WO2003106854A1

WO2003106854A1 - Friction clutch

Info

Publication number: WO2003106854A1
Application number: PCT/EP2003/005838
Authority: WO
Inventors: Klaus-Peter Oberle; Jörg Pankoke; Arnold Huisjes; Klaus Fischer; Horst Friedrich; Werner Selzam
Original assignee: Sachs Race Engineering Gmbh
Priority date: 2002-06-12
Filing date: 2003-06-04
Publication date: 2003-12-24
Also published as: AU2003246399A1; DE10225991A1

Abstract

The invention relates to a friction clutch comprising: an inertia weight assembly (12) for mounting the friction clutch (10) on a drive organ; a housing assembly (18), which is connected to the inertia assembly (12) in order to rotate with the latter about a rotational axis (A); a pressure plate assembly (32), which is coupled to the housing assembly (18) in order to rotate with the latter about the rotational axis (A) and can be displaced in relation to the housing assembly (18) in the direction of the rotational axis (A); an energy accumulator (36), which impinges on the pressure plate assembly (32) in the direction of the inertia weight assembly (12); a high-performance clutch disc (46), whose disc friction surface assembly (52) can be mounted between the pressure plate assembly (32) and the inertia weight assembly (12); and a wear compensation system (56) comprising a wear compensation element (54) on the inertia weight assembly (12), said element being displaced in the direction of the rotational axis (A) to compensate for wear.

Description

friction clutch

(Description)

Technical field

The present invention relates to a friction clutch, comprising a flywheel arrangement for attaching the friction clutch to a drive member, a housing arrangement which is connected to the flywheel arrangement for common rotation about an axis of rotation, a pressure plate arrangement which is connected to the housing arrangement for common rotation about the axis of rotation and with respect to the Housing arrangement is coupled displaceably in the direction of the axis of rotation, a force accumulator to be applied to the pressure plate arrangement in the direction of the flywheel mass arrangement, and a clutch disc arrangement which is connected to a

Clutch disk friction surface arrangement can be clamped between the pressure plate arrangement and the flywheel arrangement.

PRIOR ART With such friction clutches there is basically the problem that wear occurs in the area of the components which interact with one another over the service life. If this abrasion is not compensated for in a corresponding manner, the installation position of the energy accumulator, for example a diaphragm spring, changes, with the result that the force characteristic of the same changes as does the actuation path required for performing engagement or disengagement processes. This problem is particularly evident when various frictionally effective elements are provided as carbon components in such friction clutches, as are already used in racing. Although these have a very high stability and immunity to interference, they are subject to very heavy wear. Especially in racing, however, the change in the clutch characteristics caused by heavy wear and tear would result in an increase in the time required to carry out engaging and disengaging processes. Object of the invention

It is the object of the present invention to provide measures in a friction clutch which allow the wear in the area of the friction clutch to be compensated in a simple manner.

Presentation of the invention

According to the present invention, this object is achieved by a friction clutch, comprising: a flywheel arrangement for attaching the friction clutch to a drive member, a housing arrangement which is connected to the flywheel arrangement for common rotation about an axis of rotation, a pressure plate arrangement which is connected to the housing arrangement for common rotation around the axis of rotation and with respect to the housing arrangement in the direction of the axis of rotation is coupled, a force accumulator to be applied to the pressure plate arrangement in the direction of the flywheel mass arrangement, a clutch disc arrangement which can be clamped with a clutch disc friction surface arrangement between the pressure plate arrangement and the flywheel mass arrangement, a wear compensation arrangement which the

Flywheel arrangement comprises a wear compensation element that can be displaced in the direction of the axis of rotation for wear compensation.

It is essential in the present invention that the wear compensation is carried out in the area of the flywheel arrangement. This is an area that is particularly useful for performing manually

Wear compensation processes are comparatively easily accessible, while the clutch area, which is generally positioned facing the transmission and in which the energy accumulator and the pressure plate arrangement are provided, are covered or closed off by other assemblies. For example, it can be provided that the flywheel arrangement comprises a flywheel base body, on which the wear compensation element is supported such that it can be displaced in the direction of the axis of rotation.

The housing arrangement can be connected to the flywheel base body in a radially outer region.

In order to be able to achieve the movement of the wear compensation element with respect to the flywheel main body, it is proposed that the wear compensation element be supported by an inclined surface arrangement with respect to the flywheel main body. For example, the inclined surface arrangement can comprise threaded areas that are in engagement with one another.

