GB2338766A

GB2338766A - Clutch release bearing

Info

Publication number: GB2338766A
Application number: GB9905960A
Authority: GB
Inventors: Norbert Mebus; Holger Doerre; Christoph Hirschle
Original assignee: LuK Lamellen und Kupplungsbau GmbH; INA Waelzlager Schaeffler OHG
Current assignee: LuK Lamellen und Kupplungsbau GmbH; INA Waelzlager Schaeffler OHG
Priority date: 1998-03-20
Filing date: 1999-03-17
Publication date: 1999-12-29
Anticipated expiration: 2019-03-17
Also published as: GB2339000B; GB2338766B; FR2776350B1; KR19990078093A; DE19912432B4; BR9902337A; KR19990078092A; FR2776351A1; BR9902336A; DE19912431A1; DE19912432A1; DE19912431B4; GB9905960D0; KR100581779B1; FR2776351B1; FR2776350A1; GB9905961D0; GB2339000A; KR100627498B1

Abstract

A clutch release bearing has a bearing ring 3 with ball face 5 land is mounted rotationally rigid on a sliding sleeve 2. A rotating bearing ring 12a with associated bearing face 14a and ball face 52, and rolling bodies 21 are guided within the bearing and rotate about a common axis of rotation. Bearing ring 12a connects to or may be part of clutch diaphragm spring 15. The radius of curvature R of the ball face segments intersects the common axis of rotation provided by the rolling bodies of the release bearing and the release bearing is self-centring parallel to the axis 4 of rotation.

Description

1 1 - 1 RELEASE BEARING 2338766 The invention relates to a release bearing

for a clutch preferably in motor vehicles. Devices of this structural type are generally made from at least a bearing ring mounted rotationally rigid on a sliding sleeve, a bearing shell rotating with the speed of the clutch, wherein rolling bodies are housed between the two structural parts and rotate about a common axis of rotation. The displacement of this release bearing causes the deflection of a diaphragm spring which controls the engagement and disengagement of the clutch. The displacement takes place through a manually operated clutch pedal or through an automated operating system wherein in the case of the manual operation the movement of the pedal can be transferred to the guide tube of the release bearing through a Bowden cable and a disengagement lever. Other manual or automated operating systems are for example hydraulically operated. These comprise a master and a slave cylinder which are connected by a hydraulic lead. when activating the master cylinder the pressurised fluid located in same is transferred through the hydraulic lead to the slave cylinder and thus triggers axial displacement of the release bearing.

The construction of the release bearing corresponds substantially to that of an axial bearing or an inclined ball bearing wherein each bearing ring has an angled flange part mounted at right angles to the axis of symmetry of the release bearing. A bearing ring is thereby connected through the flange part rotationally rigid to the axially displaceable operating member. The diaphragm spring tongues or the disengagement lever of the clutch are supported on the flange part of the further S p 2 3 5 E 16 March -1999 1 1 2 circumferential bearing ring which is aligned relative to the clutch.

To prevent dust and impurities of any kind from entering into the release bearing the bearing is provided with seals which furthermore prevent lubricant from emerging from the release bearing.

In the installed state the release bearing can be exposed to a so-called tongue shock, i.e. an axial shock of the diaphragm springs which increases the wear on the release bearing and thus leads to a reduction in the service life.

This axial shock which is caused by the clutch diaphragm springs and is a condition of the production method results in sealing problems and loss of comfort in the case of the disengagement systems mentioned previously.

Furthermore the two drive components which are separated by the clutch have an axially parallel stagger between the force-transferring shafts which has to be compensated by a self-centring of the release bearing since otherwise the release bearing is exposed to increased wear and the comfort is impaired by the vibrations.

various proposals have been put forward to compensate this disadvantageous tongue shock and the axial stagger of the force- transferring shafts.

DE U 72 45 141 discloses a release bearing assembly where a centring ring is mounted between the spring tongues of the diaphragm spring and the inner ring of the release bearing. The contact bearing face is designed ball-shape between the inner ring and the centring ring whereby the centring ring can slide opposite the inner ring of the release bearing and can thus be aligned. The drawback 3 5 c, 19 19 1 3 with this proposed solution is inter alia a lack of a radial axially parallel compensation in the form of a radial self-centring so that a stagger between the forcetransferring shafts cannot be compensated. Furthermore a release bearing of the type disclosed tumbles about the ball centre of the ball-shaped centring ring since the release bearing is only mounted at this axial height by means of an elastic ring so that here irregular running and thus associated vibrations can be expected. The design of the release bearing in the form of solid structural parts made by stock-removal method furthermore requires a large amount of structural space and increased inherent weight.

