DE102015205745A1 - bearing arrangement - Google Patents

Abstract

Bearing arrangement (1) having at least one rolling bearing (2) with an inner ring (6) and an outer ring (10), which have a common axis of rotation (D), between the inner ring (6) and the outer ring (10) rolling elements (14) are arranged, and wherein on the inner ring (6) and / or on the outer ring (10) at least one axially adjustable board (18) is arranged, by means of which the rolling body (14) substantially in the axial direction by a displacement (δWK ) and a roller bearing cage (24) having a first and a second cage edge (26; 28) which are interconnected via at least two webs (27) and between them at least one pocket (30) for receiving the rolling element (14) formed, wherein the pocket (30) has an axial pocket length L, which is increased by the displacement travel (δWK) of the rolling body (14).

Description

The present invention relates to a bearing arrangement with at least one roller bearing according to the preamble of claim 1 and an associated roller bearing cage.

From the prior art, for example from the DE 102012221297 A1 , A bearing arrangement with two rolling bearings is known, each rolling bearing having an inner ring and an outer ring, between each of which a rolling bearing cage is arranged, which is adapted to receive rolling elements. Furthermore, one of the roller bearings on an adjustable rim on the inner ring and / or on the outer ring, which is axially displaceable on the inner ring and / or on the outer ring and acts on the rolling elements, so that it is displaceable in the axial direction. As a result, a desired preload is infinitely adjustable in the bearing assembly.

A disadvantage of this bearing arrangement, however, is that the rolling bearing cage used in such a bearing arrangement is guided by rolling bodies. With an axial displacement of the rolling elements can lead to increased Käfiebaschenspiel. If the Käfiebaschenspiel too big, the roller bearing cage loses its leadership properties, so that there is a risk of rolling over the rolling bearing cage. This can lead in extreme cases to a destruction of the rolling bearing cage or the rolling bearing.

Object of the present invention is therefore to provide a bearing assembly of the type mentioned with a rolling bearing cage, which ensures reliable operation even with an axial displacement of the rolling elements.

This object is achieved by a bearing assembly according to claim 1 and by a roller bearing cage for such a bearing assembly according to claim 12. Further advantages and advantageous embodiments are specified in the subclaims of the description and the drawings.

In the following, a bearing arrangement is presented with at least one rolling bearing, wherein the rolling bearing has an inner ring and an outer ring with a common axis of rotation, between which rolling elements are arranged. On the inner ring and / or on the outer ring at least one adjustable in the axial direction board is arranged, which is adapted to move the rolling elements substantially in the axial direction by a displacement. The rolling bearing further comprises a roller bearing cage having a first and a second cage edge, wherein the cage edges are connected to each other via at least two webs and form at least one pocket with an axially extending pocket length for receiving the rolling body between them.

In order to use a rolling bearing cage in a bearing assembly with adjustable board, which ensures a reliable function even with an axial displacement of the rolling elements, it is proposed to increase the pocket length by the displacement of the rolling element. Thereby, the rolling elements can be moved by means of the movable Bordes in the axial direction in the pocket of the rolling bearing cage according to the invention. Since the bag is only about the displacement of the rolling element and not arbitrarily larger, a Käfiebaschenspiel is not too large, so that a risk of rolling over of the rolling bearing cage can be reduced. In addition, it can be used by a guided on the inner and / or outer ring rolling bearing cage, so that, inter alia, results in a better load distribution. As a result, a rolling bearing with a smooth running behavior can be provided with simultaneously reduced bearing noise. Furthermore, instabilities in the rolling bearing can be counteracted by means of the guided on the inner and / or outer ring bearing cage instabilities, which in turn can be extended the life of the bearing. In addition, the use of a rolling bearing cage guided on the inner and / or outer ring can lead to a simplification of the rolling bearing mounting.

In a preferred embodiment, the inner ring and / or the outer ring to another board, which is preferably fixed. This is preferably the retaining board, which provides for a cohesion of the bearing parts in particular during storage or during transport, so that the inner ring, bearing cage and the rolling elements form a unit.

