DE4244995B4 - Car friction clutch with pressure disc - has wear compensation and operation to provide constant force and moment transfer - Google Patents

Abstract

The car friction clutch has a pressure plate fixed but able to be axially displaced relative a housing. At least one actuating spring is located between housing and plate, which operates the pressure plate in the direction of a clutch plate. A wear compensating device ensures a practically constant force on the pressure plate via the spring. An operator is provided to engage and disengage the clutch, which during disengagement provides a progressive reduction in the transferred moment force.

Description

The The invention relates to a friction clutch, in particular for motor vehicles, with a pressure plate, the rotationally fixed, but axially limited displacement with a housing is connected, between housing and pressure plate at least a pressure spring in the form of a plate spring is effective, the Pressure plate in the direction of a between this and a counter-pressure plate, like a flywheel, a clutch plate clutching, where one is the wear of friction linings the clutch disc compensating adjuster available is.

Automatic adjusting devices, which are intended to effect a practically constant application of force to the pressure plate by the Anpresstellerfeder, for example, by the DE 29 16 755 A1 and DE 35 18 781 A1 known. The adjustable depending on at least one sensor adjusting means are arranged or effective between the pressure plate and the Anpresstellerfeder. Due to the articulation of the pressure plate on the housing via tangentially arranged leaf springs whose force, because this is the contact force of the plate spring directed opposite, may only be relatively small, which owns a relatively large mass thrust washer with disengaged friction clutch axially swing, so take off from the plate spring, whereby the function of the coupling is impaired, namely because the adjusting adjusts in the open state until the pressure plate is applied to the clutch disc, so the clutch can not separate. For this reason, such adjustment have not enforced in practice.

Of the present invention was the object of such friction clutches regarding the To improve function and life. In particular, should by the invention of the operation Such friction clutches required forces are reduced and on their Life a practically geichbleibender Ausrückkraftverlauf ensured become. Furthermore, the friction clutches according to the invention in particular be simple and economical way to produce. The present Invention was still the object of adjustment to create in practice on a broad basis and even rough Operation can be used which is simple in construction and durable safe function, which continues to have a small installation space need and which are inexpensive to manufacture. In addition, the required Release forces low be over the lifetime remain low and the life of friction clutches about that even further increased become.

According to the invention This is achieved by a the wear of the friction linings the clutch disc automatically compensating adjusting device is present and the friction clutch actuating means has to move in and out and having a provision during the engagement process, at least about a portion of the actuation path the actuating means and / or the Einrückwegs the pressure plate, a gradual Structure of the transferable from the clutch disc of the friction clutch torque causes, wherein the adjusting device is characterized by that between pressure plate and disc spring a displaceable in the axial direction compensation component and at least one wear sensor is provided on the pressure plate, wherein the Wear sensor with a counter stop area acts on the compensation component and in a parallel to the axis of rotation of the pressure plate arranged opening such it is stored that when he is engaged the friction clutch by acting on the wear sensor Force of an axially fixed component corresponding to the occurring each wear of the friction linings axially across from the pressure plate is displaceable and the counter stop area of Compensating component takes off. By such a precaution can also be achieved during the Disengaging the Friction clutch and at the beginning of the clamping of the friction linings between Pressure and counter pressure plate a gradual or progressive degradation of transferable from the friction clutch Moment takes place.

The inventive design of a friction clutch ensures that the Anpreßtellerfeder, considered over the life of the friction clutch, practically always has the same bias with the friction clutch engaged and thus a virtually constant application of force to the pressure plate is given. Furthermore, a reduction or minimization of Ausrückkraftverlaufes or the maximum required disengaging force can be achieved by the additional provision, which causes a gradual reduction of the transmissible by the friction clutch torque during a disengagement. This is due to the fact that the provision supports the operation, in particular the disengagement, of the friction clutch. For this purpose, the arrangement may comprise axially resilient means which exert on the actuating means and / or on the pressure spring and / or on the pressure plate and / or on the counter-pressure plate, a reaction force which counteracts the force exerted by the pressure spring on the pressure plate and in series ge is switched.

