EP3243944A1 - Support disk for bearing for a shaft of an open-end spinning rotor and bearing for a shaft of an open-end spinning rotor - Google Patents

Abstract

A support disk (4) for a bearing (1) for a shaft (3) of an open-end spinning rotor (2) has a disc-shaped base body (8) and a covering (9) applied on an outer periphery of the base body (8) Outside surface provides a running surface (10) for the shaft (3) of the open-end spinning rotor (2). The running surface (10) is formed by two support surfaces (11) spaced from one another in the axial direction of the support disk (4), and a groove-like recess (12) is formed between the bearing surfaces (11). The groove-like recess (12) has a width (B) which is at least equal to or wider than an entire support width (AB1, AB2) of the two bearing surfaces (11). A bearing (1) for a shank (3) of an open-end spinning rotor (2), which is storable with its shank (3) in a wedge-shaped gap (7) of paired support discs (4), the support discs (4) are formed accordingly ,

Description

The present invention relates to a support disk for a bearing for a shaft of an open-end spinning rotor. The support disk has a disc-shaped base body and a coating applied to an outer circumference of the base body. The radial outer surface of the lining provides a running surface for the shaft of the open-end spinning rotor, wherein the running surface is formed by two support surfaces in the axial direction of the support disc spaced support surfaces, each having a support width, and wherein between the support surfaces a groove-like recess is formed.

Support disks for the storage of open-end spinning rotors have become known in the prior art in a variety of configurations. Due to the high rotational speed of the spinning rotors while the support disks or in particular their tread are exposed to considerable stresses, which lead to high wear of the tread. This can lead to a non-circular running of the spinning rotor, in particular after a prolonged use of the support disks, which further accelerates damage to the tread. One of the main causes of the wear of the lining consists in the occurring during operation of the open-end spinning rotor heating due to the flexing occurring in the lining.

It was therefore, for example, in the DE 34 47 600 A1 already proposed to provide a circumferential groove in the middle of the treads to improve the heat dissipation from the lining. For a good heat dissipation by air flow while the groove was carried out so deep that the depth was about half of the total pad depth. Such a deep groove can However, due to the notch effect lead to increased stress on the surface.

After DE 37 19 445 A1 however, the groove is just made so deep that the shaft of the spinning rotor just does not touch the outer surface of the tread in this area. The circumferential groove is thus made rather flat, whereby a relief of the tread in the middle region of the covering should be achieved. An increased stress by notch effect is thereby avoided.

However, the problems of heating and wear of the support disks occur with increasing rotor speeds to an increased extent. This leads due to today's spinning machines, which often have more than 500 spinning stations, also to a considerable energy consumption in the rotor bearing. Object of the present invention is therefore to propose a support disk, which can be operated with a low energy input.

The object is solved with the features of the independent claims.

A support disk for a bearing for a shaft of an open-end spinning rotor has a disc-shaped base body and a coating applied to an outer circumference of the base body. The radial outer surface of the pad provides a tread for the shaft of the open-end spinning rotor. The running surface is formed by two supporting surfaces in the axial direction of the support disc spaced support surfaces, wherein a groove-like recess is formed between the support surfaces. It is envisaged that the groove-like recess has a width which is at least equal to or wider than a sum of the support widths of the two bearing surfaces. The entire support width for the spinning rotor thus results from the sum of the individual support widths. The width refers in the context of the present invention to the extent of the support disk or the bearing surfaces of the axial direction of the support disk and thus on the relevant for the storage of the spinning rotor support width.

The present invention is based on the assumption that, in order to reduce the load on the support disks, it is not only necessary to remove the heat from the lining by cooling, but that it is also essential to reduce the heat development in the lining of the support disks from the outset. The groove-like recess is therefore designed with a particularly large width, so that this acts not only as a cooling groove, but at the same time as a deformation joint. Due to the particularly wide executed groove-like recess, the deformation of the lining is facilitated and reduces the flexing work and at the same time improves the cooling. In order to reduce the heat development in the region of the support surfaces, the wide support width achieved by the wide recess contributes to the shaft of the spinning rotor, which enables a particularly stable support of the spinning rotor. It is also advantageous that despite the groove-like recess, the entire support width of the two bearing surfaces is relatively wide. Under the total circulation width is understood to be the sum of all individual support widths of the bearing surfaces. The heat development in the support disc covering is thereby very uniform over the entire support width, so that local overheating in the covering and concomitant wear and tear can be avoided. Due to the described effect of the tread, which leads to a reduced heat development on the one hand and in addition to an improved cooling on the other hand, it is possible to operate an open-end spinning device particularly energy-efficient.

