DE102020114798B3 - Friction clutch for the frictional and positive transmission of torque - Google Patents

Abstract

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 connected to an output side (6) of the friction clutch (1) , 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, 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 a 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).

Description

The present invention relates to a friction clutch according to the preamble of claim 1, in particular for a drive train of a motor vehicle, which allows a frictional and positive transmission for high torques.

From the DE 10 2018 122 385 A1 a multi-disc clutch is known 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, not pre-published DE 10 2020 104 023.7 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 locking. 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.

From the US 2018/0031052 A1 a friction clutch is known which can be read on the preamble of claim 1.

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-plate clutches and multi-plate clutches for high torques, whereby the positive 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 specified and explained in more detail in the description, 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 disk 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 disk 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 further 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 form-fitting one second connection 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 can be used to transmit high torques 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 in particular stationary with respect to the environment, for. B. fixedly arranged on a shaft. This avoids the hub being prevented from being displaced by sliding friction, so that, as in the case of known friction clutches, the establishment of 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 as to be displaceable 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 in relation to the axial direction is in particular completely avoided in the proposed friction clutch (for example if the hub is arranged in a stationary manner on the shaft).

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 (possibly different when closing and opening the friction clutch or the second connection) is again undershot, 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 (a 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 plate 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, the one corresponds to a certain torque applied to the friction clutch (the limit torque), travels a relatively large distance along the axial direction. Depending on the length of the characteristic curve, a characteristic curve of the disc spring with a pronounced high and low point generates 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 positive second connection is established is used to reliably 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, several 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 that 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 falls 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 disc, 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. So that in particular a bias of the disc spring can be set in the force-free first state.

In particular, the hub has a flange which extends along 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 counterpressure plate and the first toothing on one side and the spring plate on the other side.

In particular, the second part has an annular cavity into which the flange of the hub extends. The cavity 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 cavity.

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 cavity.

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, the spring plate being 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 displaced along the axial direction without a large counterforce. The disc spring is designed with a pronounced high and low point in such a way that it covers a relatively large distance along the axial direction at a certain axial force, which corresponds to a certain 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 predetermined 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 added, 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 friction 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 via 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 which 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 KO clutch).

The details and advantages disclosed for the friction clutch can be 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 differentiate 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 required, this is explicitly stated here or it is obvious to the person skilled in the art when studying the specifically described embodiment. If a component can occur several times (“at least one”), the description of one of these components can apply equally to all or part of the majority of these components, but this is not mandatory.

• 1: ein erstes Beispiel eines Kraftfahrzeugs mit einer Reibkupplung;
• 2: ein zweites Beispiel eines Kraftfahrzeugs mit einer Reibkupplung;
• 3: eine Reibkupplung in einem ersten Zustand in perspektivischer Ansicht;
• 4: die Reibkupplung nach 3 nach Überschreiten eines Grenzdrehmoments in perspektivischer Ansicht;
• 5: die Reibkupplung nach 3 in perspektivischer Ansicht im Schnitt;
• 6: ein Diagramm mit einer Kennlinie der Tellerfeder der Reibkupplung nach 3 bis 5;
• 7: die Reibkupplung nach 4 in perspektivischer Ansicht im Schnitt; und
• 8: ein Diagramm mit einer Kennlinie der Tellerfeder der Reibkupplung nach 3 bis 5 und 7.

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;
• 4th : the friction clutch after 3 after exceeding a limit torque in a perspective view;
• 5 : the friction clutch after 3 in a perspective view in section;
• 6th : a diagram with a characteristic curve of the disc spring of the friction clutch according to 3 to 5 ;
• 7th : the friction clutch after 4th in a perspective view in section; and
• 8th : a diagram with a characteristic curve of the disc spring of the friction clutch according to 3 to 5 and 7th .

1 shows a first example of a motor vehicle 3 with a friction clutch 1 and a powertrain 2 . This includes a drive unit 34 , here an internal combustion engine, a friction clutch 1 , a transmission 35 and at least one driven wheel 36 . A torque can come from the drive unit 34 generated and via the friction clutch 1 and the transmission 35 on the at least one driven wheel 36 be transmitted. The friction clutch 1 is part of a friction clutch arrangement 45 where the hub 11 the friction clutch 1 opposite to the axial direction 4th stationary on a shaft 46 can be arranged. The entry page 8th is non-rotatable with the drive unit 34 , the home page 6th rotatably with the gear 35 connected.

2 shows a second example of a motor vehicle 3 with a friction clutch 1 and a powertrain 2 . The drive unit designed as an internal combustion engine 34 is with a hybrid module 37 connected that next to the friction clutch 1 also an electric drive 38 includes. The hybrid module 37 is there with a gear 35 and the transmission 35 with at least one driven wheel 36 connected. The electric drive 38 is permanent with the gearbox 35 coupled. The drive unit 34 can via the friction clutch 1 can be coupled and uncoupled.

