CN110578758B

CN110578758B - Self-energizing friction clutch with compensation adjustment

Info

Publication number: CN110578758B
Application number: CN201910489805.XA
Authority: CN
Inventors: C·拉贝尔
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2018-06-07
Filing date: 2019-06-06
Publication date: 2022-12-30
Anticipated expiration: 2039-06-06
Also published as: DE102018113555A1; CN110578758A

Abstract

A friction clutch (1) for the self-compensating adjustment of a drive train of a motor vehicle, having a clutch cover (2), a pressure plate (4) which is connected to the clutch cover in a rotationally fixed manner by means of a leaf spring unit (3) and can be moved in the axial direction relative to the clutch cover, a coil spring (5) which influences the axial position of the pressure plate, and a compensating adjustment device (6) which adjusts the position of the coil spring relative to the clutch cover, the compensating adjustment device (6) having an adjusting ring (7) and a sensor spring (8) which form a pivot point (9) about which the coil spring (5) can be pivoted for axially moving the pressure plate (4), a plurality of leaf springs (10 a, 10 b) of the leaf spring unit (3) being arranged radially within the adjusting ring (7) and the sensor spring (8), said leaf springs being arranged in such a way that, in the engaged state of the friction clutch (1), the pressure plate (4) is forced into a self-reinforcing frictional engagement with the clutch disc.

Description

Self-energizing friction clutch with compensation adjustment

Technical Field

The invention relates to a friction clutch for the self-compensating adjustment of a drive train of a motor vehicle, for example for a drive train of a passenger vehicle, a utility vehicle, a bus or another commercial vehicle, having a clutch cover, a pressure plate which is connected to the clutch cover in a rotationally fixed manner by means of a leaf spring unit and can be moved in the axial direction relative to the clutch cover, a disc spring which influences the axial position of the pressure plate, and a compensating adjustment device/wear-compensating adjustment device which adjusts the position of the disc spring relative to the clutch cover, wherein the compensating adjustment device has an adjustment ring and a sensor spring, and the adjustment ring and the sensor spring form a pivot point/lever point about which the disc spring is arranged so as to be pivotable for axially moving the pressure plate. The Self-Adjusting friction Clutch is a so-called SAC Clutch ("Self Adjusting Clutch").

Background

A friction clutch of this type is known, for example, from DE 20 2015 001 516 U1. A self-adjusting friction clutch for a drive train of a motor vehicle is disclosed.

However, the following disadvantages have proven in the embodiments known from the prior art: in particular, the embodiments are usually configured as relatively large structures, given the requirements for transmitting as large a torque as possible.

Disclosure of Invention

The object of the present invention is therefore to overcome the disadvantages known from the prior art and to provide, in particular, a self-adjusting friction clutch which is designed for transmitting as high a torque as possible without requiring an enlargement or at least a significant enlargement of the installation space.

According to the invention, this object is achieved in that a plurality of leaf springs of the leaf spring unit are arranged radially inside the adjusting ring and the sensor spring, said leaf springs being arranged in such a way that they force/press/tension the pressure plate into self-reinforcing frictional contact with the clutch disk in the engaged position of the friction clutch.

The installation space of the friction clutch is particularly compact due to the particularly smart and space-saving design of the self-adjusting and self-amplifying friction clutch. In the same installation space, therefore, on the one hand a greater maximum torque can be transmitted and, on the other hand, a reliable wear compensation adjustment is achieved during operation.

Further advantageous embodiments are set forth in the dependent claims and are set forth in detail below.

The radial installation space is particularly skillfully utilized if the leaf spring unit has a first and a second set of leaf springs, which are connected with respective ends to the tongue of the coil spring.

In this case, it is also advantageous if the leaf springs of the first group and the leaf springs of the second group are connected to the tongues of the spiral springs by means of a pressure/tension block. A particularly elegant and secure attachment of the leaf spring end to the coil spring is achieved by this common pressure/tension piece.

