DE102011003030A1 - Coupling disk, particularly for friction coupling for motor vehicle, comprises torsional vibration damper and hub disk which is arranged on hub, where friction device is arranged between hub disk and cover plate - Google Patents

Abstract

The coupling disk (1) comprises a torsional vibration damper and a hub disk (10) which is arranged on a hub (4) that is associated with a gear shaft. A friction device (24) is arranged between the hub disk and a cover plate (18,20). An element of the friction device, is connected with the hub in a rotating manner.

Description

The present invention relates to a clutch disc, in particular for a friction clutch of a motor vehicle with a torsional vibration damper according to the preamble of patent claim 1.

From the prior art clutch discs for high torques are known in which the friction linings are mounted on the hub disc of the torsion damper. Thus, the hub disc forms the part through which the torque is introduced from the linings in the clutch disc. The cover plates of the torsion damper in this case form the output parts of the torsion damper. In contrast, in the conventional coupling disks known from the prior art for lower torques, one of the cover plates is connected to the friction linings, so that the cover disk forms the input part of the torsion damper and the hub disk forms the output part of the torsion damper. However, since at high torques a symmetrical torque distribution is more important than the installation space optimization, in the case of clutch disks for high torques, the hub disks are used as the input part of the torsion damper.

Between the hub disc and the cover plates, a friction device is provided in the known clutch discs, which consists of one or more friction rings, which are axially biased by means of a plate spring or the like. The axial preload makes it possible that despite wear on the friction rings a largely constant friction over the life of the clutch disc is provided.

In this case, the friction rings and the biasing springs are usually loosely inserted in the direction of rotation or with a rotational drive (backlash) between the hub disc and the cover plates to ensure an axial jam-free mobility.

However, this backlash also requires that an increased wear occurs on the friction device, since the components can move uncontrollably relative to each other.

Object of the present invention is therefore to provide a clutch disc in which the wear on the friction device significantly reduced and the function of the friction device over the life of the clutch disc is improved.

This object is achieved by a clutch disc according to claim 1.

The present invention is based on the idea of non-rotatably connecting at least one element of the friction device, for example one of the friction rings with a hub, wherein the rotationally fixed connection should be designed such that the axial mobility of the parts is ensured.

Usually, the clutch disc on a hub disc, which is arranged with play in the circumferential direction on a transmission input shaft associated hub. In friction clutches for very high torques, this hub disc is also connected to the friction linings for torque transmission. On both sides of the hub disc cover plates are arranged, which in turn are mutually rotationally fixed and spaced from each other. In order to dampen the torsional vibrations of the engine, further torsion springs are provided, which are arranged in recesses between the hub disc and cover plates, and a friction device, which dissipates the force acting on the torsion force. In this case, the friction device has at least one friction ring and a biasing element, wherein the biasing element provides for the axial movement and ensures that the friction device provides a power dissipation over the life of the clutch disc despite wear.

The hub can be assigned directly to a transmission input shaft, but it is also possible, as a preferred embodiment shows that the hub of an inner hub with an internal payment and an external toothing, and the inner hub enclosing one-piece outer hub is formed, wherein the outer hub is a in having the external teeth of the inner hub engaging internal teeth. In this case, the outer hub rotatably coupled with the inner hub, however, it is provided a predetermined rotational clearance between the inner hub and outer hub.

Such a one-piece outer hub can be made for example by cold extrusion, forging, sintering or punching from a thick sheet.

The non-rotatable but axially movable connection between the element of the friction device and the hub can, as a preferred embodiment shows, be provided by the fact that a normally normally connected to the cover plates with the hub connecting element is also designed to rotate the at least one element of the friction device to connect with the hub. Preferably, such a connecting element is a rivet, or a pin, which is guided through openings in the at least one element of the friction device and through the corresponding openings in the hub and cover plate.

If a pin is used as a connecting element, as another embodiment shows that the axial attachment of the clutch disc components, for example, be provided by retaining rings, which are fixed axially outside the cover plates to the hub. In this case, the pin provides the anti-rotation, while the circlips specify the axial attachment.

According to a further advantageous embodiment, the at least one element of the friction device is equipped with an internal toothing, which engages without play in an external toothing of the hub. This also creates a rotationally fixed connection between the element of the friction device and the hub.

