WO2009071443A1

WO2009071443A1 - Clutch disk

Info

Publication number: WO2009071443A1
Application number: PCT/EP2008/065815
Authority: WO
Inventors: Gerald Buer; Harald Jeppe; Matthias Diemer; Anita Radic; Norbert Schmitt; Rainer Worttmann; Michael Peterseim; Winfried Bokisch
Original assignee: Zf Friedrichshafen Ag
Priority date: 2007-12-05
Filing date: 2008-11-19
Publication date: 2009-06-11
Also published as: DE102008043834A1

Abstract

A clutch disk (1) for a friction clutch, in particular for a motor vehicle friction clutch, for transmitting torque, having a hub (2) for setting on a shaft, in particular a transmission input shaft, at least two annularly arranged friction linings (4) formed from friction lining material (3), in each case with a friction surface (5), and a friction lining rear side (6) for torque transmission when the friction surfaces are impacted by a contact force via opposite friction surfaces of a friction clutch, at least one hub disk in the torque transmission path between the hub and the friction linings of a lining suspension (8), which is arranged between the friction linings and can be compressed elastically in an axial direction when the friction linings are impacted by a contact force via the opposite friction surfaces, wherein the friction linings (4) on the friction lining rear side in each case have at least one connecting element (11) embedded in the friction lining, said connecting element extending outside the friction surface of the friction lining for connecting to the lining suspension or the clutch disk with at least one connection section (10).

Description

Patent application

clutch disc

description

The invention relates to a clutch disc for a friction clutch, in particular for a motor vehicle friction clutch for transmitting torque with a hub for placement on a shaft, in particular transmission input shaft, at least two annularly arranged friction linings formed friction linings each having a friction surface and a Reibbelagückseite for torque transmission upon application of the Friction surfaces with a contact force on Gegenreibflächen a friction clutch, at least one hub disc in the torque transmission between the hub and the friction linings, arranged between the friction linings, which is elastically compressible upon application of the friction linings with a contact force on the counter friction surfaces in the axial direction.

Such a clutch disc is known from DE 195 49 388 C2. A disadvantage of this embodiment is that in such a clutch disc of the friction lining can only be worn down to a relatively large residual thickness of the friction lining. As friction lining wear progresses, the clutch disc shown there loses its rotational speed resistance and must be replaced prematurely. Furthermore, this prior art is characterized in that in the axial direction, the friction lining unit has a large footprint.

Furthermore, from EP 1 712 808 A2 a clutch disc is known in which the friction lining has a carrier element which is at least partially surrounded by friction material, wherein the carrier element is connected to the lining carrier. In this embodiment, disadvantageously results in a rigid axial design of the friction linings of the friction clutch and the need for friction lining material in this clutch disc is unfavorably high.

It is therefore an object of this invention to provide a clutch disc, which has a high reliability at low cost construction and allows the longest possible life, even under high temperature load on the friction linings. It is another object of the invention to provide a well-modulated clutch disc, which has a high bursting speed, thus allowing operation in high-revving gasoline engines.

The solution to this problem is inventively achieved in that the friction linings on the Reibbelagrückseite each have at least one embedded in the friction lining connecting element, which is suitable for connection to the Pad suspension or the clutch disc extends with at least one connection portion outside the friction surface of the friction lining.

By embedding a connection element of the Reibbelagrückseite from in the friction lining material results in a very durable connection of the connection element in the friction lining itself, wherein the connection element extends with a connection portion of the friction surface of the friction lining itself, wherein the connection portion itself to the lining suspension or on the clutch disc is connected. In this case, it is preferably carried out that the connection element is introduced from the Reibbelagrückseite in the friction lining. The connection element is therefore inserted flush in the Reibbelagrückseite. This can be created particularly advantageously already during the production process of the friction lining. By arranging a connection portion outside the friction surface of the friction lining, it is possible to keep the friction surface itself free of interruptions for the connection of the friction lining to the pad spring or clutch disc. The connection section advantageously extends radially outside the friction surface, in particular radially inward. In an alternative, equivalent embodiment to claim 1, a further solution of the problem is characterized in that the friction linings on the Reibbelagrückseite each have at least one embedded in the friction lining, provided with at least one connection to the lining suspension or the clutch disc attachment portion provided connection element, wherein the connection portion pointing both in the direction of the friction surface as well - A -

in the direction of the Reibbelagrückseite facing surface is made substantially free of friction lining material for connection to the lining suspension or the clutch disc. By the connection portion of the connection element is not at least partially covered by friction lining material, it is ensured that the connection of the connection portion to the lining suspension or the clutch disc can be made very strong and thus claiming little axial space. In this case, it is particularly advantageously provided that the connection section is located radially outside the friction surface and is also fastened radially outside the friction surface to the lining suspension or to the clutch disk, in particular hub disk. Also in this embodiment, the embedding of a connection element from the Reibbelagrückseite in the friction lining results in a heavy-duty and secure connection of the friction lining with the clutch disc or the lining suspension. The connection element according to the invention in the two aforementioned claims substantially only up to the level of Reibeblagrückseite embedded in the friction lining material.

By the connecting element is introduced, starting from the Reibbelagrückseite in the friction lining, results in an axially very little space consuming friction lining, which nevertheless has a standard wear thickness and a particularly advantageous residual volume in the axial direction upon reaching the maximum wear limit. The connection element ensures that the friction lining remains firmly connected to the clutch disc or the lining suspension during the entire service life of the friction clutch and at the same time has a very high bursting speed resistance. By the introduction of the connection element in the Reibbelagrückseite is sufficiently and very well reinforced by the connection element of the friction lining, wherein the friction lining material itself must be filled with a small proportion of fibers or reinforcing fibers, since the intrinsic stability of the friction lining and the Berstdrehzahlfestigkeit is increased in particular by the connection element accordingly. The formation of at least one connecting portion on the connecting element allows the attachment radially outside the friction surface and thus produce very thin friction linings, which have a higher proportion of substances due to the lower proportion of fibers or reinforcing fibers, which favorably influence the friction. As a result, the axial thickness of the friction linings can be further reduced for the same service life.