It is also practical for the pressure piece/tension piece to have at least one first disk and a second disk connected thereto, wherein the tongue of the coil spring is arranged in the axial direction between the first disk and the second disk.

The friction clutch is also compact in terms of operation if the spiral spring can be operated, i.e. pivoted, by means of the pressure/tension piece for moving the pressure plate.

It is also advantageous if the leaf springs of the first group are mounted with a first end on the clutch cover and with a second end (above the tongue of the disk spring) (preferably by means of a pressure/tension block) connected with the tongue of the disk spring.

In this case, it is also advantageous if the leaf springs of the second group are mounted with a first end on the pressure plate and with a second end (below the tongue of the disk spring) (preferably by means of a pressure/tension block) connected to the tongue of the disk spring. The leaf spring is thereby particularly neatly mounted.

The pivot point is preferably arranged radially inward of the cam of the compression plate in contact with the disc spring, thereby making more compact use of the installation space. In other preferred embodiments, the pivot point is arranged radially outside of the pressure plate projection in contact with the coil spring, so that the sensor spring is also arranged externally.

In this connection, it is therefore particularly practical for the adjusting ring and the sensor spring (in each case preferably completely) to be arranged radially inside the pressure plate cam.

It is also advantageous if the sensor spring is supported on the coil spring by means of a wire loop, wherein the wire loop is in turn arranged radially outside the leaf spring of the leaf spring unit. A particularly clever construction and arrangement of the pivot bearing of the coil spring is thereby achieved.

In other words, the SAC wear compensation adjustment device (compensation adjustment device) according to the invention is therefore integrated into a self-energizing clutch (friction clutch), for example a K0 clutch. The friction clutch is preferably designed as a dry clutch, and is furthermore preferably designed for attaching and detaching an internal combustion engine. In this case, the leaf spring, by means of which the pressure plate is attached in a rotationally fixed manner to the clutch cover, is arranged in the radial direction inside the adjusting ring and the sensor spring of the force-based wear compensation adjusting device (compensation adjusting device) according to the SAC principle. The end of the leaf spring, preferably the leaf spring, is fixedly connected (directly or indirectly) in the axial direction to the tongue of the wrap spring in order to apply a force to engage the clutch to the tongue of the wrap spring in traction mode of the internal combustion engine and to apply a force to disengage the clutch to the tongue of the wrap spring in slip mode of the internal combustion engine. Preferably, a leaf spring on the clutch cover side and a leaf spring on the pressure plate side are provided, which are connected to one another in a rotationally fixed manner by a pressure piece in which the tongue of the spiral spring is axially received.

Drawings

The invention is elucidated in detail below with reference to the accompanying drawings.

It shows that:

fig. 1 is a longitudinal section through a part of a friction clutch according to the invention according to a preferred embodiment, wherein the internal structure of the friction clutch is shown in terms of a compensation adjustment device and a leaf spring unit, and for the sake of clarity, the illustration of the pressure plate and the clutch disc is omitted,

fig. 2 is a detail view of the friction clutch according to fig. 1 in the region of a centrally arranged leaf spring unit, in which the direction of the action of the force acting in traction mode and increasing the engaged state is marked,

fig. 3 is a longitudinal section through the friction clutch according to fig. 1, wherein, as already shown in fig. 2, the direction of the action of the self-reinforcing force acting in traction mode is indicated,

fig. 4 is a detail view of the friction clutch according to fig. 1 in the region of a centrally arranged leaf spring unit, similar to fig. 2, wherein the force acting in slip operation and increasing the disengagement position is indicated,

FIG. 5 is a longitudinal section through the friction clutch according to FIG. 1, wherein, as already shown in FIG. 4, the direction of the action of the self-reinforcing force acting in slip operation is indicated, and

fig. 6 is a top view of the friction clutch of fig. 1-5.

