GB2119470A - A self-centring clutch release bearing assembly - Google Patents

Abstract

There is disclosed a self- centring clutch release bearing assembly comprising a sliding sleeve (10) and a rolling bearing (12) having two race rings (13, 14), one of which (13) is freely rotatable relative to the sleeve (10). In centring, the other race ring (14) rotates relative to the sleeve (10) against a frictional force acting on radially opposed and contacting surfaces (21, 22) and moves radially relative to the sleeve (10) only parallel to two parallel guide surfaces (21) and against a frictional force acting on the guide surfaces. The bearing (12) can thus centre itself easily, and when the parallel guide surfaces (21) are not vertical the bearing will not slip down. <IMAGE>

Description

SPECIFICATION A self-centring clutch release bearing assembly This invention concerns a self-centring clutch release bearing assembly, for example for motor vehicle clutches.

A known type of self-centring clutch release bearing assembly, exempiified in published Specification DE 1600080, comprises a sliding sleeve having a radially outwardly extending thrust plate and a rolling bearing arranged around the sleeve. The rolling bearing has two race rings, one of which is freely rotatable with respect to the sleeve and is adapted to engage the clutch diaphragm spring. The other race ring is prevented from rotating with respect to the sleeve by an axially acting spring which urges the other race ring towards the thrust plate so that the other race ring and hence the bearing is frictionally held in the centred position before and after disengagement or release of the clutch.

This known construction has the disadvantage that due to the various axial tolerances of the components not all the assemblies have the same axial spring force acting on the other race ring so that each assembly may have a different centring behaviour.

Furthermore, a spring, which is in addition to the sleeve and bearing, is required to provide the axial force for frictional engagement and a specially formed housing is necessary. This means that with the extra components the production of this type of assembly is expensive.

To hold the bearing in its centred position, even after receiving shock loads from, for example, the motor vehicle going over bumps in the road, the spring must be quite powerful. However this means that the bearing is not necessarily centred in the first disengagement or release of the clutch.

Also, a large shock load may cause the bearing to slip down so requiring the bearing to be centred anew.

The subject of the present invention is a selfcentring clutch release bearing assembly which is easily fitted, comprises only a few parts, the bearing is held centred by a uniformly acting friction force and slipping down of the bearing is not so frequent a problem.

The invention provides a self-centring clutch release bearing assembly comprising a sliding sleeve and a rolling bearing, the rolling bearing comprising two race rings one of which is freely rotatable with respect to the sleeve and the other of which is rotatable with respect to the sleeve against a frictional force acting on two contacting and radially opposed surfaces, one of the surfaces being fixed rotationally with respect to the sleeve and the other of the surfaces being fixed rotationally with respect to the other race ring, which other race ring is radially movable with respect to the sleeve only in a direction parallel to two parallel guide surfaces, fixed rotationally with respect to the other race ring, and against a frictional force acting on the parallel guide surfaces and on other surfaces of the assembly contacting the parallel guide surfaces.

In this construction of a clutch release bearing assembly, the centring action of the bearing in use of the assembly is for the other race ring to rotate with respect to the sleeve and then to move radially parallel to the two parallel guide surfaces until the centred position is reached.

If the parallel guide surfaces are not extending perpendicularly when the centred position is reached, then they prevent the bearing from slipping down when the bearing is subject to shock loads.

The other race ring, or a part fixed with respect to the other race ring, may have an opening defined in part by the two parallel guide surfaces, and the sleeve may extend through the opening and engage the parallel guide surfaces, the other race ring being rotatable and radially movable with respect to the sleeve against the frictional force acting on the sleeve and the parallel guide surfaces.

With such a construction in which the other race has the opening, no additional components are required and so the assembly is cheap to produce and easy to assemble. As the sliding sleeve is radially supported between the parallel guide faces, the bearing can centre itself quickly without being restrained by large forces.

The opening in the other race ring or part fixed thereto may be eccentric to the other race ring.

The other race ring or a part fixed with respect to the other race ring may engage in an annular circumferentially extending groove in the sleeve to hold the other race ring against movement in one axial direction with respect to the sleeve.

A retaining ring may be disposed around the sleeve, which retaining ring is of annular open channel section with the sides of the channel extending axially and being radially spaced from each other and the base of the channel extending radially, the other race ring may have an opening defined in part by the parallel guide surfaces and the retaining ring may extend into the opening and engage the parallel guide surfaces, the other race ring having rotatable and radially movable with respect to the sleeve against the frictional force acting on the parallel guide surfaces and the outer surface of the retaining ring.