According to the claimed invention, according to the invention, the friction lining on the friction lining rear side bears against the lining suspension both with the friction lining material and with the attachment element, advantageously resulting in a low load on the connection between the friction lining material and the attachment element. In this case, it is also particularly advantageously provided that the attachment element is made elastic in the direction of the contact pressure on the friction linings. Advantageously, the connection element made of elastic material such as sheet metal or spring steel sheet is made. Furthermore, the invention provides that the friction lining is designed as a so-called organic friction lining. The friction lining material according to the invention contains resins. These can make the friction lining particularly elastic. In return, a friction lining made of sintered material, as a closed, one-piece ring shape would be stiff and brittle. In a further advantageous embodiment, it is provided that the connection of the connecting portion to the lining suspension or to the clutch disc takes place radially within the friction surface of the friction lining or radially within the friction surface of the friction linings. By the connection is designed outside of the wear-prone area of the friction surface, the connection portion can be done with fastening means, such as rivets or screws, or other axially-mounted mounting options on the pad spring or on the clutch disc, without the achieved by the claims 1 and 2 advantageous particularly thin design of the friction linings must be omitted. In particular, the embodiment of the padding suspension according to the invention is designed to the effect that from the pad spring to the inside a tab-like extension, so a connecting portion extends, which comes in conjunction with the connection portion of the connection element in the region of the connection of the same in axial coverage for connection of the connection area the connection office.

A further embodiment of the invention provides that the lining suspension has peaks that are elastically compressible in the axial direction upon application of the friction linings with a contact force. A wave crest of a pad suspension is defined for example in such a way that it represents a part of the pad spring protruding in the axial direction toward the friction pad rear side, which has a contact surface for abutment and support of the friction pad rear side of the friction pad, and if the contact surface, ie the wave crest, is elastically deformed in the axial direction by the applied over the friction lining contact force. The friction lining is supported by the wave crest in the axial direction. According to the invention, the wave crest or the wave crests of the lining suspension each form a flat plateau formed on the wave crest to bear against the friction lining rear side. Here then according to the invention, the Reibeblagrückseite both with the friction lining itself and with the located in this overlap region of the connection section. In particular, in the engaged state of the friction clutch, so at full contact pressure, it can be provided that the Reibeblagrückseite also comes into the troughs or the wave trough following a wave trough to the plant. In this case, the lining suspension in the axial direction is then substantially completely compressed.

In an inventive development is provided here that the wave crests are formed in the direction of Reibeblagrückseite. In this case, it has turned out to be particularly advantageous if the wave crests extend over the friction surface in the radial direction. This means that wave peaks and wave troughs alternately alternate on the padding suspension in the circumferential direction.

In a further inventive embodiment, it is provided that the wave crests of the lining suspension are supported on the anchoring element embedded on the friction lining rear side. Since the connection element is designed such that it does not extend over the entire surface formed by the Reibbelagückseite, then supported at least in the engaged state of the Friction clutch both the connection element and the friction lining material itself at one or the plateau of the lining suspension formed by a wave crest.

In a further embodiment of the invention, it is provided that the connection element is embedded in the Reibbelagrückseite such that this forms a substantially flat surface with the friction lining material on the Reibbelagückseite. In this case, it can be provided in an inventive manner that the attachment element protrudes slightly in relation to the friction lining material on the lining rear side. This especially if in the production of the friction lining, the connection element has not been uniformly introduced in the entire overlap area with the friction lining. However, this essentially corresponds to a usual manufacturing inaccuracy, which has no significant influence on the function of the invention. If desired, the connection element, in particular in the new condition of the friction lining, is introduced onto the friction lining back in such a way that it protrudes slightly against the friction lining material on the friction lining back side. As a rule, such manufacturing inaccuracy or manufacturing tolerance is less than one tenth of a millimeter. However, it can also be provided that the friction lining material itself protrudes slightly in the axial direction with respect to the surface of the attachment element formed on the friction lining back. This, for example, in a highly heated friction lining, such as is present after a race start, or directly after the production of the friction lining, if not all solvents have evaporated. In a further embodiment of the invention it is provided that the connection element is embedded only in accordance with the material thickness of the connecting element of the Reibbelagrückseite starting in the friction lining material. In particular, in conjunction with claim 7, this results in a particularly advantageous embodiment of the invention, since this results in a particularly thin residual thickness of the friction lining when it is worn. In this embodiment, the connection element on the Reibbelagückseite is not substantially enclosed by the friction lining material.

According to the invention, it is further provided that the friction linings are connected to the clutch disc via the connecting sections in such a way that the friction lining rear sides abut against the brake pad suspension essentially without biasing. Here are the friction linings without forming a gap between the Reibbelagrückseite and a wave crest or the wave crests of the lining suspension together. In this case, it must be interpreted as stress-free that a slight preload can be ignored in the context of production inaccuracy. The friction linings are therefore connected only via their connection sections with the clutch disc or the lining suspension and in the region of the friction surface of the friction lining these lie substantially without the formation of a gap to the respectively associated wave crests of the lining suspension.

According to the invention it is further provided that the connection portion is designed to be axially elastic. In this case, the elasticity is particularly advantageous executed in the connection portion that this is less than the spring stiffness of the friction lining itself. In an advantageous embodiment it is therefore provided that the axial spring stiffness of the connection portion is less than the axial spring stiffness of the friction lining. This ensures that the connection of the friction lining on the coupling portion of the clutch disc and the lining suspension this axially deformed, in particular very thin running friction lining. The friction lining is thus firmly connected to the clutch disc or the lining suspension for torque transmission, wherein the inherent rigidity of the friction lining ensures the flat position of the friction lining surface in the disengaged state of the friction clutch. The friction lining or the friction lining rings form no "wave-shaped" faults or other deformations due to the attachment of the connection section to the clutch disc or the lining suspension in the contact pressure-free state of the clutch disc.

The connection section is placed in the circumferential direction in the region of a wave crest of the lining suspension. In particular, the connection section merges into the friction lining in the region of a wave crest. According to the invention, therefore, the connection section extends in the circumferential direction in the region of a wave crest of the lining suspension radially inward from the friction lining, ie out of the friction lining material.

A further embodiment according to the invention provides that the lining suspension has at least one connection region for connecting the at least one connection section of a connection element. By providing a connection region which extends directly from the lining suspension to the connecting portion of the connecting element, results in an axially exact positioning of the friction lining against the lining suspension. This allows a particularly space-saving construction of the clutch disc in the axial direction. Alternatively, it can also be provided that a connection region extends from the clutch disk, in particular the hub disk, for connecting a connection element. In this case, it will be necessary for the axial position of the connection region to the attachment section and to the lining suspension to be correspondingly precisely designed.