Preferably, the internal toothing of the at least one element of the friction device is substantially identical to the internal toothing of the outer hub, if such a hub design is used.

According to a further preferred embodiment, the rotationally fixed connection between the element of the friction device and the hub is indirectly provided that the hub is rotatably connected to the cover plate and the at least one element of the friction device is in turn rotatably connected to the cover plate.

It is particularly advantageous if the rotationally fixed connection between the at least one element of the friction device and the cover plate is realized by means of at least one nose which engages in the adjacent cover plate or in the at least one element of the friction device, wherein preferably the nose in the circumferential direction has a spring bias ,

This preload is advantageously smaller than the axial mobility of the lugs, in particular, the spring bias of the lugs in the circumferential direction is smaller than the axial spring force of the biasing device, so that an axial mobility can be ensured.

Advantageous embodiments, such as such a nose can be realized in the patent application DE 10 2010 013 632 described, the disclosure of which is hereby incorporated in full in this patent application.

According to a further advantageous embodiment, the friction device may comprise a first and a second friction ring, wherein the friction rings are arranged on both sides of the hub disc and wherein the biasing means is associated with the second friction ring and rotationally fixed to the hub, in particular the outer hub is connected. In this case, only the first friction ring rotatably connected to the hub or outer hub, while the second friction ring and the biasing means are loosely inserted. But is particularly advantageous if the biasing device enters into a rotationally fixed connection with the hub, wherein the rotationally fixed connection advantageously indirectly via a rotationally fixed connection of the biasing device with the cover plate and / or with the friction ring by means of a nose in the cover plate and / or the Engage friction ring, is feasible.

Preferably, the friction ring and the biasing means may be formed as an integral component, wherein advantageously the biasing means has a particular applied by pressing, gluing and / or spraying friction material.

Instead of having a nose, the pretensioning device can also be non-rotatably connected directly to the hub, in particular the outer hub, by means of the above-mentioned connecting element.

According to a further advantageous embodiment, at least one friction ring of the friction device is designed in several parts, the multi-part friction ring preferably consists of a rubbing part, which consists in particular of hardened steel or an organic friction material or a special surface coating, and a spacer, in particular made of steel or plastic exist. This multi-part design of the friction ring has the particular advantage that only the thin friction part can be made of correspondingly high-quality material, and the spacer is made of less expensive material manufacturable.

According to a further advantageous embodiment, elements of the friction device may be rotatably connected to the hub disc. In particular, it is conceivable that the second friction ring and / or the biasing means are rotatably connected to the hub disc. According to a particularly preferred embodiment, the lining carrier plate, on which the friction linings are fastened, is extended radially inwards and is formed at its radially inner region as a biasing element and / or friction ring. Such a configuration has the advantage that the number of components of the clutch disc can be reduced.

In this case, it is advantageous if the riveting between the hub disc and the lining carrier plate takes place in the outer region of the hub disc, so that the lining carrier plate can be formed as a biasing spring for the friction device in the inner region of the hub disc.

In addition, the formed as a biasing device pad carrier plate rotatably with the be connected to the second friction ring, wherein the second friction ring may be formed, for example by means of pressing, gluing and / or spraying of friction material on the biasing means.

According to a further preferred embodiment, the clutch disc may comprise a damper device or an idler damper, one side of which may preferably be arranged on the outer hub and the other side on the inner hub.

According to a further advantageous embodiment, the friction ring of the friction device can have a different friction over its surface. It is particularly advantageous if the friction is formed higher in the radially inner region than in the radially outer region. In this case, for example, in the radially inner region, this increased friction by roughening done, since in the radially inner region, a relative movement that would wear out the surface does not occur or only to a very limited extent.

According to a further advantageous embodiment, it may be provided to harden the friction ring in particular in the areas in which relative movement takes place. For example, can be hardened by certain hardening methods such as case hardening, targeted the frictional surface or targeted the tooth flanks.

If the friction ring consists of several individual sheets, it may be advantageous to make the sheet, which bears against the component and makes a relative movement with respect to the friction ring, harder than the other sheets.

In addition, it may be advantageous to manufacture the rubbing element from an organic friction material.