Especially It may be advantageous if the gradual construction of the of Clutch disc of the friction clutch transferable moment causing Arrangement is angeordet such that they during the disengagement of a subsection the axial displacement path acted upon by the pressure spring Pressure plate areas a gradual Dismantling of the transferable from the friction clutch or the clutch disc Momentes effected.

For some use cases Can the gradual Structure of the transferable from the clutch disc of the friction clutch Momentes effecting provision advantageously in the power flow between the actuating means and the attachment areas, such as fittings, of the housing the counter-pressure plate can be provided.

For other applications, however, it may also be advantageous if this provision is provided in the power flow between the pressure spring and the friction surface of the pressure plate. Such an arrangement is z. B. by the DE 37 42 354 A1 and the DE 1 454 201 A been proposed.

For other applications, it may be particularly advantageous if the provision is provided axially between two back to back arranged friction linings of the clutch disc, that is formed by a so-called "pad suspension", z. B. provided by between the linings pad spring segments. Such precautions are for example by the DE 36 31 863 A1 known.

Another way to achieve a progressive torque build-up or degradation, is through the DE 21 64 297 A vargehlagen been, in which the flywheel is formed in two parts and the counter-pressure plate forming member is axially resiliently supported relative to the connected to the output shaft of the internal combustion engine component.

For the function and the construction of a erfindugnsgemäßen friction clutch can be particularly appropriate if the provision of an axial, resilient compliance between Allows coupling components, wherein the provision is arranged and configured such that when opened Clutch is the force acting on the provision of the smallest and over the closing process of Clutch, so over the Einrückweg the clutch, the force acting on the precaution gradually on the maximum increases, this increase expediently only over a partial area of the closing path or Einrückweges the actuating means or the pressure plate sfattfindet. It can be particularly advantageous be when the arrangement is such that the gradual decrease or the gradual Increase of the transmittable by the friction clutch torque over at least approximately 40 up to 70% of the actuation path the actuating means and / or the maximum axial travel of the printing plate. Of the remaining area of the corresponding path becomes impeccable Separation of the power flow and to compensate for any existing Deformations on the coupling components, in particular the clutch disc, the Pressure plate and the counter-pressure plate needed.

Around the one for operation the friction clutch according to the invention required forces to minimize, it may be particularly advantageous if the pressure spring, at least about a part of the Ausrückweges the friction clutch, has a degressive force-displacement curve, that means that the pressure spring, at least about a portion of its compression or deformation path, a has sloping force course. This can be achieved that during the disengagement process the friction clutch counteracts the spring force of the provision of the force of the pressure spring, so that over one Part of the Ausrückweges the tension or deformation of the pressure spring by the spring force of Precaution supported at the same time as a result of the degressive or declining force-distance course the pressure spring, the force exerted by the latter on the pressure plate or the friction linings decreases. The effective to disengage the friction clutch required force curve arises, as far as No additional, overlapping Spring effects are present, from the difference between the of the arrangement applied force curve and the force curve of the Pressure spring. When lifting the pressure plate from the friction linings or release the clutch disc through the pressure plate is the required remaining Ausrückkraftverlauf or the required release force mainly by the pressure spring certainly. The force-displacement characteristic of the precaution and the force-displacement characteristic the pressure spring can be coordinated with each other so that when releasing the clutch disc through the pressure plate required for actuating the pressure spring Force on a relatively low Level is. So it can be done by approximation or even approximation the spring characteristic or force characteristic of the precaution to the Anpreßfedercharakteristik until release of the clutch disc by the pressure plate only a very low, in extreme cases, virtually no operating force for the contact spring to be required.

As a pressure spring is in a particularly advantageous manner, a plate spring, on the one hand order a ring-like pivot bearing supported by the housing can be pivotable and, on the other hand, acts on the pressure plate. In this case, the plate spring may have an annular body, emanating from the radially inwardly directed tongues, which form the actuating means. However, the actuating means may also be formed by levers, the z. B. are pivotally mounted on the housing. However, the contact pressure for the pressure plate can also by other types of spring, such as. As coil springs, are applied, which are angeordet in the friction clutch such that the force exerted by these on the pressure plate axial force in the engaged state of the friction clutch is greatest and this force is reduced during the disengagement process. This can be z. B. by oblique position of coil springs relative to the axis of rotation of the friction clutch.