The arrangement of a self-centring release bearing is shown in US 4 555 007. The outer bearing ring of the release bearing which is mounted rotationally rigid is supported radially displaceable on a housing which is connected rotationally secured to the displacement sleeve.

The housing thereby engages on the outside round the release bearing practically completely whereby the outer arm of the housing running axially parallel to the axis of symmetry of the release bearing is provided at the free end with a sealing disc which directed radially inwards forms a labyrinth seal with the inner ring of the rolling bearing which is formed in two parts. This arrangement allows no displacement or swivel movement of a structural part of the release bearing in order to compensate a tongue shock of the diaphragm spring tongues.

The object of the invention is therefore to design a release bearing so that the release bearing can be adapted to compensate an axially parallel stagger of the f orcetransferring shafts and the tongue shock of the diaphragm spring tongues as well as other influences which SP2358 16 Mar2h. 1993 - 4 contribute to the stagger between the two shafts can also be compensated. Furthermore the release bearing is to take up less structural space compared with the prior art and is to be manufactured more cost- effectively.

This is achieved according to the invention through designing a release bearing which consists of rolling bodies which are guided between a bearing ring mounted rotationally rigid on a sliding sleeve, a rotating bearing shell as well as between two structural parts and which rotate about a common axis of rotation and, between a diaphragm spring belonging to the clutch and the release bearing, two areas are provided having complementary ball face segments wherein the first area having one ball face segment is provided directly or indirectly on the diaphragm spring and the second area having a ball face segment is provided directly or indirectly on the release bearing and the radius of curvature of the ball face segments intersects the common axis of rotation provided by the rolling bodies of the release bearing and the release bearing is self-centring parallel to the axis of rotation.

Furthermore it is advantageous if the structural parts having the ball face segments can swivel relative to each other without resetting forces becoming active which can be produced in the proposed swivel area through stops.

The construction of the release bearing according to the invention further provides a bearing ring formed in two parts and on which the diaphragm spring tongues or the clutch diaphragm springs of the friction clutch are supported. This circumferential bearing ring is provided with a bearing shell for guiding the rolling bodies and with a flange part interacting with the spring tongues and S p 2) 3 5 8 16 March 1999 supported on the bearing shell whereby the flange part and the bearing shell form the complementary ball face segments. The section of the bearing ring f orming the support f lange or a f lange part is thus separate f rom the structural part on which the rolling bodies are guided. Through the bearing ring which is divided according to the invention, in the installed state with an axial shock of the clutch diaphragm spring which is a condition of the production method there results a single adjustment of the divided bearing ring, i.e. a displacement of the flange part relative to the bearing shell. The compulsory forces which follow from the axial shock are consequently kept away from the release bearing whereby an optimum circular running of the rolling bearing is maintained. The self adjusting rotating bearing ring of the release bearing according to the invention thus effectively stops a disadvantageous pulling up of the clutch which follows from the axial shock. The construction of the bearing ring which is designed in two parts according to the invention can thereby be used for both the pull-type and depressed operation of the friction clutch.

The invention further includes a sealed release bearing, i.e. sealing elements which are arranged each side of the rolling body. This prevents impurities from entering the inside of the release bearing i.e. onto the guide track of the rolling bearing. At the same time these sealing elements prevent lubricant from flowing out of the release bearing.

Advantageous developments are provided so that to seal the interior of the release bearing a sealing disc can be mounted on the bearing ring and a free end of the sealing disc can be guided up to the flange part whilst maintaining a sealing gap.

SP2358 16 March 19q9 1 - 6 Also the sealing disc can be made without cutting from sheet metal and/or can have an L-shaped profiled section whereby a short arm can be aligned under pretension on a cylindrical arm whilst observing a ring gap radially in the direction of the bearing ring.

The structural parts of the circumferential bearing which is designed in two parts are supported in the area of a curved contact zone. With an inclined force introduction from the clutch diaphragm springs up to the flange part of the bearing ring a certain displacement is possible relative to the bearing ring. The curved contact zone can thereby be suitably dimensioned to the forces which arise and taking into account the material used or material matching to reduce wear and improve the service life.