According to a further advantageous embodiment, the biasing spring of the friction device is provided from two closed annular regions, in which the possibility of a radial compensation is created in the connection region, to allow an axial displacement of the annular regions to each other. Such a configuration can be realized, for example, in that the connection region is at least partially S-shaped in section.

Alternatively, it is also advantageous if, as another advantageous embodiment shows, only the inner or only the outer region of the biasing spring consists of a closed ring, while the other part is not closed, but for example by tongues or by slitting the ring resulting ring segments is trained.

It is also advantageous if, as a further example, the biasing spring is formed from a closed annular element with two axially offset, mutually arranged regions, so that the spring has a pot-shaped shape.

According to a further advantageous embodiment, the spring may remain uncured in the inner region and be cured only in the outer spring region.

Further advantages and preferred embodiments are set forth in the appended claims, the following description of the drawings and the drawings themselves.

In the following, the principle of the invention will be described with reference to preferred embodiments shown in the figures. However, the embodiments shown are purely exemplary in nature and do not specify the scope of the patent application. This is defined solely by the appended claims.

In the following show:

1 a schematic partial view of a first preferred embodiment of the clutch disc according to the invention;

2 a schematic partial view of a second preferred embodiment of the clutch disc according to the invention;

3 a schematic partial view of a third preferred embodiment of the clutch disc according to the invention;

4 a schematic partial view of a fourth preferred embodiment of the clutch disc according to the invention;

5 a schematic partial view of a fifth preferred embodiment of the clutch disc according to the invention;

6 : a schematic partial view of a sixth preferred embodiment of the clutch disc according to the invention;

7a , b: a schematic plan view of a friction ring according to the invention with and without internal toothing;

8a , b: is a schematic plan view and a sectional view through a first preferred Embodiment of a biasing spring according to the invention; and

9 : A schematic plan view of a second preferred embodiment of a biasing spring according to the invention.

In the following, the same or equal functioning components are denoted by the same reference numerals.

1 to 6 show a schematic partial view through a clutch disc 1 whose components are concentric to a rotation axis 2 are constructed.

A hub 4 with an internal toothing 6 is rotatably mounted on a gear shaft, not shown. On the outer circumference, the hub 4 a gearing 8th into which a hub disc 10 engages with game in the circumferential direction. At the hub disc 10 is a friction lining carrier plate 12 rotatably by means of fasteners 14 connected, the friction linings 16 wearing. On both sides of the hub disc 10 are cover sheets 18 . 20 arranged, rotatably with the hub 4 via a connecting element 22 are connected. For this purpose, the cover plates 18 . 20 Openings (not shown), in which the connecting element 22 intervenes.

In the in 1 illustrated embodiment is the connecting element 22 designed as a rivet, so that the connecting element 22 serves in the case shown here simultaneously as an axial attachment.

As 1 also shows is inside the cover sheets 18 . 20 a friction device 24 arranged in the illustrated case of a first friction ring 26 and a second friction ring 28 and a pretensioner 30 consists. Here are the second friction ring 28 and the pretensioner 30 axially on the other side of the hub disc 10 arranged as the first friction ring 26 ,

In the in 1 illustrated embodiment, the friction ring 26 secured against rotation with the cover plate 18 and the cover plate 20 and the hub 4 via the connection device 22 executed. For this purpose, the friction ring 26 just like the cover sheets 18 . 20 Openings in which the connecting element 22 can intervene. In addition, the friction ring 26 between the cover sheets 18 and the hub disc 10 clamped so that a defined friction point between the friction ring 26 and the hub disc 10 given is.

The on the other side of the hub disc 10 arranged friction ring 28 is in the in 1 illustrated embodiment loosely inserted and with the biasing device 30 towards the hub disc 10 biased. It is also the biasing device 30 conventionally loosely inserted. The pretensioner 30 can be designed in the form of a plate spring.

It is also conceivable that, instead of the loose insertion of the friction ring 28 and the pretensioner 30 , the pretensioner 30 and / or the friction ring 28 rotatably connected to each other and by means of noses, for example, in the cover plate 20 intervention. For this example, the biasing device 30 have on their side facing the cover plate and the hub disc facing side each having lugs on the one hand in the friction ring 28 and on the other hand in the cover plate 20 intervene and ensure an anti-rotation.

