DE4306505B4 - friction clutch - Google Patents

Abstract

Friction clutch, in particular for motor vehicles, with a pressure plate (3) which is connected to a housing (2) in a rotationally fixed but axially displaceable manner, at least one actuating means (4b) and an energy accumulator (4) being provided between the housing and the pressure plate the pressure plate can be acted upon in the direction of a clutch disc (8) which can be clamped between this and a counterpressure plate, such as a flywheel (6), an adjustment mechanism (17, 34) which compensates at least for the wear of the friction linings (7) of the clutch disc being present, which a wear compensation device (16) provided between the actuating means or force accumulator and the pressure plate, which in each case assumes an axial setting between the actuating means or force accumulator on the one hand and the pressure plate on the other hand, which corresponds to the state of wear of the friction linings, which corresponds to the current state of wear of the friction linings when reached In the setting, the wear compensation device is limited in its readjustment function by at least one wear sensor (17) provided on the pressure plate, the wear sensor having at least one wear sensor component (22) which, when wear occurs and by contact with an axially fixed component with a counterstop area (33) lifts off a stop area (32) of the wear compensation device and, in the event of a disengagement process following wear, the wear compensation device is adjusted until the stop area of the same rests on the counter-stop area of the wear sensor component (22).

Description

The invention relates to a friction clutch, especially for Motor vehicles with a pressure plate that is non-rotatable but axial is displaceably connected to a housing, between casing and pressure plate at least one actuating means and an energy accumulator are effective about the pressure plate towards one between this and one Counter pressure plate, such as a flywheel, clampable clutch disc can be acted upon, wherein at least the wear of the friction linings of the clutch disc compensatory readjustment is available.

Self-adjusting clutches, in which an adjustment according to the lining wear is to be carried out, are known, for example from DE 29 20 932 C2 and the DE 35 18 781 A1 ,

With these couplings the Wear adjustment via a axially adjustable support between pressure plate and disc spring, the edition over Ramps on the pressure plate is supported and by rotating in the circumferential direction relative to the pressure plate in Is adjusted in the direction of the disc spring or by wedges between Inclined surfaces attack the pressure plate or the support, moved accordingly become.

To determine the wear of the lining are in both versions several between the pressure plate and the flywheel or the clutch cover effective sensor elements are provided when the clutch is closed adjusted according to the wear of the lining become and when disengaged Limit the lifting of the pressure plate to a defined value.

It is assumed that When the clutch is new, the disc spring when disengaging the Coupling in the area of the support executes exactly the same lifting path as the pressure plate. If lining wear occurs, the pressure plate moves towards the flywheel. The disc spring must be in this state of wear in the area of the support, make a path that is larger by wear than the pressure plate, thus the support axially according to the game then arising can be adjusted in the direction of the disc spring.

A reenactment of this kind can not reliable in practice work because the lifting movement of the disc spring even at constant declutching scattered relatively strongly on the spring washers and also very size Ausrückwegstreuungen at the release bearing occur. In addition, when setting the release system, z. B. with mechanical release system, Can make mistakes by For example, too little play or too much preload between disengagement and Belleville spring is set. This results entirely for the clutch different operating points.

When using a self-adjusting release system, z. B. hydraulic system with master and slave cylinders, can System at all don't work over there the service life always the same release path occurs on the clutch and then at all is not adjusted, provided the lifting movement of the disc spring in the area of the support less than or equal to the printing plate movement is. In contrast, the plate spring makes a larger lifting movement than that Pressure plate, so with each release actuation independent of Lining wear adjusted, and the clutch would be totally adjusted after a short time.

Another problem with the known self-adjusting clutches is that the pressure plate can be excited by natural resonance vibrations and thereby by the diaphragm spring axially lifts, causing the adjustment device to engage the clutch can completely adjust.

With a self-adjusting clutch according to DE 35 18 781 A1 in which a wear compensation device is provided between the plate spring and the pressure plate, which, depending on wear, can automatically expand axially, the size or limitation of the expansion depends on a concern for the plate spring. If wear occurs on the friction linings of the clutch disc, the pressure plate moves away from the plate spring, whereby a spring mechanism axially expands the wear compensation device, as stated above, so that the contact point of the wear compensation device on the plate spring remains in contact with the plate spring. With this clutch, the problem of an unwanted readjustment arises from a momentary lifting of the disc spring from the wear compensation device, which can result in an uncontrolled, automatic readjustment of the wear compensation device.

Friction clutches according to the DE 29 20 932 C2 have the same operating principle with regard to wear compensation as in connection with the DE 35 18 781 A1 described.

Through the PCT publication WO 91/10074 A1 , corresponds DE 4092382 T1 A self-adjusting friction clutch is also known, in which two axially displaceable support rings are provided in the pressure plate, which are arranged parallel or concentrically to one another and are pressed into corresponding receptacles of the pressure plate by the plate spring provided for actuating the clutch. If now due to wear of the friction linings, the plate spring in the engaged position of the clutch one in the 2 of the publication, the interior of the

Support rings pressed out of its receptacle in the pressure plate and thus takes a position defined by the position of the plate spring in be pull on the pressure plate. In this position of the displaced, inner support ring, the latter has moved axially away from the position of the other support ring, approximately by the size of the wear of the friction linings. If, in a subsequent disengagement process, the plate spring assumes the opposite inclined position compared to the above-described inclined position, the other, outer bearing ring is released by the plate spring due to this inclined position and can move axially out of its receptacle until it hits a stop on the inner bearing ring , which is supported on the plate spring, starts, which completes the adjustment. The clutch is adjusted depending on the respective position and the pressure of the disc spring. If for some reason the pressure of the disc spring is currently reduced or, as in the case of a disengagement, is completely eliminated, which is unavoidable, for example, even when the pressure plate is subject to unavoidable axial or vibrating vibrations, the thrust rings can experience a greater displacement than this would be necessary due to wear, which then leads to incorrect adjustment of the clutch. The disadvantage of this known clutch is therefore that its flawless operation depends on the constant concern and pressure of the disc spring on the thrust rings. A friction clutch works according to the same principle JP 63-270925 A ,

The JP 3-53628 U discloses a clutch in the, as in the FR 2 606 477 A1 , A support ring is arranged axially displaceable. This ring is over a bracket 23 axially connected to the plate spring. When the clutch disengages, the pressure plate moves away from the clutch disc through the pins 27 to the amount L2 ( 1 ) limited. If the diaphragm spring disengages further, the support ring becomes 17 by means of the bracket 23 pulled away from the pressure plate by the plate spring. It penetrates into a wedge-shaped gap 20 a ring wedge 21 one that is on the one hand under spring tension and on the other hand also under considerable centrifugal force, especially at high speed. The ring wedge pushes the support ring and the pressure plate apart as far as possible. This adjustment has no defined limit. Rather, it depends on the size of the disengagement path of the disc spring and, when the disc spring stops on the counter-stop of the clutch cover, on the strong force that occurs in the cover and the associated deformation of the cover and the large sum of the individual tolerances of the components. In addition, the known shaking of the coupling is also possible here.