Especially It may be advantageous if the plate spring on the housing between two pads is supported pivotally, forming a so-called clutch of the depressed Design type. In such couplings, the actuating means for disengaging the Friction clutch usually acted upon in the direction of the pressure plate. However, the invention is not on clutches of the pressed ones Type limited, but includes Also drawn couplings in which the actuating means to disengage the friction clutch usually be acted upon in the direction of the pressure plate away.

In Particularly advantageously, the friction clutch according to the invention a plate spring, which is designed so that they have a sinusoidal force-displacement curve has and so installed is that in the indented State of friction clutch its operating point on the first Maximum force following, degressive characteristic area provided is. It may be particularly advantageous if the plate spring a balance of power of 1: 0.4 to 1: 0.7 between the first maximum force and the following minimum.

By the embodiment of the invention can the one to disengage the friction clutch required force or the force curve be brought to a very low level, so that the clutch pedal a easier dosage of the actuating force possible is.

By the inventive design of a Friction clutch and the associated possibility of reducing the over the Lifespan of the friction clutch maximum occurring Anpreßfederkräfte can Components correspondingly reduced or reduced in their strength which makes a considerable cheapening in the production can be done. By reducing the release forces, the friction and elasticity losses reduced in the clutch and the release system and thus the efficiency of the system friction clutch / disengagement system significantly improved. It can thus optimally design the whole system and thereby the clutch comfort can be significantly improved.

The embodiment of the invention is generally applicable to friction clutches and in particular in such as they are, for example, by the DE 29 16 755 A1 . DE 29 20 932 C2 . DE 35 18 781 A1 . DE 40 92 382 C2 . FR 2 605 692 A1 . FR 2 606 477 A1 . FR 2 599 444 A1 . FR 2 599 446 A1 . GB 1 567 019 , US 4,924,991, US 4,191,285, US 4,057,31, JP 3-25026, JP 3-123 U, JP 2-124326 U, JP 1-163218 U, JP 51-126452 A, JP 3-19131 U, JP 3- 53628 U have been proposed.

The Use of a friction clutch with an automatic or automatic compensation of at least the lining wear - whereby a at least about the life of the friction clutch approximately constant clamping force of Clutch disc guaranteed is is especially advantageous in connection with clutch units, in which the friction clutch, the clutch disc and the counter-pressure plate, such as a flywheel, a mounting unit or a Form module. In such a mounting unit, it is advantageous for cost reasons, if the coupling housing with the counterpressure plate over one not without destruction releasable Compound, such as welded joint or molding compound, For example, by plastic deformation material is connected. By such a connection, the commonly used fasteners, like screws, omitted. In such assembly units is a replacement the clutch disc or clutch linings due to exceeding the wear limit without destruction of components, such as the clutch housing, practically impossible. By Use of a wear-adjusting Clutch, the mounting unit can be designed so that these over the entire vehicle life guarantees a perfect function. It can therefore due to the design of the invention, the wear reserve the clutch disc and the Nachstellreserve the friction clutch or the coupling module sized so large be that the Coupling life and thus the life of the mounting unit certainly reach at least that of the vehicle.

According to one embodiment of the invention, it may be particularly advantageous if a friction adjustment having a Verschleißnachstellvorkehrung with a so-called Zweimas senschwungrad is combined, wherein the friction clutch can be mounted with the interposition of a clutch disc on the one connected to a transmission flywheel and the second flywheel is connectable to the output shaft of an internal combustion engine. Dual-mass flywheels, in which the friction clutch according to the invention can be used, have become known, for example, by the DE 37 21 712 A1 . DE 37 21 711 A1 . DE 41 17 571 A1 . DE 41 17 582 A1 and DE 41 17 579 A1 , In particular, the coupling housing or the clutch cover can be connected via a non-destructive detachable connection with the supporting flywheel, as for example for various embodiments in the DE 41 17 579 A1 shown and described.

