EP4162169A1

EP4162169A1 - Friction clutch for transmitting a torque in a friction- and form-fitting manner

Info

Publication number: EP4162169A1
Application number: EP21725021.6A
Authority: EP
Inventors: Pascal Seifermann; Christoph Raber
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2020-06-04
Filing date: 2021-05-04
Publication date: 2023-04-12
Also published as: WO2021244698A1; CN115398112A; DE102020114798B3

Abstract

The invention relates to a friction clutch (1), in particular for the powertrain (2) of a motor vehicle (3), with a rotational axis (5) extending along an axial direction (4), comprising at least one clutch disc (7), which is connected to the output side (6) of the friction clutch (1), and a counter pressure plate (9), which is connected to the input side (8) of the friction clutch (1), said clutch disc and counter pressure plate being movable relative to each other along the axial direction (4) in order to produce a first friction-fitting connection (10) between each other, wherein the output side (6) comprises a hub (11); the clutch disc (7) comprises at least one first part (12) and a second part (13) which can be moved relative to each other along the axial direction (4) by a shifting means (14), said first part (12) forming the first connection (10) and said second part (13) being connected to the hub (11) via the shifting means (14); and the second part (13) can be moved relative to the counter pressure plate (9) along the axial direction (4) by means of the shifting means (14) in order to produce a form-fitting second connection (15) between the second part (13) and the counter pressure plate (9) in a shiftable manner.

Description

Friction clutch for frictional and form-locking transmission of torque

The present invention relates to a friction clutch, in particular for a drive train of a motor vehicle, which allows frictional and positive transmission for high torques.

A multi-disc clutch is known from DE 102018 122385.4, in which torque, on the one hand, can be transmitted frictionally, as is usual with multi-disc clutches, but on the other hand, a form-fitting connection for the transmission of torque can be switched on. However, the solution used there can only be used for multi-plate clutches.

From the older, unpublished DE 102020 104023.7, a friction clutch is known in which a torque can also be transmitted in a frictionally locking manner and, depending on a pushing or pulling operation, also positively. To form the form-fitting connection, a hub must be moved along a shaft. The displacement of the hub can, however, be hindered under the action of torque by sliding friction counteracting the displacement.

Proceeding from this, the present invention is based on the object of at least partially overcoming the problems known from the prior art and, in particular, of specifying a friction clutch in which a frictional and positive transmission of torque is possible for both multi-disc clutches and multi-disc clutches for high torques , wherein the form-fitting connection can be reliably established.

This object is achieved with the features of independent claim 1. Further advantageous embodiments of the invention are specified in the dependent claims. The features listed individually in the dependently formulated claims can be combined with one another in a technologically meaningful manner and can define further embodiments of the invention. In addition, the features specified in the claims are used in the description further specified and explained, with further preferred embodiments of the invention being presented.

A friction clutch is proposed, in particular for a drive train of a motor vehicle. The friction clutch has an axis of rotation extending along an axial direction and comprises at least one clutch disc connected to an output side of the friction clutch and a counter-pressure plate connected to an input side of the friction clutch. The counter-pressure plate and the clutch disc can be displaced relative to one another along the axial direction in order to produce a frictional first connection formed between them. The output side includes a hub. The clutch disc comprises at least a first part and a second part, which can be displaced relative to one another along the axial direction by a switching means. The first part forms the first connection. The second part is connected to the hub via the switching means.

The second part can be displaced by the switching means along the axial direction relative to the counter-pressure plate for the switchable formation of a form-fitting second connection between the second part and the counter-pressure plate.

The friction clutch can be either a single-disc or multiple-disc clutch or a multi-disc clutch. In the case of a single-disk clutch, the friction clutch has only the clutch disk and the counter-pressure plate to form the first connection. In particular, a further counter-pressure plate can be provided so that the clutch disc can be clamped between the counter-pressure plates to form the first connection. At least one of the counter-pressure plates is designed in particular as a pressure plate that can be displaced along the axial direction relative to the other (stationary) counter-pressure plate.