Instead of the rotation by means of the connecting element 22 can also friction ring 26 be equipped with a nose, in the cover plate 18 intervenes. Of course, the differently designed variant is possible in which the cover plates 18 . 20 each have the lugs on which the friction ring 26 or the biasing element 30 are mounted rotatably.

All lugs used preferably have a spring bias in the circumferential direction, whose spring force is less than the spring force of the biasing device 30 is selected so that the axial mobility is ensured despite rotation.

Preferably, the noses, as in the DE 10 2010 013 632 illustrated, be formed, which is hereby incorporated into the disclosure.

2 shows another preferred embodiment, in addition to a torsion damper 32 an idle damper 36 is provided. In addition, the hub 4 not formed as a one-piece hub, but consists of an inner hub 40 with an internal toothing 41 and an external toothing 42 and one the inner hub 40 enclosing one-piece outer hub 43 , which in turn has an internal toothing 44 and an external toothing 45 having. Here is the internal toothing 44 the outer hub 43 chosen so that they match the external teeth 42 the inner hub 40 Corresponds, so that the outer hub rotatably but with a predetermined rotational play with the inner hub 40 couples. For pre-damping of the backlash between inner hub 40 and outer hub 43 is still the predamper 36 intended. This is the pre-damper input 37 with the outer hub 43 connected and the pre-damper output 39 is with the inner hub 40 connected, so that the pre-damper acts as long as the backlash between inner hub 40 and outer hub 43 Not is applied. When the game is exhausted, the torque is directly from the outer hub 43 on the inner hub 40 transfer.

In such a design, it is useful in contrast to the design without pre-damper, the friction ring 26 inside to be provided with a toothing, which is identical to the internal toothing 44 the outer hub 43 is.

Even if in the embodiments illustrated below, a pre-damper unit 36 is not shown, it is obvious to a person skilled in the art and included in the scope of the description that such is present.

3 shows a further preferred embodiment, but in which the anti-rotation between the hub 4 , the cover sheets 18 . 20 and the friction ring 26 is not provided via a rivet, but only a pin as a connecting element 22 serves. For an axial limitation and attachment are in the in 3 illustrated embodiment retaining rings 50 . 52 provided axially outside the cover plates 18 . 20 are arranged and in the hub 4 intervention.

Like also in 3 can clearly be seen, the intermediate hub 10 consist of two sheets, one of which is the hub disc 10 and the other the pad carrier sheet 12 is. In this case, the lining carrier plate 12 over the entire radial length of the washer 10 be formed so that the friction ring 26 not in direct contact with the intermediate hub 10 but with the lining carrier plate 12 is.

Instead of just the friction ring 26 rotatably with the hub 4 it is also possible, as the embodiment of 4 shows the pretensioner 30 rotatably with the hub 4 train. For this purpose, advantageously, the biasing device 30 a mounting area 54 , a feather area 56 and a print area 58 exhibit. The attachment area 54 is pulled radially inward and provided with openings through which a connecting element 22 is feasible, so that a rotationally fixed connection between the biasing means 30 and the hub 4 arises. At the printing area 58 is the second friction ring 28 provided, which, for example, by material or positive fit against rotation and backlash with the biasing device 30 can be trained.

Instead of an additional second friction ring 28 can the pretensioner 30 also, as in 5 shown, directly on the hub disc 10 issue.

A schematic representation of a preferred embodiment of the biasing device 30 as in the embodiments of the 4 and 5 usable, is exemplary in the 8th and 9 shown.

Like the sectional view of the 8b can be seen, has the biasing device 30 the radially inner mounting area 54 , the pen area 56 and the print area 58 on, so that the entire bias direction shows in section an S-shape. How to continue the supervision of 8a it can be seen here is the attachment area 54 designed as a radially inner ring, the recordings 60 forms, through which the connecting element 22 is feasible. Radial outside shows the pretensioner 30 a pressure ring 58 by means of resiliently formed areas (tongues) 56 with the inside fixing ring 54 connected is.