By Use of a friction clutch with a provision, which at least compensates for the lining wear, can continue to optimize the design of the friction clutch take place, in particular of the clamping force for the clutch disc applying Energy accumulator. This energy storage can thus be designed he will practically only for transmission of the desired Apply torque required clamping force for the clutch disc. Furthermore, the use of a self-adjusting friction clutch advantageous in connection with dual mass flywheels in which the arranged between the two masses rotationally elastic damper radially outside the clutch disc or the outer friction diameter the friction surface provided with the transmission connectable flywheel. at such dual mass flywheels must the Friction diameter of the clutch disc to be smaller than conventional Couplings, so that the contact pressure according to the ratio increases the average Reibradien must become, to transmit a defined engine torque. at Using a conventional clutch this would increase the disengaging to lead. By using a wear-adjusting clutch with one over the Ausrückweg progressive degradation of the transferable from the clutch disc torque can but a Ausrückkraftabsenkung be achieved, thereby increasing the release force avoided can be or by appropriate interpretation of the friction clutch even a release force reduction across from a conventional clutch can be achieved.

It can therefore by the inventive design of a friction clutch guaranteed be that despite reduced friction lining outer diameter and the higher required contact pressure the release force can be kept low. Due to the lower release force is also the load of the rolling bearing, over the the two flywheels are rotatable relative to each other, reduced. Furthermore, the wear adjustment makes the life the clutch increases, so the existence Replacing the parts, especially the clutch disc during the Life of the motor vehicle, is no longer necessary. It So can the clutch cover fixed to the connectable to the transmission Flywheel can be connected, for example, by riveting or Welding. This is particularly advantageous if a limited installation space or limited Contours of the clutch bell are present, which is a connection the clutch cover with the transmission-side flywheel in conventional Way by screwing no longer allow.

In friction clutch with integrated Nachstellvorkehrung for pad wear conventional coupling of friction clutch and flywheel clutch unit on the output shaft of an internal combustion engine axial, rotational and tumbling oscillations are transmitted to the clutch unit, which are excited by the output shaft of the internal combustion engine, in particular crankshaft. So that the coupling unit or the Nachstellvorkehrung are not affected in their function by such vibrations and in particular an undesirable adjustment of the wear compensation arrangement is suppressed, the inertial forces of those components which act on this precaution must be taken into account in the interpretation of Nachstellvorkehrung. In order to avoid this particular caused by axial and tumble vibrations undesirable side effects or the associated higher effort to design a Nachstellvorkehrung to compensate for lining wear, according to a development of the invention, the Nachstellvorkehrung having clutch unit against the excited by the output shaft of the internal combustion engine Axial and bending vibrations largely decoupled. This can be done in that the coupling unit is connectable via an axially elastic or resilient component with the output shaft of the internal combustion engine. The rigidity of this component is dimensioned such that the generated by the output shaft of the internal combustion engine to the clutch unit axial and wobble or bending vibrations are damped or suppressed by this elastic member at least to a degree that a proper function of the friction clutch, in particular ensures their Nachstellvorkehrung. Such elastic components are for example by the EP 0 385 752 A2 and EP 0 464 997 A1 and the SAE Technical Paper 9 003 91 become known. By using an elastic member, it is possible to have an undesirable wear adjustment caused by axial thrust conditions of the pressure plate relative to the clutch cover - especially when disengaged friction clutch - to eliminate by flywheel vibrations and / or vibrations of the plate spring. Such oscillations can lead to a changed setting regardless of the wear state of the clutch disc in clutch units or clutch units without one of these vibrations at least substantially suppressed precaution, in particular an axially compliant disc, wherein the plate spring of the friction clutch could be controlled down in the contact force against a force minimum , whereby the transmission of the desired moment would no longer be guaranteed.

Friction clutches with an automatic or automatic compensation can advantageously be part of a drive unit, in particular for motor vehicles, which consists of an automatic or semi-automatic transmission and a drive motor, wherein arranged between the drive motor, such as an internal combustion engine, and transmission friction clutch at least in dependence Actuation of the transmission is controlled or regulated actuated. The friction clutch is preferably fully automatic actuated. An automated or fully automatic operation of a friction clutch is for example by the DE 40 11 850 A1 has been proposed so that reference is made to this document with regard to the mode of action and the necessary means. In this document, the operation of the friction clutch with slip is described to ensure, for example, a vibration isolation between the gearbox and the engine.