According to a further advantageous embodiment, the first cage edge and / or the second cage edge of the rolling bearing cage on a radially inwardly and / or radially outwardly directed projection, which forms an inner ring guide and / or outer ring guide of the rolling bearing cage. With the help of the projection, the roller bearing cage can be guided during operation of the rolling bearing in the axial and / or radial direction.

In a preferred embodiment, the inner ring and / or the outer ring on a first small and a second large diameter. Advantageously, the radially inwardly directed projection of the first cage edge is supported on the small diameter of the inner ring. Alternatively or additionally, the radially outwardly directed projection of the second cage edge Support at the large diameter of the outer ring. As a result, the roller bearing cage can be acted upon by an axial force.

Furthermore, an embodiment is advantageous in which the outer ring has an outer end face and the outwardly directed projection of the second edge of the cage engages around this outer end face. In this case, the clasping can be configured over a relatively large area, so that an axial application of force can be distributed over a large area of the outer end face. This design has the advantage that a conventional outer ring can be used, which does not require additional processing. Furthermore, can be dispensed with the axial guidance of the bearing cage on the inner ring, resulting in a material and cost savings. Similarly, an inner ring can be encompassed.

In a further preferred embodiment, the inner ring and / or the outer ring has a recess into which protrudes the projection of the roller bearing cage. As a result, the roller bearing cage can be secured in operation against slipping in the axial direction.

Advantageously, the recess may be formed as a paragraph. In particular, this paragraph may be dimensioned such that the projection of the first and / or the second cage edge of the rolling bearing cage flush with an outer end face of the bearing rings, for example, to limit the axial space.

Alternatively, the recess on the inner ring and / or on the outer ring may be groove-shaped. Thus, the projection can be supported in the groove-shaped recess of the inner ring and / or outer ring. As a result, an additional holding board can be omitted. The groove-shaped recess is preferably formed from two spaced groove walls in the axial direction. In this case, the shape of the groove may be due to a raceway running on the inner ring and / or outer ring. Alternatively, the groove walls may be formed differently depending on the application, for example, to accommodate different sized forces or to allow easy mounting of the rolling bearing cage.

In a further preferred embodiment, a securing ring, for example in the form of a snap ring, is arranged on the inner ring and / or outer ring and is designed to axially guide and / or support the rolling bearing cage. In this case, the securing ring can also be arranged in a groove, in particular in the projection receiving groove or in a groove formed on the recess. Advantageously, the retaining ring takes on the one hand, a holding function of the rolling bearing cage and thus also the rolling elements and on the other hand, in operation, the rolling bearing cage in the axial direction. An additional holding board can be omitted, which costs and material can be saved.

As mentioned above, the inner ring and / or the outer ring may have a first small diameter and a second large diameter. In addition, the first cage edge of the roller bearing cage may have a smaller diameter than the second cage edge. Furthermore, the small cage rim is preferably disposed on the small diameter side and the large cage edge on the large diameter side of the inner ring.

Furthermore, the roller bearing cage may comprise at least one substantially trapezoidal shaped pocket having a first circumferentially extending pocket width and a second circumferentially extending pocket width, the first pocket width being smaller than the second pocket width. As a result, an axial application of force to the rolling body cage can be selectively exerted. On the other hand, if the roller bearing cage were rectangular, no force would be applied.

According to a further advantageous embodiment, the rolling bearing is designed as a tapered roller bearing, the conical rolling elements each having a substantially axially extending Wälzkörperachse which intersects with the axis of rotation in an intersection, the so-called Apexpunkt. Furthermore, the tapered rolling elements each have a first circumferentially extending side surface and a second circumferentially extending side surface, wherein the first side surface is formed smaller than the second side surface. In this case, the small side surface is arranged on the side of the small diameter and the large side surface on the side of the large diameter of the inner ring.