This retaining ring may be made of, for example, spring steel, and damps movement of the bearing relative to the sleeve.

The sleeve may have a radially outwardly extending thrust plate fixed with respect to the sleeve, the retaining ring may have tabs extending radially outwardly from the radially outer side, and a portion of the other race ring providing the parallel guide surfaces may extend radially inwardly between the thrust plate and the tabs.

The free end of the radially inner side of the retaining ring may engage in an annular circumferentially extending groove in the sleeve to hold the retaining ring against movement in one axial direction with respect to the sleeve.

An angular ring may be disposed around the sleeve, which angutar ring comprises an annular axially extending portion and a portion extending radially outwardly from the annular portion, the angular ring being rotatable with respect to the sleeve against a frictional force acting on the radially opposed and contacting surfaces of the angular ring and the sleeve, the sleeve may have a radially outwardly extending thrust plate fixed with respect to the sleeve and a portion of the other race ring may extend radially inwardly between the thrust plate and the radially extending portion of the angular ring, which radially extending portion of the angular ring may have an opening defined in part by the two parallel guide surfaces, and the radially extending portion of the other race ring may have a projection extending axially through the opening and engaging the parallel guide surfaces, the other race ring being radially movable with respect to the sleeve against a friction force acting on the parallel guide surfaces and the surfaces of the projection.

In this construction, the angular ring connects the bearing to the sleeve.

The opening in the radially extending portion of the angular ring may be a slot having a narrower portion leading to the radially outer periphery of the radially extending portion of the angular ring.

The free end of the annular axially extending portion of the angular ring may engage in an annular circumferentially extending groove in the sleeve to hold the angular ring against movement in one axial direction with respect to the sleeve.

A spring ring may be fixed with respect to the other race ring and disposed in the bore of the other race ring, and the spring ring may have two parallel portions extending transversely of the sleeve and providing the two parallel guide surfaces.

The spring ring may have curved portions at the ends of the parallel portions engaging the bore of the other race ring, the radius of curvature of the curved portions being less than the radius of curvature of the bore of the other race ring.

The spring ring may be broken at one of the curved portions.

The parallel portions of the spring ring may engage in an annular circumferentially extending groove in the sleeve to hold the spring ring against movement in one axial direction with respect to the sleeve.

Embodiments of the invention will now be described by way of example, reference being made to the accompanying drawings, of which: Figure 1 is a section of I-I of Figure 2 and shows a self-centring clutch release bearing assembly, the other (outer) race ring having a radially inwardly extending flange engaging in an annular circumferentially extending groove in the outer surface of the sleeve; Figure 2 is a section on Il-I I of the assembly shown in Figure 1; Figure 3 is the same section as that of Figure 2 and shows a similar self-centring clutch release bearing assembly but in which the opening formed by the flange of the other (outer) race ring is eccentric; Figure 4 shows the same assembly as that in Figure 3 in which the other (outer) race ring has been turned through an angle;; Figure 5 is part of a longitudinal section of another embodiment of the invention in which a retaining ring of an annular channel section is disposed around the sleeve and engages the parallel guide surfaces provided by the other (outer) race ring; Figure 6 is an end view of the assembly shown in Figure 5, to a smaller scale, from the right and without the sliding sleeve; Figure 7 is half of a section of another embodiment of the invention taken on VIl-VIl of the assembly shown in Figure 8, with an angular ring disposed around the sleeve and the other (outer) race ring has a projection extending axially through an opening in the angular ring; Figure 8 is a section taken on VIll-VIll of the assembly shown in Figure 7;; Figure 9 is half a section of a further embodiment of the invention taken on IX-IX of the assembly shown in Figure 10, with a spring ring disposed in and frictionally engaging the bore of the other (outer) ring race; and Figure 10 is an end view from the right of the assembly shown in Figure 9 without the balls and inner race ring.

The clutch release bearing assembly shown in Figures 1 and 2 comprises a sliding sleeve 10 having an integral radially outwardly extending thrust plate 11 and a rolling bearing 12, the sliding sleeve extending into the bore of the rolling bearing. The rolling bearing 12 is a ball bearing having sheet metal radially inner and outer race rings 13 and 14 respectively and a row of balls 15.