The drawings are merely schematic in nature and are used only for the understanding of the present invention. Like elements are provided with like reference numerals.

Detailed Description

The basic structure of a friction clutch 1 according to the invention according to a preferred embodiment can be seen in fig. 1. As explained in detail below, the friction clutch 1 is not only designed as a self-compensating adjustment but also as a self-reinforcing friction clutch 1. The friction clutch 1 is configured as a dry-running friction clutch 1. The friction clutch 1 preferably serves in operation as a K0 clutch, i.e. a clutch for disconnecting or attaching the internal combustion engine from or to a shaft of a drive train (e.g. a transmission shaft of a transmission). The friction clutch 1 is designed as a single-disk clutch. For the sake of clarity, only the subassembly shown in fig. 1 is represented from the friction clutch 1, i.e. that part of the friction clutch 1 which lacks the counter plate and the clutch disk.

The friction clutch 1 generally has a clutch cover 2, which is preferably fixedly connected to the counterplate at its radially outer edge 27 (in the form of a flange region) with respect to the rotational axis 24 of the clutch cover 2. The counterplate is usually fixedly connected to this edge 27 and projects from there inward in the radial direction, so that it is arranged partially axially adjacent (relative to the axis of rotation 24) to the stripper plate 4. In operation, the friction linings of the clutch disk are arranged generally axially between the counterpressure plate and the pressure plate 4. The clutch disks in turn usually form the output of the friction clutch 1 during operation, which is connected in a rotationally fixed manner to a transmission shaft of the drive train. In particular, the clutch cover 2 and the counter plate usually also form the input of the friction clutch 1, which is connected to the output shaft of the internal combustion engine in a rotationally fixed manner. The pressure plate 4 is also connected to the clutch cover 2 in a rotationally fixed manner. However, the attachment of the input and output can in principle also be reversed.

As can be further seen in fig. 1, the pressure plate 4 is also received (on the clutch cover 2) in an axial direction, i.e. along the rotational axis 24 of the friction clutch 1/clutch cover 2, in a manner movable relative to the clutch cover 2. The clutch cover 2 is substantially cup-shaped (fig. 6). The clutch cover 2 has, in addition to its edge 27, a disk/plate-shaped bottom region 28 which also extends in the radial direction. The bottom region 28 and the edge 27 are connected to one another by an axially extending side wall region 32. The side wall region 32 radially surrounds the receiving space 29, in particular in which the pressure plate 4 is arranged, from the outside.

The pressure plate 4 is coupled (i.e., rotationally fixed) to the clutch cover 2 by means of the leaf spring unit 3 and is axially displaceable relative to one another. As explained in detail below, the leaf spring unit 3 has a plurality of

leaf springs

10a and 10b, which are fastened with

respective ends

13 or 15 to the pressure plate 4 or to the clutch cover 2. The

leaf springs

10a and 10b are normally used to pretension the pressure plate 4 in the engaged position of the friction clutch 1. Furthermore, the

leaf springs

10a, 10b in the engaged position of the friction clutch 1 enable the pressure plate 4 to be arranged in a torque-free manner relative to the clutch disk.

The friction clutch 1 is designed as a self-adjusting clutch. For this purpose, the friction clutch 1 has a (wear) compensation adjustment device 6, which acts on the disk spring 5. The disk spring 5 is generally used as an engaging or disengaging element for the friction clutch 1 and for generating a static pressing force and thus for directly moving the pressing plate 4 between the engaged and disengaged state. The disk spring 5 bears axially with a radially outwardly arranged force edge 31 against a plurality of pressing plate cams 21 of the pressing plate 4 distributed in the circumferential direction.