In a further embodiment, the invention provides that the connecting region is formed in the circumferential direction in the region of a friction lining associated wave crest of the lining suspension. According to the invention, the connecting region extends radially inwardly from the friction surface region from a wave peak of the lining suspension formed in overlap with the friction lining back side. The coupling of the friction lining is therefore outside the friction surface. The connecting portion is connected to the connecting portion radially inside the friction surface. In particular, over the axial surface, which form the distributed over the circumference connecting portions, the exact position of the friction lining against the pad spring can be achieved. By the connecting region is formed in the region of a wave crest of the lining suspension associated with the respective friction lining, it is advantageous if the friction lining is exposed to a contact pressure force without special load the connection between the attachment element and the friction lining material can follow the axial compression of the lining suspension.

According to the invention, it is therefore provided that the connection region is formed on the lining suspension in such a way that it essentially has an axial position corresponding to a wave crest. This particular in the Anpresskraftfreien state of the friction clutch, so when it is disengaged. It does not form

Axial distance of the connecting portion to the connection portion, which would lead to a plate spring-like deformation of the friction lining, in particular a friction lining in embodiment as a closed ring Unvorteilhafterweise.

In a further embodiment of the invention, it is therefore provided that the connection region extends out of a wave crest of the lining suspension. The connection region can be molded integrally with the manufacture of the lining suspension, in the region of an associated wave crest. In a coupling operation, this results in a lesser relative movement or a lesser sliding in the circumferential direction between the Reibeblagrückseite and the lining suspension.

In an inventive manner, therefore, it is further provided that the connection of the at least one connection section takes place at the connection region or on the clutch disc radially inside the friction lining.

By the connecting portion or the connecting portion are connected radially within the friction lining to each other, there is a small Mass moment of inertia of the clutch disc and the friction lining diameter can be extended to the maximum size.

Alternatively, it is provided that the connection of the at least one connection section takes place at the connection region or at the clutch disc radially inside the friction surface. Especially in cases where the

Clutch disc is designed with a relatively small torsional vibration damper, it can be provided that the inner diameter of the friction lining is smaller than the inner diameter of the associated counter friction surfaces, such. the pressure plate or the washer in a multi-plate clutch or the

Friction surface on a flywheel.

In a further embodiment according to the invention it is provided that the connection of the connection element takes place at the connection area or at the clutch disc by means of rivets. Alternatively it can be provided that the connection of the connection element takes place at the connection area on the clutch disc or on the pad suspension by welding, in particular spot welding or resistance welding.

In a further embodiment of the invention, it is provided that the connection section extends just from the connection element. According to the invention, the connection section is designed such that it extends substantially within the circular area enclosed by the friction lining rear side. This allows the lining suspension to relax axially can act without negatively on the friction lining, if no contact force is exerted on the friction linings.

In a further embodiment according to the invention, it is therefore provided that the connection section is connected to the connection region or the clutch disc in such a way that the friction lining rear side bears against the wave crests of the lining suspension substantially without bias in the contact pressure-free state of the friction linings.

According to the invention it is further provided that the lining suspension is formed by individual, in the circumferential direction successively arranged pad springs.

According to the invention, it is further provided that the friction linings are connected directly or indirectly to the lining suspension by in the circumferential direction substantially in the region of a respective wave crest of the lining suspension on the friction linings formed connecting portions of the connection elements. By the connecting portions are connected directly or indirectly in the region of the respectively associated wave peaks of the lining suspension, results in the coupling and disengaging of the friction linings a particularly advantageous behavior. In particular, this ensures that the lining suspension can be compressed and relieved substantially without interference and uninfluenced between the friction linings. It has been shown, in particular in tests, that the effect of the lining suspension is particularly advantageous due to these features. It is provided in a further embodiment of the invention that the friction linings are connected directly or indirectly to the clutch disc by in the circumferential direction substantially in the region of a respective wave crest of the lining suspension formed on the friction linings connecting portions of the connecting element. Even if the friction linings are connected via the connection elements not directly to the lining suspension but over the clutch disc extending connecting areas, the advantage of claim 22 results in particularly effective and lossless function of the pad suspension during a coupling or disengaging.

In a further embodiment according to the invention, it is provided that the friction linings are fastened exclusively to the pad suspension or the clutch disc via the connecting sections. This ensures that the maximum friction lining volume in the friction surface area of the friction linings can be used.

In a further embodiment according to the invention it is provided that the torque to be transmitted is introduced from the friction linings on the lining suspension in the clutch disc. In this case, it is assumed that the friction linings are connected directly or indirectly to the lining suspension via the connecting sections.

In a further embodiment according to the invention, it is provided that the connection element is formed by a thin, essentially flat sheet metal part. In a further embodiment, it is provided that the connecting element extends a closed ring shape substantially in overlapping of the friction surface of the friction lining. In this case, according to the invention, the attachment element does not have the surface formed by the friction lining on the Reibbelagückseite, but extends only over a portion of the surface formed by the Reibbelagrückseite from which the attachment portions extend radially inward. In particular, embedded in the Reibbelagrückseite state of the connecting element of this forms a closed ring shape or a nearly closed ring shape to absorb the centrifugal forces acting on the friction lining material during operation of the friction clutch optimally and without elastic deformation of the friction lining. In a further embodiment according to the invention, it is therefore provided that the connection element covers less than 40% of the surface of the friction lining rear side. In this case, a sufficient connection between the connection element and the friction lining material can be achieved.

In a further embodiment according to the invention it is provided that the connection element covers less than 25% of the surface of the friction lining back. In a further embodiment according to the invention it is provided that the plate thickness of the connecting element is less than the plate thickness of the lining suspension. In particular, if it is advantageously provided that the connection element is formed by a spring steel sheet, the sheet thickness and thus the weight of the connection element or its size can be greatly reduced. According to the invention, the connection element is provided with an adhesion-promoting layer at least on the surface in contact with the friction lining material. This can be done, for example, by phosphating or by applying a primer.

In a further embodiment according to the invention, it is also provided that the sheet thickness of the connecting element in the region of the embedding in the friction lining rear side is less than the plate thickness of the lining suspension. In particular, if the connection sections are to have sufficient rigidity, it may be provided that the connection sections have a greater axial thickness in the region outside the friction surface, that is, have greater plate thickness than the remaining region of the connection element. For applications in which an axially greater stiffness or stiffness of the friction lining element is desired as described e.g. In the case of pad springs with a large pad spring travel, it can be provided according to the invention that the plate thickness of the connection element in the region of the embedding in the friction lining back is greater than the plate thickness in the region of the connection sections.

Alternatively, it can also be provided that the sheet thickness of the connection element is made thicker in the region of the connection section than in the remaining area of the connection element. This is especially true when particularly large torques are transmitted via the friction linings. In a further embodiment of the invention, it is provided that in the axial direction of the coupling disc, the rigidity of the connecting element in the region of the connecting portion or the connecting portions is greater than in the remaining region of the connecting element. This allows a secure positioning of the friction lining and a particularly flat surface of the friction lining on the friction surface. The friction lining can be positioned exactly opposite the pad spring in the axial direction.