In the case of a multi-disc clutch, at least one more clutch disc and at least one z. B. designed as an intermediate plate provided counter pressure plate. In the case of a multi-disc clutch, at least one outer disc and at least one inner disc are provided, which replace the at least one counter-pressure plate and the at least one clutch disc. To establish the first connection, the at least one clutch disc and the counter-pressure plate are pressed against one another. For this purpose, a conventional actuating device is designed, which consists, for example, of a pressure pot with a corresponding hydraulic actuating cylinder or of a hydraulically actuated lever spring. It can also be actuated mechanically or by an electric motor.

A torque can be transmitted into the friction clutch via the input side as well as the output side. To transmit torque via the friction clutch, the input side is connected to the output side at least via the first connection and, if necessary, additionally via the second connection. The second connection, which acts positively, enables the transmission of high torques.

In particular, a torque of at least 700 Nm [Newton meters], preferably at least 800 Nm or even at least 900 Nm, can be transmitted via the friction clutch proposed here. Of course, the friction clutch can also be used for lower torques.

In particular, a friction radius, which designates the largest radius between the axis of rotation and the first connection, of less than 180 millimeters, in particular less than 170 millimeters, is required.

In particular, only small forces acting in the axial direction of between 4 and 10 kN [kilonewtons] are required to form the second connection.

In this way, the proposed friction clutch enables high torques to be transmitted with a compact design at the same time.

In the friction clutch proposed here, the second connection is established by moving the second part relative to the hub. The hub is particularly stationary with respect to the environment, for. B. arranged stationary on a shaft. This avoids the hub being prevented from shifting by sliding friction, so that, as with known friction clutches, the Establishing the second connection would at least be hindered. The hub can, however, also be arranged displaceably on a shaft.

In particular, the second part of the clutch disc is only connected to the hub via at least part of the switching means. Furthermore, the second part is positively connected to the first part with respect to the circumferential direction, but is arranged so that it can be displaced in the axial direction with respect to the first part. The second part can also be displaced along the axial direction with respect to the hub via the switching means. In particular, only spring forces counteract the displacement of the second part in the axial direction.

The first part and the second part are in particular connected to one another with respect to the axial direction, e.g. B. positively, but connected to one another in a displaceable manner.

Sliding friction occurring between the hub and a shaft does not have to be overcome in the proposed friction clutch, in particular, since the second connection is not established via the hub, but via the second part. The occurrence of sliding friction acting against the axial direction is in particular completely avoided in the proposed friction clutch (e.g.

B. when the hub is fixed on the shaft).

In particular, the switching means establishes the second connection only when a limit torque acting in a first circumferential direction is exceeded.

When the torque acting in the circumferential direction is below the limit torque, the friction clutch transmits the torque exclusively by frictional engagement (exclusively via the first connection) and when the limit torque is exceeded frictionally (via the first connection) and positively (additionally via the second connection). If the limit torque is undershot again (when closing and opening the friction clutch or the second connection, which may differ), the form-fitting second connection is released and the transmission is again purely frictionally only via the first connection. The switching torques defining the limit torque are particularly dependent on the internal spring forces or the internal friction of the switching means used, e.g. B. a leaf spring or a plate spring.

In particular, the positive second connection is only established when the friction clutch is operated in a pulling mode (positive torque is transmitted from the input side to the output side). In the case of overrun operation (a positive torque is transmitted from the output side to the input side), the second connection is in particular not established.

In particular, the switching means comprises at least one disc spring which is supported on the one hand on the second part and on the other hand on the hub in relation to the axial direction, the disc spring defining the limit torque.

The plate spring extends in particular in a ring around the axis of rotation. The plate spring counteracts a displacement of the second part along the axial direction with respect to the hub.

In particular, in a force-free first state of the friction clutch, the plate spring is arranged preloaded between the second part and the hub.