The US 5,069,322 discloses a self-adjusting clutch with a sensor disk 36 for wear adjustment depending on the axial pressure plate position. The pressure plate is fastened to the cover in an elastic and axially movable manner using leaf springs. When the clutch is disengaged, the pressure plate is pulled back over the leaf springs. When disengaging, the pressure plate always assumes roughly the same position (with a greater or lesser spread), regardless of the wear on the pad, since the pressure plate path is not adjusted depending on wear. Wear-dependent readjustment is therefore not possible. There is also no adjustment limitation to the lining wear, since there is no functional wear detection. The pressure plate can either be retracted so far that the levers are not lifted off the adjusting ring, so that it cannot be adjusted, or with less preloaded leaf springs, they pull the pressure plate back to a lower height. The levers are raised 8b from the adjusting ring 20 from and this can adjust up to the sensor disc 36 at the stop 37 is applied, but the pressure plate is pulled back to the same height by the leaf springs, so that the contact of the sensor disc with the stop always occurs simultaneously with the lifting of the levers 8b from the ring 20 he follows. In the event of wear, no further readjustment can be made after the one-time setting described above. In addition, this coupling construction also shakes itself automatically.

The DE 29 16 755 A1 discloses a self-adjusting clutch with a plate spring. The wear sensor is formed here by an actuating drum rotated by a disk spring lobe, which is rotated back and forth by the disk spring lobe when the clutch is actuated. When the clutch is engaged and the corresponding pivotal movement of the plate spring is carried out, the actuation drum is rotated and during the subsequent disengagement, the actuation drum is rotated in the opposite direction, with a one-way clutch rotating a worm body. The abutment ring which can be acted upon by the plate spring is rotated against the pressure plate and the height between the pressure plate friction surface and the plate spring is increased by means of a ramp device. The adjustment of the clutch depends on the size of the pivoting of the plate spring or disengagement position and the disengagement stroke. It is therefore at least not possible to readjust exactly according to the wear of the lining.

Through the DE 28 36 840 A1 an automatic wear compensation device for a friction clutch actuated by means of a diaphragm spring has been excited. Here, a compensating ring, which is rotatable relative to the thrust washer and supported by ramps, is rotated in accordance with the wear. This is done via a two-armed lever rotatably mounted on the thrust washer, which rests on the compensating ring via one arm and is supported on the flywheel via the second arm in such a way that it depends on the loading wear of the thrust washer undergoes a twist which is passed on to the compensating ring in accordance with the existing lever ratio. However, such a device has the disadvantage that the adjustment takes place when the friction clutch is closed, practically in the end region of the engagement path, especially when the clutch disk is already clamped between the flywheel and the pressure disk. This in turn means that practically the full contact pressure of the disc spring prevents the compensation ring from rotating, which prevents proper functioning.

The present invention was the Task based on friction clutches of the type mentioned and according to the state the technology regarding to improve the function and lifespan. In particular, by the invention one against improved readjustment precautions created in the prior art become. The adjustment precaution should be simple in structure and require a small installation space. Furthermore, the activity Such friction clutches required release force curve over their Life span remain practically constant. The friction clutches according to the invention are also intended be manufactured in a particularly simple and economical manner.

According to the invention, this will do achieved that between those intended for engaging and disengaging the friction clutch actuating means and the pressure plate or between the energy accumulator and the pressure plate a wear compensation device is provided, each corresponding to the state of wear of the friction linings axial adjustment between actuating means or energy storage on the one hand and pressure plate on the other, when reaching the current state of wear of the friction linings Setting the wear compensation device by at least one wear sensor provided on the pressure plate in its adjustment function is limited, the wear sensor at least a wear sensor component owns that when wear occurs and by contact with one axially fixed component with a counter stop area from a stop area the wear compensation device takes off, and in the event of a disengagement following wear the setting of the wear compensation device takes place until the stop area of the same on the counter-stop area of the wear sensor component again.

For the function and structure of the friction clutch can be particularly special be advantageous if an axially braced between the housing and the pressure plate A plate spring is provided which can be pivoted about an annular support carried by the housing is a ring-shaped, has the basic body forming the energy store, of which radially Inwardly extending tongues to form actuators go out and the wear compensation device is arranged between the plate spring and the pressure plate.

The limiting means of the compensation device can in a simple manner by at least one wear sensor or wear sensor formed be the one opposite at least the pressure plate has a wearable sensor component that can be moved through the system limits the release travel of the pressure plate on an axially fixed component.

That with a wear sensor component of a wear sensor interacting axially fixed component can be by a clutch housing or a counter pressure plate, z. B. a flywheel.

For a perfect balance wear of the lining to ensure, it can be particularly advantageous if the wear sensor component across from the pressure plate is held axially displaceable. For that it can Wear sensor component either indirectly or directly with the pressure plate via an automatic or automatic adjustment device and connected by system on at least one axially fixed component in relation to the pressure plate the wear of the lining shifted become. This shift conveniently takes place during a Coupling process instead. The contact area for the wear sensor component can on the clutch housing and / or be provided on the counter pressure plate.

The compensation device can while a disengagement process are relieved, which, if there is wear on the pads Compensation device can adjust until this adjustment by cooperation of an adjusting element of the compensation device the wear sensor component is limited.

Advantageously, more than one Distributed wear sensors are provided around the circumference of the pressure plate, the one in disengagement State of the friction clutch against the axis of rotation of the Ensure friction clutch non-impact positioning of the pressure plate.

The wear sensor components can advantageously have a contact area which interacts with a counter-contact area of a compensation component or an adjusting element of the compensation device when the friction clutch is disengaged. The wear sensor components can advantageously with an axially displaceable component, for. B. the pressure plate, can be connected via an automatic or automatic adjustment device. Such an adjustment device can, for. B. generated by means of a frictional connection between the wear sensor component and the pressure plate are, the frictional engagement being overcome when a certain force is exceeded during a coupling process, as a result of which the wear sensor component is adjusted relative to the pressure plate in accordance with the current wear that has occurred. However, the readjustment can also be carried out using a mechanism similar to a freewheel, which allows the wear sensor component to be readjusted with respect to the pressure plate during a coupling process, whereas when the friction clutch is disengaged, the wear sensor component is blocked by the measure with respect to the pressure plate.

It can be advantageous if that Wear sensor component is secured against rotation on the printing plate.

For the function of the readjustment can be useful if the wear sensor component has a radially extending counterstop area on which after wear and tear Setting a wear compensation component the wear compensation device can be brought into contact with a stop area. Can be advantageous it be when the wear compensation device at least one ring-shaped Contains component with ramp. The at least one wear sensor component can have a radially extending area to rest on a lid-fixed Have area by means of which a wear corresponding Positioning of the wear sensor component towards the Pressure plate can be done.

The friction clutch can be used as a so-called "pressed" clutch or as so-called "drawn" coupling formed his.

A particularly simple and reliable Establishment of an adjustment precaution to compensate for the lining wear within a friction clutch can be ensured that the Compensation device a support component for the energy store, such as in particular a disc spring, and between this support component and the pressure plate, a compensation device is provided, which at move out the friction clutch an automatic wear adjustment of the support component and self-locking when engaging the clutch is. This means that the compensation device is released when the support component is relieved is and when loading the support component, the compensation device maintains their attitude, so is blocked or is. Therefor it can be advantageous if the support component axially in the direction displaceable away from the pressure plate, in the axial direction on the Pressure plate is lockable. The compensation device can when disengaging the friction clutch freewheel act when engaging the clutch, however, should be self-locking.