The inner race ring 13 is freely rotatable with respect to the sleeve 10 and has, at the end nearer the thrust plate 11 of the sleeve 10, a radially inwardly extending flange 1 6 which stops short of the sleeve 10. At the other end, nearer the clutch, the inner race ring 13 has a flange 1 7 extending radially outwardly to form an abutment surface for the clutch diaphragm spring (not shown). The free end portion 1 8 of the flange 1 7 is bent to extend axially inwardly to the bearing chamber and is spaced a short distance from the outer race ring 14. The flanges 16 and 17 seal the two ends of the bearing 12.

The outer race ring 14 has a radially inwardly extending flange 19 adjacent to the thrust plate 11 of the sleeve 10. The flange 19 forms an opening 20 defined in part by two parallel guide surfaces 21 which engage in an annular circumferentially extending groove 22 in the sleeve 10 so fixing the bearing 12 axially with respect to the sleeve. The parallel guide surfaces 21 frictionally engage the base of the groove 22 so that any rotational movement of the outer race ring 14 with respect to the sleeve 10 and any radial movement of the outer race ring 14, parallel to the parallel guide surfaces 21, and with respect to the sleeve 10 must overcome a frictional force acting on the radially opposed and contacting surfaces of the parallel guide surfaces 21 and the annular groove 22.

In use of the clutch release bearing assembly, when the clutch is disengaged or released and the flange 1 7 of the inner race ring 13 engages the clutch diaphragm spring, the outer race ring 14 rotates against a frictional force and with respect to the sleeve 10 in the same direction or in the opposite direction of rotation relative to the inner race ring 13, depending upon where the centred position is, and then moves radially against a frictional force and with respect to the sleeve 10 to the centred position. No further means are required to prevent rotation of the outer race ring 1 4 with respect to the sleeve 10 since it remains in the centred position.The frictional resistance to rotation of the outer race ring 14 with respect to the sleeve 10 increases with increasing offset of the axes of the bearing 12 and the clutch diaphragm spring.

The assembly shown in Figures 3 and 4 is the same as that shown in Figures 1 and 2 except that this opening 23 formed by the flange 1 9 of the outer race ring 14 is offset to the outer race ring. Figure 3 shows the assembly before centring and Figure 4 shows the bearing centred after rotating through an angle a.

Figures 5 and 6 show a clutch release bearing assembly comprising a sliding sleeve 30 having a radially outwardly extending thrust plate 31 and a rolling bearing having an outer race ring 32, the sleeve 30 extending into the bore of the bearing.

The outer race ring 32 has a radially inwardly extending flange 33 which abuts the thrust plate 31 of the sleeve 30. The flange 33 forms an opening 34 defined in part by two parallel guide surfaces 35.

A retaining ring 36 of, for example, spring steel is disposed around the sleeve 30 and is of annular open channel section with two axially extending sides 37 and 38 radially spaced from each other, and a radially extending base 39 adjacent the thrust plate 31 of the sleeve. The radially outer surface of the radially outer side 38 of the retaining ring 36 frictionally engages the parallel guide surfaces 35 of the outer race ring 32. Tabs 40 extend radially outwardly from the free end of the radially outer side 38 of the retaining ring 36 so that the bearing is located against movement in either axial direction by the tabs 40 and thrust plate 31 extending on opposite axial sides of the flange 33 of the outer race ring 32.The free end 41 of the radially inner side 37 of the retaining ring 36 is sprung into an annular circumferentially extending groove 42 in the outer surface of the sleeve 30 to hold the retaining ring against movement with respect to the sleeve in the axial direction away from the thrust plate 31.

Any rotational movement of the outer race ring 32 with respect to the sleeve 30 and any radial movement of the outer race ring 32, parallel to the parallel guide surfaces 35, and with respect to the sleeve 30 must overcome a frictional force acting on the radially opposite and contacting surfaces of the parallel guide surfaces 35 and the radially outer side 38 of the retaining ring 36.

In use of the clutch release bearing assembly, when the clutch is disengaged or released and the inner race ring engages the clutch diaphragm spring and is rotating therewith, the outer race ring 32 is caused to rotate by the rotation of the inner race ring against a frictional force and with respect to the sleeve 30, and then moves radially, in a direction parallel to the parallel guide surfaces 35, against a friction force and with respect to the sleeve 30 to the centred position.