The compensation adjustment device 6 has an adjustment ring 7 which is particularly clearly visible in the section according to fig. 1. The adjusting ring 7 has an abutment region 30 which, together with the sensor spring 8 and the wire loop 22 (of the compensation adjusting device 6), forms a pivot point 9 of the disk spring 5 on the clutch cover 2. The pivot point 9 is formed by the above-mentioned elements radially inside the force edge 31/pressure plate cam 21, i.e. radially inside the contact area between the cup spring 5 and the pressure plate 4. The adjusting ring 7 is designed as a ramp ring and has (on its axial side facing away from the contact region 30) a plurality of ramps distributed in the circumferential direction, which in each case bear/bear on corresponding ramps (on the bottom region 28) of the clutch cover 2, which ramps are configured complementarily thereto. If the friction linings and also the pressure plates of the clutch disk and/or the pressure plate 4 are worn to a certain extent (axially) during operation, the adjusting ring 7 is twisted relative to the clutch cover 2. By twisting the adjusting ring 7 relative to the clutch cover 2, the adjusting ring 7 is usually slid along in the circumferential direction on a corresponding ramp of the clutch cover 2, so that the axial position of the adjusting ring 7 relative to the clutch cover 2/bottom region 28 is varied.

The adjusting ring 7 rests with its bearing region 30 on the axial side of the coil spring 5 facing the base region 28, while the wire loop 22 rests/is supported by means of the sensor spring 8 on the axial side of the coil spring 5 facing away from the base region 28. The sensor spring 8 is also generally configured in a ring shape. The likewise encircling wire loop 22 is arranged and clamped axially directly between the sensor spring 8 and the coil spring 5. The contact area 30 and the contact area between the wire ring 22 and the coil spring 5 are located at substantially the same level, as seen in the radial direction. The sensor spring 8 is also received/supported/retained by a plurality of retaining pegs 26 fixed to the clutch cover 2. The sensor spring 8 is elastically deformable, essentially in order to press the wire loop 22 resiliently against the spiral spring 5 or the spiral spring 5 against the contact region 30 of the adjusting ring 7 with a specific prestress.

According to the invention, the leaf spring unit 3 is arranged with its

leaf springs

10a and 10b radially inside the pivot point 9, i.e. radially inside the adjusting ring 7 and the sensor spring 8. As will be explained in more detail below, the leaf spring unit 3 serves to design the friction clutch 1 as a self-reinforcing friction clutch 1.

The

leaf springs

10a and 10b are divided into two

groups

11, 12, which are connected to each other with constituting a separation and engagement unit, respectively. The

leaf springs

10a and 10b are in particular fixedly attached/supported in the axial direction (by means of a pressure piece 18) on the tongue 17 of the coil spring 5. The tongue 17 of the disk spring 5 is a tab-shaped projection of the disk spring 5 which projects in the radial direction inwardly from the pivot point 9 and constitutes with its radial inside the radial inside of the leaf spring 5.

The

leaf springs

10a and 10b extend between the first and

second end portions

13, 15, 14, 16, respectively, at least in the circumferential direction and in the axial direction of the clutch cover 2. The

leaf springs

10a and 10b, in this case the second ends 14, 16 of the

leaf springs

10a and 10b, respectively, are fixedly connected in the axial direction by means of a pressure piece 18 to the tongues 17 of the disk springs 5, in order to apply a force engaging the friction clutch 1 to the tongues 17 of the disk springs 5 during traction operation of the internal combustion engine (the accelerating torque being transmitted via the clutch cover 2 to the pressure plate 4 and to the counter-pressure plate and from these to the clutch disk), as is apparent in connection with fig. 2 and 3, and in slip operation of the internal combustion engine (the clutch cover 2 being driven by the clutch disk), as is apparent in connection with fig. 4 and 5, a force disengaging the friction clutch 1 is applied to the tongues 17 of the disk springs 5. The

leaf springs

10a and 10b are therefore connected indirectly (via the pressure piece 18) to the tongue 17 in this embodiment, but are also connected directly to the tongue 17 in other embodiments. The pressure piece 18 is also designed as a tension piece in other embodiments, so that the pressure piece is also denoted as a pressure piece/tension piece 18.