The compensating function according to the invention of the divided circumferential bearing ring causes an optimum force flow which has a positive effect on the ser-vice life of the release bearing. This action is set by dividing the bearing ring into a bearing shell for guiding the rolling bodies and into a flange part on which the spring tongues of the clutch diaphragm spring are guided. The bearing shell has on the side remote from the track of the rolling body a contact zone on which the flange part is supported. The bearing shell as well as the f lange part are f ormed complementary shaped as ball segments in the contact zone and are arranged concentric with each other so that in an installed position the flange part can slide along the curvature on the bearing shell. The desired self adjustment of the circumferential bearing ring which is designed in two parts is thereby improved in that the bearing shell and the flange part each form a ball segment in the area of a contact zone. This shaping makes it 6 Mare', 1?9 easier for the flange part to slide as required along the curved contact bearing face on the bearing shell when an axial or spring tongue shock occurs.

An alternative design provides a thin-walled bearing shell preferably made from steel without cutting and inserted in a flange part enclosing round the bearing shell. To this end the flange part is provided with a locator adapted to the outer curvature of the bearing shell and forming a contact zone to allow the flange part to slide along the curvature of the bearing shell.

A swivel angle 0 of +_ 10', pref erably 1. 50 has proved sufficient as the angle for the flange part to swivel relative to the bearing shell in the case of the circumferential bearing ring divided according to the invention. The invention includes a contact zone treated with antifriction means as a supporting measure for the bearing invention to allow the flange part to slide on the shell with reduced friction.

The invention further proposes that the inner bearing ring or the outer bearing ring are formed as a divided circumferential bearing ring. Thus the invention does not affect the arrangement or installation position of the bearing rings of the release bearing and the arrangement of the areas having the ball face segments. Thus by way of example the area having the second ball face segment can be formed from the bearing shell, the areas forming 30 the ball face segments can be arranged radially outside or radially inside the circumference formed by the rolling bodies and/or the area having a first ball face segment can be formed out of the f lange part or directly on the diaphragm spring.

S PI 3 5 H ' ma--U71999 - 8 A further design of the invention relates to the position of the contact zone between the bearing shell and the flange part. This is located according to the invention in a projection of a pressure line which connects the two contact points of the rolling body on the bearing shell and the rotationally rigid mounted bearing spring and which runs through the centre point of the rolling body whereby the radius of curvature intersects the axis of rotation defined by the rolling bodies. The agreement of the bearings favours the introduction of force from the flange part into the release bearing.

As a preferred embodiment the invention includes a bearing shell which encloses the ball shaped rolling bodies over an angle of < 1000. The flange part encloses in turn the bearing shell completely. To restrict the swivel movement of the flange part relative to the thin walled bearing shell stops are provided in the locator of the flange part each spaced form the relevant end of the bearing shell.

The invention further includes measures for producing a pre-assembled release bearing. For this a retaining member is used which is fixed on the bearing ring and engages round the further bearing ring with keyed engagement and liable to play. With the retaining member according to the invention a release bearing unit is obtained which cannot be lost and through which assembly is simplified and cost-effective storage is obtained.

According to the invention the release bearing comprise bearing rings which are made from sheet metal without cutting, for example by a deep drawing process and which can be manufactured in large numbers in a costeffective reliable process. The same preconditions apply to the S p 23 5 16 1999 1 9 - manufacture and use of all the remaining structural parts, by way of example the retaining member.

According to a preferred embodiment of the invention it is proposed to f ix the retaining member or retaining ring on the rotationally fixed bearing ring of the release bearing. The f ree end of the retaining member encloses a section of the associated further circumferential bearing ring whilst observing a ring gap. The f ree end of the retaining member thereby f ollows radially at distance an outer contour of the radially stepped section of the bearing ring and thus causes a secure hold of the two bearing rings to produce a pre-assembly unit of the entire release bearing. The retaining member thereby undertakes the task of sealing the functionally-conditioned gap between the bearing rings so that dirt and impurities of any kind are effectively prevented from entering the release bearing.