Instead of two concentric rings, it is also possible, as 9 shows, also the attachment area 54 form over resilient tongues, so that the spring area 56 and the attachment area 54 is formed by means of the tongues. Radially inside the tongues are again the shots 60 for the connecting element 22 ,

Of course, the pressure range 58 be formed over ring segments or tongues, during the attachment area 54 is annular.

As another alternative, instead of the tongue-shaped spring areas 56 the entire pretensioner 30 be annular, having two axially offset from each other arranged areas, so that the biasing means 30 overall cup-shaped.

Is the pretensioner 30 , as in 4 shown, additionally with a friction ring 28 provided, the biasing device 30 made of a non-friction material, while only the friction ring 28 designed for friction. In general, the friction ring 28 and also the friction ring 26 made of plastic or an organic friction material.

In addition, it may be advantageous if the pretensioning device 30 only in the outer resilient area 58 is hardened, and the inner area 54 remains unhardened.

As 4 can also be seen, can between the first friction ring 26 and the hub disc 10 an additional friction element 62 be present, which may for example consist of organic friction material and either with the friction ring 26 directly or with the hub disc 10 can be firmly connected. Such a connection can be made for example by gluing or pressing.

Instead of the additional friction element 62 only in the area of the hub disc 10 It is also conceivable, as the embodiment in FIG 5 shows to perform the friction ring in total over its entire extent in several parts. In 5 is a two-part friction ring 26 represented by a rubbing part 62 and a spacer 64 consists. This can be the rubbing part 62 For example, made of hardened steel or a special organic friction material or have a special surface coating, so that the friction properties are improved. To the spacer 64 On the other hand, fewer requirements are made so that this part can be made of steel or even plastic.

6 shows a further preferred embodiment in which the friction ring 26 opposite Reibeinrichtungselemente, namely the second friction ring and the biasing means not rotatably with the hub, but rotatably with the hub disc 10 are formed. Although it is possible in this example, the friction ring and the biasing device 30 However, it is also possible to train as independent components 6 shows, the lining carrier plate 12 such form that there is a spring range 66 and a friction area 70 having, wherein the friction region 70 on the cover plate 18 rubs.

As above with respect to the pretensioner 30 described here, too, the area can be 70 be provided with an additional friction ring. This is preferably also again rotationally fixed, for example by gluing or other rotationally fixed connection with the lining carrier plate 12 connected. The non-rotatable connection between lining carrier plate 12 and washer 10 itself is in this case preferably radially outward on the intermediate disc 10 , for example by rivet 72 ,

Such a configuration has the great advantage that the number of components of the clutch disc are reduced, so that a faster and thus more cost-effective production is possible.

The 7a and 7b each show preferred embodiments of a friction ring, such as friction ring 26 , where the in 7a shown friction ring has an internal toothing, while in 7b shown friction ring has no internal teeth.

The in 7a The friction ring shown is preferably used in conjunction with an outer hub, wherein the internal toothing 74 the friction ring 26 preferably the internal toothing 44 the outer hub 43 (please refer 2 ) corresponds.

Like that 7a and 7b can be seen, the friction ring 26 openings 76 on, for receiving the connecting element 22 serve. Is the connecting element 20 a rivet, the openings can 76 greater than when the connecting element 22 a pin is because in the case of the rivet, the Verdrehmitnahme can also be done via a friction between the friction ring and hub or cover plate. Like that 7a and 7b can still be seen, the friction ring 26 at its radially outer edge recesses 78 on, which absorb the torsion springs of the torsion damper 32 serve.

If the Verdrehmitnahme, as described above, realized by friction, it may be appropriate that the surface of the friction ring 26 is relatively high in the radially inner region, while it may be formed lower in the radially outer region. Since there is hardly any relative movement in the radially inner region which could wear out the surface, the provision of the increased friction can take place, for example, by roughening. In the area where, however, a relative movement takes place, namely the radially outer area, it is also advantageous if this area is hardened. In this case, for example, a special hardening process, in particular case hardening can be used, with the targeted the rubbing surface or in the case of in 7a illustrated example of the friction ring 26 with internal toothing, specifically the tooth flanks can be hardened.

Is the friction ring 26 , as in 5 shown, from several sheets, it may also be appropriate that the sheet, which rests against the component and makes the relative movement relative to the friction ring, is made harder than the other sheets. However, the rubbing member may also be made of an organic friction material as described above.