The disc spring is designed in particular with a pronounced high and low point, so that when a certain force acting in the axial direction is exceeded, which corresponds to a certain torque applied to the friction clutch (the limit torque), it travels a relatively long way along the axial direction covered. Depending on the length of the characteristic curve, a characteristic curve of the disc spring with pronounced high and low points creates the desired, relatively large, path for switching the second connection. So that before reaching the limit torque, as little or no distance as possible can be covered in the axial direction, the disc spring, z. B. be arranged biased via stops.

The long distance to be covered when the limit torque is exceeded until the second positive connection is established is used to securely establish the second connection. Should z. If, for example, the teeth forming the second connection cannot be found directly, there is a force acting in the axial direction, which ensures that a further relative rotation with respect to the circumferential direction can take place and the second connection is successively established via a bevel of the teeth of the teeth can.

In particular, the switching means comprises at least one leaf spring which extends at least along a circumferential direction and along the axial direction and is fastened with a first end to the hub and with a second end to the second part. In particular, a plurality of leaf springs are provided, which are arranged next to one another along the circumferential direction.

In particular, the at least one leaf spring extends between the two ends, on the one hand in the circumferential direction and on the other hand in the axial direction, so that the leaf spring exerts a torque-dependent shifting force acting in the axial direction on the second part when a torque is applied (in pulling operation of the friction clutch) . As an alternative to the leaf spring, the switching means comprises a ramp or a ramp device or a thread, by means of which a torque-dependent switching force acting in the axial direction can also be generated. The switching force enables the second part to be shifted relative to the first part, relative to the hub and relative to the counterpressure plate, so that the second connection can be made switchable and can be released again.

In all variants (leaf spring and ramp or thread) an inclination (of the leaf spring or the ramp or the thread) in relation to the circumferential direction, i.e. a course in the axial direction as well, enables a torque-dependent force to be generated in the axial direction, which ultimately leads to the establishment of the form-fitting second connection between the second part and the counterpressure plate or the input side and the output side. In particular, however, a ramp or a thread is not self-retaining. In the case of a self-retaining configuration (e.g. leaf spring), the form-fitting second connection remains in engagement until a thrust torque of a corresponding magnitude is applied. For the exact definition of the limit torque, the plate spring (or a leaf spring which works almost frictionlessly with respect to the plate spring) is preferably designed, which applies a counterforce against the switching direction on the second part. If the shifting force exceeds the counterforce, the second part is displaced in the axial direction in which the shifting force acts. Since the shifting force depends on the torque, the limit torque can be defined in this way. If the shifting force drops until it is smaller than the counterforce in terms of magnitude, the second part is shifted again, so that the positive transmission of torque is ended.

In particular, the first part and the second part are connected to one another in a form-fitting manner with respect to a circumferential direction and displaceable relative to one another along the axial direction via a spring plate. In this way, a torque acting in the circumferential direction can be transmitted via the clutch disk, the displacement of the second part in relation to the first part along the axial direction being made possible.

In particular, the second connection can be established via a first toothing of the counter-pressure plate and a second toothing of the second part. In particular, the teeth can interact in the manner of a freewheel, so that a torque can only be transmitted via the teeth in one direction. Alternatively, the teeth can also be designed so that a torque can be transmitted in each direction.

If the limit torque is not exceeded, the toothings are arranged at a distance from one another along the axial direction. Only when the limit torque is exceeded do the gears mesh with one another and form the second connection. The toothings can each be formed on surfaces pointing in the axial direction or on surfaces pointing in the radial direction. The formation on surfaces pointing in the axial direction is preferred, since in this way a successive construction of the second connection can be implemented at least more easily. In particular, in a force-free first state of the friction clutch, the second part is supported on the hub via a first stop relative to the axial direction. In this way, in particular, a pretensioning of the plate spring can be set in the force-free first state.

In particular, the hub has a flange that extends in a radial direction into the second part, with at least one leaf spring forming the switching means on a first end face of the flange pointing in the axial direction and a second one opposite the first end face End face a plate spring forming the switching means is arranged.