As an alternative the invention provides a retaining member which is fixed on the bearing shell or the flange part of the divided bearing ring and with the f ree end engages over the associated component part of the divided bearing ring. A retaining member of this kind can additionally be provided with a radially aligned edge which engages radially over a f ree end of the associated further bearing ring to provide a preassembly unit.

A suitable retaining member is a structural part made from sheet metal without cutting, preferably by a deep drawing process. For fixing, this structural part can be secured by a press-fit or welding. In the installed state the retaining member has a sufficient elasticity so that its radially stepped section during assembly of the bearing SP: 35e l5 Marc, -990 rings escapes radially and thus allows a positive locking hold of the individual component parts.

The invention includes a further sealing element which to produce a seal on both sides of the inner space of the release bearing is preferably mounted on the side of the rolling body remote from the retaining member. A sealing disc is suitable for this which is fixed on the rotationally rigid mounted bearing and is guided up to the opposite bearing ring whilst maintaining a ring gap. A sealing disc of this kind can be a structural part shaped from sheet metal without cutting and having an L-shaped profiled section. The short arm of this sealing disc is thereby supported under pretension on the rotationally 1-5 rigid mounted bearing ring. The long arm of the sealing disc bridges the distance between the two bearing rings. To obtain a labyrinth like sealing gap between the sealing disc and the rotating bearing ring the f ree end of the sealing disc can further be mounted parallel to a vertically aligned section of the rotating bearing ring. This design extends the sealing gap and thus improves the effectiveness of the seal.

A further inventive idea proposes a release bearing 25 wherein the bearing shell and the flange part are formed from structural parts which are supported on each other with linear contact. A displacement or a swivel movement of the flange part relative to the bearing ring can now be possible on a curvature of the bearing ring which advantageously forms a linear guide.

The invention will now be explained in further detail with reference to Figures 1 to 5 in which:

SP-Z 35e 999 - 11 Figure 1 shows a release bearing according to the invention in semi- section with a divided outer ring; Figure 2 shows a release bearing with a likewise divided outer ring wherein the bearing shell is integrated in the flange part; Figure 3 Figure 4 Figure 5 shows an alternative design of release bearing whose circumferential inner ring is divided into two; shows a two-part outer ring with a retaining member fixed on the bearing shell; and shows on an enlarged scale a detail of the release bearing shown in Figure 1.

Figure 1 shows a release bearing la which is f ixed on an axially displaceable operating member 2. The release bearing la comprises an inner bearing ring 3 which is connected rotationally rigid to the operating member 2. To this end the bearing ring 3 is provided with a f lange part which is vertically aligned i.e. runs at right angles to an axis 4 of rotation and which is supported on a retaining element 6 which is shaped from sheet metal. A diaphragm spring 7 inserted between an inner cylindrical section of the retaining element 6 and the flange part 5 is used to produce a force-locking bearing of the flange part 5 against the retaining element 6. The retaining element 6 which adjoins an end side 8 of the operating member 2 engages with an outer cylindrical section 9 round an end area of the operating member 2 and engages with a snap-fitting nose 10 into a radial recess 11 of the p 2.3 _z E a r ch 9 12 operating member 2 in order to produce a positive- locking engagement. The circumferential outer bearing ring 12a consists of two structural parts, namely a flange part 13a as well as a bearing shell 14a.

The flange part 13a f orms two arms 16, 17 arranged at right angles to each other. The vertically aligned arm 16 thereby serves to support spring tongues 15 which are in communication with a friction clutch which is not shown in Figure 1. The arm 17 which is angled in the opposite direction to the spring tongues 15 is provided with a radially outwardly rounded end section 18 and is supported on the inside on the bearing shell 14a through a contact zone 19. The contact zone 19 is thereby located on the outside on an area 20 of the bearing shell 14a having a ball face segment whereby the radius R of the ball face segment intersects the axis of rotation 4. As a result of the inner contour of the end section 18 which is formed complementary with the curvature 20 the flange part 13a and the bearing shell 14a form a ball segment 22. In order to achieve a direct introduction of force and to avoid a compulsory force the contact zone 19 and the pressure line 23 of the release bearing la are matched in position. The pressure line 23 is determined by the pressure angle (x of the release bearing la. AS a result of the divided arrangement of the bearing ring 12a according to the invention and a curved contact zone 19 the flange part 13a has a certain degree of f reedom. so that this can be aligned in the event of an axial shock of the spring tongue 15 and the bearing shell 14a can thereby perform a certain displacement corresponding to the swivel area 5 which is characterised by a double arrow.