Common to all embodiments described above is that at least one element of the friction device is rotatably connected directly to the hub or indirectly via the cover plate with the hub, so that the occurring due to relative movement wear is reduced. In all non-rotatable connections of the friction ring, however, care must be taken that an axial mobility of the friction ring is still given to compensate for the wear and to keep the friction element in contact with the corresponding friction surface.

LIST OF REFERENCE NUMBERS

1

clutch disc

2

axis of rotation

4

hub

6

internal gearing

8th

external teeth

10

hub disc

12

Backplate

14

rivet

16

friction linings

18, 20

cover plates

22

connecting element

24

friction device

26, 28

friction ring

30

biasing means

32

torsion spring

36

pre-damper

37

Vordämpfereingang

39

Vordämpferausgang

40

inner hub

41

Inner hub internal toothing

42

Inner hub outer toothing

43

outer hub

44

External hub internal toothing

45

Outer hub outer toothing

50, 52

circlip

54

Preload attachment area

56

Preloading spring area

58

Pretensioner pressure range

60

Pretensioner openings

62

Friction ring friction part

64

Friction ring spacer

66

Pad carrier sheet spring area

70

Lining carrier plate friction area

72

rivet

74

Friction ring internal toothing

76

Friction ring openings

78

Friction ring recess for torsion spring

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• DE 102010013632 [0019, 0058]

Claims (22)