At the same time, the rolling element contacts the axially directed webs of the roller bearing cage along a contact edge line. Depending on the configuration of the pocket shape of the rolling bearing cage, different force effects of the rolling elements on the pocket, which can be explained by means of a displacement of the intersection Berührkantenlinie / axis of rotation on the axis of rotation.

If the pocket is of rectangular design, the contact edge line intersects with the axis of rotation in a reference intersection point RS, which is usually located on the axis of rotation between the apex point of the rolling elements and the bearing arrangement. An axial force from the rolling elements on the bearing cage is not given. Is the Bag, however, formed substantially trapezoidal, wherein the small pocket width is located on the small cage edge of the rolling bearing cage, shifts the intersection of the Berührkantenlinie / axis of rotation in the direction Apexpunkt the rolling elements or beyond. If the apex point and the point of intersection of the contact edge line / axis of rotation coincide, the pocket shows an exact trapezoidal shape with straight side lines, which is particularly easy to manufacture. In this orientation of the substantially trapezoidal pocket results in an axial force on the roller bearing cage, which is directed towards the small inner ring diameter, so that the roller bearing cage should preferably be supported in the direction of the small inner ring diameter. This can preferably take place either via the retaining ring arranged on the inner ring or via an axial support of the roller bearing cage on the outer ring. If the outer ring takes over the axial guidance of the roller bearing cage, then only a radially outwardly directed projection of the roller bearing cage may be required. The displacement of the rolling element results in only a small change in the cage pocket clearance, so that even a radial support on the outer ring can be dispensed with and the projection can engage around the outer ring. This reduces manufacturing costs. If no securing ring is provided, the inner ring preferably has a retaining board in order to support the rolling bodies in particular during transport or during assembly of the bearing.

If, in contrast, the small pocket width is arranged on the large cage edge of the roller bearing cage, the point of intersection of the contact edge line / axis of rotation shifts in the direction of the bearing arrangement. This results in an axial application of force to the roller bearing cage in the direction of the large inner ring diameter, so that the roller bearing cage must be supported only on the inner ring. This has the advantage that embodiments are possible in which only the inner ring, in particular in the region of the small inner ring diameter, must be processed. On a machining of the outer ring can be omitted. In order to guide the rolling bearing cage axially, the inner ring may have a retaining board. But it is also possible to axially guide the roller bearing cage via a groove in the inner ring. For this purpose, the groove preferably has a first and a second groove wall, which are axially spaced. It is further preferred that the first groove wall is formed larger than the second groove wall to accommodate acting on the roller bearing cage axial force acting in the direction of the large inner ring diameter, and to guide the roller bearing cage axially, but still to ensure easy mounting. Alternatively, instead of the second groove wall and a locking ring may be provided to provide a simple mounting option.

According to a further preferred embodiment, the bearing arrangement described above has at least one second rolling bearing, which has two fixed shelves. The two bearings can be arranged in X or O arrangement, with an O arrangement is preferred. Due to the adjustable board of the first bearing, the bearing assembly can be biased in the axial direction in the desired manner, whereby a complex measurement of components for adjusting the bias can be omitted. Thus again working hours and costs can be saved.

Another aspect of the invention relates to a roller bearing cage for a bearing arrangement described above.

In the following, the invention will be explained in more detail with reference to embodiments illustrated in the drawings. The embodiments are purely exemplary in nature and are not intended to determine the scope of the application. This is defined solely by the claims.

Show it:

1 a schematic representation of a cross section through a known from the prior art bearing assembly;

2 a schematic representation of a cross section through a first embodiment of the bearing assembly according to the invention;

3 a schematic representation of a cross section through a second embodiment of the bearing assembly according to the invention;

4 a schematic representation of a cross section through a third embodiment of the bearing assembly according to the invention;

5 a schematic representation of a cross section through a fourth embodiment of the bearing assembly according to the invention;

6 a schematic plan view of an embodiment of the rolling bearing cage according to the invention;

7 a schematic plan view of a further embodiment of the rolling bearing cage according to the invention; and

8th a schematic view of a rolling element with respect to the bearing pivot axis.