At a certain free angle, a rotationally fixed attachment of the pressure plate 4 to the clutch cover 2 is achieved. In the exemplary embodiment shown, a friction clutch 1 is shown with a compressed (alternatively also tensioned) spiral spring 5, which is actuated via a transmission shaft (transmission input shaft). Fig. 3 shows the braking direction 33 of the pressure plate 4, which braking direction 33 is opposite to the direction of rotation of the clutch cover 2 (when viewed in half section, the braking direction 33 extends inward in the plane of the drawing, and the direction of rotation extends outward from the plane of the drawing).

The plate springs 10a and 10b are divided into two

groups

11, 12, i.e., into a clutch cover-side (first) group 11 having the first plate spring 10a and a pressing plate-side (second) group 12 having the second plate spring 10 b. The

leaf springs

10a and 10b are also connected to one another via a pressure piece 18, the tongue 17 of the disk spring 5 being received axially fixed between two (pressure piece)

disks

19, 20. For this purpose, the pressure piece 18 has a pressure plate-side (second) disk 20 attached in a rotationally fixed manner to the pressure plate 4 via the leaf springs 10b of the second group 12 and a clutch cover-side (first) disk 19 attached in a rotationally fixed manner to the clutch cover 2 via the leaf springs 10a of the first group 11. The leaf springs 10a of the first group 11 are connected with a first end 13 to the clutch cover 2 and with a second end 14 to the pressure piece 18. The leaf springs 10b of the second group 12 are connected with a first end 15 to the pressure plate 4 and with a second end 16 to a pressure piece 18.

In particular, the first disk 19 and the second disk 20 are connected to one another in the circumferential direction in a non-axial manner by rivets 25. Each leaf spring plane is connected to a pressure/tension disc (first disc 19 or second disc 20) respectively, so that the

discs

19, 20 are axially connected to each other. The tongue 17 of the disc spring 5 is arranged/received between the first disc 19 and the second disc 20, seen in axial direction. The

leaf springs

10a, 10b are in turn connected to the pressure piece 18 or the

respective disk

19, 20 by means of rivets 25, i.e. rivets 25 which are also provided for connecting the

disks

19, 20 to one another. The disk spring 5 can thus be pivoted about the pivot point 9 in the region of its tongue 17 by an axial displacement of the pressure piece 18. In particular, the pressure piece 18 additionally has an annular hub part 23 on which the two

disks

19, 20 are arranged in an axially fixed manner. In operation, therefore, the pressure piece 18 is actuated by the hub part 23 (and the disk spring 5 is actuated by the pressure piece 18).

Each (first) leaf spring 10a of the first set 11 extends in a first circumferential direction from the first end 13 towards the second end 14, wherein each (second) leaf spring 10b of the second set 12 also extends in a first circumferential direction, which is identically oriented, from the first end 15 towards the second end 16. The first leaf spring 10a extends in the axial direction between the first end 13 and the second end 14 at a maximum first angle relative to the first circumferential direction, wherein the first angle in fig. 2 corresponds to the inclination of the force arrow 34, which shows the direction of the force acting in the first leaf spring 10a during traction operation, relative to a radial line extending only in the radial direction. The second leaf spring 10b also extends in the axial direction between the first end 15 and the second end 16 at a maximum second angle (inclination of the force arrow 35 with respect to the radial line, which force arrow shows the direction of the force acting in the second leaf spring 10b in traction operation) with respect to the first circumferential direction. The first angle and the second angle are equal in magnitude in the traction mode and preferably also in the slip mode, but are only opposite in direction.

