FR2776351A1 - SELF-CENTERED RELEASE SLEEVE - Google Patents

Abstract

The invention relates to a clutch sleeve (1a) of a coupling, preferably for vehicles, which consists of at least one bearing ring (3) arranged in a fixed manner in rotation on a sliding bushing, of a ring rotating (12a) bearing as well as rotating bodies (21) guided between the two components and rotating about a common axis of rotation. In this coupling, two zones (18, 20) which have complementary segments of spherical surfaces are provided between a disc spring (15) which belongs to the coupling and the clutch sleeve; the first (18) and the second (20) zones which include segments of spherical surfaces are provided, immediately or not, respectively on the disc spring and on the clutch release sleeve; the radius of curvature of the segments (19) of spherical surfaces intersects the common axis of rotation (4) predefined by the rotating bodies of the sleeve; and the latter is centered automatically, parallel to the axis of rotation.

Description

The present invention relates to a release sleeve for a

  coupling, preferably in motor vehicles, referred to simply as vehicles in the following. Devices of this type generally consist of at least one bearing ring arranged in a fixed manner in rotation on a sliding bushing, a bearing shell which rotates at the speed of rotation of the coupling, as well as rotating bodies mounted between the two components and rotating about a common axis of rotation. The displacement of this clutch sleeve causes the excursion of a disc spring, which controls the engagement of the coupling and its release. The movement is effected under the effect of a coupling pedal, to be actuated by a user, or of an automated operating system, the movement of the pedal being able to be transmitted to the guide tube of the clutch sleeve by the 'through a Bowden cable and a release lever in the case of operation by the user. Other automated maneuvering systems or actuated by a user are for example hydraulic maneuver. These systems include a master cylinder and a slave cylinder which are connected by a hydraulic line. Upon activation of the master cylinder, the pressurized fluid therein is displaced through the hydraulic line to the slave cylinder and thus triggers an axial displacement of the clutch sleeve. The structure of the declutching sleeve corresponds to a very large extent to that of an axial bearing or an oblique ball bearing in which each bearing ring comprising an inclined flange, arranged perpendicular to the axis of symmetry of the declutching sleeve. . The bearing ring is then fixedly connected in rotation via the flange part to the axially movable operating member, The disc spring blades or the clutch release lever are pressed on the part flange of the other bearing ring, rotating and oriented towards the coupling. To prevent the entry of dust and impurities of all types into the clutch sleeve, the latter is provided with sealing devices which also prevent the lubrication means from leaving the clutch sleeve. In the assembled state, the clutch sleeve can be

  exposed to what is called a blade shock, that is

  say an axial shock of the disc springs, which increases the wear of the clutch sleeve and therefore leads to a reduction in its service life. This axial shock which depends on the manufacturing and is caused by the disc springs of the coupling, leads to sealing problems and reductions in comfort in the

  declutching systems mentioned above.

  There may also be, between the two drive components separated by the coupling, a parallel offset of the power transmission shafts, which must be compensated by an automatic centering of the clutch sleeve, because the clutch sleeve would be otherwise exposed to increased wear and that reductions in comfort caused by vibration should then be tolerated. Various solution elements have been proposed in order to compensate for such a blade shock, a source of drawbacks, as well as the axial offset of the shafts of

power transmission.

  DE-A-72 45 141 proposes a clutch sleeve arrangement in which a centering ring is arranged between the spring leaves of the springs

  disks and the inner ring of the clutch sleeve.

  The bearing surface is spherical between the inner ring and the centering ring, so that the centering ring can move relative to the inner ring of the clutch sleeve and can therefore be oriented. It is a drawback, among other things, of the proposed solution that no radial compensation, parallel to the axis, in the form of radial self-centering is provided, so that an offset of the power transmission shafts cannot be compensated. In addition, a clutch sleeve in accordance with this teaching oscillates around the center of the sphere of the ring with a spherical configuration because the clutch sleeve is housed at this axial height only by means of an elastic ring, so that 'non-uniform operation and associated vibrations are to be expected in this case too. The configuration of the clutch sleeve as solid components produced by chip removal also involves a relatively large necessary mounting space and a weight

own high.