An embodiment which is very advantageous due to the small number of components required can provide that the wear compensation element is in threaded engagement with the flywheel mass body and can be displaced in the direction of the axis of rotation by rotating with respect to the flywheel mass body. Alternatively, it is possible for the wear compensation element to be supported with respect to the flywheel mass body and to be displaceable in the direction of the axis of rotation by means of support elements which are threadedly engaged with this and / or the flywheel main body.

According to a further alternative embodiment, the inclined surface arrangement can comprise a wedge or ramp surface arrangement, so that a relative axial displacement of the components opposite one another with corresponding surfaces is also achieved.

In order to ensure that no undesired compensation movements, for example caused by shocks or vibrations, occur during operation, it is proposed that the A flywheel base body is provided with a movement blocking arrangement that blocks the wear compensation element against movement and can be brought into a release state for carrying out wear compensation processes. In this case, increased security can be ensured by the fact that the movement blocking arrangement comprises at least one blocking element which is pretensioned in a blocking position and engages in a blocking recess of the wear compensation element in the blocking position. In order to ensure after a wear compensation movement has been carried out that the movement blocking arrangement can come into effect again, it is proposed that a plurality of blocking recesses which follow one another in the circumferential direction are provided on the wear compensation element.

For increased security, it can further be ensured that the movement blocking arrangement comprises a plurality of, preferably two, blocking elements.

In order to be able to manually induce the movement of the wear compensation element to carry out a wear compensation process in a simple manner, it is proposed that an adjustment tool engagement formation be provided on the wear compensation element. Blocking recesses can simultaneously form at least part of the adjustment tool attack formation.

Above all, if the threaded relative areas cause the axial relative movement required for compensation between the wear compensation element and the flywheel base body, care must be taken that excessive twisting does not lead to a loosening of the thread engagement. It is therefore proposed to provide a maximum movement limitation for the wear compensation element. This can, for example, at least comprise an axial movement stop provided on the housing arrangement for the wear compensation element.

The friction clutch according to the invention can be constructed in such a way that the clutch disc arrangement has a plurality of friction elements, a counter-friction element which is connected in a rotationally fixed manner to the housing arrangement being arranged between each two friction elements of the clutch disc arrangement. This design, constructed in the manner of so-called multi-plate clutches, has a comparatively compact size and a relatively large surface that becomes frictionally effective, so that very large torques can also be transmitted, which is particularly important in the racing field.

Furthermore, it can be provided in the friction clutch according to the invention that on the flywheel support area and / or on the pressure plate support area, a counter-friction element, which is connected in a rotationally fixed manner to the housing arrangement or the flywheel mass arrangement and can be brought into frictional interaction with a friction element of the clutch disc arrangement, is supported.

The present invention further relates to a flywheel arrangement for a friction clutch, comprising a flywheel base body provided for coupling to a drive element and a wear compensation element which is supported on the flywheel base body such that it can be displaced in the direction of an axis of rotation.

The invention is described in detail below with reference to the accompanying drawings on the basis of preferred embodiments. It shows:

Figure 1 is a longitudinal sectional view of a friction clutch according to the invention. Fig. 2 is a perspective view of a housing shown in Fig. 1

Friction clutch;

Fig. 3 is a longitudinal sectional view of the housing shown in Fig. 2;

FIG. 4 is a perspective view of a flywheel base body of the friction clutch shown in FIG. 1;

5 shows a longitudinal sectional view of the flywheel body shown in FIG. 4;

FIG. 6 is an axial view of a wear compensation element of the friction clutch shown in FIG. 1;

FIG. 7 is a longitudinal sectional view of the wear compensation element shown in FIG. 6;

8 is a perspective view of the friction clutch shown in FIG.

1 used flywheel arrangement, which are the essential components of the flywheel body according to FIG. 4 and the

6 comprises wear compensation element;

Fig. 9 is a longitudinal sectional view of the assembly shown in Fig. 8;

10 is a view of an adjusting tool to be used to carry out wear compensation processes;

Fig. 1 1 is a perspective view of a for deactivating a

Movement blocking arrangement of the tool to be used.

First of all, the structure of a friction clutch 10 according to the invention is described in principle with reference to FIG. 1, the so-called Multi-plate clutch is built and can be used for example in racing.