In the pulling operation represented in fig. 2 and 3, the clutch cover 2 pulls the pressure piece 18 in a first circumferential direction (see force direction 34 in combination with the direction of rotation out of the plane of the drawing) by means of the first set 11 of leaf springs 10 a. At the same time, the pressure piece 18 pulls the pressure plate 4 in a first circumferential direction by means of the second group 12 (or brakes the pressure plate 4 in a second circumferential direction opposite to the first circumferential direction, i.e. in the braking direction 33). The first and second angles of the

leaf springs

10a, 10b are chosen such that they are as equal as possible and act in opposition. In the illustrated traction mode, the resulting axial force of the

leaf springs

10a, 10b acts in the same axial direction and presses the friction clutch 1 further, i.e. acts in the engagement direction (on the pressure piece 18 in the axial direction indicated by the arrow 36) by means of a self-reinforcing force.

In the slip operation illustrated in fig. 4 and 5, the resulting axial forces of the

leaf springs

10a, 10b also act in the same direction and pull the friction clutch 1 up, i.e. disengage the friction clutch 1. The pressure plate 4 introduces its torque via the second leaf spring 10b into the pressure piece 18/second disk 20 a. This torque is introduced into the first disk 19 by means of the rivet 25. As already mentioned, the pressure piece 18/the first plate 19 is in turn fastened to the clutch cover 2 by the first leaf spring 10 a.

In the illustrated slip operation, the clutch cover 2 is pulled by the pressure piece 18 in the second circumferential direction (the force direction 34, the braking direction 33, the direction in which the drawing plane faces outward, and the rotational direction in which the drawing plane faces inward) by the leaf springs 10a of the first group 11. At the same time, the pressure pieces 18 are drawn by the pressing plate 4 in the second circumferential direction 21 through the second group 12. In the slip mode, the resulting axial forces of the

leaf springs

10a, 10b (see the action on the pressure piece 18 in the axial direction indicated by the arrow 36) also act in the same direction and pull the friction clutch 1 up, i.e. disengage the friction clutch 1.

In other words, the torque of the pressure plate 4 is not directly introduced into the clutch cover 2. This moment is introduced into the cover 2 by means of a tension/compression piece (compression piece 18) acting on the disk spring 5. The two leaf spring assemblies (to which the

leaf springs

10a, 10b each belong) are arranged in such a way that they pull the spiral spring 5 when pulled and generate a greater compression force by the conversion of the clutch 1/KD. This arrangement causes a reduction in the torque capacity during slip operation. For applying this protocol to SAC1, a separation clamp (Abhub-Bugel) (not shown) can also be used. This measure makes it possible to reduce the working range of the

leaf springs

10a, 10b, since they do not have to pull the pressure plate 4 over the entire range.

In the structural embodiment, there are pressure pieces above and below the disk spring 5 (pressure piece 18 with two disks 19, 20). The pressing plate 4 introduces its torque into the pressing piece 20 located below the disc spring 5 through the plate spring 10 b. The torque is introduced into the second pressure piece 19 via the rivet head of the first leaf spring rivet (rivet 25). This pressure piece 19 is fixed to the cover 2 by means of the second leaf spring assembly 10 a. The two

pressure pieces

19, 20 are connected in the center of rotation by an additional component (hub part 23) axially by a detachable connection. The torque-locking of the two

pressure pieces

19, 20 can also be achieved by this additional component. The leaf spring angles are chosen such that they act as equally and oppositely as possible. In the pulling direction, the axial forces generated by the

leaf spring assemblies

10a, 10b act in the same direction and further tighten the clutch 1. In the pressing direction, the resulting axial force of the

leaf spring assemblies

10a, 10b acts in the same direction and presses the clutch 1. The angle of the

leaf springs

10a, 10b which is as identical as possible facilitates the holding of the two leaf spring sets 10a, 10b; 11. the relative displacement of 12 is as uniform as possible. The opposite arrangement achieves that the sum of the displacements remains close to zero. The working area of the

leaf springs

10a, 10b can be reduced by this measure, since they do not have to pull the pressure plate 4 over the entire area when using the separating clip. This embodiment can also be used in a conventionally pressurized clutch.