A particularly simple structure of the Compensation device can be used by using an annular component be guaranteed to form a compensation component. The ring-shaped component can over Ramps opposite supported the pressure plate his. These ramps can be used Counter ramps cooperate, these advantageously over at least a spring element can be clamped to each other. The ramps and the counter ramps can through individual components, e.g. wedge-like components, arranged between the pressure plate and the annular component could be. However, at least one of these ramp groups can be used directly on the ring-shaped Component or the pressure plate be molded. A simple structure the friction clutch can be achieved in that the annular component as a hollow sheet metal part with a U-shaped Cross-section is formed, the free space of the component over the Circumferentially distributed and the ramp-forming wedge-like components added are. These wedge-like components can be more advantageous Way with the annular Component be non-rotatable. An advantageous embodiment of the compensation device can be achieved in that the wedge-like components compared to the annular component guided axially displaceable are. The counter ramps can also by wedge-shaped Components are formed, at least partially in the ring-shaped compensation component axially engage enclosed space and opposite the Pressure plate and the compensation component can be rotated. there it can also be advantageous if the compensation component across from the pressure plate is held in a rotationally fixed manner. An automatic re-adjustment to ensure the compensation device, the Counter ramps in the direction of the ramps must be spring loaded. This spring loading can be created between the ramps and the counter ramps Components tensioned springs, e.g. Coil springs, these also in the annular space of the compensation component recorded and designed in an advantageous manner as compression springs could be. The components forming the counter ramps can be axially between the Ramp-forming components and the annular compensation component at least partially included. To a perfect bracket and leadership of the to ensure the springs tensioning the ramps and counter ramps, it can be advantageous if at least the end regions of this Springs through which the components forming the ramps and counter ramps are guided. Therefor can the corresponding component approaches or projections have at least in the end regions of the prestressed Extend feathers. These springs can each between one with the annular support component Non-rotatable, but axially displaceable coupled wedge-like component and one that is adjacent in the circumferential direction and rotatable with respect to the support component wedge-like component can be provided.

The ramps and / or counter ramps forming components can are easily made of plastic, e.g. by a spraying process. As a plastic are more advantageous Way thermally insulating or temperature-resistant plastics, such as Thermoplastics or thermosets. It can be advantageous if the material forming the ramp components and / or counter ramp components a higher one Has coefficient of friction in the order of magnitude the coefficient of friction of a friction lining material. By appropriate choice the run-up angle of the ramps and / or the counter ramps and the The compensation device can use coefficients of friction between the ramps and counter ramps be designed so that self-locking takes place with axial bracing can. Therefor can the ramps and / or counter ramps are designed such that they have a pitch angle in the axial direction, which is between 5 ° and 20 °, preferably in the order of magnitude from 8 ° to 12 °. It can therefore by appropriate design of the compensation device guaranteed that during the Coupling phase of the friction clutch is self-locking, so that none additional Means are required to unintentionally reset the compensation device to avoid.

The bracing the ramps and counter ramps Lift mechanism can be biased in such a way that always when a occurs or is present pad wear an adjustment takes place, i.e. the wear adjustment even when the clutch is rotating can be done. The spring loading of the ramps and counter ramps can advantageously be such that the function the rest Springs, such as the actuator plate spring in particular and connecting the pressure plate to the housing or cover Leaf springs, is not or practically not affected.

For some use cases However, it can also be advantageous if the readjustment speed-dependent is. So z. B. the individual elements of the readjustment acting centrifugal force for actuation and / or to lock the readjustment at certain operating conditions the internal combustion engine can be used. In particular, the Readjustment by centrifugal force-dependent means at a certain Speed or when exceeded of a certain speed range can be blocked. For many use cases it may also be advantageous if the readjustment arrangement is such is designed so that it is only at least approximate Idle speed or speed below the idle speed effective is, so the wear adjustment can only take place at low engine speeds. The locking or unlocking the wear adjustment effective means advantageously be part of the compensation device and z. B. formed by the components forming the ramps and / or counter ramps his.

For the adjustment function of the compensation device can do it particularly well be beneficial when disengaging the clutch the disc spring travel in the diameter range of the pressure plate is larger due to the disc spring than that caused by the limiting means or the wear sensors specified lift of the printing plate. This can ensure be that after applying the limiting means to an axially fixed Component relieves the compensation device and thus for adjustment is released.

According to another inventive The compensation device can feature two abutting one another Have ramp arrangements, one of the ramp arrangements opposite the pressure plate is non-rotatable and the other ramp arrangement opposite one compensation component acted upon by the energy accumulator is rotationally fixed, wherein the compensation component is rotatable relative to the pressure plate is.

The invention further relates on a friction clutch, especially for motor vehicles, with a Pressure plate that is non-rotatable, but axially displaceable with limited a housing is connected, a pressure spring between the housing and pressure plate is axially clamped, on the one hand around a carried by the housing ring-like pivot bearing is pivotable and on the other hand the pressure plate towards one between this and a backing plate like a flywheel, clampable clutch disc, one being the wear of the friction linings of the clutch disc to compensate for the adjustment is a practically constant application of force to the Pressure plate caused by the pressure spring, being between Pressing spring and pressure plate a wear compensation device is provided, the at least one axially displaceable compensation component owns, which is acted upon by the contact spring the axial release travel the pressure plate by between the pressure plate and at least one axially fixed component, e.g. the housing and / or the counter pressure plate, effective limiting means limited and at least approximately constant is kept and still the limiting means, at least when move out the friction clutch, the axial displacement of the compensation component across from limit the pressure plate.

Another advantageous embodiment according to the invention a friction clutch is characterized by the combination of features contained in claim 40.

For the function of the friction clutch, in particular to minimize the release force curve or the maximum required release force, it can also be particularly advantageous if the one between the pressure plate and the counter pressure plate Clampable clutch disc has friction linings, between which a so-called pad suspension, as for example by the DE 36 31 863 A1 has become known, is ordered. By using such a clutch disc, the actuation, in particular the disengagement process of the friction clutch, is supported. This is due to the fact that in the engaged state of the friction clutch, the tensioned pad suspension exerts a reaction force on the pressure plate which is opposite to the force exerted on this pressure plate by the contact pressure spring or actuation control spring. During the disengagement process, during the axial displacement of the pressure plate, the pressure plate is initially pushed back by the spring-loaded pad suspension, while at the same time, due to the relatively steeply falling characteristic section of the pressure spring in the disengagement area, the force exerted on the pressure plate by the latter decreases. As the force exerted by the contact pressure spring on the pressure plate decreases, the restoring force exerted by the pad spring on this pressure plate can also decrease. The force effectively required to disengage the friction clutch results from the difference between the restoring force of the pad spring and the contact force of the contact spring, whereby the axial force of the leaf springs, which may be tensioned between the pressure plate and the housing, must also be taken into account. After the pad spring has relaxed, i.e. when the pressure plate is lifted from the friction linings or the clutch disc is released by the pressure plate, the required release force is mainly determined by the contact pressure spring. The force-displacement characteristic of the pad suspension and the force-displacement characteristic of the contact spring as well as the force-displacement characteristic of the leaf springs can be coordinated with one another in such a way that when the clutch disc is released by the pressure plate, the force required to actuate the contact spring is on one low level. Thus, by approximating or even aligning the pad suspension characteristics to the force curve formed or resulting by the contact pressure spring and possibly existing leaf springs, only a very small, in the extreme case practically no, operating force for the contact pressure spring until the clutch disc is released.