It is advantageous, for example, if the groove-like recess has a width which is 1.3 times, preferably 1.5 times as wide as the entire support width of the two bearing surfaces. If the bearing surfaces are rounded or provided with a chamfer, the rounded or bevelled areas are not part of the bearing surface.

It is particularly advantageous if the groove-like recess is rounded concave. In this case, a radius of curvature of the groove-like recess is at least 0.6 times, preferably at least 0.7 times and particularly preferably at least 0.8 times the width of the recess. It is particularly advantageous if the groove-like recess is rounded completely concave, in the present case a rounding over the entire width of the recess is understood with a constant radius of curvature. This means that the groove-like recess has a circular arc-shaped contour in a cross section through the axis of rotation of the support disk. It has been found that by means of such a geometry, a particularly good flow of cooling air and heat dissipation from the lining into the base body of the support disk can take place.

According to an alternative embodiment, however, it is also possible that the groove-like recess has two mutually opposite groove flanks and a groove base connecting them. The transition regions between the groove base and the groove flanks are each rounded concave, wherein preferably a rounding radius is at least 0.2 times the width of the recess. By rounding the transition regions with a comparatively large radius of curvature, it is also possible, as described above, to improve the cooling air flow and the heat dissipation from the lining into the base body.

According to an advantageous embodiment of the invention, the bearing surfaces are flat. This in turn results in a particularly stable support of the spinning rotor with a uniform load and heat generation, so that the risk of local overheating is reduced.

In order to achieve the widest possible support for the spinning rotor and to avoid local overheating, it is also advantageous if the running surface between the groove-like recess and adjacent to the recess bearing surfaces each having a convexly rounded transition.

By this measure it is ensured that the spinning rotor can actually rest on the newly executed bearing surfaces. It is also advantageous if the transition region between the bearing surfaces and the outwardly facing side surfaces of the lining is provided with a chamfer or a rounding.

Furthermore, it is advantageous if the two bearing surfaces have the same contact width. A uniform heat development within the lining and thus a uniform discharge into the body is thereby supported.

According to another embodiment of the invention, it is advantageous if the covering consists of nitrile rubber (NBR), preferably of hydrogenated acrylonitrile-butadiene rubber (HNBR). The bearing surfaces are thereby antistatic, so that contamination of the treads are avoided.

In addition, it is advantageous if an adhesive surface of the main body without protrusions or depressions, i. smooth, and preferably executed flat. The burden of the lining can thus be made uniform and thus reduced overall.

In a storage for a shaft of an open-end spinning rotor with paired, forming a wedge-gap supporting discs of open-end spinning rotor with its shaft in the wedge-gap storable. It is provided that the support disks are formed according to one or more of the features described above. It is thereby possible a particularly energy-saving and low-wear operation of the storage for the open-end spinning rotor.

Figur 1

eine Lagerung für einen Schaft eines Offenend-Spinnrotors in einer schematischen Draufsicht,

Figur 2

einen Querschnitt einer Stützscheibe in einer Übersichtsdarstellung,

Figur 3

eine abgebrochene, geschnittene Detaildarstellung einer Stützscheibe nach einer ersten Ausführung sowie

Figur 4

eine abgebrochene, geschnittene Detaildarstellung einer Stützscheibe in einer zweiten Ausführung.

Further advantages of the invention will be described with reference to the embodiments illustrated below. Show it:

FIG. 1

a bearing for a shaft of an open-end spinning rotor in a schematic plan view,

FIG. 2

a cross section of a support disk in an overview,

FIG. 3

a broken, cut detail of a support disk according to a first embodiment as well as

FIG. 4

a broken, cut detail of a support disk in a second embodiment.

FIG. 1 shows a schematic overview of an open-end spinning device with an open-end spinning rotor 2 and a storage 1 for supporting a shaft 3 of the open-end spinning rotor 2. The storage 1 includes in a conventional manner a bearing block 6, which carries two support disk bearings 17. The support disk bearings 17 are held in recordings of the bearing block 6 for this purpose. In the support disk bearings 17 each have an axis 5 of the support disks 4 is mounted, which in turn carries two support disks 4 in turn.

The two axes 5 with their support disks 4 are now arranged such that two support disks 4 each form a support disk pair. In each case, a wedge gap 7 is formed between the two support disks 4 of a support disk pair, in which the shaft 3 of the open-end spinning rotor 2 is accommodated. The open-end spinning rotor 2 is driven by means of a drive device, not shown, for example by means of a tangential belt, and transmits its rotation to the support disks 4th

For storage of the open-end spinning rotor 2, a thrust bearing 18 is further provided on the bearing block 6, which may be formed for example as a thrust bearing or as an air bearing. The axes 5 of the support disks 4 are slightly inclined to each other, so that an axial thrust is exerted on the open-end spinning rotor 2 and this is pressed in the direction of the thrust bearing 18.

