WO2011064062A1

WO2011064062A1 - Anti-friction bearing having bump-like projections which are attached to the bearing outer ring

Info

Publication number: WO2011064062A1
Application number: PCT/EP2010/066217
Authority: WO
Inventors: Norbert Radinger; Tomas Smetana; Florian Dörrfuß
Original assignee: Schaeffler Technologies Gmbh & Co. Kg
Priority date: 2009-11-30
Filing date: 2010-10-27
Publication date: 2011-06-03
Also published as: CN102667194A; DE102009056352B4; DE102009056352A1; CN102667194B

Abstract

The invention relates to an anti-friction bearing (1) having a bearing inner ring and a bearing outer ring (2) which is arranged radially outside the former, between which rolling bodies are positioned, wherein there is a single-piece decoupling element (3) radially outside the bearing outer ring (2) as vibration damper which engages around the bearing outer ring (2) at least in sections and rests with a bearing section (4) of at least partially cylindrical design on the outer circumferential surface of the bearing outer ring (2), wherein the bearing section (4) is interrupted in the axial direction by a spring section (5), in which the decoupling element (3) is spaced apart from the outer circumferential surface of the bearing outer ring (2). According to the invention, two bump-like projections (6) which extend at least partially over the circumference and on which the bearing section (4) rests are present on the outer circumferential surface of the bearing outer ring (2).

Description

Name of the invention

Rolling bearing mounted on the bearing outer ring hump-like projections Description

Field of the invention

The invention relates to a rolling bearing with a bearing inner ring and a radially outwardly disposed bearing outer ring, between which rolling elements are positioned, wherein radially from outside the bearing outer ring a one-piece decoupling element is provided as a vibration damper, which surrounds the bearing outer ring at least partially and with an at least teilzy- linderförmig designed support portion rests on the outer circumferential surface of the bearing outer ring, wherein the support portion is interrupted in the axial direction by a spring portion, wherein the decoupling element is spaced from the outer circumferential surface of the bearing outer ring.

Background of the invention

Such roller bearings, which comprise rolling elements rolling elements, are known from the prior art as DE 10 2007 045 671 A1, DE 221409 A1 or DE 3041804 A1. As rolling elements balls, rollers, rollers, needles, cones or similar elements can be used. These rolling elements are usually held in a cage which is present between the bearing inner ring and the bearing outer ring.

Such bearings are used for the storage of waves. Such waves find u. a. also in continuously variable transmissions application. Such transmissions are referred to as CVT transmissions.

On a shaft used in such a CVT transmission conical disk wheels are often mounted, which are at least. By a belt be partially entwined. The conical disk wheels are mutually adjustable, but the belt means, such as. Lamella chains, remain in contact with the conical disk wheels. In such CVT transmissions unwanted vibrations occur, which are then transmitted via the shaft, the bearing inner shell, the rolling elements and the outer bearing shell on a rolling bearing receiving housing. It is mainly transmitted structure-borne noise. Since the housing is often used together with the CVT transmission in motor vehicles such as cars or trucks, but also tractors and earth-moving machinery, there is the increased demand for noise emissions to take into account.

This fundamental task of sound reduction or avoidance of sound transmission is already discussed in the prior art. Thus, DE 10203307 A1 discloses a storage concept for rotating shafts. There, three different approaches are explained to prevent sound transmission from the bearing outer ring to a housing. Thus, for example, it is suggested to put a partially cylindrical sleeve over the bearing outer ring, wherein the sleeve has projections which project alternately inwards or outwards. The projections are aligned in an axial direction of the bearing and interrupted in the circumferential direction to each other.

It is also disclosed in DE 10203307 A1 that a sleeve-like combination element is used which has an elastic layer between two metal layers, wherein one metal layer is in contact with the housing and the other metal layer is in contact with the outer ring of the bearing.

Another solution is offered in DE 10203307 A1 in that a plurality of wave-shaped spring elements, which have no continuous cross-section, are combined with each other, wherein the elevations and depressions are arranged offset from one another. This thus created ring of several elements is then positioned on the outside of the bearing outer shell. It is also known to combine several resilient elements and to press from the outside with a fuse bushing on the bearing outer ring. Furthermore, it is known to combine two semi-cylindrical segments complementary to each other from the outside of the bearing outer ring. The elements lie flat on the outer surface of the bearing outer ring. Arranged orthogonally inwardly from this area, shelves are arranged which are in abutment with the axial outer sides of the bearing outer ring. Furthermore, slits are made both in the rims and in the sections which are in contact with the outer surface of the bearing outer ring.

DE 10307842 A1 also discloses a multiplicity of potential solutions for the general task in the field of application. Thus, for example, a sleeve enclosing the bearing outer ring is disclosed, which has radial bulges projecting radially outward in a central region of abutment sections.

However, the known from the prior art solutions are complex in manufacturing and therefore very expensive. Thus, for example, the introduction of the illustrated slots was previously only possible by expensive wire or laser cutting process. However, it then raises the disadvantage that in addition to a radial displacement of the rolling bearing then an axial displaceability due to the distortion of the outer sleeve surrounding the sleeve is the result.