S 3 58 16 Y.arcn ggg 13 The inner bearing ring 3 which is mounted rotationally rigid f orms at the end remote from the flange part 5 a cylindrical section 24 on which is fixed a retaining member 25 which is shaped from sheet metal like a sleeve.

This encloses the release bearing la practically completely whereby an end zone 26 of the retaining member 25 is angled radially inwards and thereby radially covers the end section 18 of the flange part 13a to secure all the individual parts of the release bearing la safe against loss. In the installed state of the release bearing la the retaining member 25 is mounted radially spaced from both the bearing shell 14a and the flange part 13a. Furthermore the retaining member 25 covers a gap 27 between the bearing shell 14a and the bearing ring 3 and thereby prevents dirt and impurities from entering into the release bearing la. The bearing ring 3 is provided with an L-shaped sealing disc 28 on the side of the rolling body 21 remote from the gap 27. A short arm 29 of the sealing disc 28 is held in force locking engagement under pretension on the bearing ring 3 for fixing. The radially aligned arm 30 is guided up to the flange part 13a whilst observing a sealing gap 31.

Figure 2 shows the release bearing 1b according to the invention. The individual component parts substantially agree with those in Figure 1 whereby the same parts are provided with the same reference numerals.

The release bearing 1b is provided with an outer bearing ring 12b which is shaped differently from the release bearing la. The flange part 13b of the bearingring encloses the rolling bodies 21 at the same time. A thin walled sheet metal dish formed without cutting serves as the bearing shell 14b. The dish is supported on a locator 37 of the flange part 13b whose contour is adapted to the SP2 3 5 e 16 Mach, 199? 14 ball segment face of the bearing shell 14b. A contact zone 19 is thereby set between the bearing shell 14b and the flange part 13b in accordance with Figure 1 and coincides with the pressure line 23 of the pressure angle a. This two-part bearing ring 12b also allows a displacement between the flange part 13b and the bearing shell 14 as a result of the bearing shell 14b which is mounted movable in the locator 37. The stops 35, 36 mounted on the flange part 13b and which are each mounted spaced from the end of the bearing shell 14b determine an adjustment area between the bearing ring 12b and the flange part 13b.

In Figure 3 the release bearing lc has as an alternative to the embodiments previously explained a divided circumferential inner bearing ring 32 which is comprised of the flange part 33 and the bearing shell 34. The outer bearing ring 38 is however connected rotationally secured to the retaining element 39 which is fixed on an operating member (not shown in Figure 3). The formation of the flange part 33 and the bearing shell 34 and their support is comparable with the design of the bearing ring 12a according to Figure 1, the flange part 33 likewise forms a ball face segment 40 with the radius R which with an outer contour of the bearing shell 34 forms the contact zone 41 which is mounted on the pressure line 43 of the pressure angle wherein R intersects the axis of rotation 4. A retaining member 42 which is fixed resiliently on the bearing shell 34 and radially covers the end area 40 of the flange part 33 serves to secure the two individual parts of the bearing ring 32 safe against loss. The release bearing ic furthermore has a sealing disc 44 which is fixed on the bearing ring 38 at the end directed towards the spring tongue 15. The sealing disc 44 is S E 2 3 _ 8 16 199 1 thereby directed radially inwards and is guided up to the bearing shell 34 whilst maintaining a sealing gap 45.

The release bearing 1d formed in Figure 4 likewise encloses a circumferentially divided outer ring 12a in a design which deviates from Figure 1. Since the principle construction does not however differ the structural parts relating to the bearing rings 3, 12a are provided with the reference numbers according to Figure 1 and are not explained in further detail. As opposed to Figure 1 the bearing shell 14a encloses an end area of the bearing ring 3. A sheet metal sleeve which is fixed rotationally secured on the bearing shell 14a and with a radially inwardly directed edge 46 covers a free end of the bearing ring 3 serves as the retaining member 46. The retaining member 46 forms at the end remote from the edge 47 several spring clips 48 which are spread out circumferentially and which here are supported with pretension on the flange part 13a. A sealing disc 49 fixed on the flange part 13a serves as a further seal for the release bearing id between the flange part 13a and the inner bearing ring 3. The free end of the sealing disc runs parallel to the vertically aligned flange part 5 of the bearing ring 3 and thus forms a desired extended sealing gap 50.