3 shows a friction clutch 1 in a first state 39 in perspective view. 4th shows the friction clutch 1 to 3 after exceeding a limit torque 17th in perspective view. 5 shows the friction clutch 1 to 3 in perspective view in section. 6th shows a diagram with a characteristic 40 the disc spring 18th the friction clutch 1 to 3 to 5 . 7th shows the friction clutch 1 to 4th in perspective view in section. 8th shows a diagram with a characteristic 40 the disc spring 18th the friction clutch 1 to 3 to 5 and 7th . The 3 to 8th are described together below. On the remarks too 1 and 2 is referred.

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

The friction clutch 1 has one extending along an axial direction 4th extending axis of rotation 5 and includes one, with an exit side 6th the friction clutch 1 connected, clutch disc 7th and one, with an entry side 8th the friction clutch 1 connected, counter pressure plate 9 . The counter pressure plate 9 and the clutch disc 7th are along the axial direction 4th for producing a frictional connection formed between them 10 displaceable relative to each other. The starting page 6th includes a hub 11 . The clutch disc 7th comprises a first part 12th and a second part 13th by a switching means 14th along the axial direction 4th are displaceable relative to each other. The first part 12th forms the first connection 10 out. The second part 13th is via the switching means 14th with the hub 11 connected. The second part 13th is through the switching means 14th along the axial direction 4th relative to the counter pressure plate 9 displaceable for the switchable formation of a form-fitting second connection 15th between the second part 13th and the counter pressure plate 9 .

To make the first connection 10 become the clutch disc 7th and the counter pressure plate 9 pressed against each other. 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 both on the input side 8th as well as the exit page 6th into the friction clutch 1 be transmitted. For the transmission of torque via the friction clutch 1 becomes the entry page 8th with the exit side 6th at least over the first connection 10 and, if necessary, also via the second connection 15th connected.

With the friction clutch proposed here 1 the second connection is established 15th by relocating the second part 13th opposite the hub 11 . The hub 11 stationary with respect to the environment, e.g. B. stationary on a shaft 46 (please refer 1 ) be arranged.

The second part 13th the clutch disc 7th is only about part of the switching means 14th who have favourited leaf springs 19th , with the hub 11 connected. Next is the second part 13th opposite to the circumferential direction 20th form-fitting with the first part 12th , but in the axial direction 4th relocatable compared to the first part 12th arranged. Via the switching means 14th is the second part 13th also along the axial direction 4th opposite the hub 11 relocatable. Only spring forces of the displacement of the second part act here 13th in the axial direction 4th opposite.

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

The friction clutch 1 so transmits at one in the circumferential direction 20th acting torque below the limit torque 17th the torque is exclusively frictionally engaged (exclusively via the first connection 10 , e.g. B. according to 3 and 5 ) and when the limit torque is exceeded 17th frictionally engaged (via the first connection 10 ) and form-fitting (also via the second connection 15th , e.g. B. according to 4th and 7th ). Becomes the limit torque 17th If it falls below this again, the form-fitting second connection is released 15th and the transmission is again purely frictional, only via the first connection 10 .

The form-fitting second connection 15th is only produced when the friction clutch 1 in a pulling operation (a positive torque is obtained from the input side 8th to the exit page 6th transmitted) is operated. In the case of overrun operation (a positive torque is applied from the output side 6th on the entry page 8th transmitted) the second connection 15th not made.

The switching means 14th includes a disc spring 18th that are opposite to the axial direction 4th on the one hand on the second part 13th (here on the first front wall 32 of the second part 13th ) and on the other hand on the hub 11 supported, the disc spring 18th the limit torque 17th Are defined.

The disc spring 18th extends annularly around the axis of rotation 5 . The disc spring 18th acts to relocate the second part 13th along the axial direction 4th opposite the hub 11 opposite.

The disc spring 18th is in a powerless first state 39 the friction clutch 1 (e.g. 3 and 5 ) between the second part 13th and the hub 11 arranged prestressed.

The disc spring 18th is designed with a pronounced high and low point, so that when a certain point is exceeded in the axial direction 4th acting force 41 that a specific at the friction clutch 1 applied torque (the limit torque 17th ) corresponds to a relatively long way 42 along the axial direction 4th (see diagram in 8th ). A characteristic 40 the disc spring 18th with a pronounced high and low point generates the desired, relatively large, path depending on the length of the characteristic curve 42 to switch the second connection 15th . So before reaching the limit torque 17th as little or no way as possible 42 in the axial direction 4th can be covered (see 6th ), the disc spring can 18th , e.g. B. be arranged biased via stops.

When the limit torque is exceeded 17th until the positive second connection is established 15th great way to be covered 42 is used for the second connection 15th safe to manufacture. Should z. B. the, the second connection 15th forming gears 24 , 25th cannot find directly, one lies in the axial direction 4th Acting force 41 which ensures that a further relative rotation with respect to the circumferential direction 20th (e.g. caused by the torque that is not to be transmitted) and via a bevel of the teeth of the toothing 24 , 25th (please refer 5 ) the second connection 15th can be produced successively.

The switching means 14th includes leaf springs 19th extending along a circumferential direction 20th and along the axial direction 4th extend and with a first end 21 at the hub 11 and with a second end 22nd on the second part 13th are attached. There are several leaf springs 19th provided along the circumferential direction 20th are arranged side by side.