The clutch release bearing assembly shown in Figures 7 and 8 comprises a sliding sleeve 50, having an integral radially outwardly extending thrust plate 51, and a rolling bearing 52, the sleeve 50 extending into the bore of the bearing.

The rolling bearing 52 comprises inner and outer race rings 53 and 54 respectively and a row of balls 55. The inner race ring 53 is freely rotatable with respect to the sleeve 50 and is adapted to engage the clutch diaphragm spring (not shown).

The outer race ring 54 has a radially inwardly extending flange 56 adjacent to the thrust plate 51 and a projection 57 extending axially from the radially inner periphery of the flange 56 away from the thrust plate.

An angular ring 58 is disposed around the sleeve 50 and comprises an annular axially extending portion 59 and a portion 60 extending radially outwardly from the end of the annular portion nearer to the thrust plate 51 so that the radial flange 56 of the outer race ring 54 is disposed between the portion 60 and the thrust plate 51. The bearing 52 is thus located against movement in either axial direction. The free end 61 of the annular portion 59 of the angular ring 58 engages in an annular circumferentially extending groove 62 in the outer surface of the sleeve 50 to hold the angular ring against movement with respect to the sleeve in the axial direction away from the thrust plate 51.

The radially extending portion 60 of the angular ring 58 has a slot 63, defined in part by two parallel guide surfaces 64, with a narrower portion 65 leading to the radially outer periphery of the radially extending portion 60. The narrower portion 65 allows flexing of the opening 63.

The projection 57 of the outer race ring 54 extends through the opening 63 and engages the parallel guide surfaces 64.

Any rotational movement of the angular ring 58 with respect to the sleeve must overcome a frictional force acting on the radially opposed and contacting surfaces of the annular portion 59 of the angular ring 58 and the sleeve 50. Any radial movement of the outer race ring 54, parallel to the parallel guide surfaces 64 and with respect to the sleeve 50, must overcome a frictional force acting on the parallel guide surfaces 64 and the surfaces of the projection 57.

In use of the clutch release bearing assembly, when the clutch is disengaged or released and the inner race ring 53 of the bearing 52 engages the clutch diaphragm spring and is rotating therewith, the outer race ring 54 is caused to rotate by the rotation of the inner race ring 53 against a frictional force and with respect to the sleeve 50, and then moves radially, in a direction parallel to the parallel guide surfaces 64, against a frictional force and with respect to the sleeve 50 to the central position.

Figures 9 and 10 show a clutch release bearing assembly comprising a sliding sleeve 70, having an integral radially outwardly extending thrust plate 71, and a rolling bearing 72, the sleeve extending into the bore of the bearing. The bearing 72 comprises radially inner and outer race rings 73 and 74 and a row of balls 75. The inner race ring 73 is freely rotatable with respect to the sleeve 70 and is adapted to engage a clutch diaphragm spring (not shown). The outer race ring 74 has a radially inwardly extending flange 76 adjacent to the thrust plate 71, forming a large opening 77.

Disposed in the bore of the outer race ring 74 is a spring ring 78 which comprises two parallel portions 79, extending transversely of the sleeve 70, and two curved portions 80 at the ends of the parallel portions. One of the curved portions 80 is broken at 81. The spring ring 78 forms an opening into which the sleeve 70 extends, which opening is defined in part by two parallel guide surfaces 82 provided by the two parallel portions 79. The sleeve 70 has an annular circumferentially extending groove 83 in which the two parallel portions 79 frictionally engage.

The curved portions 80 of the spring ring 78 bear against the bore of the outer race ring 74. The radius of curvature of the bore the outer race ring 74 is greater than the radius of curvature of the curved portions 80. The two radii are so chosen relative to each other that the curved portions 80 wedge against the bore of the outer race ring 74 so that there is no relative rotation between the spring ring 78 and the outer race ring 74.

Any rotational movement of the outer race ring 74 with respect to the sleeve 70 and any radial movement of the outer race ring 74, parallel to the parallel guide surfaces 82, and with respect to the sleeve 70 must overcome a frictional force acting on the radially opposed and contacting surfaces of the parallel guide surfaces 82 and the annular groove 83.