In particular, the first part and the second part overlap each other in relation to the axial direction. The second part is preferably arranged opposite the axial direction between the counter pressure plate and the first toothing on one side and the spring plate on the other side.

In particular, the second part has an annular flea space into which the flange of the hub extends. The flea space is delimited in relation to the axial direction by a first end wall and a second end wall. The disc spring is arranged between the first end wall and the flange of the hub. The at least one leaf spring is arranged between the flange of the hub and the second end wall. The first end of the leaf spring is attached to the first end face of the flange and the second end of the leaf spring is attached to the second end wall of the flea space.

The second toothing, which interacts with the first toothing of the counterpressure plate, is formed on the second end wall or on an outer circumferential surface, in any case outside the flea space.

In the proposed friction clutch, the second part is connected to the hub in particular by at least one (pre-corrugated) leaf spring. The angle of attack of the leaf spring creates a force acting in the axial direction when a torque load is applied, which force can move the second part and its second toothing into engagement with the counter-pressure plate and the first toothing. This is counteracted in particular by a plate spring and a spring plate, with the spring plate is responsible for the torque transmission between the friction lining or the first part and the second part. In particular, the spring plate is designed to be soft (that is, easily deformable) with respect to the axial direction, has a low spring constant and thus allows the second part to be shifted along the axial direction without a large counterforce. The disc spring is designed with a pronounced floch point and low point in such a way that it covers a relatively large distance along the axial direction at a specific axial force, which corresponds to a specific torque (the limit torque). So that no distance can be covered before the limit torque is reached, the disc spring is particularly preloaded with the aid of at least one stop.

In pulling mode, the friction clutch works in particular up to the defined limit torque (which can be predefined by the selection of the disc spring) via the first connection (i.e. via frictional engagement) until the second connection (i.e. the form fit) is switched on, which significantly increases the torque capacity. This connection of the second connection takes place in particular exclusively by torque from a drive train (that is, not via a separate actuating device). All frictional losses in the switching mechanism represent only minimal losses of drive power for the short time it is switched on. In particular, the friction clutch realizes the function described (i.e. switching on the second connection) only in one torque direction (pulling operation), since the additionally generated axial force is in the other Torque direction (thrust operation) is supported by the stop or causes a displacement of the second part along the axial direction away from the counter pressure plate or from the first toothing. Thus, in overrun mode, a torque is transmitted in particular only via the first connection.

A friction clutch arrangement is also proposed, at least comprising the described friction clutch and a shaft that extends along the axial direction, the hub of the friction clutch being arranged in particular stationary on the shaft opposite the axial direction. The hub can in particular also be arranged displaceably on the shaft. The proposed friction clutch can in particular be used for the switchable connection of a drive unit with a transmission or for the switchable connection of several drive units (e.g. internal combustion engine, electrical machines, generators, etc.).

In a configuration in which the friction clutch is detachably connected to a drive shaft of a drive unit, this friction clutch is also referred to as K0 [clutch zero]. In a configuration in which the friction clutch is detachably connected to a transmission shaft, this friction clutch is also referred to as K1 [clutch one].

A drive train is therefore proposed, at least comprising a drive unit and the described friction clutch. Here, the friction clutch is used in particular as a separating clutch (or K0 clutch).

The details and advantages disclosed for the friction clutch can be transferred and applied to the drive train and the friction clutch arrangement and vice versa.

The use of indefinite articles (“a”, “an”, “an” and “an”), especially in the patent claims and the description reproducing them, is to be understood as such and not as a numerical word. The terms or components introduced in this way are therefore to be understood in such a way that they are present at least once and, in particular, can also be present several times.