List of reference numerals

1. Friction clutch

2. Clutch cover

3. Leaf spring unit

4. Extrusion disc

5. Coil spring

6. Compensation adjusting device

7. Adjusting ring

8. Sensor spring

9. Pivot point

10a first leaf spring

10b second leaf spring

11. First group

12. Second group

13. First end of first leaf spring

14. Second end of the first leaf spring

15. First end of the second plate spring

16. Second end of the second leaf spring

17. Tongue part

18. Pressing/pulling block

19. First disk

20. Second plate

21. Extrusion plate lug

22. Wire loop

23. Hub component

24. Axis of rotation

25. Rivet

26. Retaining bolt

27. Edge of a container

28. Bottom zone

29. Receiving space

30. Contact area

31. Force edge

32. Sidewall region

33. Direction of braking

34. Force arrow of first leaf spring

35. Force arrow of second leaf spring

36. Arrows.

Claims

1. A friction clutch (1) for self-compensating adjustment of a drive train of a motor vehicle, having a clutch cover (2), a pressure plate (4) which is connected torsionally fixed to the clutch cover (2) by means of a leaf spring unit (3) and is movable in an axial direction relative to the clutch cover (2), a disc spring (5) which influences the axial position of the pressure plate (4), and a compensation adjustment device (6) which adjusts the position of the disc spring (5) relative to the clutch cover (2), wherein the compensation adjustment device (6) has an adjustment ring (7) and a sensor spring (8), and the adjustment ring (7) and the sensor spring (8) form a pivot point (9), around which the disc spring (5) is arranged so as to be pivotable for axially moving the pressure plate (4), characterized in that a plurality of leaf springs (10 a, 10 b) of the leaf spring unit (3) are arranged radially inside the adjustment ring (7) and the sensor spring (8) in such a way that the contact with the pressure plate (4) in a self-locking engagement in the friction clutch (1) intensifies the friction clutch disk (4).

2. The friction clutch (1) according to claim 1, characterized in that the leaf spring unit (3) has a first (11) and a second (12) group of leaf springs (10 a, 10 b), and the leaf springs (10 a, 10 b) of the first (11) and second (12) groups are connected with respective ends (14, 16) with a pressure/pull block (18) with a tongue (17) of the disc spring (5).

3. The friction clutch (1) according to claim 2, characterized in that the pressure piece/pull piece (18) has at least one first disk (19) and a second disk (20) connected to the first disk (19), wherein the tongue (17) of the disc spring (5) is arranged in the axial direction between the first disk (19) and the second disk (20).

4. The friction clutch (1) according to claim 3, characterized in that the disc spring (5) can be operated by means of the pressure/pull piece (18) for moving the pressure plate (4).

5. The friction clutch (1) according to claim 2, characterized in that the leaf springs (10 a) of the first group (11) are mounted with a first end (13) on the clutch cover (2) and with a second end (14) connected with a tongue (17) of the disc spring (5) by means of the pressure/pull piece (18).

6. The friction clutch (1) according to claim 2, characterized in that the leaf springs (10 b) of the second group (12) are mounted with a first end (15) on the pressure plate (4) and with a second end (16) connected with the tongue (17) of the disc spring (5) by means of the pressure/pull piece (18).

7. The friction clutch (1) according to claim 1, characterized in that the pivot point (9) is arranged radially inside a pressure plate cam (21) in contact with the disc spring (5).

8. The friction clutch (1) according to claim 7, characterized in that the adjusting ring (7) and the sensor spring (8) are arranged radially inside the pressure plate cam (21).

9. The friction clutch (1) according to one of claims 1 to 8, characterized in that the sensor spring (8) is supported on the spiral spring (5) by means of a wire loop (22), wherein the wire loop (22) is in turn arranged radially outside the leaf springs (10 a, 10 b) of the leaf spring unit (3).