In use of the clutch release bearing assembly, when the clutch is disengaged or released and the inner race ring 73 of the bearing 72 engages the clutch diaphragm spring and rotated therewith, the outer race ring 74 is caused to rotate by the rotation of the inner race ring 73 against a frictional force and with respect to the sleeve 70, and then moves radially, in a direction parallel to the parallel guide surfaces 82, against a frictional force and with respect to the sleeve 70 to the centred position.

Modifications to the illustrated and described embodiments are envisaged. For example, the freely rotating race ring which engages the clutch diaphragm spring may be the outer race ring. The two parallel guide surfaces can be provided by the inner race ring or a part fixed with respect to the inner race ring.

Claims (29)

Claims

1. A self-centring clutch release bearing assembly comprising a sliding sleeve and a rolling bearing, the rolling bearing comprising two race rings one of which is freely rotatable with respect to the sleeve and the other of which is rotatable with respect to the sleeve against a frictional force acting on two contacting and radially opposed surfaces, one of the surfaces being fixed rotationally with respect to the sleeve and the other of the surfaces being fixed rotationally with respect to the other race ring, which other race ring is radially movable with respect to the sleeve only in a direction parallel to two parallel guide surfaces, fixed rotationally with respect to the other race ring, and against a frictional force acting on the parallel guide surfaces and on other surfaces of the assembly contacting the parallel guide surfaces.

2. An assembly as claimed in claim 1, wherein the other race ring, or a part fixed with respect to the other race ring, has an opening defined in part by the two parallel guide surfaces, and the sleeve extends through the opening and engages the parallel guide surfaces, the other race ring being rotatable and radially movable with respect to the sleeve against the frictional force acting on the sleeve and the parallel guide surfaces.

3. An assembly as claimed in claim 2, wherein the opening is eccentric to the other race ring.

4. An assembly as claimed in claim 1,2 or 3, wherein the other race ring or a part fixed with respect to the other race ring engages in an annular circumferentially extending groove in the sleeve to hold the other race ring against movement in one axial direction with respect to the sleeve.

5. An assembly as claimed in claim 1, wherein a retaining ring is disposed around the sleeve, which retaining ring is of annular open channel section with the sides of the channel extending axially and being radially spaced from each other and the base of the channel extending radially, the other race ring having an opening defined in part by the parallel guide surfaces and the retaining ring extending into the opening and engaging the parallel guide surfaces, the other race ring being rotatable and radially movable with respect to the sleeve against the frictional force acting on the parallel guide surfaces and the outer surface of the retaining ring.

6. An assembly as claimed in claim 5, wherein the sleeve has a radially outwardly extending thrust plate fixed with respect to the sleeve, the retaining ring has tabs extending radially outwardly from the radially outer side, and a portion of the other race ring providing the parallel guide surfaces extends radially inwardly between the thrust plate and the tabs.

7. An assembly as claimed in claim 5 or 6, wherein the free end of the radially inner side of the retaining ring engages in an annular circumferentially extending groove in the sleeve to hold the retaining ring against movement in one axial direction with respect to the sleeve.

8. An assembly as claimed in claim 1, wherein an angular ring is disposed around the sleeve, which angular ring comprises an annular axially extending portion and a portion extending radially outwardly from the annular portion, the angular ring being rotatable with respect to the sleeve against a frictional force acting on the radially opposed and contacting surfaces of the angular ring and the sleeve, the sleeve has a radially outwardly extending thrust plate fixed with respect to the sleeve and a portion of the other race ring extends radially inwardly between the thrust plate and the radially extending portion of the angular ring, which radially extending portion of the angular ring has an opening defined in part by the two parallel guide surfaces, the radially extending portion of the other race ring having a projection extending axially through the opening and engaging the parallel guide surfaces, the other race ring being radially movable with respect to the sleeve against a friction force acting on the parallel guide surfaces and the surfaces of the projection.

9. An assembly as claimed in claim 8, wherein the opening in the radially extending portion of the angular ring is a slot having a narrower portion leading to the radially outer periphery of the radially extending portion of the angular ring.

10. An assembly as claimed in claim 8 or 9, wherein the free end of the annular axially extending portion of the angular ring engages in an annular circumferentially extending groove in the sleeve to hold the angular ring against movement in one axial direction with respect to the sleeve.

11. An assembly as claimed in claim 2, wherein a spring ring is fixed with respect to the other race ring and is disposed in the bore of the other race ring, the spring ring having two parallel portions extending transversely of the sleeve and providing the two parallel guide surfaces.