In a further embodiment according to the invention, it is provided that the connecting section is connected to the connecting section in such a way that the friction lining rear side essentially remains in direct abutment with the lining suspension in the state without contact pressure. Here, the friction lining back remains in

Essentially in the area of the associated peaks of the pad suspension in direct contact. To realize the smallest possible axial space of the clutch disc.

A further embodiment of the invention provides that the connection portion is connected to the clutch disc such that the Reibbelagückseite remains in direct contact with the lining suspension in the contact force-free state. This also results in a particularly space-optimized design in the axial direction.

In order to achieve a particularly good plant of Reibeblagrückseite on the lining suspension in the contact pressure-free state of the clutch disc and to eventual Production inaccuracies, in particular to compensate for plan errors of the clutch disc, the invention provides that the connection portion or the connection portions with respect to the plane of Reibbelagrückseite is tilted obliquely in pad spring direction or are. In this case, it may in particular be provided according to the invention that the connection section is angled by about 3 ° to 30 °.

In a particularly advantageous embodiment, it is provided that the connection portion is angled obliquely by about 3 ° to 1 5 °. Here, the angle indication corresponds to the angle between the plane defined by the Reibbelagrückseite surface and the angled leg of the connection section. In particular, when the connection portion is formed from a spring steel sheet or an elastic sheet, can be achieved by the low spring action of the connection sections a safe, only a small biasing force of the friction linings on the lining suspension performing connection of the friction linings. In order to achieve the selbigen advantages according to claims 35 to 37, may be provided alternatively or in combination thereto, that the connection area is inclined relative to the plane of Reibbelagückseite. In this case, it can be provided in a further embodiment according to the invention, that the connection region has a slope of about 3 ° to 30 °, and in further inventive development of the connection region has a slope of about 3 ° to 15 °. In order to achieve a particularly flat, currently running clutch disc, in particular in the region of the friction linings, it is proposed that the friction linings have an annular, substantially disc-shaped form. Here, the friction lining is particularly advantageously designed as a closed ring shape.

Show it:

Fig. 1: a clutch disc according to the invention as an exploded view

Fig. 2: a lining suspension according to the invention in plan view

3 shows a lining suspension according to the invention in the course of the cutting according to FIG. 2

Fig. 4: a section of the friction lining with the lining suspension in the inventive design prior to assembly

5 shows a section of the friction lining with the lining suspension in the embodiment according to the invention according to FIG. 4 after assembly

6 shows a detail of the friction lining with the lining suspension in a further alternative embodiment according to the invention prior to assembly Fig. 7: a section of the friction lining with the lining suspension in a further, alternative embodiment of the invention according to FIG. 6 prior to assembly

8a: sectional drawing of a friction lining according to the invention

8b: sectional drawing of a further friction lining according to the invention

Fig. 9: half section of a friction clutch with a friction lining according to the invention

In the exploded view of a clutch disc according to the invention shown in FIG. 1, the hub 2 is connected to the hub disc 7 via a torsional vibration damper equipped with three coil springs 20 and designed as an idling damper 14. Here, the idle damper 14 is arranged by both sides of the hub disc 7 arranged cover plates 15 and corresponding, forming a friction friction rings 16 between the hub 2 and the hub disc 7. The idle damper 14 essentially operates only when the engine is idling. On the hub disc 7, the pad spring 8 is mounted in the radially outer region via fasteners 17 formed as rivets. Here, the covering spring 8 formed by individual circumferentially successively arranged covering spring plates 13 and the hub disc 7 have corresponding bores 17a and 17b for receiving the rivets 17. The bores 17a are preferably formed on the respective pad spring plate 13 in the radially inner foot region of the pad spring plates 13. additionally To these bores 17a and 17b for the rivets 17, in this exemplary embodiment, further connecting bores 18 are formed on the lining suspension 8 in the region of the connecting regions 12, 12a and 12b of the pad spring plate 13 or the pad spring 8 (FIGS. 2 and 3). On both sides of the lining suspension 8 are further at least one friction lining 4, comprising a friction surface 5 and a Reibbelagrückseite 6, made of a corresponding friction lining material 3, respectively. The friction lining material 3 is advantageously made of an organic friction lining material 3 or contains organic friction lining material 3, such as resins or rubber. Furthermore, the friction lining material 3 can be offset with fibers to increase the speed resistance. The friction linings 4 have on their Reibbelagrückseite 6 embedded in the friction lining material 3 connecting elements 1 1, which are already introduced from the Reibbelagrückseite 6 in the friction lining 3 during the manufacturing process. The connecting element 1 1 and the friction lining material 3 overlap axially within the friction surface of the clutch disc 1. The surface area of the attachment element 1 1 projected onto the friction surface plane is approximately 10% of the total friction surface of a friction lining 4. The remaining friction surface of the friction lining 4 accounts for approximately 90% of the projected area in relation to the surface of the attachment element 1 1 projected onto the friction surface plane. In this case, a sufficient connection between the connecting element 1 1 and the friction lining material 3 is achieved. It is therefore advantageously provided in the embodiment of the friction lining 4, that the plate thickness of the connecting element 1 1 is tuned such that the wearable volume of the friction lining 4 at least 70%, 80% of the total contained in the friction lining 4 friction lining material 3 corresponds particularly advantageous.