The solution possibilities disclosed in DE 10307842 A1 are also still capable of improvement, since their implementation is relatively complicated.

Object of the invention

Based on the stated disadvantages of the solutions of the known prior art, it is an object of the present invention to avoid the disadvantages of the prior art and an inexpensive, efficient and to provide long-lasting noise avoidance capability for the storage of CVT transmission shafts.

Description of the invention

The object is achieved in that on the outer circumferential surface of the bearing outer ring two at least partially extending over the circumference hump-like projections are present, on which rests the support portion.

The support is no longer necessarily present at the ends of the Borden, but is kept on the inside of the decoupling elements in the region of the largest inner diameter. In order to provide a resilient region of the decoupling element, ie also to provide a region in which a part of the decoupling element is movable in the direction of the bearing inner ring, the hump-like projections provide a compression region between them.

Noise optimization in continuously variable transmissions can thus be realized efficiently. The resulting vibrations on the chain links of the CVT chain, which are transmitted via the bearings on the gear housing, can be reduced thereby. A decoupling of the housing in the radial direction is possible even with fixed bearings, which are still fixed in the axial direction. The housing vibrations and thus the sound emissions can be significantly reduced.

The tolerance chain is not extended either. Also, the diameters of the shelves do not necessarily need to be ground to ensure proper function at all. As a result, a large number of grinding tolerances no longer add up.

The decoupling element may have a closed continuous cross-section or be broken at one point. In other words For example, the decoupling element may have a tubular shape or the shape of a slotted sleeve. In this way, different types of installation can be realized, which increases the freedom of design. Advantageous embodiments are claimed in the subclaims and are explained in more detail below.

Thus, it is advantageous if the spring portion is located between two radially oriented imaginary planes through the projections. The spring portion can then insert into a compression region between the projections and thereby provide the desired vibration reduction effect.

The anti-friction bearing can be designed to be particularly slip-resistant if the decoupling element is designed as a sleeve with a cylindrical bearing section.

If in the axial direction, outside of the support portion and arranged transversely to the bearing inner ring facing shelves, are formed, so the decoupling element can be positioned precisely on the bearing outer ring in the axial direction. It is also advantageous if the shelves take an orthogonal angle to the cylindrical support portion. The positionability of the decoupling element relative to the bearing outer ring can then be realized while simultaneously simplifying the production process.

It is also advantageous if in a further embodiment, the spring portion has recesses. In this way, the spring behavior can be specifically adjusted so that the necessary radial rigidity is ensured. It is then possible to realize radial stiffnesses of 150,000 N / mm ² with a setting range of 20,000 N / mm ² around this value. The recesses may be circular, triangular or slot-shaped. If the triangles are formed isosceles, this is further advantageous. It is also advantageous if the triangles are aligned with each other and offset from each other. In a circular design of the recesses, it has proven to be advantageous if three staggered rows are introduced into the section. The recesses do not necessarily end outside of the support portion, but may even partially project into it. If the shelves are configured recess-free, an axial displacement of the decoupling element is prevented because the shelves have a stabilizing effect on the decoupling element under the action of axial forces and are not weakened. It is also advantageous if the decoupling element in a connecting region between one of the ribs and the support section has a dilution to the disposal position of a crimping step. In this way, a cup-shaped preformed decoupling element with a continuous opening from the one side can be applied to the bearing outer ring and then reshape it by a crimping process so that the second board extends inwardly away from the crimping step. A simple manufacturing process with simultaneous precise production of the rolling bearing can then be realized.

If the shelves have radially inwardly extending abutment surfaces, which lie opposite each other and are in planar contact with a shoulder of a recess on the outer surface of the bearing outer ring, wherein the recess is formed in each case as a preferably circumferential groove at the axial end of the bearing outer shell, can be to further increase the quality of the rolling bearing.

It is also advantageous if the projections extend without interruption over the circumference of the outer lateral surface of the bearing outer shell. A uniform force transfer is then the result. Furthermore, it is advantageous if the outer sides of the shelves are flush with the outer sides of the bearing outer shell in the axial direction. The housing then does not have to be specially prepared for the rolling bearing.

If the dilution is formed as formed on the inside of the decoupling element circumferential groove, so the decoupling element can be prepared with simple means for the crimping.

Brief description of the drawings

The invention will be explained in more detail in several preferred embodiments with reference to the accompanying drawings. Showing:

1 shows a section shown in cross section through a first

Embodiment of a rolling bearing in the region of a bearing outer ring and a first decoupling element;

Figure 2 is a perspective view of the decoupling element of the first embodiment of FIG. 1;

Figure 3 shows a second embodiment of a decoupling element on a bearing outer ring in a cross-sectional view;

Figure 4 shows the second embodiment of a decoupling element in a perspective view;

Figure 5 shows a third embodiment of a decoupling element on the bearing outer ring in cross section;

Figure 6 shows the third embodiment of the decoupling element in a perspective view. Detailed description of the drawings

The figures are merely schematic in nature and are for the sole purpose of understanding the invention. The same reference numbers are used for the same elements.