This friction clutch 10 comprises a flywheel arrangement, generally designated 12, which in turn comprises a flywheel base body 14 designed for connection to a crankshaft or another drive shaft. On its side facing the drive unit, the latter has a projection arrangement 16 which is arranged around an axis of rotation A and which can serve as an incremental encoder for a magnetic sensor. A housing 18 of the friction clutch 10, which can be seen in FIG. 2 and also in FIG. 3, has an annular region 20 to be positioned at a distance from the flywheel base body 14. A plurality of connecting webs 22 extend from this ring-like region 20 in the axial direction and extend axially onto the flywheel base body 14. A passage opening 24 is provided in each of these connecting webs 22 for a screw bolt 26 which can also be seen in FIG. 1. These bolts 26 are screwed into the corresponding openings of the flywheel main body 14 for the fixed connection of the housing 18 to the flywheel main body 14. On the side facing away from the flywheel main body 14, a starter ring gear 30 can be fixed to the housing 18 by a plurality of screw bolts 28.

A pressure plate 32 is provided in the volume area generally surrounded by the housing 18 and the flywheel base body 14. This has radial projections 34 on different circumferential areas, each of which engages between two connecting webs 22 of the housing 18, so that the pressure plate 32 is held in a rotationally fixed manner with the housing 18, but is movable in the direction of the axis of rotation A. A force accumulator 36, for example in the form of a diaphragm spring, is supported in its radially outer region via a support ring 38 on the housing 18 and acts on the pressure plate 32 radially further inward, so that it is pressed in the direction of the flywheel arrangement 12. Here is the Support ring 38 partially received in a groove-like recess 40 of the housing 18.

A plurality of outer plates 42 are also coupled in a rotationally fixed manner to the housing 18. These outer disks 42 also have radial projections 44 on a plurality of circumferential areas, each of which engages between two connecting webs 22 of the housing 18, so that the outer disks 42 are non-rotatably coupled to the housing 18, but can be displaced in the direction of the axis of rotation A with respect thereto. A clutch disk, generally designated 46, has a hub 48 which is formed in the radially inner region with teeth 50 provided for rotationally fixed coupling to a transmission input shaft. In its radially outer region, this hub 48 is in non-rotatable engagement with a plurality of inner disks 52, the inner disks 52 also being coupled to the hub 48 so as to be axially movable. The outer fins 42 and the inner fins 52 are made of a material that can meet the requirements that arise during operation. For example, the inner fins 42 can be designed as so-called carbon discs or carbon-containing discs, while the outer fins can be constructed from sintered material for improved heat dissipation from the area of the surfaces that become frictionally effective. Through the energy accumulator 36, which acts on the pressure plate 32 in the direction of the flywheel arrangement 12, the outer plates 42 and the inner plates 52 are brought into mutual frictional engagement in the engaged state of the friction clutch 10, so that a rotationally fixed coupling of the clutch disc 46 to the flywheel arrangement 12 and the housing 18 comprising assembly is obtained. It can be seen that an outer plate 42 is positioned axially immediately adjacent to the flywheel arrangement 12, that is to say a compensation ring 54 described in more detail below, and axially adjacent to the pressure plate 32, so that in the transition region from the flywheel arrangement 12 to the various plates and in Transition area from the pressure plate 32 to the various slats no friction will occur. The flywheel arrangement 12 and the pressure plate 32 can thus be kept essentially free from wear. In the field of Depending on the material used, however, outer disks 42 or inner disks 52 will wear to a greater or lesser extent, which basically has the consequence that their axial thickness decreases. An axial decrease in the thickness of the various plates 42 or / and 52 would, however, result in the pressure plate 32 moving closer to the flywheel arrangement 14 in the engaged state of the friction clutch 10 and thus the energy accumulator 36 changing its installation position.

In order to prevent such a change in the installation position of the energy accumulator 36 or the installation position of the pressure plate 32 taking place over the service life, the friction clutch 10 according to the invention has a wear compensation arrangement, generally designated 56. This essentially comprises the compensation ring 54 already mentioned above, which provides a flywheel contact surface 58 for engaging the disk pack 42, 52, which, however, as already explained above, does not have a frictional effect. In a corresponding manner, the pressure plate 32 provides a pressure plate contact surface 60 that does not become frictionally effective.

The various assemblies or measures provided in the friction clutch 10 according to the invention, which are primarily related to the wear adjustment, are described below.