During operation, the open-end spinning rotor 2 rolls with its shaft 3 on running surfaces 10 of the support disks 4. The structure of the support disks 4 is now based on the FIG. 2 explained. FIG. 2 shows a cross section or a section through the axis of rotation of a support disk 4. The support disk 4 in this case has a disc-shaped base body 8, on the outer circumference of a covering 9 is applied from an elastic material. The covering 9 in turn provides on its outer circumference the running surface 10 for the shaft 3 of the open-end spinning rotor 2. Due to the very high rotational speeds of the open-end spinning rotor 2, due to the flexing work occurring between the shaft 3 and the running surfaces 10, the lining 9 heats up, which leads to wear and damage to the lining 9 of the support disks 4 over time.

The design of the pad 9 with the tread 10 will now be based on the FIG. 3 described. FIG. 3 shows a broken, cut detail of a support disk 4 with the pad 9. The pad 9 has two spaced and separated by a groove-like recess 12 bearing surfaces 11, which each have a bearing width AB1, AB2. In the present case, both bearing surfaces 11 each have the same bearing width AB1, AB2. The entire support width for the shaft 3 of the open-end spinning rotor 2 is formed by the sum of the individual support widths AB1, AB2 of the two individual support surfaces 11.

The groove-like recess 12 in this case has a width B, which is at least the same width or even wider than the entire support width, ie the sum of the support widths AB1, AB2 of the two support surfaces 11. In contrast to the recesses 12 on known support plates 4, which as Rectangular grooves have been performed, the present recess 12 is concave rounded, the rounding radius R of the groove-like recess 12 over the width B of the groove-like recess 12 is constant. The bearing surfaces 11 are also formed flat according to the present illustration. By the flat bearing surfaces 11, which cause a wide span for the shaft 3 due to the relatively wide recess 12, a particularly uniform support of the spinning rotor 2 can be achieved, which avoids local overheating. At the same time the deformation of the lining 9 is facilitated by the particularly wide recess 12, so that despite the wide bearing surfaces 11, the flexing work in the pad 9 can be reduced. Furthermore, a particularly good cooling air flow and a particularly good heat dissipation from the claimed areas of the bearing surfaces 11 can be achieved by in the direction of the groove bottom 14 toward increasing depth of the recess 12.

In order to reduce local overheating of the lining 9, furthermore, the transitions 16 between the recess 12 and the bearing surfaces 11 are also rounded. By rounding with the radius of curvature r ₂ , which is substantially smaller than the rounding radius R of the groove-like recess 12, it can be ensured that the shaft 3 of the open-end spinning rotor 2 can rest over the full support width AB1, AB2 of the two bearing surfaces 11. In addition, for the same reason, the transition from the bearing surfaces 11 to the outer surfaces of the pad 9 may be provided with a chamfer or a rounding, even if this is not shown here.

The entire covering 9 of the support disk 4 preferably has a covering width BB of at least 8 mm. Preferred is a covering width BB of at least 9 mm and more preferably of at least 9.8 mm. While in support discs 4 of the prior art has often been trying to reduce the width of the support plates 4 and the covering width BB, thereby reducing the flexing work, the present invention assumes that a reduction in the load of the covering 9 also by a Homogenization of the load of the covering is possible. In this case, due to the comparatively wide design of the support disk 4 and the covering 9 and the adhesive surface 19 between the base body 8 and the pad 9 made comparatively wide, which improves the adhesion of the pad 9 and also improved heat dissipation from the pad 9 in the Base 8 allows.

According to the present illustration, the covering width BB corresponds to the sum of the total support width AB1, AB2 of the two support surfaces 11 and the width B of the groove-like recess 12, ie BB = AB1 + AB2 + B. However, it is also within the scope of the invention, the covering width greater than to choose the sum of the total support width AB1, AB2 and the width B of the groove-like recess 12. For example, one or both bearing surfaces 11 may in this case be set back relative to the adjacent, circular end face of the support disk 4. A slightly wider covering width BB than the sum of the total support width AB1, AB2 and the width B continues to be obtained even if the bearing surfaces at the transition to the outer surfaces of the lining 9 or to the end faces of the support disc have a chamfer or a rounding.