Clutch disc ( 1 ), in particular for a friction clutch of a motor vehicle, with a torsional vibration damper consisting of - a hub disc ( 10 ), which on a transmission shaft associated hub ( 4 . 40 ) is arranged and with friction linings ( 16 ) is connected to the torque transmission, - on both sides of the hub disc ( 10 ) arranged cover plates ( 18 . 20 ), which are rotationally fixed to each other and spaced from each other, - Torsionsfedern ( 32 ), which in recesses between hub disc ( 10 ) and the cover plates ( 18 . 20 ), and - a friction device ( 24 ) between the hub disc ( 10 ) and at least one of the cover plates ( 18 . 20 ) is arranged, and the at least one friction ring ( 26 ; 28 ) and a biasing device ( 30 ) with which the friction ring ( 26 ; 28 ) is axially acted upon by pressure, has; characterized in that at least one element of the friction device ( 24 ) rotatably with the hub ( 4 . 43 ) connected is. Clutch disc ( 1 ) according to claim 1, wherein the hub associated with the transmission input shaft ( 4 ) an inner hub ( 40 ) with an internal toothing ( 41 ) and an outer toothing ( 42 ) and one the inner hub ( 40 ) enclosing one-piece outer hub ( 43 ), wherein the outer hub ( 43 ) one into the external toothing ( 42 ) of the inner hub ( 40 ) engaging internal toothing ( 44 ), which the outer hub ( 43 ) rotatably but with a predetermined rotational play with the inner hub ( 40 ) couples. Clutch disc ( 1 ) according to claim 2, wherein the one-piece outer hub ( 43 ) Is made by cold extrusion, forging, sintering or punching from a thick sheet. Clutch disc ( 1 ) according to any one of the preceding claims, wherein the cover sheets ( 18 . 20 ) with the hub ( 4 ), in particular the outer hub ( 43 ), rotationally fixed by means of a connecting element ( 22 ), preferably by means of a rivet, wherein the connecting element ( 22 ) is further adapted to the at least one element of the friction device ( 24 ) rotatably with the hub ( 4 . 43 ) connect to. Clutch disc ( 1 ) according to one of the preceding claims, wherein the connecting element ( 22 ) is a pin and still axially outside the cover plates ( 18 . 20 ) a circlip is provided for the axial securing of cover plates ( 18 . 20 ), Hub ( 4 . 43 ) and friction device ( 24 ). Clutch disc ( 1 ) according to one of the preceding claims, wherein the at least one element of the friction device ( 24 ) has an internal toothing. Clutch disc ( 1 ) according to claim 2 and 6, wherein the internal toothing of the at least one element of the friction device ( 24 ) substantially identical to the internal toothing ( 44 ) the outer hub ( 43 ). Clutch disc ( 1 ) according to one of the preceding claims, wherein the hub ( 4 . 43 ) rotatably with the cover plates ( 18 . 20 ) and at least one element of the friction device ( 24 ) rotatably with the cover plate ( 18 . 20 ) connected is. Clutch disc ( 1 ) according to claim 8, wherein the rotationally fixed connection between the at least one element of the friction device ( 24 ) and the cover plate ( 18 . 20 ) is realized by means of at least one nose, which in the adjacent cover plate ( 18 . 20 ) or in the at least one element of the friction device ( 24 ), wherein preferably the nose has a spring bias in the circumferential direction. Clutch disc ( 1 ) according to claim 9, wherein the provided by the spring bias clamping force of the lugs in the circumferential direction is smaller than the axial mobility of the lugs in the recesses, preferably wherein the spring bias of the lugs in the circumferential direction is smaller than the axial spring force of the biasing device ( 30 ). Clutch disc ( 1 ) according to one of the preceding claims, wherein the friction device ( 24 ) a first friction ring ( 26 ) and a second friction ring ( 28 ), wherein the friction rings ( 26 ; 28 ) on both sides of the hub disc ( 10 ) are arranged and wherein the biasing device ( 30 ) the second friction ring ( 28 ) and rotationally fixed with the hub ( 4 ), in particular the outer hub ( 43 ), connected is. Clutch disc ( 1 ) according to claim 10, wherein the rotationally fixed connection of the pretensioning device ( 30 ) with the hub via a non-rotatable connection of the biasing device ( 30 ) with the cover plate and / or the friction ring ( 26 ; 28 ) is realized by means of at least one nose, which in the cover plate and / or the friction ring ( 26 ; 28 ) intervenes. Clutch disc ( 1 ) according to any one of the preceding claims, wherein friction ring ( 26 ; 28 ) and pretensioning device ( 30 ) are formed as an integral component, wherein preferably the biasing device ( 30 ), in particular by pressing, gluing and / or spraying, applied friction material. Clutch disc ( 1 ) according to claim 4 and 11, wherein said biasing means ( 30 ) by means of the connecting element ( 22 ) rotatably connected to the hub, in particular the outer hub is connected. Clutch disc ( 1 ) according to one of the preceding claims, wherein at least one friction ring ( 26 ; 28 ) of the friction device ( 24 ) is made of several parts, wherein the multi-part friction ring ( 26 ; 28 ) preferably consists of a rubbing part, which consists in particular of hardened steel or an organic friction material or has a special surface coating, and a spacer, which consists in particular of steel or plastic. Clutch disc ( 1 ) according to one of the preceding claims, wherein the friction linings ( 16 ) of the clutch via a friction lining carrier plate ( 12 ) with the hub disc ( 10 ), wherein the friction lining carrier plate ( 12 ) as biasing means ( 30 ) for the friction device ( 24 ) is trained. Clutch disc ( 1 ) according to claim 16, wherein said biasing means ( 30 ) further rotatably with a second friction ring ( 28 ) connected is. Clutch disc ( 1 ) according to one of the preceding claims, wherein the clutch disc ( 1 ) furthermore a pre-damper device ( 36 ) having. Clutch disc ( 1 ) according to claim 2 and 18, wherein the pre-damper device ( 36 ) with one side ( 37 ) on the outer hub and with its other side ( 39 ) is arranged on the inner hub. Clutch disc ( 1 ) according to one of the preceding claims, wherein at least one friction ring ( 26 ; 28 ) of the friction device ( 24 ) has a different friction across its surface, in particular a radially inner region of the friction ring (FIG. 26 ; 28 ) has a higher friction than a radially outer region. Clutch disc ( 1 ) according to one of the preceding claims, wherein at least one friction ring ( 26 ; 28 ) of the friction device ( 24 ) is formed in several pieces. Clutch disc ( 1 ) according to one of the preceding claims, wherein the pretensioning device ( 30 ) of the friction device ( 24 ) a fastening area ( 54 ), a spring area ( 56 ) and a print area ( 58 ), wherein in particular the pressure range ( 58 ) and / or the attachment area ( 56 ) annular and / or the attachment area ( 56 ) and / or the spring area ( 54 ) is tongue-shaped.

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