In order to compensate for the decrease in thickness of the various lamellae 42 and / or 52, an axial displacement of the compensation ring 54 with respect to the flywheel base body 14 is generated according to the present invention. For this purpose, the flywheel base body 14 has an internal thread 62 into which an external thread 66 provided on an axial, ring-like projection 64 of the compensation ring 54 is screwed. The two threads 62, 66 which are in engagement with one another are designed as fine threads, that is to say as threads with a small pitch, to enable very finely metered wear compensation. By changing the rotational position of the compensation ring 54 with respect to the flywheel main body 14, the axial position of the same is also changed the axial position of the flywheel contact surface 58 also changed. If wear occurs, this can be brought closer to the pressure plate 32 to such an extent that exactly the wear that previously occurred in the area of the various slats 42 and / or 52 is compensated for. In order to recognize when the necessary compensation has taken place in the manual wear adjustment described in detail below, an adjustment groove 68, which preferably encircles the entire circumference, is provided on the housing 18 in the region of the connecting webs 22, which represents the position of the pressure plate 32 in the unsealed state. When the wear compensation is carried out, the compensation ring 54 can thus be rotated until, based on visual observation, it is recognized that the pressure plate 32 is again in the correct position with respect to the adjustment groove 68.

4, 5 and 9, two circumferentially adjacent openings 70 are formed on the flywheel main body 14. These are of stepped design and have a larger cross-sectional dimension on their side facing the housing 18 than on their side facing away from the housing 18. A blocking pin 74 with a close fit is passed through the opening area 72 with a smaller diameter. This is achieved in that both the opening 70 and the bolt 74 are manufactured with a high degree of accuracy. A pot-like sleeve 78 is accommodated in the opening section 76 with a larger diameter, which is also manufactured with high precision, so that it can basically be moved in the axial direction with only very little radial movement play. The locking bolt 74 passes through an opening 82 in the bottom region of the sleeve 78 with an end section 80 with a smaller diameter and is fixed to the sleeve 78 by a snap ring or locking ring 84. Between the bottom area of the sleeve 78 and the transition area between the two opening sections 72, 76, a helical compression spring 86 is held under pre-tension, so that in principle the composite consisting of the blocking bolt 74 and the sleeve 78 is directed out of the opening 70 and onto the housing 18 or the compensation ring 54 is too biased. Basically, however, the compensation ring 54 covers the opening 70, see above that the sleeve 78 is held in the opening 70 or in the section 76 thereof. The region 81 of the section 80 of the blocking bolt 74 which projects axially beyond the securing ring 84 engages in one of a plurality of cutouts 88 formed on the outer peripheral region of the compensation ring 54. The recesses 88 have a mutual circumferential spacing which also corresponds to the circumferential spacing of the two openings 70 which can be seen in FIG. 4, for example, and thus the two blocking bolts 74 accommodated in these openings 70. Thus, two blocking bolts 74 always protrude with their areas 81 into two of the cutouts 88. Thus, in principle, a rotation of the compensation ring 54 with respect to the flywheel base body 14 is not possible if the blocking bolts 74 are in their blocking position which can be seen in FIG. 9. It should also be pointed out here that balancing openings 90 are provided on the side of the centrifugal mass base body 14 opposite in the circumferential direction of the positioning of the blocking bolts 74, which serve to accommodate balancing masses. The assembly shown in FIG. 9 can thus be balanced on its own and can thus be provided essentially without any imbalance.

In association with the two blocking bolts 74, the housing 18 has circumferential and facing one another in the region of two connecting webs 22

Recesses 92, which allow axial movement of the blocking bolts 74 or of the sleeves 78 firmly coupled to them. Furthermore, preferably all

In their axial end region, connecting webs 22 have a stop shoulder 94, which forms a maximum movement stop for the compensation ring 54. That is, with the flywheel arrangement 12 assembled with the housing 18, the compensation ring 54 can only be rotated until it is in its

Outer peripheral area comes into contact with these stop shoulders 94. Is this

Condition reached, is still ensured that by fixed

Thread engagement of the compensation ring 54 is connected to the flywheel base body 14 in a defined manner, but further wear compensation is then no longer possible. In order to ensure that the housing 18 is connected to the flywheel arrangement 12 in the correct positioning, there are markings 96 in FIG. 2 on two connecting webs, preferably those between which the two blocking bolts 74 lie and which thus have the recesses 92 intended. Corresponding markings are provided on the flywheel arrangement 12, so that when these markings are assigned to one another it can be seen that the housing 18 is correctly positioned with respect to the flywheel arrangement.