An alternative embodiment of a support plate 4 with a wide groove-like recess 12 is in FIG. 4 shown. The support disk 4 has substantially the same structure as that of the FIG. 3 on, so that in the following only on the differences to FIG. 3 will be received. In contrast to the recess 12 of the FIG. 3 In this case, the recess 12 is not completely concave rounded, but has a groove bottom 14 and lateral groove flanks 13. The transition regions 15 between the groove bottom 14 and the groove flanks 13 are rounded with a comparatively large rounding radius r ₁ . This in turn can be achieved that the groove-like recess 12 can serve as a deformation joint and thereby the flexing work between the pad 9 and the shaft 3 of the open-end spinning rotor 2 is reduced. The transitions 16 between the recess 12 and the support surfaces 11 are in turn rounded with a rounding radius r ₂ to ensure a uniform support of the shaft 3 of the open-end spinning rotor 2 and to reduce overheating of the covering 9 in this area. For reasons of clarity, the groove flank 13, the transition 16 between recess 12 and bearing surface 11, the transition region 15 between groove base 14 and groove flank 13, and the radius of curvature r _{1 of} the transition region 15 are only shown on one side of the symmetrically constructed support disk 4.

In the Figures 3 and 4 are the two bearing surfaces 11 always shown with a respective same bearing width AB1, AB2. Although it is conceivable in principle to provide the two bearing surfaces 11 with a different bearing width AB1, AB2, for a uniform load of the lining 9 of the support disk 4 and a uniform heat development, it is advantageous to equip the two bearing surfaces 11 each with the same support width AB , Furthermore, it is advantageous in both cases if the lining 9 consists of a rubber-based material such as, for example, acrylonitrile-butadiene rubber (HNBR). This has good damping properties and thereby also ensures a round, smooth running of the spinning rotor 2, so that shocks and vibrations, which also contributed to the wear of the lining 9, are reduced. In addition, although such a material has antistatic properties, so that contamination of the tread 10 by fiber and dust deposits, which can also cause a smooth running of the spinning rotor 2, are prevented.

The invention is not limited to the illustrated embodiments. Variations and combinations within the scope of the claims also fall under the invention.

LIST OF REFERENCE NUMBERS

1

storage

2

Open-end spinning rotor

3

shaft

4

support disc

5

axis

6

bearing block

7

nip

8th

body

9

covering

10

tread

11

bearing surface

12

groove-like recess

13

flank

14

groove base

15

Transition area between groove base and groove flank

16

Transition between recess and bearing surface

17

Supporting disk bearing

18

thrust

19

adhesive surface

B

Width of the groove-like recess

R

Rounding radius of the groove-like recess

FROM

Support width

r ₁

Rounding radius of transition areas

r ₂

Rounding radius of the transitions

BB

layer width

Claims (10)

Support disk (4) for a bearing (1) for a shaft (3) of an open-end spinning rotor (2), wherein the support disk (4) has a disc-shaped base body (8) and a covering (9) applied on an outer periphery of the base body (8) ), the radial outer surface of which provides a running surface (10) for the shaft (3) of the open-end spinning rotor (2), wherein the running surface (10) is formed by two bearing surfaces (11) spaced from one another in the axial direction of the supporting disk (4) , each having a support width (AB1, AB2), and wherein between the support surfaces (11) has a groove-like recess (12) is formed, characterized in that the groove-like recess (12) has a width (B), at least the same width or wider than a sum of the support widths (AB1, AB2) of the two bearing surfaces (11). Support disc according to the preceding claim, characterized in that the groove-like recess (12) is rounded concave, wherein a radius of curvature (R) of the groove-like recess (12) at least 0.6 times, preferably at least 0.7 times and especially preferably at least 0.8 times the width (B) of the recess (12) is. Supporting disc according to claim 1, characterized in that the groove-like recess (12) has two mutually opposite groove flanks (13) and a groove base (14) connecting them, and that transition regions between the groove base (14) and the groove flanks (13) are each concavely rounded , wherein preferably a rounding radius (r1) is at least 0.2 times the width (B) of the recess (12). Supporting disc according to one of the preceding claims, characterized in that the bearing surfaces (11) are planar. Supporting disc according to one of the preceding claims, characterized in that the running surface (10) between the groove-like recess (12) and the recess (12) adjacent bearing surfaces (11) each have a convexly rounded transition (16). Supporting disc according to one of the preceding claims, characterized in that the two bearing surfaces (11) have the same bearing width (AB1, AB2). Supporting disc according to one of the preceding claims, characterized in that the covering (9) has a covering width (BB) of at least 8 mm, preferably of at least 9 mm and particularly preferably of at least 9.8 mm. Supporting disc according to one of the preceding claims, characterized in that the covering (9) consists of nitrile rubber (NBR), preferably of hydrogenated acrylonitrile-butadiene rubber (HNBR). Supporting disk according to one of the preceding claims, characterized in that an adhesive surface (19) of the base body (8) without projections or depressions and preferably is flat. Bearing (1) for a shaft (3) of an open-end spinning rotor (2) with paired, a wedge gap (7) forming support discs (4), said open-end spinning rotor (2) with its shaft (3) in the wedge gap ( 7) is storable, characterized in that the supporting discs (4) are formed according to one of the preceding claims.

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