The connection elements 1 1 are thus introduced during the manufacturing process in the non-aging friction lining material 3 on the Reibbelagrückseite 6, advantageously inserted. Here, it is desirable that the connecting element 1 1 and the Reibbelagrückseite 6 of the friction lining 4 form a common plane for engagement with the wave crests 9 of the pad springs 8. Particularly advantageous is the production of the friction lining 4, when the connecting element 1 1, which advantageously a closed circular ring shape with at least partially meandering contour in the circumferential direction and radially inwardly beyond the friction surface or the projection surface of the friction lining 3 extending connecting portions 10 to Connection of the friction lining to the clutch disc 1, is first inserted into a form corresponding to the friction lining 4 and on the friction lining material 3 is applied. Here, the advantageously designed as a flat support plate connecting elements 1 1 are introduced substantially only according to their material thickness in the friction lining material 3. The connecting elements 1 1 thus form a unit connected to the friction linings 4 when the friction lining is produced. In each of the friction linings 4, at least one connecting element 11 is placed on the friction lining back 6. Advantageously, the facing in the direction of the pad spring 8 surfaces of the connecting element 1 1 and the Reibbelagückseite 6 form a flat surface. The connection element 1 1 according to the invention is embedded only in the friction lining material 3 up to the level of Reibbelagrückseite 6. The connecting element 1 1 is special Advantageously provided with a coating on the friction lining material 3 improving coating, such as a paint surface or a phosphating to affect the adhesive connection between the connecting element 1 1 and the friction lining material 3 low. Furthermore, each connection element 1 1 has at least one connection section 10, which is provided for connection to the lining suspension 8 or a pad spring plate 13. As shown by way of example in the inventive embodiment according to FIG. 1, the connecting element 11 is designed as a closed ring with connection sections 10 formed on it distributed over the circumference. According to the invention the connecting element is designed as a substantially flat sheet metal part. The sheet thickness is advantageously less than 1, 1 mm, particularly advantageous for applications in the car range below 0.75 mm. The friction lining 4 containing the connection element 1 1 is advantageously designed, for example, for passenger vehicle applications with an axial thickness of up to 3.5 mm, for example for applications in the heavy load range with an axial thickness of up to 5.5 mm in the new condition of the clutch disk 1. Particularly advantageous, the invention, if the friction lining 4 in the friction region has an axial thickness between 1, 5 to 2.5 mm. As a particularly efficient friction linings 4 have been found when the axial thickness, ie the plate thickness of the connecting element 1 1 in the range of 15 to 35% of the axial thickness of the connecting element 1 1 having friction lining 4 is performed. In a further embodiment of the invention, it is therefore provided that the mass moment of inertia of a friction lining 4 according to the invention is less than 0.001 kilogram times square meter. The connection section 10 is placed in the circumferential direction in the region of a wave crest 9 of the lining suspension 8. In particular, the connection section 10 merges into the friction lining 4 in the region of a wave crest 9. According to the invention, therefore, the connecting section 10 extends in the circumferential direction in the region of a wave crest 9 of the lining suspension 8 radially inward out of the friction lining 4, ie out of the friction lining material 3.

According to the invention, the friction lining 4 is in this case designed as a closed ring shape having a friction surface 5 and a friction lining rear side 6. About the connection portions 10 of the friction lining 4 is connected to the clutch disc. In an alternative embodiment can also be provided that the connection portion 10 is not connected as shown in Fig. 1 directly to the lining suspension 8, but is indirectly connected to the lining suspension 8. In this case, it can also be alternatively provided that the connecting sections 10 are connected directly to the hub disk 7 or via connecting areas 12, 12a and 12b formed correspondingly on the hub disk 7.

In the example shown in FIG. 1, each connecting section 10 of the connecting element 1 1 of a respective friction lining 4 is connected to the lining suspension 8 in such a way that the one connecting section 10 at a connecting region 12, formed on a lining spring plate 13, transmits the torque from the friction linings 4 comes over the connecting elements 1 1 to the plant. For this purpose, the connection sections 10 and the connection regions 12, 12a and 12b each pass through connection rivets 21. For this purpose, the connection rivets 21 penetrate in the respectively associated connection region 12, 12a and 12b connecting bores 18 formed on the lining suspension 8 and corresponding bores 27 formed on the respective connection sections 10 of the connection element 11 and thus ensure a secure abutment of the connection sections 10 at their respective associated connection regions 12 , 12a and 12b. In this case, it can be advantageously provided that the connection regions 12a on the pressure plate side wave crests 9a and the connection regions 12b on the flywheel side connection regions 12b are assigned. This is particularly in the formation of the axial plane in which the respective connection regions 12a or 12b are arranged. Accordingly, it is also alternatively provided that pressure-plate-side connecting regions 12a are assigned to pressure plate-side wave crests 9a and flywheel-side connecting regions 12b are each assigned to flywheel-side wave crests 9b, in which case the respective connection regions 12a and 12b each form separate axial planes in which the riveting or connection with the respectively associated one Anpressplattenseitig or flywheel side arranged friction lining 4 and thus the respective connection portions 10 is executed.

The inventive design of a pad spring plate 13 of the pad spring 8 is further shown in FIGS. 2 and 3, wherein the invention provides that the connecting portions 12, with their connection holes 18, are formed on a respective pad spring plate 13 that the Connection region 12 is located in the circumferential direction in the region of an associated Wellenberg of the lining suspension. Here, in the illustrated embodiment, the invention provides that a pad spring plate 13 each having a first crest 9a, which is associated with a first friction lining 4, and formed with a second crest 9b, which is associated with a second friction lining 4. According to the invention, these two aforementioned friction linings 4 in this case with their respective Reibbelagückseiten 6 to each other. The one pad spring plate 13 is therefore advantageously provided with a wave crest or several crests 9, that is, at least one crest 9a and one crest 9b, which point in the direction of a friction lining 4 and provided with at least one or more further crests 9, which in the opposite direction in the direction of another friction lining 4 assign. In the section corresponding to FIG. 3 of the application, the corresponding embodiment of the two, respectively oppositely directed wave crests 9 is shown. Accordingly, a pad spring plate 13 advantageously has wave crests 9 facing the respective friction lining rear sides 6, wherein the pressure plate side wave crest 9a forms a corresponding wave valley on the side facing the flywheel 26 and the flywheel side wave crest 9b on the side of the lining suspension 8 facing the pressure plate 25 ., the pad spring plate 13 forms a corresponding wave trough. So here is advantageously provided that a pressure plate-side wave crest 9a also formed in the corresponding axial plane connecting portion 12a and a flywheel side wave crest 9b also in the corresponding axial plane trained connection area 12a is advantageously assigned. As explained later for the embodiment of FIG. 8b, according to the invention such an embodiment can also be bypassed by a corresponding embodiment, in particular connecting sections 10 of at least one friction lining 4. If at least the connecting portions 10 of a friction lining 4 are axially offset axially with respect to the plane of Reibbelagrückseite 6, it is alternatively feasible that the connecting portions 12, so both connecting portions 12a and 12b are formed in a common plane and an axial offset against at least one level of the wave crests 9a or 9b is compensated by an embodiment according to FIG. 8b. Alternatively, it is also possible that pad springs 13 are provided, which have a multi-layer structure and thus independently of each other the respective facing side of the friction lining each have wave peaks for conditioning the Reibeblagrückseite 6 of the friction linings 4. Advantageously, it is provided in the embodiment shown according to FIGS. 1 and 2, that the corresponding peaks 9 are formed as flat plateaus to provide the respective associated friction linings 4 as large a contact surface. Furthermore, it is advantageously provided in accordance with the embodiments shown that the respective connection region 12 extends out of an associated wave crest 9. It is thereby achieved that the corresponding height or corresponding axial positioning for surface contact of the Reibbelagrückseite 6 and the friction lining 4 on the pad spring 8 is easy to achieve by the connection of the friction lining on the connection portion 10 at the connection portion 12. Furthermore, in the compression of the pad spring 8 by the contact force of the friction clutch an undesirable relative movement between Friction lining 4 and pad suspension 8 avoided. The Einkuppelverhalten is better because no hysteresis is generated in the clutch disc on the pad spring 8. The wave peaks 9 formed on the lining suspension 8 are elastically compressed in the axial direction when the friction linings 54 are acted upon by a contact force. Due to the advantageous connection of the friction linings 4 via the connecting elements 1 1 by means of the connecting portions 10 at the connecting portion 12 it is ensured that the lining suspension 8 works trouble-free and low-friction during a disengaging and coupling operation. In particular, by the connecting portions 12 are formed in the circumferential direction in the respective associated peaks of the pad spring 8, resulting in the disengaged state of the clutch disc 1 is a tight, space-saving concerns of the friction linings 4 on the pad spring 8 and undisturbed work the pad suspension during a Einkuppelvorganges , It has proved to be particularly advantageous here that the connecting region 12 extends directly from a wave crest 9.