When adjusting the individual spring forces must So those of those effective between the pressure plate and the housing Axial force applied to leaf springs must be taken into account. Farther When designing the coupling, it should be noted that the displacement or adjusting force of the wear sensors or wear sensors through the at least one contact pressure accumulator, such as in particular Disc spring, must be applied and thus this energy storage correspondingly stronger should be trained. It is also advantageous if the Adjustment force of the wear sensors is dimensioned such that it is certainly larger than that caused by the bracing of the ramps and counter ramps Wedges generated the resulting axial force, which is transmitted through the wear sensors can be intercepted.

Based on 1 to 7 the invention is explained in more detail.

It shows:

1 a friction clutch according to the invention in view,

2 a section along the line II-II of 1 .

3 a section along the line III-III of 1 .

4 a partial section along the line IV-IV of 1 .

5 one in the friction clutch according to the 1 and 2 used adjustment ring in view,

6 and 7 two further design options for a friction clutch according to the invention.

The in the 1 and 2 illustrated friction clutch 1 has a housing 2 and a thrust washer connected to it in a rotationally fixed manner but axially displaceable to a limited extent 3 , Axially between the thrust washer 3 and the lid 2 is a contact spring 4 braced by one from the case 2 worn ring-like swivel bearing 5 is pivotable and the thrust washer 3 towards one with the housing 2 firmly connected counter pressure plate 6 , such as a flywheel, acts on the friction linings 7 the clutch disc 8th between the friction surfaces of the thrust washer 3 and the counter pressure plate 6 be clamped.

The thrust washer 3 is with the housing 2 via circumferential or tangential linkage means in the form of leaf springs 9 non-rotatably connected. In the illustrated embodiment, the clutch disc 8th so-called pad spring segments 10 , which ensure a progressive build-up of torque when engaging the friction clutch by providing a limited axial displacement of the two friction linings 7 towards each other towards a progressive increase in the friction linings 7 allow acting axial forces. However, a clutch disc could also be used in which the friction linings 7 axially practically rigid would be applied to at least one carrier disk.

In the illustrated embodiment, the plate spring 4 an annular base body exerting the contact pressure 4a , of which radially inward operating tongues 4b out. The disc spring 4 is so turned on builds the thrust washer with areas located radially further out 3 apply and with radially inner areas around the pivot bearing 5 is tiltable. The swivel bearing 5 includes two swivel pads 11 . 12 , which are formed here by wire rings and between which the plate spring is axially held or clamped. For securing the actuator plate against rotation 4 and for centering and holding the wire rings 11 . 12 towards the housing 2 are holding devices in the form of rivet elements 15 attached to the lid, each with an axially extending shaft 15a by a between adjacent disc spring tongues 4b provided cutout.

The coupling 1 has axial wear on the friction surfaces of the thrust washer 3 and the counter pressure plate 6 and the friction linings 7 compensating readjustment, which consists of a between the contact spring 4 and thrust washer 3 provided wear compensation device 16 as well as the disengagement path of the thrust washer 3 limiting means 17 , which are designed as a displacement sensor.

The limiting means effective as wear sensors 17 each have a socket 18 that are in a hole 20 the thrust washer 3 is rotatably received. The socket 18 forms a slit 21 , through which two leaf spring elements extend axially 22 extend. The leaf spring elements 22 are supported on one another, at least one leaf spring element being curved, preferably both leaf spring elements being curved in opposite directions. The leaf spring elements 22 are received in the socket with a defined preload and are therefore against a predetermined frictional resistance to the socket 18 in the axial direction of the clutch 1 displaced. The axial length of the leaf spring elements 22 is selected such that when the friction clutch is engaged 1 these leaf spring elements in relation to an axially fixed coupling component - in the exemplary embodiment shown in relation to the outer edge region 23 of the housing 2 - a defined game 24 have the predetermined disengagement path of the thrust washer 3 equivalent. The leaf spring elements come when the friction clutch is engaged 22 with their the housing 2 opposite end 22a on the counter pressure plate 6 to the system, which ensures that if the friction linings wear 7 the thrust washer 3 corresponding to this lining wear compared to the leaf spring elements 22 is axially displaced, namely against the effect of the frictional engagement between the leaf spring elements 22 and the socket 18 , which is preferably made of plastic or a friction material.

In the illustrated embodiment, the bore 20 into which the can 18 is fixed by pressing in both the axial and circumferential directions in a pressure plate cam 25 provided, which extends radially outwards and on each of which a leaf spring element 9 via a riveted joint 9a is articulated. Moving the socket 18 towards the counter pressure plate 6 can also be avoided by using the socket 18 on their the housing 2 end facing a covenant 18a owns, by means of which it sits on the thrust washer 3 can support. A migration of the socket 18 out of the hole 20 towards the housing or clutch cover 2 can be avoided by doing that as in 1 The leaf springs are indicated by dash-dotted lines 9 the socket 18 partially overlap radially and, if necessary, additionally firmly in the bore 20 clamp axially. Rotation of the bushing can further be prevented by the bushing having a profiling, in particular a shoulder, which extends over the areas overlapping the bushing 19 the leaf springs 9 receives.

The wear compensation device 16 has one of the disc spring 4 acted upon compensation component in the form of a sheet metal ring with a U-shaped cross section 26 who in 5 is shown in plan view. The compensation component 26 has on the disc spring 4 facing side of the floor 27 at least one annular axial projection 28 or several tabs 28 which are preferably evenly distributed over the circumference and are formed by beads embossed into the sheet metal material. Segment-like projections 28 ensure that in the area between adjacent projections in the circumferential direction 28 radial passages between the diaphragm spring body 4a and the compensation ring 26 are formed, which allow an air passage for cooling. How especially out 2 can be seen is the compensation ring 26 opposite the thrust washer 3 centered. For this, the thrust washer 3 at least one gradation 29 that the radially inner, axially extending wall 30 of the compensation ring 26 centric to the thrust washer 3 positioned. The gradation 29 can be formed by a closed surface that extends over the circumference, or else by segment-shaped surfaces that are spaced apart from one another over the circumference. The compensation ring 26 also has a radially outer axially extending wall 31 that together with the inner wall 30 and the floor 27 an annular space 26a forms. The compensation ring has a radial outside 26 radial arms or cams 32 , which form stops, which with counter-stops 33 the axially displaceable components in the form of leaf spring elements 22 the wear sensor 17 interact. The counterstops 33 are through to the leaf spring elements 22 molded noses are formed, which point radially inwards and the boom 32 spread. As a result, the axial displacement of the compensation ring 26 towards the thrust washer 3 away, i.e. towards the housing, through the counter stops 33 limited.