In the following, the same or functionally equivalent elements are identified with the same reference numerals.

1 shows schematically a cross section through a known from the prior art bearing assembly 1 with a first and a second tapered roller bearing 2 . 4 , Such a bearing arrangement is in the DE 102012221297 A1 to which reference is hereby made and the disclosure of which is fully incorporated.

Like in the 1 shown, the two tapered roller bearings 2 . 4 each an inner ring 6 . 8th and an outer ring 10 . 12 on, between each of which rolling elements 14 . 16 are arranged. In this case, the inner ring 6 a first small diameter d _IR and a second large diameter D _IR . In 1 is further shown that the rolling elements 14 . 16 are designed as a truncated cone with a small side surface 20 and with a large side surface 22 , where the small side surface 20 at the small diameter d _IR and the large side surface 22 at the large diameter D _{IR of} the inner ring 6 is arranged.

The in the 1 shown tapered roller bearings 2 . 4 are executed in an O arrangement. Furthermore, the bearings are 2 . 4 designed such that both inner rings 6 . 8th stuck on a wave 5 are mounted. To set a desired preload, is on the inner ring 6 of the rolling bearing 2 an adjustable board 18 arranged in the axial direction on the inner ring 6 can be adjusted. The displacement δ _{vB of} the adjustable board 18 This results in a displacement of the rolling elements 14 by a displacement δ _WK , such as in the 1 shown.

A disadvantage of the bearing arrangements known from the prior art, however, is that a rolling body guided roller bearing cage is used, which allows insufficient axial displacement of the rolling elements, otherwise a Käfiebaschenspiel would be too large and there would be a risk of rolling over the rolling bearing cage.

The idea of the present invention is therefore to design the pockets of the rolling bearing cage in such a way that an axial displacement is possible, but the cage pocket play is not too large.

In the following, various rolling bearing cages are presented, which allow such axial displacement. Common to them is that their rolling body receiving pockets are enlarged so that an axial displacement of the rolling elements is possible. The show 2 - 5 schematically cross sections through preferred embodiments of a tapered roller bearing 2 with an axially adjustable board 18 and a rolling bearing cage 24 , wherein the embodiments shown all in the in the 1 shown bearing assembly 1 can be used, but can also be used in other applications. In the 6 - 7 is in each case a plan view of preferred embodiments of the bearing cage according to the invention 24 shown.

In this case, the rolling bearing cage according to the invention 24 a first cage edge 26 with a small diameter d _LK and a second cage edge 28 with a large diameter D _LK on, with the cage edges 26 . 28 over footbridges 27 (please refer 6 - 7 ) and bags 30 for receiving the rolling elements 14 form. The 2 - 5 continue to show that the small cage edge 26 on the side of the small inner ring diameter d _IR and the large cage edge 28 is arranged on the side of the large inner ring diameter D _IR .

As in the 2 - 5 further shown, the bag points 30 an axially extending pocket length L on. The pocket length L is chosen such that it is not just the rolling element 14 can take, but to the displacement δ _{WK of} the rolling body 14 is enlarged. This allows the rolling element 14 by means of the adjustable Bordes 18 in the axial direction inside the bag 30 be moved so that despite the enlarged pocket 30 during operation of the warehouse 2 a quiet running behavior can be provided, reducing the life of the bearing 2 can be extended.

Continue to show 2 and 3 that the first cage edge 26 of the rolling bearing cage 24 a radially inwardly directed projection 36 which is on the inner ring 6 , in particular in the region of the small diameter d _IR , supported. This is the rolling bearing cage 24 guided on the inside and during operation of the bearing 2 in the axial direction on the inner ring 6 fixable and supportable in the radial direction.