Figure 5 shows on an enlarged scale the structural parts of the release bearing la which are in rolling contact. According to this the flange part 13a is thus supported on the bearing shell 14a so that the pressure line 23 of the release bearing la is guided through the contact zone 19. The pressure line 23 connects the contact points 51 and 52 which are set between the rolling body 21 and the bearing ring 3 and bearing shell 14a respectively and runs through the centre point of the rolling body 21. The extension of the pressure line 23 defined by the pressure angle a to SP2353 16 Mard- 1999 16 - the axis of rotation (not shown) clearly shows that to achieve a ball segment face the ball radius has to intersect the axis of rotation.

The patent claims filed with the application are proposed wordings without prejudice for obtaining wider patent protection. The applicant retains the right to claim further features disclosed up until now only in the description and/or drawings.

References used in the sub-claims refer to further designs of the subject of the main claim through the features of each relevant sub-claim; they are not to be regarded as dispensing with obtaining an independent subject protection for the features of the sub-claims referred to.

The subjects of these sub-claims however also form independent inventions which have a design independent of the subjects of the preceding claims.

The invention is also not restricted to the embodiments of the description. Rather numerous amendments and modifications are possible within the scope of the invention, particularly those variations, elements and 25 combinations and/or materials which are inventive for example through combination or modification of individual features or elements or process steps contained in the drawings and described in connection with the general description and embodiments and claims and which through combinable features lead to a new subject or to new process steps or sequence of process steps insofar as these refer to manufacturing, test and work processes.

S P 2 3 5 16 V.arcn 19q9 - 17

Claims

1. Release bearing for a clutch, preferably for motor vehicles at least comprising a bearing ring mounted rotationally rigid on a sliding sleeve, a rotating bearing ring, as well as rolling bodies guided between the two structural parts and rotating about a common axis of rotation with the following features:

a) two areas having complementary ball face, segments are provided between a diaphragm spring belonging to the clutch and the release bearing; b) the first of the areas having the ball is c) e) f ace segments is provided directly or indirectly on the diaphragm spring; the second of the areas having the ball face segments is provided directly or indirectly on the release bearing; d) the radius of curvature of the ball f ace segments intersects the common axis of rotation provided by the rolling bodies of the release bearing; the release bearing is self-centring parallel to the axis of rotation.

2. Release bearing, more particularly according to claim 1 characterised in that the two areas having the ball face segments are able to swivel relative to each other.

3. Release bearing according to claim 1 and/or 2 characterised in that the structural parts having the ball face segments are free of the effect of resetting forces which are caused by stops mounted in the proposed swivel area of the structural parts.

4. Release bearing more particularly according to one of the preceding claims, characterised in that the two areas SP3se 16 Marcn 1999 - 18 forming the ball face segments form a preferably swivel area of 0 = +/10', preferably 0 = +/- 1.5'.

5. Release bearing more particularly according to one of the preceding claims, characterised in that the circumferential bearing ring is divided into a flange part forming the contact pressure plate for the diaphragm spring and a bearing shell.

6. Release bearing more particularly according to one of the preceding claims characterised in that the second area having a ball face segment is shaped out from a structural part belonging to the circumferential bearing ring.

7. Release bearing more particularly according to one of the preceding claims characterised in that the areas forming the ball face segments are mounted radially outside of the circumference formed by the rolling bodies.

8. Release bearing more particularly according to one of the preceding claims, characterised in that the areas forming the ball face segments are mounted radially inside the circumference formed by the rolling bodies.

9. Release bearing more particularly according to one of the preceding claims, characterised in that the first area having a ball face segment is shaped out from the flange part.

10. Release bearing more particularly according to one of the preceding claims characterised in that the first area having a ball face segment is shaped from tongues of the diaphragm spring.

S P 2 e 19

11. Release bearing more particularly according to one of the preceding claims characterised in that all the structural parts of the areas having the ball face segments are fixed with keyed engagement and with play on each other by means of a retaining member f ixed on the release bearing.

12. Release bearing more particularly according to one of the preceding claims, characterised in that the retaining 10 member is fixed on the bearing ring.