Between the compensation ring 26 and the thrust washer 3 is a compensation device 34 provided when disengaging the friction clutch 1 and presence of lining wear an automatic adjustment of the compensation ring 26 enables and acts when locking the clutch self-locking, so blocking, which ensures that during the engagement phase of the friction clutch 1 the combination ring 26 a defined axial position in relation to the thrust washer 3 maintains. This defined position can only change during a disengagement process and in accordance with the wear of the lining.

The adjustment device 34 comprises several pairs of wedges, preferably evenly distributed over the circumference 35 . 36 that are in the annular space 26a of the sheet metal ring 26 are included. Which is on an annular surface 37 the thrust washer 3 supporting wedges 36 are with the sheet metal ring 26 non-rotatably connected but axially displaceable. For this the sheet metal ring has 26 in the area of its axially extending walls 30 . 31 Formations in the form of beads 38 . 39 that are in the area of free space 26a Form projections, which in correspondingly adapted recesses or grooves 40 . 41 the wedges 36 intervention. The grooves 40 . 41 or the formations 38 . 39 run in the axial direction of the coupling 1 , The wedges 35 are essentially axial between the bottom 27 of the sheet metal ring 26 and the wedges 36 added. The wedges 35 and 36 form ramp ramps that extend in the circumferential direction and rise axially 42 . 43 over which the wedges assigned to a pair 35 . 36 support each other. The wedges 35 lean on the other hand 27 of the ring 26 and are opposite this ring 26 displaceable in the circumferential direction. The ramp 42 . 43 are braced against each other. For this purpose, energy storage devices are in the form of coil springs 44 in the annulus 26a added, which is at one end to one with the ring 26 non-rotating wedge 36 and with its other end on a circumferentially displaceable wedge 35 support. For holding the lift mechanism 44 own the wedges 35 . 36 projections at their ends facing the corresponding energy stores 45 . 46 , which engage in the spring windings and thus hold the spring ends. The feathers 44 continue through the wall areas 30 . 31 and the floor 27 of the ring 26 guided.

In the illustrated embodiment, the compensation ring 26 opposite the thrust washer 3 secured against rotation. For this are how out 4 can be seen on the thrust washer 3 axial projections in the form of pins 47 provided axially through recesses 48 that in the field of the boom 32 are provided to extend. This anti-rotation device ensures that the stop areas of the tabs are in operation during the operation of the friction clutch 32 always below the boundary tabs 33 the leaf spring elements 22 stay positioned.

In the illustrated embodiment, the wedges are 35 . 36 made of a heat-resistant plastic, such as a thermoset or thermoplastic, which can also be fiber-reinforced. This allows the wedges, which act as adjusting elements 35 . 36 produce easily as molded parts. However, it can also be advantageous if at least one of the wedges 35 . 36 a pair of friction material, such as lining material. The wedges or adjusting elements 35 . 36 However, can also be made as a sheet metal part or as a sintered part. The pitch angle as well as the extent and the ramp 42 . 43 are designed so that the entire life of the friction clutch 1 an adjustment of the on the friction surfaces of the thrust washer 3 and the counter pressure plate 6 as well as the friction linings 7 occurring wear is guaranteed. The wedge angle 49 or the pitch angle 49 the ramp 42 . 43 in relation to a plane perpendicular to the axis of rotation of the friction clutch is chosen such that when the run-up ramps are pressed together 42 . 43 friction prevents slipping between these ramps. Depending on the material pairing in the area of the ramp 42 . 43 can the angle 49 are in the range between 5 and 20 degrees, preferably in the order of 10 degrees. The wedges that can be displaced in the circumferential direction 35 are arranged in such a way that their wedge tip points in the direction of rotation 50 demonstrate.

The tension through the energy storage 44 the ramp 42 . 43 as well as the pitch angle 49 are designed so that the adjustment ring 26 resulting axial force is less than the required displacement force of the wear sensor 22 the limiting means 17 ,

Furthermore, when designing the disc spring 4 be taken into account that the pressure force to be applied by this for the thrust washer 3 the required displacement force for the wear sensor 22 and the clamping force between the lid 2 and thrust washer 3 tense leaf springs 9 must be increased. Furthermore, the individual components must be designed in such a way that the support wear between the disc spring 4 and support ring 26 as well as the system wear between the wear sensors 22 and the counter pressure plate 6 or between the wear sensors and the housing 2 in relation to the wear on the pads 7 stay low.

To prevent the arched or corrugated leaf springs 22 as a result of the clutch disc being engaged 3 The very high temperatures that arise lose their clamping force, are the bushings 18 preferably made of a material with low thermal conductivity and high coefficient of friction. The wedges 35 . 36 can be made of the same material.

To better cool the clutch, ins special of the thrust washer 3 , in the thrust washer 3 radial grooves distributed over the circumference, of which in 2 one shown in dashed lines and with 51 is marked, be provided. These radial grooves 51 are, viewed in the circumferential direction, provided between two adjacent pairs of wedges and extend between the ring 26 and the thrust washer 3 , It could also be in the area of the feathers 44 the ring 26 from the floor 27 have outgoing axial cutouts, whereby between the plate spring 4 and the ring 26 radial passages would be formed.

To increase the wear resistance at the various contact points, the corresponding areas can be provided with a wear-resistant layer, such as hard chrome plating, molybdenum coating, or special wear-resistant components can be provided in the area of the contact points. For example, on the wear sensors 22 Plastic shoes in the contact area to the counter pressure plate 6 and to the housing 2 be provided.

The torque on the thrust washer 3 transmitting leaf springs 9 are between the thrust washer 3 and the housing 2 biased so that when you disengage the friction clutch 1 the thrust washer 3 towards the case 2 relocate. This ensures that practically the entire disengagement phase or until the limiting means take effect 17 the ring 26 on the disc spring 4 stays in plant.

The clutch disengagement path in the area of the tongue tips 4c is preferably selected such that the outer edge of the plate spring when the clutch is disengaged 4 by a small amount from the ring 26 takes off. So this means that when disengaging the friction clutch 1 the disc spring travel in the diameter range of the pressure disc loading by the disc spring 4 is greater than that due to the path limitation means 22 specified lift path 24 the thrust washer 3 ,