To the rolling bearing cage 24 on the inner ring 6 support and determine how 2 shows the inner ring 6 a recess 40 in the form of a paragraph 42 on, on which the cantilever 36 of the rolling bearing cage 24 radially supported.

It is on the inner ring 6 continue a circlip 44 , For example, a snap ring, in a groove 46 arranged to the rolling bearing cage 24 on the inner ring 6 to hold and fix axially.

Alternatively shows 3 that the recess 40 may also be groove-shaped, so that a locking ring 44 can be waived. The axial support of the rolling bearing cage 24 over a groove wall 48 but would not be enough the rolling bearing cage 24 to keep, since the groove wall 48 should be designed as small as possible to a mounting of the rolling bearing cage 24 to enable. To the rolling bearing cage 24 nevertheless support axially, has the second cage edge 28 a radially outwardly directed projection 38 on, located on the outer ring 10 supports and so a outer ring bearing bearing cage 24 formed. Such a projection is also in 4 shown. The cantilever 38 can either be in a recess 50 on the outer ring 10 protrude or, as in the 3a respectively. 4a shown the outer ring 10 embrace. Thus, the rolling bearing cage 24 over the outer ring 10 be guided axially, so that the groove wall 48 can be made sufficiently small. In this case, the recess 50 be dimensioned such that the projection 38 with an outer face 52 of the outer ring 10 flush. As a result, the axial space requirement can be limited.

Will the outer ring 10 embraced, as in the 3a - 4a shown, can on a recess 50 and thus on a radial guide of the roller bearing cage 24 on the outer ring 10 be waived. The cantilever 38 is dimensioned so large area that an axial force over a large area of the outer end face 52 distributed. This design offers the advantage that the outer ring 10 does not require additional processing, which can reduce costs.

Will the rolling bearing cage 24 on the outer ring 10 supported and guided, can also, like 4 points to a cantilever 36 be dispensed with the small inner ring diameter d _IR . But then anyway for the rolling elements 14 To provide a stop, for example, for the mounting of the rolling bearing cage, is at the small inner ring diameter d _IR a holding board 54 educated.

5 shows analogously to 3 in that with an inner ring guide on the inner ring 6 a recess 40 may be formed in the form of a groove into which the projection 36 of the first rolling bearing cage ring 26 protrudes. In this case, the groove-shaped recess 40 via two groove walls spaced apart in the axial direction 48 . 56 educated. The groove wall 56 is larger than the groove wall 48 designed to operate in the rolling bearing 2 the axial guidance of the roller bearing cage 24 to take over. The groove wall 48 is formed lower, so that snapping the rolling bearing cage 24 is possible.

As in the 2 - 8th furthermore shown, the rolling elements 14 in each case a substantially axially extending rolling body axis WA, which coincides with the axis of rotation D in the Apexpunkt A _{WK of} the rolling elements 14 cuts. At the same time contact the bars 27 of Wälzlagerkä 24 the rolling elements 14 along a Berührkantenlinie BK.

Depending on the design of the bags 30 of the rolling bearing cage 24 arise different forces of the rolling elements 14 on the pockets 30 and thus on the rolling bearing cage 24 , In the following, the different force effect is explained by means of a displacement of the intersection of the contact edge line / axis of rotation on the axis of rotation D.

Is the bag 30 formed rectangular, the Berührkantenlinie BK intersects the axis of rotation D in a reference intersection RS, located between the Apexpunkt A _{WK of} the rolling elements 14 and the rolling bearing 2 is located as in 8th illustrated. For rectangular bags 30 is no or only a negligible axial force from the rolling element 14 on the rolling bearing cage 24 given.

Is the bag 30 However, formed substantially trapezoidal, there is an axial application of force, wherein the intersection Berührkantenlinie / axis of rotation S _BD in the direction Apexpunkt A _WK or in the direction of rolling bearings 2 shifts, wherein at a shift (-δS _BD ) in the direction Apexpunkt A _{WK of} the rolling bearing cage 24 with a force in the direction of the small inner ring diameter d _IR and with a displacement (+ δS _BD ) in the direction of rolling bearings 2 with a force in the direction of the large inner ring diameter D _{IR is} applied.