  The arrangement of a self-centering declutching sleeve is shown in US 4,555,007. The outer bearing ring, arranged in a rotationally fixed manner, of the declutching sleeve is supported by being able to move radially on a casing, which is fixedly connected in rotation to the movable sleeve. The casing here almost entirely surrounds the clutch sleeve on the outside, and the outer branch of the casing whose axis is parallel to the axis of symmetry of the clutch sleeve is provided at its free end with a sealing disc. , which forms, being oriented radially inwards, a labyrinth seal with the inner ring of the roller bearing produced in two elements. This arrangement does not allow movement or pivoting of a component of the clutch release sleeve

  to compensate for a shock from the disc spring blade.

  It is therefore the object of the invention to produce a clutch sleeve which makes it possible to adapt the clutch sleeve to compensation for an offset of parallelism between the axes of the power transmission shafts, and to compensation for blade shock from disc spring blades and other influences that contribute to the offset of the two shafts. In addition, the clutch sleeve must allow a reduced mounting space compared to the state of the art, and must be able

  be made more economically.

  To achieve these goals, the invention provides a clutch release sleeve, preferably for vehicles, which consists of at least one bearing ring arranged in a fixed manner in rotation on a sliding bushing, with a rotating ring. bearing as well as rotating bodies guided between the two components and rotating about a common axis of rotation, characterized in that a) two zones which have complementary segments of spherical surfaces are provided between a disc spring which belongs to the 'coupling and release sleeve; b) the first of the zones which comprise segments of spherical surfaces is provided, immediately or not, on the disc spring; c) the second of the zones which comprise segments with spherical surfaces is provided, immediately or not, on the clutch release sleeve; d) the radius of curvature of the spherical surface segments intersects the common axis of rotation predefined by the rotating bodies of the clutch release sleeve; e) the clutch sleeve is centered

  automatically, parallel to the axis of rotation.

  The two areas which have spherical surface segments can preferably rotate one

compared to each other.

  The areas which comprise the spherical surface segments may not be subjected to any effect of restoring forces which are exerted by stops

  arranged in the range of pivoting of the zones.

  The two areas which form spherical surface segments can preferably form a pivot range of $ = 10, preferably

= 1.5.

  The rotating bearing ring can be divided into a flange part which forms a pressure plate

  for the disc spring and a bearing shell.

  The second zone which includes a spherical surface segment can be shaped from a

  component that belongs to the rotating bearing ring.

  The zones which form the segments of spherical surfaces can be arranged radially, either outside or inside the perimeter formed by

the rotating bodies.

  The first zone which includes a spherical surface segment can be shaped from the

flange part.

  The first zone which includes a spherical surface segment can be shaped from the blades of the disc spring. It can be provided that all the components of the zones which comprise the spherical surface segments are attached to each other in positive engagement with play by a holding member attached to the

clutch sleeve.

  The holding member can be attached to the

bearing ring.

  In particular, the holding member can be attached to the bearing ring by welding or by adjustment

tight.

  The holding member can surround on the perimeter side the components of the zones which include segments of spherical surfaces. The holding member may surround at their internal perimeter the components of the zones which comprise the spherical segments or, as a variant, the holding member may surround at their external perimeter, the components of the zones which comprise the segments of spherical surfaces. The bearing shell can be shaped, at its internal perimeter which is in connection with the rotating bodies, to form a zone which comprises a spherical surface segment, the flange part which forms the pressure plate connecting in positive engagement to this area at the outer perimeter, and a retaining member surrounding, in positive engagement with each other and with play, the bearing shell and the flange part at the outer perimeter of the flange part. 15 The bearing shell surrounded by the flange part can surround the rotating bodies at an angle

i <1000.