As a precaution, it should be noted that the numerals used here (“first”, “second”, ...) primarily (only) serve to distinguish between several similar objects, sizes or processes, so in particular no dependency and / or sequence of these objects, sizes or prescribe processes to each other. Should a dependency and / or sequence be necessary, this is explicitly stated here or it is obvious to a person skilled in the art when studying the specifically described embodiment. If a component can occur more than once ("at least one"), the description for one of these components can be apply equally to all or some of the majority of these components, but this is not mandatory.

The invention and the technical environment are explained in more detail below with reference to the accompanying figures. It should be pointed out that the invention is not intended to be restricted by the exemplary embodiments cited. In particular, unless explicitly stated otherwise, it is also possible to extract partial aspects of the facts explained in the figures and to combine them with other components and findings from the present description. In particular, it should be pointed out that the figures and in particular the size relationships shown are only schematic. Show it:

1: a first example of a motor vehicle with a friction clutch;

2: a second example of a motor vehicle with a friction clutch;

3: a friction clutch in a first state in a perspective view;

4: the friction clutch according to FIG. 3 after a

Limit torque in perspective view;

FIG. 5: the friction clutch according to FIG. 3 in a perspective view in section; FIG.

6: a diagram with a characteristic curve of the disk spring of the friction clutch according to FIG

Figures 3 to 5;

FIG. 7: the friction clutch according to FIG. 4 in a perspective view in section; FIG. and

Fig. 8: a diagram with a characteristic curve of the plate spring of the friction clutch according to

Figures 3 to 5 and 7.

1 shows a first example of a motor vehicle 3 with a friction clutch 1 and a drive train 2. This includes a drive unit 34, here an internal combustion engine, a friction clutch 1, a transmission 35 and at least a driven wheel 36. A torque can thus be generated by the drive unit 34 and transmitted to the at least one driven wheel 36 via the friction clutch 1 and the transmission 35. The friction clutch 1 is part of a friction clutch arrangement 45, in which the hub 11 of the friction clutch 1 can be arranged in a stationary manner on a shaft 46 with respect to the axial direction 4. The input side 8 is non-rotatably connected to the drive unit 34, and the output side 6 is non-rotatably connected to the transmission 35.

2 shows a second example of a motor vehicle 3 with a friction clutch 1 and a drive train 2. The drive unit 34 designed as an internal combustion engine is connected to a hybrid module 37 which, in addition to the friction clutch 1, also includes an electric drive 38. The hybrid module 37 is connected to a transmission 35 and the transmission 35 is connected to at least one driven wheel 36. The electric drive 38 is permanently coupled to the transmission 35. The drive unit 34 can be coupled and uncoupled via the friction clutch 1.

3 shows a friction clutch 1 in a first state 39 in a perspective view. FIG. 4 shows the friction clutch 1 according to FIG. 3 after a limit torque 17 has been exceeded in a perspective view. FIG. 5 shows the friction clutch 1 according to FIG. 3 in a perspective view in section. 6 shows a diagram with a characteristic curve 40 of the plate spring 18 of the friction clutch 1 according to FIGS. 3 to 5. FIG. 7 shows the friction clutch 1 according to FIG. 4 in a perspective view in section. 8 shows a diagram with a characteristic curve 40 of the plate spring 18 of the friction clutch 1 according to FIGS. 3 to 5 and 7. FIGS. 3 to 8 are described jointly below. Reference is made to the statements relating to FIGS. 1 and 2.

In the diagrams, the force 41 is plotted on the vertical axis and the path 42 is plotted on the horizontal axis. The characteristic curve 40 of the plate spring 18 is shown in each of the diagrams. The plate spring 18 is arranged pretensioned, so that initially a large force 41, the limit torque 17, is required to overcome a small path 42 (see FIG. 6). If the limit torque 17 is exceeded, only a small force 41 is required to overcome a large distance 42 until the second connection 15 is established (see FIG. 8). In the diagrams, the first curve 43 shows the curve acting in the axial direction 4 and the force 41 resulting from the applied torque. The second curve 44 shows the force 41 actually acting in the axial direction 4, reduced by the spring plate 23.