The 6 - 7 show a view of a rolling bearing cage 24 , at which essentially trapezoidal pockets 30 are formed. The bags 30 have a first circumferentially extending pocket width 32 and a second circumferentially extending pocket width 34 on, with the first pocket width 32 smaller than the second pocket width 34 , In the pockets 30 are rolling elements 14 led, partly from the jetties 27 are covered.

Now, as in 6 and 8th illustrates the small pocket width 32 on the small cage edge 26 of the rolling bearing cage 24 arranged, so the rolling bearing cage 24 the rolling element 14 also on its large side include what results in that the rolling bearing cage 24 at the large inner ring diameter D _IR lower over the rolling element 14 slips. As a result, the rolling body axis WA and the contact edge line BK are angled in such a way that the point of intersection of the contact edge line / rotation axis S _BD shifts by -δS _BD from the reference intersection point RS in the direction Apexpunkt A _WK or above. Are the bags 30 exactly trapezoidal with straight side lines 21 , the Apexpunkt A _WK and the intersection Berührkantenlinie / axis of rotation S _BD coincide, as in the embodiments of 2 - 4 and 6 shown. The essentially trapezoidal configuration of the pockets 30 and their design with the small pocket width 32 on the small cage edge 26 conditionally an axial force of the rolling element 14 on the rolling bearing cage 24 in the direction of the small inner ring diameter d _IR . The axial force on the rolling bearing cage 24 at the small diameter d _{IR of} the inner ring 6 can, as already stated above, on the inner ring 6 arranged circlip 44 or via an axial support of the roller bearing cage 24 on the outer ring 10 respectively.

Is against it, as in the 5 . 7 and 8th shown, the trapezoidal shape of the bag designed such that the small pocket width 32 on the big cage edge 28 is arranged, the intersection Berührkantenlinie / rotational axis S _BD shifts (+ δS _BD ) in the direction of rolling bearings 2 , The greater a distance between the reference intersection point RS and the intersection of the contact edge line / rotation axis S _BD , the larger the pocket width becomes 34 on the small cage edge 26 so that the rolling bearing cage 24 at the small inner ring diameter d _IR can slip deeper over the rolling elements. The axial application of force to the rolling bearing cage 24 then takes place in the direction of the large inner ring diameter D _IR , whereby the axial guidance, as the 5 shows, alone from the inner ring 6 can be taken.

With the help of the bearing assembly according to the invention and the associated rolling bearing cage, a smooth running behavior and thus an extended life of the bearing can be provided. For this purpose, the bearing assembly has an adjustable on an inner ring and / or an outer ring board, which can be moved in the axial direction by a displacement and a roller bearing cage having a running in the axial direction pocket length, which is increased by the displacement of the rolling element. By such a bearing arrangement in combination with a second rolling bearing a desired preload can be adjusted. It is used for example in a pinion bearing application.

LIST OF REFERENCE NUMBERS

1

bearing arrangement

2, 4

Tapered roller bearings

5

wave

6, 8

 inner ring

10, 12

outer ring

14, 16

rolling elements

18

adjustable board

20, 22

Side surface of the rolling element

21

sidelines

24

Rolling bearing cage

26

first cage edge of the rolling bearing cage

27

web

28

second cage edge of the rolling bearing cage

30

bag

32, 34

pocket width

36, 38

projection

40, 50

recess

42

paragraph

44

circlip

46

groove

48, 56

groove wall

52

Outside front side

54

holding board

d _IR

small diameter of the inner ring

D _IR

large diameter of the inner ring

d _LK

small diameter of the first cage edge

D _LK

large diameter of the second cage edge

δ _vB

Displacement of the adjustable Bordes

δ _WK

Displacement of the rolling element

L

pocket length

D

axis of rotation

WA

rolling member

BK

Berührkantenlinie

S _BD

Intersection Berührkantenlinie with the axis of rotation

A _WK

Apex point of the rolling elements

RS

Reference intersection

δS _BD

Shift intersection of touch edge line with the axis of rotation

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102012221297 A1 [0002, 0035]