The following describes how a wear compensation process is carried out in the friction clutch 10 according to the invention.

When carrying out a wear compensation process, it must first be ensured that the blocking bolts 74, which basically counteract rotation of the compensation ring 54, are brought into a release state. For this purpose, a release tool 100 shown in FIG. 11 is used. This has a fork-like end tapering wedge-like in its longitudinal direction with two notches 102, 104. The tool 100 is brought to the friction clutch 10 from the radially outside, in the area in which the two connecting webs 22 bearing the markings 96 lie. The tool 100, with its wedge-like end region 106, is inserted between the flywheel main body 14 and the enlarged head regions 108 of the bolts 74, each bolt 74 entering one of the notches 102, 104. Due to the wedge-like configuration, the bolts 74 are pulled to the left in the illustration in FIG. 9, ie the sections 80 emerge from the recesses 88 of the compensation ring 54 which initially still receive them. The locking bolts 74 are then in a release position which no longer blocks the rotation of the adjusting ring 54. Due to the precise manufacture of the locking bolts 74, the sleeves 78 and the openings 70 receiving them, as already mentioned, precise guidance is provided, so that even after the locking bolts 74 are released, they can again move axially towards their locking position in a reliable manner , To here the To avoid the occurrence of the smallest canting, the components that can be moved relative to one another can be slightly chamfered in the respective edge areas. This also applies to tool 100.

If the blocking bolts 74 are brought into their release position, the compensation ring 54 is rotated from the outside with a further tool 110. For this purpose, the tool 110 has an engagement projection 112, which is inserted between two connecting webs 22 into one of the radially outwardly open recesses 88 and is then tilted in the circumferential direction, for example with support on one of the connecting webs 22, so that the compensation ring is generated on the basis of the lever action then generated 54 is rotated. In order to be able to gain free access to the recesses 88 in the compensation ring 54 from the radially outside for the tool 110, the flywheel base body 14 has a circumferential recess 116 in a ring-like extension 114 provided in the outer circumferential region thereof, through which the tool 110 with its projection 112 can then be guided and positioned engaging in a recesses 88.

This adjustment process can be repeated successively until, under observation of the position of the pressure plate 32, it assumes the desired relative position with respect to the adjustment groove 68 already mentioned above.

Once this position has been reached, the tool 100 is withdrawn radially outward, so that the blocking bolts 74 are basically released again to return to their blocking position. However, since in this state two of the blocking recesses 88 will not necessarily be aligned with the respective sections 80 of the blocking bolts 74, the blocking bolts 74 initially remain in an inactive position, in which they with their sections 80 cover the compensation ring 54 in areas between two of each Apply recesses 88. A further rotation of the compensation ring 54 is then induced with the tool 110 until two of the cutouts 88 come into alignment with the sections 80 of the blocking bolts 74 and these blocking bolts 74 then with the regions 81 of sections 80 snap axially into these recesses 88. A further rotation of the adjusting ring 54 is then no longer possible. Only when the tool 100 is brought in again radially from the outside and the blocking bolts 74 are moved into their release position can the compensation ring 54 also be rotated further using the tool 110 in order to carry out a new wear compensation process.

The friction clutch constructed according to the invention makes it possible to carry out a wear compensation process manually in a simple manner, so that, for example, friction clutches can also be used for longer in racing, i.e. the axial thickness of the fins that rub off during operation can be better used. It is of particular importance here that wear compensation arrangements that work automatically due to the carbon material used can be added, especially when used in racing, due to the dust generated during abrasion, so that their functionality is not guaranteed. It is also important that racing is done at high speeds and when strong vibrations occur, which further increases the susceptibility to failure of automated wear compensation arrangements. In contrast, the wear compensation arrangement according to the invention is functionally reliable even under difficult conditions, since no components have to be displaced with respect to one another, particularly in rotary operation, in order to achieve wear compensation. Another advantage of the friction clutch designed according to the invention is that the measures required to carry out the compensation process are to be carried out on the side of the friction clutch 10 which is closer to the drive unit. This is advantageous since this area is generally more easily accessible than the other axial end area of the friction clutch 10, in which, for example, a starter also makes free access difficult.

It should be pointed out here that the arrangement and procedure for wear compensation according to the invention can be used not only with the multi-plate clutch shown in the figures, but also with conventional multi-disc clutch using a normal clutch disc with two friction linings or possibly two clutch discs can be used.