The friction clutch 1 has an axis of rotation 5 extending along an axial direction 4 and comprises a clutch disc 7 connected to an output side 6 of the friction clutch 1 and a counter pressure plate 9 connected to an input side 8 of the friction clutch 1 Clutch disks 7 can be displaced relative to one another along the axial direction 4 in order to produce a frictionally engaged first connection 10 formed between them. The output side 6 comprises a hub 11. The clutch disc 7 comprises a first part 12 and a second part 13, which can be displaced relative to one another along the axial direction 4 by a switching means 14.

The first part 12 forms the first connection 10. The second part 13 is connected to the hub 11 via the switching means 14. The second part 13 can be displaced by the switching means 14 along the axial direction 4 relative to the counter-pressure plate 9 for the switchable formation of a form-fitting second connection 15 between the second part 13 and the counter-pressure plate 9.

To produce the first connection 10, the clutch disc 7 and the counter-pressure plate 9 are pressed against one another. For this purpose, a conventional actuating device (not shown) is designed, which consists for example of a pressure pot with a corresponding hydraulic actuating cylinder or of a hydraulically actuated lever spring. It can also be actuated mechanically or by an electric motor.

A torque can be transmitted into the friction clutch 1 via the input side 8 as well as the output side 6. To transmit torque via the friction clutch 1, the input side 8 is connected to the output side 6 at least via the first connection 10 and, if necessary, also via the second connection 15.

In the case of the friction clutch 1 proposed here, the second connection 15 is established by displacing the second part 13 with respect to the hub 11. The hub 11 can be stationary with respect to the environment, e.g. B. be fixedly arranged on a shaft 46 (see Fig. 1).

The second part 13 of the clutch disc 7 is connected to the hub 11 only via part of the switching means 14, the leaf springs 19. Furthermore, the second part 13 is positively connected to the first part 12 with respect to the circumferential direction 20, but is arranged so that it can be displaced in the axial direction 4 with respect to the first part 12. The second part 13 can also be displaced along the axial direction 4 with respect to the hub 11 via the switching means 14. Only spring forces counteract the displacement of the second part 13 in the axial direction 4.

The switching means 14 establishes the second connection 15 only when a limit torque 17 acting in a first circumferential direction 16 is exceeded.

When the torque acting in the circumferential direction 20 is below the limit torque 17, the friction clutch 1 transmits the torque exclusively by frictional engagement (exclusively via the first connection 10, e.g. according to FIGS first connection 10) and form-fitting (additionally via the second connection 15, e.g. according to FIGS. 4 and 7). If the torque falls below the limit torque 17 again, the form-fitting second connection 15 is released and the transmission takes place again with a purely frictional connection only via the first connection 10.

The positive second connection 15 is only established when the friction clutch 1 is operated in a pulling mode (a positive torque is transmitted from the input side 8 to the output side 6). In the case of overrun operation (a positive torque is transmitted from the output side 6 to the input side 8), the second connection 15 is not established.

The switching means 14 comprises a disc spring 18 which, in relation to the axial direction 4, is supported on the one hand on the second part 13 (here on the first end wall 32 of the second part 13) and on the other hand on the hub 11, the disc spring 18 defining the limit torque 17. The disk spring 18 extends in a ring around the axis of rotation 5. The disk spring 18 counteracts a displacement of the second part 13 along the axial direction 4 with respect to the hub 11.

In a force-free first state 39 of the friction clutch 1 (e.g., FIGS. 3 and 5), the plate spring 18 is arranged preloaded between the second part 13 and the hub 11.

The plate spring 18 is designed with a pronounced high and low point so that it travels a relatively long distance when a certain force 41 acting in the axial direction 4 is exceeded, which corresponds to a certain torque applied to the friction clutch 1 (the limit torque 17) 42 travels along the axial direction 4 (see diagram in FIG. 8). Depending on the length of the characteristic curve, a characteristic curve 40 of the plate spring 18 with a pronounced high and low point generates the desired, relatively large path 42 for switching the second connection 15. Thus, before reaching the limit torque 17, a path 42 in the axial direction that is as small as possible, or even no path, is as small as possible 4 can be covered (see Fig. 6), the plate spring 18, for. B. be arranged biased via stops.