For the exact definition of the limit torque 17th is the disc spring 18th formed that a counterforce against the switching direction on the second part 13th brings up. If the switching force exceeds the counterforce, the second part becomes 13th in the axial direction 4th , in which the shifting force acts, is shifted. Since the shifting force depends on the torque, the limit torque can 17th To be defined. The shifting force decreases until it is smaller in terms of amount than the counterforce or the force 41 is, will be the second part 13th relocated again so that the positive transmission of torque via the second connection 15th is terminated.

The first part 12th and the second part 13th are over a spring plate 23 against a circumferential direction 20th positively and along the axial direction 4th connected to one another displaceably relative to one another. This can use the clutch disc 7th one in the circumferential direction 20th acting torque are transmitted, with the displacement of the second part 13th compared to the first part 12th along the axial direction 4th is made possible.

The second connection 15th is about a first interlocking 24 the counter pressure plate 9 and a second toothing 25th of the second part 13th manufacturable. The teeth 24 , 25th work together in the manner of a freewheel, so that a torque is only applied to the teeth in one direction 24 , 25th is transferable.

The teeth 24 , 25th are when the limit torque 17th is not exceeded along the axial direction 4th arranged at a distance from each other (see 5 ). Only when the limit torque 17th is exceeded, the teeth come 24 , 25th engage with each other and form the second connection 15th out. Here are the gears 24 , 25th each on in the axial direction 4th facing surfaces.

The second part 13th supports itself in a force-free first state 39 the friction clutch 1 about a first stop 26th opposite to the axial direction 4th at the hub 11 from. This can preload the disc spring 18th in the powerless first state 39 can be set.

The hub 11 has a flange 27 on, which extends along a radial direction 28 in the second part 13th extends into it, at one, in the axial direction 4th pointing first face 29 of the flange 27 die, the switching means 14th forming, leaf springs 19th are arranged and on one of the first end face 29 opposite second end face 30th one, the switching means 14th forming, disc spring 18th is arranged

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

The second part 13th has an annular cavity 31 into which the flange is located 27 the hub 11 extends into it. The cavity 31 becomes opposite to the axial direction 4th through a first front wall 32 and a second end wall 33 limited. Between the first front wall 32 and the flange 27 the hub 11 is the disc spring 18th arranged. Between the flange 27 the hub 11 and the second end wall 33 are the leaf springs 19th arranged. The first ending 21 every leaf spring 19th is on the first face 29 of the flange 27 and the second end 22nd every leaf spring 19th on the second front wall 33 of the cavity 31 attached.

On the second front wall 33 , outside the cavity 31 , is the second toothing 25th formed with the first toothing 24 the counter pressure plate 9 cooperates.

List of reference symbols

1

Friction clutch

2

Powertrain

3

Motor vehicle

4th

axial direction

5

Axis of rotation

6th

Exit page

7th

Clutch disc

8th

Entry page

9

Counter pressure plate

10

first connection

11

hub

12th

first part

13th

second part

14th

Switching means

15th

second connection

16

first circumferential direction

17th

Limit torque

18th

Disc spring

19th

Leaf spring

20th

Circumferential direction

21

first end

22nd

second end

23

Spring plate

24

first toothing

25th

second toothing

26th

first stop

27

flange

28

radial direction

29

first face

30th

second face

31

cavity

32

first front wall

33

second front wall

34

Drive unit

35

transmission

36

wheel

37

Hybrid module

38

Electric drive

39

first state

40

curve

41

force

42

path

43

first turn

44

second curve

45

Friction clutch assembly

46

wave

Claims (9)

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 connected to an output side (6) of the friction clutch (1) , 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, 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 along the axial direction (4) by switching means (14), 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), characterized in that the switching means (14) establishes the second connection (15) only when a limit torque (17) acting in a first circumferential direction (16) is exceeded. Friction clutch (1) Claim 1 , wherein the switching means (14) comprises at least one disc spring (18) which is supported against the axial direction (4) on the one hand on the second part (13) and on the other hand on the hub (11), the disc spring (18) the limit torque (17) defined. Friction clutch (1) Claim 2 , wherein the plate spring (18) is arranged preloaded between the second part (13) and the hub (11) in a force-free first state (39) of the friction clutch (1). Friction clutch (1) according to 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 is fastened with a first end (21) to the hub (11) and with a second end (22) to the second part (13). Friction clutch (1) according to one of the preceding claims, wherein the first part (12) and the second part (13) are positively connected to one another via a spring plate (23) relative to a circumferential direction (20) and displaceable relative to one another along the axial direction (4) are. Friction clutch (1) according to one of the preceding claims, wherein the second connection (15) can be produced via a first toothing (24) of the counter-pressure plate (9) and a second toothing (25) of the second part (13). 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 to the axial direction (4) on the hub (11) ) is supported. Friction clutch (1) according to 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), in one, in the axial direction (4) the first end face (29) of the flange (27) facing at least one leaf spring (19) forming the switching means (14) and one on a second end face (30) opposite the first end face (29), the switching means (14) forming, plate spring (18) is arranged. 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 on the opposite to the axial direction (4) Shaft (46) is arranged.

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