Claims

Expectations

1. A friction clutch comprising: - a flywheel arrangement (12) for attaching the friction clutch

(10) on a drive element, a housing arrangement (18), which with the flywheel arrangement

(12) for common rotation about an axis of rotation (A), a pressure plate arrangement (32) which is connected to the housing arrangement (18) for common rotation about the axis of rotation (A) and with respect to the

Housing arrangement (18) is displaceably coupled in the direction of the axis of rotation (A), the pressure plate arrangement (32) in the direction of the

Flywheel mass arrangement (12) to be acted upon energy accumulator (36), - a clutch disc arrangement (46), which with a

Clutch disc friction surface assembly (52) between the

The pressure plate arrangement (32) and the flywheel arrangement (12) can be clamped, a wear compensation arrangement (56) which on the flywheel arrangement (12) comprises a wear compensation element (54) which can be displaced for wear compensation in the direction of the axis of rotation (A).

2. Friction clutch according to claim 1, characterized in that the flywheel arrangement (12) comprises a flywheel base body (14), on which the wear compensation element (54) is supported displaceably in the direction of the axis of rotation (A).

3. Friction clutch according to claim 2, characterized in that the housing arrangement (18) with the flywheel base body (14) is connected in a radially outer region.

4. A friction clutch according to claim 2 or 3, characterized in that the wear compensation element (54) is supported by an inclined surface arrangement (62, 66) with respect to the flywheel body (14).

5. Friction clutch according to claim 4, characterized in that the inclined surface arrangement (62, 66) comprises mutually engaging threaded areas (62, 66).

6. Friction clutch according to claim 5, characterized in that the wear compensation element (54) with the flywheel base body (14) is in threaded engagement and can be displaced with respect to the flywheel base body (14) in the direction of the axis of rotation (A).

7. A friction clutch according to claim 5, characterized in that the wear compensation element (54) is supported by this or / and the flywheel base body (14) in threaded engagement support elements with respect to the flywheel base body (14) and is displaceable in the direction of the axis of rotation (A).

8. A friction clutch according to claim 4, characterized in that the inclined surface arrangement comprises a wedge or ramp surface arrangement.

9. A friction clutch according to one of claims 2 to 8, characterized in that a movement blocking arrangement (74, 78) is provided on the flywheel base body (14) which blocks the wear compensation element (54) against movement and can be brought into a release state for carrying out wear compensation processes.

10. A friction clutch according to claim 9, characterized in that the movement blocking arrangement (74, 78) comprises at least one blocking element (74) which is pretensioned in a blocking position and engages in a blocking recess (88) of the wear compensation element (54) in the blocking position.

11. A friction clutch according to claim 10, characterized in that a plurality of blocking recesses (88) following one another in the circumferential direction are provided on the wear compensation element (54).

12. Friction clutch according to one of claims 9 to 11, characterized in that the movement blocking arrangement (74, 78) comprises a plurality of, preferably two, blocking elements (74).

13. A friction clutch according to one of claims 1 to 12, characterized in that an adjustment tool engagement formation (88) is provided on the wear compensation element (54).

14. A friction clutch according to claim 11 and claim 13, characterized in that the blocking recesses (88) form the adjustment tool engagement formation (88) at least in part.

15. Friction clutch according to one of claims 1 to 14, characterized by a maximum movement limitation (94) for the wear compensation element (54).

16. A friction clutch according to claim 15, characterized in that the maximum movement limitation (94) comprises at least one axial movement stop (94) provided on the housing arrangement (18) for the wear compensation element (54).

17. A friction clutch according to claim 16, characterized in that the clutch disc arrangement (46) has a plurality of friction elements (52), with a counter-friction element connected in a rotationally fixed manner to the housing arrangement (18) between each two friction elements (52) of the clutch disc arrangement (46) (42) is arranged.

18. Friction clutch according to one of claims 1 to 17, characterized in that on a flywheel support area (58) and / and on a pressure plate support area (60) with the housing arrangement (18) or the flywheel arrangement (12) rotatably connected and in frictional interaction with one The friction element (52) of the clutch disc arrangement (46) can be brought against the counter-friction element (42).

19. Flywheel mass arrangement for a friction clutch, comprising a flywheel base body (14) provided for coupling to a drive element and a wear compensation element (54) which is supported on the flywheel base body (14) so as to be displaceable in the direction of an axis of rotation (A).