In the 2 Relative position of the individual components shown corresponds to the new condition of the friction clutch. With axial wear, especially the friction linings 7 , the position of the thrust washer shifts 3 towards the counter pressure plate 6 , which initially changes the conicity and thus also that of the plate spring in the engaged state of the friction clutch 1 applied contact pressure arises, preferably in the sense of an increase. This change causes the thrust washer 3 their axial position compared to that on the backing plate 6 axially supporting wear sensors 22 changes. As a result of being on the ring 26 This ring is followed by cup spring force 26 the axial displacement of the counter pressure plate caused by lining wear 3 , creating the stop areas 32 of the ring 26 axially from the areas serving as counter-stops in the form of noses 33 the wear sensor 22 lift off, by an amount that essentially corresponds to the wear of the lining. The balance ring 26 maintains its axial position in relation to the thrust washer during a coupling process 3 at because it was through the disc spring 4 towards the thrust washer 3 is applied and the wear compensation device 34 is self-locking during the coupling process, i.e. it acts as an axial lock. When disengaging the friction clutch 1 is the thrust washer through the leaf springs 9 towards the case 2 acted upon and shifted until the wear sensor 22 on the housing 2 or at the housing stop areas 23 come to the plant. Up to this disengagement path, which is the lift path of the thrust washer 3 corresponds, the axial position of the ring remains 26 opposite the thrust washer 3 receive. If the disengagement process continues, the thrust washer remains 3 stand axially, whereas the ring 26 axially follows the disengagement movement of the disc spring in the area of the loading diameter, until the stop areas 32 of the ring 26 at the counter stop areas 33 the wear sensor 22 come back to the plant. The axial displacement of the compensation ring 26 is through the wedges 35 caused by the springs 44 are acted upon. These wedges 35 so long as against the wedges 36 shifted circumferentially until the ring 26 against the counter-attacks 33 the wear sensor 22 is tense. The lifting of the thrust washer 3 is in the illustrated embodiment on the leaf springs 9 ensures that between housing 2 and thrust washer 3 are installed that they have an axial preload, which the thrust washer 3 towards the case 2 urges. Will the disc spring 4 still pivoted in the disengaging direction, it lifts with its radially outer region from the adjusting ring 26 since the latter, as already described, by the wear sensor 22 opposite the thrust washer 3 is retained axially. Such a, at least slight lifting of the disc spring 4 opposite the adjusting ring 26 during a disengagement process is for the function of the adjustment system 17 + 34 particularly advantageous.

The adjustment arrangement according to the invention 17 + 34 ensures that the adjustment on the support ring 26 through the adjustment wedges 35 . 36 always takes place in accordance with the amount of lining wear. This is due to the fact that the adjuster ring 26 between the adjusting means in the form of wedges 35 . 36 and the wear sensors 22 is clamped axially, thereby preventing the compensation component in the form of the ring 26 is adjusted by a larger amount than the corresponding lining wear. Furthermore, the design of the readjustment arrangement according to the invention ensures that even when crossing over in the area of the disengaging means, such as the plate spring tongues 4b , or in the event of axial vibrations of the pressure plate ne adjustment of the readjustment 17 + 34 can be done because the wear sensor 22 even with a hard impact on the housing 2 opposite the thrust washer 3 through the self-locking wear compensation device 34 are supported axially, namely via the counter stops 32 , So it can in the disengaged state of the friction clutch on the wear sensor 22 axial forces in the direction of the counter pressure plate 6 act that are larger than the non-positive connection between the wear sensors 22 and the thrust washer 3 without the wear sensor compared to this thrust washer 3 be axially displaced.

The adjustment arrangement according to the invention ensures that the diaphragm spring works practically over the same range of characteristics over the entire life of the clutch and in the engaged state of the friction clutch 1 has a clamping position that remains practically constant and thus also a practically constant contact pressure on the pressure plate 3 applies. This makes it possible to use a disc spring with a degressive force characteristic over the disengagement path, and preferably in combination with a clutch disc, the linings of which 7 via spring segments 10 are cushioned against each other, whereby the effective release force can be brought to a relatively low level and can be kept practically constant over the life of the clutch, provided that the lining spring characteristic curve does not change significantly over the life of the clutch. When disengaging such a clutch, the plate spring 4 for their lid storage 5 pivoted, wherein over a predetermined portion of the axial disengagement path of the thrust washer 3 the spring segments 10 relax and thus that of the spring segments 10 applied axial force the disengagement process of the friction clutch 1 supported. This means that a lower maximum release force must be applied than that which is in the engaged position of the clutch 1 theoretically results from the installation position of the disc spring 4 and the leaf springs 9 , As soon as the spring or relaxation area of the segments 10 is exceeded, the friction linings 7 released, due to the degressive characteristic range in which the disc spring 4 works, the disengagement force still to be applied is already considerably reduced compared to that which corresponds to the installation point or installation position 2 would correspond. As the disengagement process continues, the disengagement force continues to decrease, at least until the minimum or the valley point of the preferably sinusoidal characteristic of the disc spring 4 is reached.

The in the 1 and 2 shown readjustment 17 + 34 can advantageously be designed in such a way that with a rotating friction clutch 1 the individual spring turns of the adjustment springs 44 itself on the outer wall 31 the adjustment ring 26 support and that of the springs 44 adjusting forces applied in the circumferential direction as a result of the between the spring windings and the adjusting ring 26 generated frictional resistance can be reduced or even completely canceled. The feathers 44 can occur when the friction clutch rotates 1 behave practically rigid due to the frictional forces suppressing the spring action. The adjustment wedges can also be used 35 due to the centrifugal forces acting on them also on the wall 31 the adjustment ring 26 support radially and through between the wedges 35 and the adjusting ring 26 generated frictional forces are secured against rotation. It can thereby be achieved that the wear compensation device at least at speed ranges above the idling speed of the internal combustion engine 34 not through the feathers 44 be twisted. So it can be the friction clutch 1 be designed in such a way that the friction lining wear is only compensated for when the friction clutch is actuated 1 at idle speed or at least approximately at idle speed. The blocking of the adjuster ring 26 can by appropriate design of the wear compensation device 34 however, also take place such that only when the internal combustion engine is at a standstill, that is to say when the friction clutch is not rotating 101 or an adjustment of the lining wear can take place at very low speeds.

The material pairing between the components forming the adjustment ramps 35 . 36 and the material of the components interacting with these components is preferably selected such that there is no adhesion between the ramps and the components interacting with them over the operating life of the friction clutch. In order to avoid such liability, at least one of these components can be provided with a coating at least in the area of the ramps or support surfaces.

A bond between ramp ramps and avoiding counter approach ramps can also be at least one precaution be provided when disengaging the friction clutch or an axial force when adjusting for wear exerts on the adjustment element or elements that separate or tear away the Ramps causes.

When the friction clutch is in new condition 1 , that is, in the state that the clutch has before interposing the clutch disc 8th on the counter pressure plate 6 the wedges are attached 35 compared to the in 3 shown position in a further retracted position opposite the wedges 36 so that the adjuster ring 26 its towards the thrust washer 3 most retracted position and thus the unit thrust washer 3 / adjusting ring 26 require the smallest axial installation space. Around the wedges 35 before the Assembly of the friction clutch 1 The wedges have to keep in their retracted position 35 Attack areas in the form of recesses 52 for a torsion or restraint. Such retention means can be used in the manufacture or assembly of the friction clutch 1 be provided and after installing the friction clutch 1 on the flywheel 6 are removed, causing the adjustment device 34 is activated. In the illustrated embodiment are in the adjusting ring 26 circumferential elongated slots 53 provided by which the engagement areas of the retaining means or the twisting tool for engaging in the recesses 52 can be passed through. The elongated recesses placed in the circumferential direction 53 must have at least one extent that a twist corresponding to the largest possible wear adjustment angle of the wedges 35 corresponds in the circumferential direction. The wedges held in their retracted position in the circumferential direction when the friction clutch is new 35 can be in this position by the wear sensor 22 which the adjuster ring 26 secure in its retracted position, be held. The self-adjusting connections between the wear sensors 22 and the thrust washer 3 must be designed in such a way that the displacement force required to displace the wear sensor 22 opposite the thrust washer 3 is larger than that on the ring 26 resulting force that is generated by the wedges 35 acting springs 44 ,

In the embodiment according to the 1 and 2 can the ramps 43 also directly through the ring 26 be formed, for example by embossing oblique surfaces 43 , the ring 26 then through the feathers 44 opposite the thrust washer 3 must be rotatable. The wedges 36 are in such an embodiment with the thrust washer 3 non-rotatably or directly formed on this. Furthermore, in such an embodiment, the boom 32 trained stops in the circumferential direction according to the required adjustment rotation angle of the ring 26 lengthened to ensure that there is an axial limit between the wear sensors 22 and the ring 26 is maintained over the life of the friction clutch.