The long path 42 to be covered when the limit torque 17 is exceeded until the positive second connection 15 is established is used to reliably establish the second connection 15. Should z. If, for example, the teeth 24, 25 forming the second connection 15 cannot be found directly, there is a force 41 acting in the axial direction 4, which ensures that a further relative rotation with respect to the circumferential direction 20 (e.g. caused by the not torque to be transmitted) can take place and the second connection 15 can be established successively via a bevel of the teeth of the toothings 24, 25 (see FIG. 5).

The switching means 14 comprises leaf springs 19 which extend along a circumferential direction 20 and along the axial direction 4 and are fastened with a first end 21 on the hub 11 and with a second end 22 on the second part 13. A plurality of leaf springs 19 are provided, which are arranged next to one another along the circumferential direction 20. For the precise definition of the limit torque 17, the plate spring 18 is designed, which applies a counterforce to the second part 13 against the switching direction. If the shifting force exceeds the counterforce, the second part 13 is displaced in the axial direction 4 in which the shifting force acts. Since the shifting force is torque-dependent, the limit torque 17 can be defined in this way. If the shifting force falls until it is smaller in magnitude than the counterforce or the force 41, the second part 13 is shifted again, so that the positive transmission of torque via the second connection 15 is ended.

The first part 12 and the second part 13 are connected to one another in a form-fitting manner with respect to a circumferential direction 20 and displaceable relative to one another along the axial direction 4 via a spring plate 23. A torque acting in the circumferential direction 20 can thus be transmitted via the clutch disk 7, the displacement of the second part 13 relative to the first part 12 along the axial direction 4 being made possible.

The second connection 15 can be established via a first toothing 24 of the counter-pressure plate 9 and a second toothing 25 of the second part 13. The teeth 24, 25 interact in the manner of a freewheel, so that a torque can only be transmitted in one direction via the teeth 24, 25.

If the limit torque 17 is not exceeded, the toothings 24, 25 are arranged at a distance from one another along the axial direction 4 (see Fig.

5). Only when the limit torque 17 is exceeded do the toothings 24, 25 engage with one another and form the second connection 15. The toothings 24, 25 are each formed on surfaces pointing in the axial direction 4.

In a force-free first state 39 of the friction clutch 1, the second part 13 is supported on the hub 11 via a first stop 26 relative to the axial direction 4. In this way, a pretensioning of the plate spring 18 in the force-free first state 39 can be set. The hub 11 has a flange 27 which extends along a radial direction 28 into the second part 13, the leaf springs 19 forming the switching means 14 being arranged on a first end face 29 of the flange 27 pointing in the axial direction 4 and on a second end 30 opposite the first end 29 a plate spring 18 forming the switching means 14 is arranged

The first part 12 and the second part 13 overlap each other opposite the axial direction 4. The second part 13 is arranged opposite the axial direction 4 between the counter pressure plate 9 and the first toothing 24 on the one hand and the spring plate 23 on the other side. The second part 13 is arranged in the radial direction 28 inside the first part 12.

The second part 13 has an annular flea space 31 into which the flange 27 of the hub 11 extends. The flea space 31 is delimited in relation to the axial direction 4 by a first end wall 32 and a second end wall 33. The plate spring 18 is arranged between the first end wall 32 and the flange 27 of the hub 11. The leaf springs 19 are arranged between the flange 27 of the hub 11 and the second end wall 33. The first end 21 of each leaf spring 19 is attached to the first end face 29 of the flange 27 and the second end 22 of each leaf spring 19 is attached to the second end wall 33 of the flea space 31.

The second toothing 25, which interacts with the first toothing 24 of the counterpressure plate 9, is formed on the second end wall 33, outside the flea space 31.