12. An assembly as claimed in claim 11, wherein the spring ring has curved portions at the ends of the parallel portions engaging the bore of the other race ring, the radius of curvature of the curved portions being less than the radius of curvature of the bore of the other race ring.

13. An assembly as claimed in claim 12, wherein the spring ring is broken at one of the curved portions.

14. An assembly as claimed in claim 11, 12 or 13, wherein the parallel portions of the spring ring engage in an annular circumferentially extending groove in the sleeve to hold the spring ring against movement in one axial direction with respect to the sleeve.

1 5. A self-centring clutch release bearing assembly substantially as herein described with reference to and as shown in Figures 1 and 2, or with reference to and as shown in Figures 3 and 4, or with reference to and as shown in Figures 5 and 6, or with reference to and as shown in Figures 7 and 8, or with reference to and as shown in Figures 9 and 10 of the accompanying drawings.

1 6. Rolling bearing disengager, especially for motor vehicle clutches, consisting of a sliding sleeve and a clutch bearing which abuts with the non-rotating bearing race ring radially displaceably on a thrust plate of the sliding sleeve and is held in the centred position by appropriate means, characterised in that the non-rotating bearing race ring is arranged pivotably within certain limits in the peripheral direction in relation to the sliding sleeve, a radially acting friction force being overcome, and is arranged displaceably in a radial direction along two guide faces extending parallel with one another.

1 7. Rolling bearing disengager according to claim 16, characterised in that the non-rotating bearing race ring or a part connected therewith comprises a bore of longitudinal slot type having two guide faces extending parallel with one another, the distance of which faces from one another is smaller than the diameter of the section of the sliding sleeve or the like engaging in this bore.

1 8. Rolling bearing disengager according to claim 1 6 or 17, characterised in that the bore is arranged eccentrically in the non-rotating bearing race ring or in a part connected therewith.

1 9. Rolling bearing disengager according to one of claims 1 6 to 18, characterised in that the sliding sleeve has in the region of contact with the guide faces a ring groove into which there is snapped the non-rotating bearing race ring or a part connected therewith.

20. Rolling bearing disengager according to one of claims 1 6 to 18, characterised in that between the non-rotating bearing race ring and the circumferential surface of the sliding sleeve or the like there is provided a retaining ring having a U-shaped cross-section, the legs of which rest on the guide faces, extending parallel with one another, of the bearing race ring and the circumferential surface of the sliding sleeve.

21. Rolling bearing disengager according to claim 20, characterised in that the retaining ring is provided with radially outwardly directed lugs which abut on the inside of the non-rotating bearing race ring.

22. Rolling bearing disengager according to claim 20 or 21, characterised in that the leg is provided at the outer end with an edge which engages in a turned recess on the circumference of the sliding sleeve.

23. Rolling bearing disengager according to claim 16, characterised in that the non-rotating bearing race ring is provided with an axially directed projection which engages in an opening of slot form of a flange part which is arranged for pivoting in the circumferential direction within certain limits on the circumference of the sliding sleeve and abuts with slight play on the inner surface of the non-rotating bearing race ring.

24. Rolling bearing disengager according to claim 16, characterised in that the non-rotating bearing race ring is provided in the bore of the flange with a projection directed axially towards the clutch, which projection engages in an opening of slot form of a flange part which is arranged pivotably within certain limits in the circumferential direction on the circumference of the sliding sleeve, is made L-shaped in crosssection and abuts with slight play on the inner surface of the non-rotating bearing race ring.

25. Rolling bearing disengager according to claim 23 or 24, characterised in that the flange part has on the outer marginal portion, in the region of the opening of slot form a slot extending through to the exterior.

26. Rolling bearing disengager according to one of claims 23 to 25, characterised in that the axially extending leg of the flange part is provided with an edge which engages in a circumferential groove on the circumference of the sliding sleeve.

27. Rolling bearing disengager according to one of claims 1 6 to 19, characterised in that in the bore of the outer race ring there is inserted a spring ring bent into oval form and having two side faces extending parallel with one another, which ring bears through two diametrically opposite, semi-circularly bent sections on the bore surface of the outer race ring.

28. Rolling bearing disengager according to claim 27, characterised in that the radius of the outer race ring bore is larger than the radius of the semi-circularly bent sections of the spring ring.

29. Rolling bearing disengager according to one of claims 27 or 28, characterised in that the spring ring is provided with a slot.