FIG. 1 shows a section of a first rolling bearing 1 according to the invention. A bearing inner ring is not shown, just as the rolling elements, which are stored in a cage. Only the bearing outer ring 2 is shown. Also, a radially outside of the bearing outer ring 2 arranged decoupling element 3 is shown. The decoupling element 3 has a support section 5 interrupted by a spring section 4. The support section 5 abuts on hump-like projections 6. The axial length of the protrusion surface 7 plus the axial length of the spring portion 4 gives the axial length of the support portion 5. The support portion 5 is thus ultimately only in the region of the protrusion surface 7 on a radial peripheral surface 8 of the bearing outer ring 2 at , Arranged orthogonally from the support section 5 of the decoupling element 3, the ends of the decoupling element 3 are formed by two ribs 9 angled at 90 ° and projecting radially inwards. The ribs 9 are integral components of the decoupling element 3. However, one of the ribs 9 has a dilution region 10 in the transition region to the support section 5. This can be caused by the beading. Centered in the support section 5, namely introduced into the spring section 4, formed in the first embodiment as slots recesses 1 1 are present.

The decoupling element 3 is made of a ferrous material, such as steel. Also, non-ferrous metals are also used, especially at low loads. The decoupling element 3 is made of hardened or uncured material to a beading one of the ribs 9 to enable. When using a hardened decoupling element 3, this is annealed inductively in the region of the ribs 9. On the shelves 9 existing inner sides 12 are formed as contact surfaces 13. The contact surfaces 13 are aligned parallel to a radial direction y. This radial direction y is aligned perpendicular to an axial direction x.

The ribs 9 are flush in a respective groove 14 at the axial ends of the bearing outer ring 2 and touch the bearing outer ring 2 only in the region of the contact surfaces 13. Between the distal ends of the ribs 9 and the bearing outer ring 2 is preferably a small gap. With appropriate manufacturing techniques can be dispensed with this gap.

In Figure 2, the decoupling element 3 of the first embodiment is visualized in a perspective view, wherein the recesses 1 1 are formed as slots. In contrast to the first embodiment, has the second embodiment shown in Figures 3 and 4 on the decoupling element 3 recesses 1 1, which are formed as equilateral triangles. In principle, however, all other triangular shapes are usable. The triangles are aligned with one of their tips facing each other and arranged in two rows.

As a further variant, a third embodiment of a rolling bearing 1 with a decoupling element 3 is shown in Figures 5 and 6, the circular recesses 1 1 has. These recesses 1 1 are arranged in three mutually offset rows. Reference Number List Rolling Bearings

Bearing outer ring

decoupling element

spring section

bearing section

head Start

projection surface

radial peripheral surface

Borde

dilution range

recess

insides

contact surfaces

groove

Claims

claims

1 . Rolling bearing (1) with a bearing inner ring and a radially outwardly disposed bearing outer ring (2), between which rolling elements are positioned, wherein radially outside of the bearing outer ring (2) an integral decoupling element (3) is provided as a vibration damper, the bearing outer ring (2) at least engages in sections and with an at least partially cylindrical configured support portion (4) rests on the outer surface of the bearing outer ring (2), wherein the support portion (4) in the axial direction by a spring portion (5) is interrupted, wherein the decoupling element (3) is spaced from the outer circumferential surface of the bearing outer ring (2), characterized in that on the outer circumferential surface of the bearing outer ring (2) has two at least partially extending over the circumference hump-like projections (6) are present, on which the support portion (4) rests.

2. rolling bearing (1), characterized in that the spring portion (5) is located between two radially oriented imaginary planes through the projections (6).

3. rolling bearing (1) according to one of claims 1 or 2, characterized in that the decoupling element (3) is designed as a sleeve with a cylindrical bearing portion (4).

4. Rolling bearing (1) according to one of claims 1 to 3, characterized in that in the axial direction outside of the support portion (4) and arranged transversely thereto, to the bearing inner ring facing shelves (9) are formed.

5. Rolling bearing (1) according to one of claims 1 to 4, characterized in that the spring portion (5) has recesses (1 1).

6. rolling bearing (1) according to claim 5, characterized in that the recesses (1 1) are circular, triangular or slot-shaped.

7. rolling bearing (1) according to one of claims 4 to 6, characterized marked, that the rims (9) are designed recess-free.

8. Rolling bearing (1) according to one of claims 4 to 7, characterized in that the decoupling element (3) in a connection region between one of the shelves (9) and the support section (4) a dilution area (10) for the disposal position of a Bördelstufe has.

9. Rolling bearing (1) according to one of claims 4 to 8, characterized in that the shelves (9) radially inwardly extending contact surfaces (13) which lie opposite each other and flat in contact with a shoulder ter ever a recess the outer circumferential surface of the bearing outer ring (2) are, wherein the recess in each case as a preferably circumferential groove (14) at the axial end of the bearing outer shell (2) is formed.

10. Rolling bearing (1) according to any one of claims 1 to 9, characterized marked, that the projections (6) extend without interruption over the circumference of the outer circumferential surface of the bearing outer ring (2).