13. Release bearing more particularly according to one of the preceding claims, characterised in that the retaining member is fixed by welding and/or by a pressed fit on the 15 bearing ring.

14. Release bearing more particularly according to one of the preceding claims characterised in that the retaining member surrounds the structural parts of the areas having the ball face segments on the circumferential side.

15. Release bearing more particularly according to one of the preceding claims, characterised in that the retaining member surrounds the structural parts of the areas having 25 the ball face segments within the inner circumference.

16. Release bearing more particularly according to one of the preceding claims, characterised in that the retaining member surrounds the structural parts of the areas having 30 the ball face segments within the outer circumference.

17. Release bearing more particularly according to one of the preceding claims characterised in that the bearing shell is shaped on its outer circumference which is in connection with the rolling bodies into an area having a S pl- 35 8 6 v - a re ' Q 9 - ball face segment and that this area is adjoined with keyed engagement on the outer circumference by the flange part which forms the contact pressure plate whereby a retaining member surrounds on the outer circumference of the flange part the bearing shell and flange part with keyed engagement and with play.

18. Release bearing more particularly according to one of the preceding claims characterised in that the bearing shell enclosed by the flange part encloses the rolling bodies over an angle 0:! 1000.

19. Release bearing more particularly according to one of the preceding claims, characterised in that stops are provided on the locators of the bearing shell to def ine the swivel area of the flange part.

20. Release bearing more particularly according to one of the preceding claims characterised in that a retaining member is fixed on the rotationally rigid mounted bearing ring and the free end of the retaining member engages over a radially stepped section of the flange part by maintaining a radial ring gap and at the same time covers any gap which is set between the bearing ring and the bearing shell.

21. Release bearing, more particularly according to one of the preceding claims, characterised by a bearing shell on which a retaining member is fixed which is formed at one end as a spring clip wherein by means of the spring clip a force- locking contact is produced between the flange part and the bearing shell and the retaining member has at the end remote from the spring a radially inwardly aligned edge which radially covers a tree end of the bearing ring which is mounted rotationally fixed.

S F2, 35!E March 1999 21

22. Release bearing more particularly according to one of the preceding claims characterised in that the retaining member is snap-fitted with a further associated structural part, preferably with the flange part.

23. Release bearing more particularly according to one of the preceding claims, characterised in that a sealing disc is mounted on the bearing ring to seal an inner space of the rolling bearing and that a free end of the sealing disc is guided up to the flange part by maintaining a sealing gap.

24. Release bearing more particularly according to one of the preceding claims characterised in that the sealing disc is made without cutting from sheet metal and/or has an L-shaped profiled section wherein a short arm is aligned under pretension on a cylindrical arm by maintaining a ring gap radially in the direction of the flange part.

25. Release bearing more particularly according to one of the preceding claims characterised in that a sealing disc is fixed rotationally secured on the flange part and its free end runs by forming a sealing gap parallel to a vertically aligned flange part of the flange part.

26. Release bearing more particularly according to one of the preceding claims characterised in that at least one structural part is made without cutting.

27. Release bearing more particularly according to one of the preceding claims characterised in that a retaining member which is fixed on the bearing ring or bearing shell engages with keyed engagement and with play round each S ?2 358 16 March 1999 22 other bearing ring or a f lange part associated with the bearing ring.

28. Release bearing more particularly according to one of the preceding claims characterised in that sealing elements are mounted on either side of the rolling bodies.

29. Release bearing more particularly according to one of the preceding claims characterised in that the bearing shell and the flange part form structural parts which are supported with linear contact wherein the linear contact support allows the flange part to slide along a curvature of the bearing ring.

30. Release bearing more particularly according to one of the preceding claims characterised in that at least one structural part is made by the deep drawing process.

31. Release bearing more particularly according to one of the preceding claims characterised in that the release bearing is formed by the circumferential inner bearing ring which encloses the bearing shell and the flange part.

32. Release bearing more particularly according to one of the preceding claims characterised in that the contact zone between the bearing shell and the flange part is mounted on a pressure line of the release bearing which is defined by the pressure angle (x and which connects the two contact points of the rolling body on the bearing shell and on the bearing ring and is guided through the centre point of the rolling body.

33. Release bearing substantially as herein described with reference to the accompanying drawings.

SP'358 16 Marc, 1999