  Stops which limit the swivel range of the flange part can be provided on the

housing of the bearing shell.

  A retaining member, the free end of which overlaps a portion comprising radially steps of the flange portion while maintaining a radial annular space and simultaneously covers a gap which is established between the bearing ring and the bearing shell can be attached to the bearing ring arranged

fixedly in rotation.

  The declutching sleeve may comprise a bearing shell to which a holding member is attached, one end of which is configured as an elastic clip, the elastic clip causing the flange part to be pressed by force on the bearing shell and the 'retaining member having at its end opposite the elastic clip an edge oriented radially inwardly which radially covers a free end of the bearing ring arranged in a fixed manner in rotation. The holder can be snapped onto another associated component, preferably with the flange portion. A sealing disc can be arranged on the bearing ring to seal an interior space of the roller bearing, a free end of the sealing disc being guided up to the flange part while maintaining a

sealing interval.

  Provision may be made for the sealing disc to be made of sheet metal without removal of chips and / or to have an L-shaped profile, a short branch of which is held by force under stress on the bearing ring and a branch of which is oriented radially. is guided by maintaining a sealing gap up to the flange part A sealing disc can be fixedly fixed in rotation on the flange part, its free end being in a line parallel to an oriented flange part vertically from the flange part forming

a sealing space.

  We can predict that at least one component is

  manufactured without chip removal.

  A holding member which is attached to the bearing ring or to the bearing shell may surround in positive engagement with play the other respective bearing ring or a flange part belonging to the ring.

bearing.

  Sealing elements can be arranged on

  both sides of the rotating bodies.

  The bearing shell and the flange part can form components which are supported by linear contact, the support by linear contact allowing a displacement of the flange part along a curvature

of the bearing ring.

  Provision may be made for at least one component to be manufactured by a deep drawing process. The release sleeve can be formed by the rotating inner bearing ring, which includes the

  bearing shell and flange part.

  The contact zone between the bearing shell and the flange part can be arranged on a pressure line of the clutch sleeve which is defined by the pressure angle "a" 'of the clutch sleeve and which connects the two points of contact of each rotating body, with the bearing shell and with the ring

  bearing, and which passes through the center of the rotating body.

  The aims, features and advantages of the invention set out above, as well as others,

  will emerge more from the detailed description of

  preferred embodiments, with reference to the accompanying drawings in which: Figure 1 shows in cross section one half of the clutch sleeve according to the invention with divided outer ring; Figure 2 shows a declutching sleeve also comprising an outer ring divided into two parts, in which the bearing shell is integrated in the flange part; Figure 3 a variant configuration of a declutching bearing, the inner rotating ring is made of two elements; Figure 4 an outer ring in two parts with holding member attached to the bearing shell; and Figure 5 a detail, on a larger scale, of the

  clutch release sleeve shown in Figure 1.

  In Figure 1 is shown a clutch sleeve 1a which is attached to an operating member 2 arranged to slide axially. The declutching sleeve la comprises an inner ring 3 for the bearing fixedly connected in rotation to the operating member 2. For this purpose, the bearing ring 3 is provided with a flange part 5 which is oriented vertically, c 'that is to say 5 of a path perpendicular to an axis of rotation 4, and which rests on a holding element 6 made of sheet metal. A disc spring 7 is mounted between an inner cylindrical part of the retaining element 6 and the flange part 5 and is used to achieve pressing force 10 on the flange part 5 on the retaining element 6. L holding element 6 which rests on a front side 8 of the operating member 2 surrounds by its external cylindrical part 9 an end zone of the operating member 2 and thus penetrates, by a latch 15 10 to snap , in a radial recess 11 of the operating member 2 to achieve safety in positive engagement. The outer rotating ring 12a of the bearing consists of two components, a part 13a

  flange and a bearing shell 14a.