Reference list

1 friction clutch

2 drive train

3 motor vehicle

4 axial direction

5 axis of rotation

6 Exit page

7 clutch disc

8 Entrance page

9 counter pressure plate

10 first connection

11 hub

12 first part

13 second part

14 switching means

15 second connection

16 first circumferential direction

17 limit torque

18 disc spring

19 leaf spring

20 circumferential direction

21 first end

22 second end

23 spring plate

24 first toothing

25 second toothing

26 first stop

27 flange

28 radial direction

29 first face

30 second face

31 Flea room 32 first front wall

33 second end wall

34 Drive unit

35 transmission

36 wheel

37 hybrid module

38 electric drive

39 first state

40 characteristic

41 power

42 way

43 first corner

44 second curve

45 Friction Clutch Assembly

46 wave

Claims

1. Friction clutch (1), in particular for a drive train (2) of a motor vehicle (3), with an axis of rotation (5) extending along an axial direction (4), comprising at least one with an output side (6) of the friction clutch (1) ) connected, clutch disc (7) and a counter-pressure plate (9) connected to an input side (8) of the friction clutch (1), which can be displaced relative to one another along the axial direction (4) to produce a frictional first connection (10) between them are, wherein the output side (6) comprises a hub (11); wherein the clutch disc (7) comprises at least a first part (12) and a second part (13) which can be displaced relative to one another by switching means (14) along the axial direction (4), the first part (12) being the first Forms connection (10), the second part (13) being connected to the hub (11) via the switching means (14); wherein the second part (13) can be displaced by the switching means (14) along the axial direction (4) relative to the counter pressure plate (9) for the switchable formation of a form-fitting second connection (15) between the second part (13) and the counter pressure plate ( 9).

2. Friction clutch (1) according to claim 1, wherein the switching means (14) produces the second connection (15) only when a limit torque (17) acting in a first circumferential direction (16) is exceeded.

3. Friction clutch (1) according to claim 2, wherein the switching means (14) comprises at least one plate spring (18) which is supported on the one hand on the second part (13) and on the other hand on the hub (11) in relation to the axial direction (4) , wherein the plate spring (18) defines the limit torque (17).

4. Friction clutch (1) according to claim 3, wherein the plate spring (18) is arranged preloaded in a force-free first state (39) of the friction clutch (1) between the second part (13) and the hub (11).

5. friction clutch (1) according to any one of the preceding claims, wherein the switching means (14) comprises at least one leaf spring (19) which extends at least along a circumferential direction (16, 20) and along the axial direction (4) and with a first End (21) is attached to the hub (11) and with a second end (22) to the second part (13).

6. friction clutch (1) according to any one of the preceding claims, wherein the first part (12) and the second part (13) via a spring plate (23) relative to a circumferential direction (20) positively and along the axial direction (4) displaceable relative to one another are connected to each other.

7. friction clutch (1) according to any one of the preceding claims, wherein the second connection (15) via a first toothing (24) of the counter-pressure plate (9) and a second toothing (25) of the second part (13) can be produced.

8. Friction clutch (1) according to one of the preceding claims, wherein the second part (13) in a force-free first state (39) of the friction clutch (1) via a first stop (26) opposite the axial direction (4) on the hub (11) is supported.

9. friction clutch (1) according to any one of the preceding claims, wherein the hub (11) has a flange (27) which extends along a radial direction (28) into the second part (13), wherein at one, in the The first end face (29) of the flange (27) pointing in the axial direction (4) has at least one leaf spring (19) forming the switching means (14) and, on one of the first end face (29) opposite the second end face (30), the switching means ( 14) forming plate spring (18) is arranged.

10. Friction clutch arrangement (45) comprising a friction clutch (1) according to one of the preceding claims and a shaft (46) which extends along the axial direction (4), the hub (11) being stationary relative to the axial direction (4) is arranged on the shaft (46).