleable to a spindle drive (5.1, 5.2), a front bearing shaft (16.1) connected to the rear bearing shaft (16.2) being coupled to the chuck (12) and the front bearing shaft (16.1) being damped relative to a seat (17.1) of the hollow support (20) by a plurality of damping elements (25.1, 25.2), wherein the seat (17.1) comprises two roller bearing units (26.1, 26.2), the roller bearing units (26.1, 26.2) being arranged in a bearing bush (21.1), the bearing bush (21.1) is supported relative to the hollow support (20) by means of the damping elements (25.1, 25.2), characterized in that an additional damping device (22) is provided between the front bearing shaft (16.1) and the hollow support (20), which additional damping device (22) is arranged axially offset outside the bearing seat (17.1).

2. Spooling machine as claimed in claim 1, characterized in that the damping device (22) is arranged on the shaft part of the front bearing shaft (16.1) between the abutment (17.1) and the end connected to the chuck (12).

3. Spooling machine as claimed in claim 1 or 2, characterized in that the damping device (22) is formed by a damping bearing (23) which is held on the circumference of the front bearing shaft (16.1).

4. Spooling machine as claimed in claim 3, characterized in that the damping bearing (23) is formed by at least one roller bearing (23.1) and another damping element (23.2) supported on the outer ring of the roller bearing (23.1).

5. Spooling machine as claimed in claim 4, characterized in that the damping element is formed by a damping ring (23.2) having an inner sleeve (31) and an outer sleeve (30), the outer sleeve (30) surrounding the inner sleeve (31) in a spaced-apart manner from the inner sleeve (31), the inner sleeve (31) and the outer sleeve (30) being resiliently interconnected by a rubber element (32).

6. Spooling machine as claimed in claim 5, characterized in that the damping ring (23.2, 25.1, 25.2) is at the width (b) of the inner sleeve (31)_I) Is smaller or larger than the width (b) of the outer sleeve (30)_A) The method (1) is as follows.

7. Spooling machine as claimed in claim 4, characterized in that the roller bearing (23.1) is formed by two spindle bearings (33.1, 33.2) held side by side in an O-shaped arrangement on the front bearing shaft (16.1).

8. Spooling machine as claimed in claim 1, characterized in that the bearing (17.1) of the front bearing shaft (16.1) is formed by two roller bearing units (26.1, 26.2) arranged at a distance from each other, the roller bearing units (26.1, 26.2) being arranged in a bearing bush (21.1), and the bearing bush (21.1) being held in the hollow support (20) by means of a plurality of damping elements (25.1, 25.2).

9. Spooling machine as claimed in claim 1, characterized in that the abutment (17.2) of the rear bearing shaft (16.2) is damped relative to the hollow support (20) by means of damping rings (28.1, 28.2).