  The flange part 13a forms two branches 16, 17 perpendicular to each other. The vertically oriented branch 16 here serves as a support for spring blades 15 which are in connection with a friction coupling not shown in Figure 1. The branch 17 inclined in the opposite direction to the spring blades 15 is provided with a part end 18 rounded radially outward and bears on the inner side by means of a contact zone 19 on the bearing shell 14a. The contact zone 19 is then located on the outside in a zone 20 of the bearing shell 14a which has a spherical surface segment, the radius R of the spherical surface segment intersecting the axis of rotation 4. Due to the contour inside the end part 18 whose configuration is complementary to the curvature 20, the flange part 13a and the bearing shell 14a form a spherical segment 22. The positions of the contact zone 19 and of the pressure line 23 of the declutching sleeve coincide so that the force application is direct and to avoid a stress reaction. The pressure line 23 is defined by the pressure angle "'" l of the disengaging sleeve la. Since the bearing ring 12a is divided according to the invention and the structure of a contact area 19 is curved, the flange part 13a has a certain degree of freedom, so that it can be oriented in the event of axial shock of the leaf 15 of spring, and that a displacement of the bearing shell 14a which corresponds to the range of pivoting "I" designated by a double arrow can therefore be effected. The inner ring 3 of the bearing arranged in a fixed manner in rotation constitutes at the end opposite to the flange part 5 a cylindrical part 24 to which a sheet metal holding member 25 is attached, with a socket configuration. This member almost entirely surrounds the declutching sleeve la, an end region 26 of this retaining member 25 being folded radially inwards and thus radially covering the end part 18 of the flange part 13a in order to form a protection which makes captive all the individual parts of the clutch sleeve. In the mounted state of the declutching sleeve 1a, the retaining member 25 is thus arranged radially at a distance both from the bearing shell 14a and from the flange part 13a. The retaining member 25 also covers a gap 27 between the bearing shell 14a and the bearing ring 3, and thus prevents dust and impurities from entering the bearing ring 1a. On the side of the rotating bodies 21 opposite the gap 27, the bearing ring 3 is provided with a sealing disc 28 with an L configuration. A short branch 29 of the sealing disc 28 is held under stress by effect force on the bearing ring 3 to attach this disc. The radially oriented branch 30 is on the other hand guided as far as the flange part 13a while maintaining a sealing gap 31. FIG. 2 shows the declutching sleeve 1b according to the invention. The individual components are to a large extent similar to those in Figure 1, and similar elements are designated by the same

digital references.

  The declutching sleeve 1b is provided with an outer ring 12b, the configuration of which differs from that of the declutching sleeve 1a and the flange portion 13b of which simultaneously encloses the rotating bodies 21. A thin-walled sheet metal shell produced without removal of chips, which serves as a bearing shell 14b, is supported on a housing 37 of the flange portion 13b, the outline of which is adapted to the surface of the spherical segment of the bearing shell 14b. As in FIG. 1, there is then established between the bearing shell 14b and the flange part 13b a contact area 19 which coincides with the pressure line 23 of the pressure angle a. This two-part bearing ring 12b also allows movement between the flange part 13b and the bearing shell 14 because the shell 14b of

  bearing is movably arranged in the recess 37.

  The stops 35, 36 arranged on the flange part 13b, which are respectively arranged at a distance towards the end of the shell 14b, determine an adjustment zone between the bearing ring 12b and the part 13b

flange.