In the last described embodiment, the adjusting ring 26 even when the friction clutch is installed 1 can be rotated in a simple manner from the radially outside, in particular via the stop tabs extending in the circumferential direction 32 that over on the outer jacket of the clutch housing 2 provided radial passages are accessible. These radial passages can in particular also be the torque transmission cams 25 the thrust washer 3 as well as the leaf springs 9 take up. The adjustment arrangement according to the invention has the further advantage that its principle can also be used in so-called drawn friction clutches, in which the plate spring is pivotally supported on a cover with a radially outer edge region and acts on the thrust washer with radially further inner edge regions. Such a clutch is in 6 shown. Between disc spring 104 and thrust washer 103 is a wear compensation device 134 provided, which can be designed similarly, as in connection with the 1 and 2 has been described. The adjusting ring 126 in turn acts via sensor elements 117 with wear sensor 122 together. The adjustment of the wear sensor 122 opposite the thrust washer 103 is done by creating the stop areas 122a on the housing or cover 102 , The wear sensor 122 again carry attacks 133 that the axial path of the thrust washer 103 limit when disengaging. To ensure that the readjustment precautions function properly 6 the ring has to enable 126 at least a slight axial possibility of movement compared to the wear sensors 122 , This can be done by a corresponding impact connection 133a with play between the wear sensors 122 and the ring 126 is present or because of the ring 126 radial areas 126a has, which are resiliently deformable in the axial direction, that is to say have elastic resilience.

It is also conceivable that the wear sensor 122 rather than with the lid 102 with the disc spring 104 interacts at least in an axial direction, preferably at least when the clutch is engaged. It can be advantageous if the stop between the wear sensor 122 and the disc spring 104 at least approximately at the radial height of the diaphragm spring support or support diameter on the housing 102 he follows. For towed couplings, it can be useful if the support diameter of the wear sensor on the plate spring is larger than the support diameter of the plate spring on the pressure plate.

At the in 7 The exemplary embodiment shown are the wear sensor elements 217 directly in the base of the thrust washer 203 added. The wear sensor 222 have stop areas 222a that with lid areas 223 , which form counterstops, work together. The lid areas 223 are in one piece with fasteners 202a over which the disc spring 204 on the lid 202 is pivotally mounted. In the illustrated embodiment, the fastening or holding means 202a by tabs formed in one piece from the cover material, which extend axially through the plate spring 204 stretch through, formed. Radially outside that in the radial area of the diaphragm spring body 204a provided wear sensors 217 is the wear compensation device 234 intended.

It is also conceivable that the wear sensor 222 rather than with the case 202 or with the lid areas 223 interact axially on the disc spring 204 can be supported at least in an axial direction, preferably at least when the clutch is engaged. The disc spring can be used for this 204 have an axial recess through which the wear sensor 222 extends through so that the stop areas 222a in the engaged state of the friction clutch instead of at the counter-stop areas 223 on the disc spring 204 support axially. When disengaging the friction clutch, the stop areas 222a from the disc spring 204 take off because the stop areas 222a are provided on a smaller diameter than the support diameter of the plate spring 204 on the pressure plate 203 , This is due to the fact that the stop areas 222a closer to the swivel diameter of the disc spring 204 are the support diameter between the pressure plate 203 and disc spring 204 ,

The invention is not shown on and described embodiments limited, but also includes variants by combining individual features described in connection with the various embodiments or elements can be formed. Farther can individual features described in connection with the figures or How it works for to represent yourself an independent invention.

The submitted with the registration claims are suggestions for wording without prejudice for the Obtaining further patent protection. The applicant reserves the right before, still more, so far only in the description and / or drawings claimed combination of features.

Relationships used in subclaims point to the further training of the subject of the main claim by the features of the respective subclaim; you are not as a waiver of achieving an independent, objective Protection for the combinations of characteristics of the back-related under claims to understand.

Since the subjects of the subclaims with regard own and independent inventions based on the state of the art on the priority day the applicant retains imagine they are the subject of independent claims or Declarations of division do. You can also independent inventions contain a design independent of the objects of the preceding subclaims exhibit.

The exemplary embodiments are not as a limitation to understand the invention. Rather, within the scope of the present Revelation numerous changes and modifications possible, in particular such variants, elements and combinations and / or materials, which, for example, by combining or modifying individual into Link to those in the general description and embodiments and the claims described and features or elements contained in the drawings or Process steps for the expert with regard to the solution of the task can be removed are and through combinable features to a new item or lead to new process steps or process step sequences, too as far as they manufacture, test and work procedures

Claims (39)