The connection element 1 1 is particularly advantageous for applications in the passenger car area of a spring steel sheet, in particular a spring steel sheet with a thickness of 0.3 to 0.6 mm, particularly advantageously formed with a thickness of 0.4 to 0.5 mm. By the connection element 1 1 is made of a substantially flat spring steel sheet, in particular, the connection portions 10 have a high elastic deformability. Alternatively, it is provided in a further embodiment of the invention that the connection element 1 1 is made of sheet iron or other metal with high strength such as aluminum by means of a punching operation. Advantageously, this with a later Hardening process or a carburizing or nitriding process in the strength and in terms of elastic deformability can be improved. According to the invention, it is provided in FIG. 1 that the connecting elements 1 1 are in each case designed as an annular closed contour with connection sections 10 extending radially inward therefrom.

In a further embodiment of the invention, it is provided that the connection portions 10 with respect to the plane of Reibbelagrückseite 6, ie with respect to the region of the connecting element 1 1, which is baked with the friction lining material 3, having an axial offset. This allows in particular in embodiments with pad springs 8 with a particularly large travel the plane of connection of the connecting portions 10 to the clutch disc respectively the connecting portions 12 axially offset from the Reibbelagrückseite 6.

4 and 5 show a section through a friction lining 4 according to the invention for connection to a lining suspension 8. In FIG. 4, the friction lining 4 provided with the connection element 1 1 is shown via the connecting region 12 prior to connection to the lining suspension 8. It can be seen that the connection portion 10 is angled relative to the plane of Reibbelagrückseite 6 in the direction of the pad spring 8. In an advantageous embodiment, in this case the connection portion 10 or the connection portions 10 are angled by about 3 ° to 30 °. After the connection of the friction lining 4 with the pad spring 8 via the connecting portions 10 at the connecting portions 12, the results in Fig. 5 system shown the two components together. Due to the angling of the connecting sections 10 in the direction of the connecting regions 12, an advantageous planar contact of the friction lining back 6 of the friction lining 4 on the lining suspension 8 or the lining plates 13 in the contact pressure-free state of the coupling disk results after the connection. Here, the friction lining 4 with a small, generated by the bending or pre-bending of the connection portions 10 spring force or slight biasing force with the Reibbelagrückseite 6 on the pad springs 13 and the wave crests 9. The bending or pre-bending of the connecting sections 10 results in a clean and flat contact of the friction linings 4 on the pad spring 8, wherein the biasing force generated thereby is not so high to overcome the inherent rigidity of the friction linings 4 so as to elastic deformation and thus to trigger a non-planar system of friction linings 4 on the pad springs 8.

FIGS. 6 and 7 show an alternative embodiment according to FIGS. 4 and 5. In this advantageous variant of the connection portion 10 extends straight out of the plane of the connection element 1 1 and thus the plane of Reibbelagrückseite 6 out. Alternatively, it is provided that the connecting region 12 is angled relative to the plane formed by the pad spring 8, in particular the plane formed by a wave crest 9 in the direction of the respectively associated friction lining 4. Since the embodiment of the lining suspension 8 is generally formed from a relative to the connecting element 1 1 and the connection portion 10 significantly stiffer sheet, the required bend in Fig. 6 and 7 must be smaller than in Figs. 4 and 5 to achieve a correspondingly similar effect, namely the direct contact of Reibbelagrückseite 6 on the pad spring 8 after connection of the connection portion 10 at the connection portion 12. It has been shown that in this case a slope of 2 ° to 15 ° proves to be sufficient. In the embodiment according to FIGS. 6 and 7, it is particularly advantageous if the connection, in particular via connecting rivets 21, takes place in such a way that they are placed as close as possible in the direction of the extent of the friction linings.

As can be seen from FIG. 7, a secure abutment of the friction lining rear side 6 on the lining suspension 8 can be achieved by a corresponding bending of the connecting regions 12 relative to the plane formed by the lining suspension 8 or by the wave peaks 9 on the coupling disk. After connecting or connecting the connection regions 10 to the connection regions 12, according to the examples of FIGS. 4 to 7, the connection region 10 is correspondingly elastically deformed in order to bring the friction lining 4 into contact with the lining suspension with a slight preload. This in particular if no contact force is applied via the counter friction surfaces of the friction clutch on the Kupplungsscheibei. The slight bias is achieved by the elastic deformation of the attachment regions 10. Here, the bias is dimensioned such that the friction lining 4 is not deformed substantially by this biasing force. This allows to provide a clutch disc with a small axial space requirement. FIG. 8a shows a sectional drawing of a friction lining 4 according to the invention, in which the cutting profile cuts through the attachment element 11 in the region of the attachment section 10. The holes 27, by means of which by the connecting rivets 21 of the friction lining 4 is connected to the pad spring plates 13 or the hub disc 7 in cooperation with the connecting holes 17b or the rivet holes 18 are indicated here in the section. The friction lining material 3 forms on the Reibbelagrückseite 6 together with the connection portion 1 1 a common contact surface for engagement with the pad spring 13. Furthermore, in the radially outer region of the Reibbelagrückseite 6, the connection element 1 1 in the region of a meandering annular structure outwardly extending radially Extension 22 cut. These extensions 22 are distributed on the connecting element 1 1 distributed over the circumference for reinforcing the connection between the friction lining material 3 and the connection element 1 1 and for stiffening the friction lining 4th

FIG. 8b shows a further embodiment according to the invention of a friction lining 4 as a sectional drawing corresponding to FIG. 8a, in which the connecting section 10 of the connecting element 11 is offset axially relative to the plane of the friction lining rear side 6 in a further development of the invention. For example, in pad springs 8 with a particularly large travel, such a design may be useful if due to the axial extent of the pad spring 8, the plane of the corresponding friction lining 4 associated peaks 9 not a common plane with this friction lining 4 extending connecting portions 10 associated rivet holes 18 and in order to Connecting regions 12 forms. In order to compensate for such an offset of the mutually associated wave crest 9 and the rivet hole 18 or connecting areas 12 for connection to the connecting section 11, it is proposed that the connecting sections 10 are offset axially with respect to the area of the connecting element 11 located in the overlapping area of the friction lining.