  The declutching sleeve lc of FIG. 3 comprises, as a variant to the embodiments previously exposed, a divided rotating internal ring 32 of bearing which consists of the flange part 33 and the bearing shell 34. The outer ring 38 of the bearing, on the other hand, is fixedly connected in rotation to the holding element 39 which is fixed to an operating member not shown in FIG. 3. The configuration of the flange part 33 and that of the shell 34 bearing, as well as their support, are comparable to the case of the structure of the bearing ring 12a of Figure 1: the flange portion 33 also constitutes a segment 40 of spherical surface of a radius R which forms with a contour outside of the shell 34 of the bearing, the contact zone 41 which is arranged on the pressure line 43 of the pressure angle, the radius R intersecting the axis of rotation 4. To make captive the two individual elements of the ring 32 bearing, using a retaining member 42 which is attached elastically to the bearing ring 34 and radially covers the end region 40 of the flange portion 33. The clutch sleeve lc further comprises a sealing disc 44 which is attached to the bearing ring 38 at the end

  oriented towards the leaf 15 of spring.

  The sealing disc 44 is then oriented radially inwards and is guided to the bearing shell 34 while maintaining an interval

sealing 45.

  The declutching sleeve ld shown in FIG. 4 also comprises a divided external rotating ring 12a, in a configuration which deviates from that of FIG. 1. Since the structure is not distinguished in principle, however, the components which relate to the bearing rings 3, 12a are designated by the same reference numerals as in Figure 1 and are not explained in more detail. Unlike Figure 1, the bearing shell 14 surrounds an end region of the bearing ring 3. A sheet metal sleeve 46 is used as the retaining member 46 which is fixedly fixed in rotation on the bearing shell 14a and which covers a free end of the bearing ring 3 by means of an edge 47 oriented radially inwards. . On the end opposite the edge 47, the retaining member 46 forms several elastic staples which are arranged in a distributed manner on the perimeter and which rest under stress on the flange part 13a. To increase the tightness of the declutching sleeve ld between the flange part 13a and the inner ring 3, a sealing disc 49 is provided which is attached to the flange part 13a and the free end of which is of parallel layout. to the vertically oriented flange portion 5 of the sealing ring 3, and thus forms a desired extended sealing gap 25. In Figure 5 are shown on a larger scale components of the clutch sleeve la which are in rotational contact. According to this figure, the flange part 13a rests on the bearing shell 14a in such a way that the pressure line 23 of the clutch sleeve passes it through the contact zone. The pressure line 23 connects the contact points 51 and 52 which are established between each rotating body 21 on the one hand and the bearing ring 3 or the bearing shell 14a on the other hand, and passes through the middle of the body turning 21. The extension of the pressure line 23 defined by the pressure angle a towards the axis of rotation not shown indicates that the radius of the sphere must cut the axis of rotation to achieve

a spherical segmented surface.

  The claims appended to this application

  are wording proposals, without prejudice to obtaining continuous patent protection. The plaintiff reserves the right to claim yet other particularities which have not so far been explained

  as in the description and / or the drawings.

  References used in the sub-

  claims relate to further development

  the subject matter of the main claim through

  peculiarities of the respective subclaims; he

  should not be considered as a renunciation of obtaining independent protection of the subject of

  peculiarities of the subclaims concerned.

  But the objects of these subclaims

  also constitute autonomous inventions, which represent an independent configuration of objects

  previous subclaims.

  The invention is also not limited to the example

  or to the embodiments of the description. Well

  rather, many alterations and modifications are possible within the framework of the invention, in particular variants, elements and combinations and / or materials which are for example inventive by combination or transformation of the particularities or elements or stages

  described in the general description and the

  embodiments as well as the claims and

  contained in the drawings, and which lead by particulars to be combined with a new object or with new process steps or sequences of process steps, insofar as they relate to

  manufacturing, verification and machining processes.