Claims (12)

Bearing arrangement ( 1 ) with at least one roller bearing ( 2 ) with an inner ring ( 6 ) and an outer ring ( 10 ), which have a common axis of rotation (D), wherein between the inner ring ( 6 ) and the outer ring ( 10 ) Rolling elements ( 14 ) are arranged, and wherein on the inner ring ( 6 ) and / or on the outer ring ( 10 ) at least one axially adjustable board ( 18 ) is arranged, by means of which the rolling elements ( 14 ) is movable substantially in the axial direction about a displacement path (δ _WK ), and a rolling bearing cage ( 24 ), a first and a second cage edge ( 26 ; 28 ), which via at least two webs ( 27 ) and at least one pocket ( 30 ) for receiving the rolling element ( 14 ), characterized in that the bag ( 30 ) has an axial pocket length L which is about the displacement (δ _WK ) of the rolling body ( 14 ) is enlarged. Bearing arrangement ( 1 ) according to claim 1, characterized in that the inner ring ( 6 ) and / or the outer ring ( 10 ) another board ( 54 ), which is preferably fixed. Bearing arrangement ( 1 ) according to one of claims 1 or 2, characterized in that the first cage edge ( 26 ) and / or the second cage edge ( 28 ) of the roller bearing cage ( 24 ) a radially inwardly and / or radially outwardly directed projection ( 36 ; 38 ), which has an inner ring guide and / or outer ring guide of the roller bearing cage ( 24 ) trains. Bearing arrangement ( 1 ) according to one of the preceding claims, characterized in that the inner ring ( 6 ) and / or the outer ring ( 10 ) a recess ( 40 ; 50 ) into which the projection ( 36 ; 38 ) of the roller bearing cage ( 24 ) protrudes. Bearing arrangement ( 1 ) according to claim 4, characterized in that the recess ( 40 ; 50 ) is groove-shaped. Bearing arrangement ( 1 ) according to one of the preceding claims, characterized in that on the inner ring ( 6 ) and / or the outer ring ( 10 ) a retaining ring ( 44 ) is arranged, which is adapted to the rolling bearing cage ( 24 ) and / or support. Bearing arrangement ( 1 ) according to one of the preceding claims, characterized in that the first cage edge ( 26 ) of the roller bearing cage ( 24 ) has a smaller diameter (d _LK ) than the second cage edge ( 28 ). Bearing arrangement ( 1 ) according to claim 7, characterized in that the at least one pocket ( 30 ) of the roller bearing cage ( 24 ) is formed substantially trapezoidal with a first extending in the circumferential direction pocket width ( 32 ) and with a second circumferentially extending pocket width ( 34 ), where the first pocket width ( 32 ) is smaller than the second pocket width ( 34 ). Bearing arrangement ( 1 ) according to one of claims 7 or 8, characterized in that the smaller pocket width ( 32 ) on the smaller cage edge ( 26 ) of the roller bearing cage ( 24 ) is arranged. Bearing arrangement ( 1 ) according to one of claims 7 or 8, characterized in that the smaller pocket width ( 32 ) on the large cage edge ( 28 ) of the roller bearing cage ( 24 ) is arranged. Bearing arrangement ( 1 ) according to one of the preceding claims with at least one second rolling bearing ( 4 ), wherein the second rolling bearing ( 4 ) has two fixed shelves, characterized in that the bearing arrangement ( 1 ) by means of the displaceable board ( 18 ) of the first rolling bearing ( 2 ) is adjustable in the axial direction with respect to the bias voltage. Rolling bearing cage ( 24 ) for a bearing assembly ( 1 ) according to one of claims 1 to 11.

Images