Friction clutch, especially for motor vehicles, with a pressure plate ( 3 ), which is non-rotatable, but axially limited displaceable with a housing ( 2 ) is connected, whereby at least one actuating means ( 4b ) and an energy store ( 4 ) are provided, via which the pressure plate in the direction of a between this and a counter pressure plate, such as a flywheel ( 6 ), clampable clutch disc ( 8th ) can be acted upon, whereby at least the wear of the friction linings ( 7 ) adjustment mechanism to compensate for the clutch disc ( 17 . 34 ) is present, which is a wear compensation device provided between the actuating means or energy accumulator and the pressure plate ( 16 ), each of which assumes an axial setting between the actuating means or energy accumulator on the one hand and the pressure plate on the other hand, which corresponds to the state of wear of the friction linings, and when the setting corresponding to the current state of wear of the friction linings is reached, the wear compensation device by at least one wear sensor provided on the pressure plate ( 17 ) is limited in its readjustment function, the wear sensor having at least one wear sensor component ( 22 ) which, when wear occurs and by contact with an axially fixed component with a counterstop area ( 33 ) from a stop area ( 32 ) the wear compensation device lifts off and, in the event of a disengagement process following wear that has occurred, the wear compensation device is adjusted until the stop area thereof on the counter-stop area of the wear sensor component ( 22 ) again. Friction clutch according to claim 1, characterized in that between the housing ( 2 ) and pressure plate ( 3 ) an axially tensioned disc spring ( 4 ) is provided, which is around a ring-like support carried by the housing ( 11 . 12 ) is pivotable and has an annular base body ( 4a ) to form the energy accumulator, from which radially inwardly extending tongues ( 4b ) and that the wear compensation device ( 16 ) is arranged between the plate spring and the pressure plate. Friction clutch according to claim 1 or 2, characterized in that the axially fixed component, the flywheel ( 6 ) is. Friction clutch according to one of claims 1-2, characterized in that the axially fixed component, the housing ( 2 ) is. Friction clutch according to at least one of the preceding claims, characterized in that the wear sensor component ( 22 ) opposite the pressure plate ( 3 ) is held axially displaceable. Friction clutch according to at least one of the preceding claims, characterized in that between the wear sensor component ( 22 ) and the pressure plate ( 3 ) there is an automatic or automatic axial displacement option. Friction clutch according to at least one of the preceding claims, characterized in that the wear sensor component ( 22 ) by friction on the pressure plate ( 3 ) is supported. Friction clutch according to at least one of the preceding claims, characterized in that the wear sensor component ( 22 ) on a free-wheel-like arrangement on the pressure plate ( 3 ) is supported. Friction clutch according to at least one of the preceding claims, characterized in that the wear sensor component ( 22 ) secure against rotation on the pressure plate ( 3 ) is supported. Friction clutch according to at least one of the preceding claims, characterized in that the wear sensor component ( 22 ) a radial counterstop area ( 33 ), on which, after an adjustment corresponding to wear, a wear compensation component of the wear compensation device can be brought into contact with a stop area. Friction clutch according to at least one of the preceding claims, characterized in that the wear sensor component has a radially extending region ( 122a . 222a ) to rest on a lid-tight area ( 102 . 223 ) has. Friction clutch according to at least one of the preceding claims, characterized in that the friction clutch is designed as a so-called "pressed" clutch ( 1 - 5 and 7 ). Friction clutch according to at least one of the preceding claims, characterized in that the friction clutch is designed as a so-called "drawn" clutch ( 6 ). Friction clutch according to one of claims 1 to 13, characterized in that the wear sensor is a wear sensor component ( 22 ), which limits the disengagement path of the pressure plate by contact with an axially fixed component. Friction clutch according to claim 14, characterized in that the wear sensor component is axially displaceable and with an axially displaceable component, z. B. the pressure plate, about an automatic Adjustment device is connected and by contact with at least an axially fixed component, such as the housing and / or the counter pressure plate, is adjustable. Friction clutch according to one of claims 1 to 15, characterized in that that the relocatable wear sensor component of the wear sensor with the pressure plate over an automatic adjustment device connected is. Friction clutch according to one of claims 1 to 16, characterized in that the compensation device is a support component ( 26 ) for the energy accumulator and a compensating device between this support component and the pressure plate ( 34 ) is provided which, when the friction clutch is disengaged, automatically adjusts the wear of the support component ( 26 ) and is self-locking when the clutch is engaged. Friction clutch according to claim 17, characterized in that the support component ( 26 ) can be axially displaced away from the pressure plate, but can be locked in the axial direction towards the pressure plate. Friction clutch according to one of claims 1 to 18, characterized in that that the compensation device acts like a freewheel when disengaging the friction clutch, when indenting the However, friction clutch is self-locking. Friction clutch according to one of claims 1 to 19, characterized in that that the compensation device by a ring-shaped component formed compensation component. Friction clutch according to claim 20, characterized in that the annular component via ramps ( 42 ) is supported against the pressure plate. A friction clutch according to claim 21, characterized in that the ramps ( 42 ) with Ge genrampen ( 43 ) work together. Friction clutch according to claim 22, characterized in that ramps ( 42 ) and counter ramps ( 43 ) about feathers ( 44 ) are tense to each other. Friction clutch according to one of claims 20 to 23, characterized in that the annular component ( 26 ) is formed as a hollow sheet metal part with a U-shaped cross-section, with the component being distributed over the circumference in the free space of the component and the ramps ( 42 ) forming wedge-like components ( 36 ) are included. Friction clutch according to claim 24, characterized in that the wedge-like components ( 36 ) compared to the ring-shaped component ( 26 ) are secured against displacement in the circumferential direction. Friction clutch according to claim 24 or 25, characterized in that the wedge-like components ( 36 ) compared to the ring-shaped component ( 26 ) are axially displaceable. Friction clutch according to claim 22 to 26, characterized in that the counter ramps ( 43 ) through wedge-shaped components ( 35 ) are formed, which are at least partially in the ring-shaped compensation component ( 26 ) engage enclosed space and can be rotated relative to the pressure plate and the compensation component. Friction clutch according to claim 1 to 27, characterized in that the compensation component ( 26 ) is secured against rotation against the pressure plate. Friction clutch according to one of claims 22 to 28, characterized in that that the counter ramps are spring loaded in the direction of the ramps. Friction clutch according to claim 29, characterized in that the spring loading between the ramps and the Components forming counter-ramps tensioned springs, such as. B. coil springs, he follows. Friction clutch according to one of claims 21 to 30, characterized in that the counter ramps ( 43 ) forming components ( 35 ) axially between which the ramps ( 42 ) forming components ( 36 ) and the compensation component ( 26 ) are at least partially included. Friction clutch according to one of claims 21 to 31, characterized in that that at least the end areas of the bracing the ramps and counter ramps Springs through which the components forming the ramps and counter ramps are guided. Friction clutch according to one of claims 21 to 32, characterized in that that the components forming the ramps and / or counter ramps a thermally insulating and temperature-resistant material are formed. Friction clutch according to one of claims 21 to 33, characterized in that that the components forming the ramps and / or counter ramps a temperature resistant Material, such as thermoplastic or thermoset. Friction clutch according to one of claims 1 to 34, characterized in that that when disengaging the clutch the disc spring travel in the diameter range of the pressure plate is larger due to the disc spring than that determined by the wear sensor Lifting the printing plate. Friction clutch according to claim 35, characterized in that with each disengagement process the compensation device is relieved. Friction clutch according to at least one of Claims 1 to 36, characterized in that the compensation device has two ramp arrangements resting against one another ( 42 . 43 ), wherein one of the ramp arrangements is non-rotatable with respect to the pressure plate and the other ramp arrangement with respect to one of the energy store ( 4 ) loadable compensation component ( 26 ) is non-rotatable, the compensation component being rotatable relative to the pressure plate. Friction clutch according to at least one of the preceding claims, characterized in that the wear compensation device ( 16 ) at least one ring-shaped component ( 26 ) with ramp ( 43 ) contains. Friction clutch, in particular for motor vehicles, with a pressure plate which is connected to a housing in a rotationally fixed but axially displaceable manner, wherein a pressure spring is axially clamped between the housing and the pressure plate, which can be pivoted on the one hand about an annular swivel bearing carried by the housing and on the other hand the pressure plate in Direction of a clutch disc that can be clamped between this and a counterpressure plate, such as a flywheel, wherein an adjustment device is provided to compensate for the wear of the friction linings of the clutch disc and between the pressure spring ( 4 ) and pressure plate ( 3 ) a wear compensation device ( 16 ) is provided, the at least one axially displaceable Kompen station component ( 26 ), which is acted upon by the contact pressure spring, the axial disengagement path of the pressure plate is further limited and kept at least approximately constant by limiting means effective between the pressure plate and at least one axially fixed component, and the limiting means, at least when the friction clutch is disengaged, the axial displacement of the compensation component limit against the pressure plate.