Claims (32)

  1. Clutch release sleeve, preferably for vehicles, which consists of at least one bearing ring arranged in a fixed manner in rotation on a sliding bushing, a bearing rotating ring as well as guided rotating bodies. between the two components and rotating around a common axis of rotation, characterized in that a) two zones (18, 20) which have complementary segments of spherical surfaces are provided between a disc spring (15) which belongs to the coupling and release sleeve (la, lb, lc, ld); b) the first (18) of the zones which include spherical surface segments is provided, immediately or not, on the disc spring (15); c) the second (20) of the zones which comprise segments with spherical surfaces is provided, immediately or not, on the clutch release sleeve (la, lb, lc, ld); d) the radius of curvature of the segments (19) of spherical surfaces intersects the common axis of rotation (4) predefined by the rotating bodies (21) of the clutch release sleeve; e) the clutch sleeve is centered   automatically, parallel to the axis of rotation (4).   2. Release sleeve according to claim 1, characterized in that the two zones (18, 20) which comprise segments of spherical surfaces can pivot one compared to each other.   3. Release sleeve according to claim 1 or claim 2, characterized in that the zones (18, 20) which comprise the segments of spherical surfaces are not subjected to any effect of restoring forces which are exerted by stops (35 , 36) arranged in the range of pivoting of the zones (18, 20).   4. Release sleeve according to any one of   previous claims, characterized in that   the two zones (18, 20) which form segments of spherical surfaces preferably form a pivot range of 1 = 10, preferably = + 1.50. 5. Release sleeve according to any one of   previous claims, characterized in that   the bearing rotating ring (12a) is divided into a flange part (17) which forms a pressure plate for the disc spring (15) and a shell (20) bearing.   6. Release sleeve according to any one of   previous claims, characterized in that   the second zone (20) which comprises a spherical surface segment is shaped from a component   which belongs to the rotating bearing ring (12b).   7. Release sleeve according to any one of   previous claims, characterized in that   the zones (18, 20) which form the segments of spherical surfaces are arranged radially outside the perimeter formed by the rotating bodies (21).   8. Release sleeve according to any one of   previous claims, characterized in that   the zones (20) which form the segments of spherical surfaces are arranged radially inside the perimeter formed by the rotating bodies (21). 9. Release sleeve according to any one of   previous claims, characterized in that   the first zone (20) which comprises a spherical surface segment is shaped from the part (13a) flange.   10. Release sleeve according to any one of the preceding claims, characterized in that   the first zone (20) which has a spherical surface segment is shaped from blades (15) of the disc spring.   11. Release sleeve according to any one of the preceding claims, characterized in that   all the components (12a, 14) of the zones (18, 20) which comprise the spherical surface segments are fixed to each other in positive engagement with play by means of a holding member (25) attached to the clutch sleeve (la).   12. Release sleeve according to any one   of the preceding claims, characterized in that   the holding member (25) is attached to the ring (5) bearing.   13. Release sleeve according to any one   of the preceding claims, characterized in that   the holding member (25) is attached to the ring   (5) bearing by welding or press fitting.   14. Release sleeve according to any one   of the preceding claims, characterized in that   the holding member (25) surrounds on the perimeter side the components (14a, 12a) of the zones (18, 20)   which have segments of spherical surfaces.   15. Release sleeve according to any one   of the preceding claims, characterized in that   the holding member (42) surrounds at their internal perimeter the components (33, 34) of the zones (41) which   have spherical segments.   16. Release sleeve according to any one   of the preceding claims, characterized in that   the holding member (25) surrounds at their outer perimeter, the components (12a, 14a) of the zones (20) which   contain the spherical surface segments.   17. Release sleeve according to any one   of the preceding claims, characterized in that   the bearing shell is shaped, at its internal perimeter which is in connection with the rotating bodies, to form a zone which comprises a spherical surface segment, in that the flange part which forms the pressure plate is connected in positive engagement to this zone at the outer perimeter, and in that a holding member (46) surrounds, in positive engagement with one another and with play, the bearing shell (14a) and the flange part (13a) at the perimeter   outside of the flange part (13a).   