FIG. 9 shows the half-section of a friction clutch 23 comprising a dual-mass flywheel 24 and a pressure plate 25 and a flywheel 26, each with a corresponding friction surface for cooperation with the friction surfaces 5 of the friction lining 4 according to the invention. It can be seen here that the connecting rivets 21 are arranged radially outside the friction surface 5, that is, they are not formed within the region which is swept over during engagement by the friction surfaces 5 in engagement with the pressure plate 25 and the flywheel 24. Here, the friction linings are connected to the clutch disc 1 according to the explanations to the preceding figures. The pressure plate 25 has on the side facing away from the friction linings 4 a ramp ring in particular for forming a wear compensating device to compensate for the wear of the axial thickness of the friction linings 4 due to frictional engagement.

It is therefore advantageous in an embodiment of a friction clutch provided with the inventive friction lining 4, that the axial thickness of the friction region of the clutch disc 1 within such a friction clutch 23 is a maximum of 6 mm. The first friction lining 4 for engagement with the pressure plate 25 together with The second friction lining 4 for engagement with the friction region on the flywheel 26 and the lining suspension 8 introduced therebetween is thus maximally 6 mm thick. It is further provided that the flywheel 26 in the region of engagement with the associated friction lining 5 advantageously 3 to 9 times stronger, so axially thicker than the axial extent of a friction lining 4 is executed. In a further development of this specification, it is provided that in an optimization of the friction clutch with respect to the axial space dimensions, the axial thickness in this area 3 to 5 times stronger, so axially thicker than the axial extent of the friction lining 4 is executed. In order to achieve a particularly high temperature load of the friction clutch is provided that the flywheel 26 in the area of engagement with the associated friction lining 5 is advantageously 5 to 9 times stronger, so axially thicker than the axial extent of a friction lining 4 is executed.

It is further provided that the pressure plate 25 in the area of engagement with the associated friction lining 5 advantageously 3 to 1 0 times stronger, so axially thicker than the axial extent of the friction lining 4 is executed. In a further development of this specification, it is provided that in an optimization of the friction clutch with respect to the axial space dimensions, the axial thickness of the pressure plate 25 in this area 3 to 6 times stronger, so axially thicker than the axial extent of the friction lining 4 is executed. In order to achieve a particularly high temperature load of the friction clutch is provided that the pressure plate 25 in the area of engagement with the associated friction lining 5 advantageously 6 to 1 0 times stronger, so axially thicker than the axial extent of the friction lining 4 is executed. In a further development of the invention it is therefore provided that the equivalent thickness of the pressure plate 25 is advantageously 7 to 1 5 times thicker than the associated one friction lining 4. The equivalent thickness corresponds to an average thickness of the pressure plate calculated from their volume divided by their friction surface.

The sum of the axial thickness of the friction clutch 23 configured in FIG. 9 is not greater than 25 mm. This includes the pressure plate 25, the two friction linings 4, the pad spring 8 and the flywheel 26 in the region of the friction linings 4. Here, the dual mass flywheel 24 is not taken into account.

By the invention is advantageously carried out that the moment of inertia of the two mounted on a clutch disc 1 friction linings 4 is less than 40% of the mass moment of inertia of the clutch disc 1. In a further embodiment, it is provided that the mass moment of inertia of the two mounted on a clutch disc 1 friction linings 4 is less than 35% of the moment of inertia of the clutch disc 1. So far, only values of 50% could be reasonably achieved.

LIST OF REFERENCE NUMBERS

1 clutch disc

2 hub

3 friction lining material

4 friction linings

5 friction surface

6 friction lining back

7 hub disc

8 lining suspension

9 wave mountain

1 0 connection section

1 1 connection element

1 2 connection area

1 3 rubber pads

14 idle damper

1 5 cover sheets

1 6 friction rings

17a rivets

17b connection holes

1 8 Rivet holes in the lining spring plate

1 9 Rivet holes in the hub disc

20 foot area (on the pad spring plate)

21 connecting rivets Extension friction clutch dual-mass flywheel pressure plate flywheel bores

Claims

claims

Coupling ungsscheibe for a friction clutch, in particular for a motor vehicle friction clutch for transmitting torque with a hub for placement on a shaft, in particular transmission input shaft, at least two annularly arranged friction lining material formed friction linings each having a friction surface and a Reibbelagrückseite for torque transmission upon application of the friction surfaces with a Contact pressure on counter friction surfaces of a friction clutch, at least one hub disc in the torque transmission path between the hub and the friction linings of a arranged between the friction linings, which is elastically compressible when acting on the friction linings with a contact force on the counter friction surfaces in the axial direction, characterized in that the friction linings on Reibbelagrückseite each have at least one embedded in the friction lining attachment element, which is for connection to the lining suspension or the Ku pplungsscheibe with at least extends a connection portion outside the friction surface of the friction lining.

2. Coupling ungsscheibe for a friction clutch, in particular for a motor vehicle friction clutch for transmitting torque with a hub for placement on a shaft, in particular transmission input shaft, at least two annularly arranged, formed from friction lining friction linings each having a friction surface and a Reibbelagückseite for torque transmission upon application of the

Friction surfaces with a contact force on Gegenreibflächen a friction clutch, at least one hub disc in the torque transmission path between the hub and the friction linings - a arranged between the friction linings spring suspension at

Actuation of the friction linings with a contact force on the counter friction surfaces in the axial direction is elastically compressible, characterized in that the friction linings on the Reibbelagrückseite each embedded at least one friction lining, with at least one for connection to the

Belagfederung or the clutch disc trained connection portion provided connecting element, wherein the connection portion pointing both in the direction of the friction surface and in the direction of the Reibbelagrückseite facing surface is made essentially free of friction lining material for connection to the lining suspension.

3. Coupling ungsscheibe according to claim 1 or 2, characterized in that the connection of the connecting portion of the lining suspension takes place radially within the friction surface of the friction lining.

4. Clutch disc according to one of claims 1 to 3, characterized in that the lining suspension has wave crests which are elastically compressible upon application of the friction linings with a contact force in the axial direction.

5. clutch disc according to claim 4, characterized in that the wave crests are formed in the direction of Reibbelagrückseite.

6. Clutch disc according to claim 4 or 6, characterized in that the peaks of the pad suspension are supported on the embedded on the Reibbelagrückseite connecting element.

7. Clutch disc according to one of the preceding claims, characterized in that the connection element is embedded in the Reibbelagrückseite such that the connection element forms a flat surface with the friction lining material on the back of the pad.

8. Coupling disc according to one of the preceding claims, in particular claim 7, characterized in that the connecting element only according to the material thickness of

At binding element of the Reibbelagrückseite starting is embedded in the friction lining material.

9. Clutch disc according to one of the preceding claims, characterized in that the friction linings are so connected via the connection sections to the clutch disc, that the Reibbelagückseiten are substantially biased to the lining suspension.

1 0. clutch disc according to one of the preceding claims, characterized in that the connecting portion is axially elastic.

1 1. Clutch disc according to one of the preceding claims, characterized in that the lining suspension has at least one connecting region for connecting the at least one connection portion of a connection element.

12. Clutch disc according to claim 1 1, characterized in that the connecting region is formed in the region of an introduced in the direction of the associated Reibbelagückseite on the lining suspension wave crest.

13. Clutch disc according to one of claims 1 1 or 12, characterized in that the connection region is formed on the lining suspension such that it has a corresponding axial position corresponding to a wave crest.

14. Clutch disc according to one of claims 1 1 to 13, characterized in that the connection region extends out of a wave crest.

1 5. clutch disc according to one of claims 9 to 14, characterized in that the connection of the at least one connection section to the connection region or to the clutch disc takes place radially inside the friction lining.

16. Clutch disc according to one of claims 9 to 1 5, characterized in that the connection of the at least one connection portion takes place at the connection region or on the clutch disc radially within the friction surface.

17. Clutch disc according to one of claims 9 to 16, characterized in that the connection of the connecting element takes place at the connection region or on the clutch disc by means of rivets.

1 8. Coupling disc according to one of claims 9 to 1 7, characterized in that the connection of the connecting element takes place at the connection region or on the coupling plate by welding, in particular spot welding or resistance welding.

1 9. Coupling disc according to one of the preceding claims, in particular one of claims 9 to 1 8, characterized that the connection portion extends straight out of the connection element.

20. Clutch disc according to one of claims 9 to 1 9, characterized in that the connection portion is so connected to the connecting portion or the clutch disc that the Reibbelagückseite abuts substantially bias-free at the wave crests of the lining suspension in the contact pressure-free state of the friction linings.

21. Clutch disc according to one of the preceding claims, characterized in that the lining suspension is formed by individual, circumferentially successively arranged pad springs.

22. Coupling disc according to one of the preceding claims, characterized in that the friction linings are connected directly or indirectly to the lining suspension by trained in the circumferential direction substantially in the region of a respective wave crest of the lining suspension on the friction linings

At connecting sections of the connection elements.

23. Clutch disc according to one of the preceding claims, characterized the friction linings on the clutch disc are connected directly or indirectly by connection sections of the connection elements formed in the circumferential direction essentially in the region of a respective wave crest of the lining suspension on the friction linings.

24. Clutch disc according to one of the preceding claims, characterized in that the friction linings are fastened exclusively via the connecting portions of the lining suspension or the clutch disc.

25. Clutch disc according to one of the preceding claims, characterized in that the torque to be transmitted is introduced from the friction linings on the lining suspension in the clutch disc.

26. Clutch disc according to one of the preceding claims, characterized in that the connection element is formed by a thin, substantially planar sheet metal part.

27. Clutch disc according to one of the preceding claims, characterized in that the connection element covers less than 40% of the surface of Reibbelagrückseite.

28. Coupling disc according to one of the preceding claims, characterized in that the connecting element covers less than 25% of the surface of Reibbelagrückseite.

29. Coupling disc according to claim 26, characterized in that the sheet thickness of the connecting element is less than the plate thickness of the lining suspension.

30. Coupling disc according to claim 26, characterized in that the plate thickness of the connecting element in the region of the embedding in the Reibbelagrückseite is less than the plate thickness of the lining suspension.

31. Coupling disc according to one of claims 26 to 30, characterized in that the sheet thickness of the connecting element in the region of the binding portion to thicker than in the remaining region of the

Is executed on binding element.

32. coupling disc according to one of claims 26 to 31, characterized that in the axial direction of the coupling disk, the rigidity of the connecting element in the region of the connecting portion is greater than in the remaining region of the connecting element.

33. Clutch disc according to claim 17, characterized in that the connection portion is connected to the connecting portion such that the Reibbelagrückseite remains in direct contact with the lining suspension in the non-contact state.

34. Coupling disc according to one of the preceding claims, characterized in that the connection portion is connected to the clutch disc such that in the non-pressing state Reibbelagückseite remains substantially in direct contact with the lining suspension.

35. Coupling disc according to one of the preceding claims, characterized in that the connection portion is angled obliquely with respect to the plane of Reibbelagrückseite in pad spring direction.

36. Coupling disc according to claim 35, characterized in that the connection portion is angled by about 3 ° to 30 °.

37. Clutch disc according to claim 35, characterized in that the connection portion is angled by about 3 ° to 1 5 °.

38. Clutch disc according to one of the preceding claims, characterized in that the connection region is inclined relative to the plane of Reibbelagrückseite.

39. Clutch disc according to claim 38, characterized in that the connecting region is inclined relative to the plane of Reibbelagrückseite.

40. Clutch disc according to claim 37, characterized in that the connection region has a slope of about 3 ° to 15 °.

41. Clutch disc according to one of the preceding claims, characterized the friction linings have an annular, substantially disc-shaped form.

42. Clutch disc according to one of the preceding claims, characterized in that the connection elements 10 formed on the connection element 1 are free of friction lining material on their side facing the friction surface of the friction lining.

43. Clutch disc according to claim 42 or one of the preceding

Claims, characterized in that the on the connecting portions 10 on its the friction surface of the friction lining facing side in the region of the connecting rivets are free of friction lining material.