18. Release sleeve according to any one   of the preceding claims, characterized in that   the bearing shell (14a) surrounded by the flange part (13a) surrounds the rotating bodies (21) on a angle Z C 1000.   19. Release sleeve according to any one   of the preceding claims, characterized in that   stops (35, 36) which limit the pivot range of the flange part (12b) are provided on   the housings (37) of the bearing shell (14b).   20. Release sleeve (la) according to one   any of the preceding claims, characterized   in that a holding member (25), the free end (26) of which overlaps a part (18) radially comprising steps of the flange part (13a) while maintaining a radial annular space and simultaneously covers a gap (27) which is established between the bearing ring (12a) and the bearing shell (14a) is fixed on the   bearing ring (5) arranged in a fixed manner in rotation.   21. Release sleeve (ld) according to one   any of the preceding claims, characterized   in that it comprises a bearing shell (14a) to which is attached a holding member (46), one end of which is configured as an elastic clip (48), in that the elastic clip (48) brings the part (12a ) flange to be pressed by force on the bearing shell (14a) and in that the holding member (46) has at its end opposite the elastic clip (48) an edge (47) oriented   radially inwards which radially covers a free end of the bearing ring (3) arranged in a fixed manner in rotation.   22. Release sleeve (ld) according to one   any of the preceding claims, characterized   in that the holding member (46a) is engaged with another associated component, preferably with the part (12a) flange.   23. Release sleeve (la, lb) according to one   any of the preceding claims, characterized   in that a sealing disc (28) is arranged on the bearing ring (3) to seal an interior space of the roller bearing (la, lb), and in that a free end of the disc seal (28) is guided to the flange part (12a, 12b) in   maintaining a sealing gap (31).   24. Release sleeve (la, lb) according to one   any of the preceding claims, characterized   in that the sealing disc (28) is made of sheet metal without removal of chips and / or has an L-shaped profile, a short branch (29) of which is held by force under stress on the ring (3) bearing and of which a radially oriented branch (30) is guided by maintaining a sealing gap (31) up to the flange part (13a, 13b)   25. Release sleeve according to any one of the preceding claims, characterized in that   a sealing disc (49) is fixedly fixed in rotation on the flange part (12a) and its free end is of a line parallel to a vertically oriented flange part (5) of the flange part   flange (3) forming a sealing space (50).   26. Release sleeve according to any one   of the preceding claims, characterized in that   at least one component (12a, 12b, 14a, 14b, 13a, 13b, 32, 3, 38, ...) is produced without removing chips. 27. Release sleeve according to any one   of the preceding claims, characterized in that   a holding member (25, 42, 46) which is attached to the bearing ring (3) or to the bearing shell (14a, 34) surrounds in positive engagement with play the other respective bearing ring or part of flange belonging to the bearing ring.   28. Release sleeve according to any one   of the preceding claims, characterized in that   sealing elements (50, 49) are arranged   on both sides of the rotating bodies (21).   29. Release sleeve according to any one   of the preceding claims, characterized in that   the bearing shell (14a, 14b, 34) and the flange part (13a, 13b, 33) form components which are supported by linear contact and in that the support by linear contact allows a displacement of the part ( 13a, 13b, 33) flange along a   curvature (20) of the bearing ring (14a, 14b, 34).   30. Release sleeve according to any one   of the preceding claims, characterized in that   at least one component is manufactured by a process deep drawing.   31. Release sleeve according to any one   of the preceding claims, characterized in that   the declutching sleeve (lc) is formed by the rotating internal bearing ring (32), which comprises the bearing shell (34) and the flange part (33). 32. Release sleeve according to any one   of the preceding claims, characterized in that   the contact area (19, 41) between the bearing shell (14a, 14b, 34) and the flange part (13a, 13b, 33) is arranged on a pressure line (23, 43) of the clutch sleeve ( la, lb, lc, ld) which is defined by the pressure angle "g" of the clutch sleeve (la, lb, lc, ld) and which connects the two contact points (51, 52) of each rotating body (21), with the bearing shell (14a, 14b, 34) and with the bearing ring (3, 38), and which passes through the center of the rotating body (21).