In the previously known drive units with automatic or semi-automatic transmission and conventional friction clutch previously had considerable problems for the clutch actuation and the interpretation of the required actuators such. B. piston / cylinder units and / or electric motors. Due to the relatively high release forces required for conventional clutches very large or large sized actuators are required. This means a large construction volume, high weight and high costs. Also, such large sized actuators are relatively slow due to their inertia in the response time. When using actuators also a larger volume flow of pressure medium is required, so that the supply pump must be relatively large dimensions to ensure the desired operating time for the corresponding friction clutch. To partially remedy the aforementioned disadvantages, for example, by the DE 33 09 427 A1 has been proposed to reduce the actuation force to disengage the clutch by appropriate compensation springs, thereby using smaller sized actuators can. However, since the release force in conventional couplings varies greatly over the life, that is, the release force is relatively low in new condition and increases over the life of increasing pad wear, only a part of the normally required release force can be reduced by a compensation spring. Taking into account all tolerances, despite the use of compensation springs, a release capacity of the actuators will be required which is greater than that for a new conventional clutch. By using a friction clutch according to the invention with lining wear compensation in conjunction with a drive unit consisting of a motor and an automatic or semi-automatic transmission, the release force compared to the aforementioned prior art can be lowered considerably, directly in the clutch, this Ausrückkraftwert or Ausrückkraftverlauf the new clutch over the entire life of the same remains virtually unchanged. This results in significant advantages for the design of the actuators, since their drive power or operating power can be kept down accordingly, with the forces and pressures occurring in the entire release system are correspondingly lower. As a result, the losses occurring in the release system due to friction or elasticity of the components are eliminated or reduced to a minimum.

According to a not belonging to the scope of claim 1 coupling construction, the objects can also be achieved that in a friction clutch with a plate spring loadable pressure plate, wherein the contact pressure is generated by a plate spring, which is supported on the one hand on a component, such as a housing and on the other hand pivotable about a housing provided in a circular arrangement pivot bearing, between the cover and disc spring an automatic, the housing side edition wear away from the housing wegverlagernde adjusting is effective, which is further transported by a feed device and the plate spring in the direction of the pivot bearing under the effect a supporting force is. This support force is expediently permanently available, so that the plate spring against the release force only by force and by a spring force and not by positively articulated hinged means supported. The diaphragm spring is installed over their workspace with degressive curve, in such a way that the supporting force and the Belleville spring force are coordinated so that the support force at the intended installation position of the plate spring and without wear Konizitätsveränderung and on the Ausrückweg the Tel lerfeder is greater than the force applied by the plate spring of the supporting force counteracting force in wear-related change in the conicity of the plate spring, the supporting force over portions of the Ausrückweges the plate spring is less than the shape of the plate spring against the supporting force applied force. The support force can be applied by a single spring element or at least substantially by a single spring element or spring element system. Under "support force" is nevertheless the sum of all effective against the plate spring spring forces - as far as they occur noticeably - to understand, for example, or only by (torque transmission or Abhub-) leaf springs effective, the (residual) suspension of pad suspension or their "replacement".

When Power storage, the supporting force at least substantially applies, can be conveniently used a spring be over the reenactment changes shape, e.g. a plate spring. However, the force-storing force applying the supporting force can also be formed by the leaf springs.

A the support force applying diaphragm spring can be mounted directly on the plate spring, e.g. at the radial height the axially displaceable, cover-side support.

Especially It is advantageous if the adjusting device axially between Disc spring and lid is arranged. The adjustment can in a particularly convenient way Ramps, like ramps, included.

By Such a design of a friction clutch is ensured that the Plate spring over considered the life of the friction clutch, practically always the same taper or tension when engaged Has friction clutch and a virtually constant application of force the pressure plate and thus the clutch disc - regardless of the wear of the friction linings, the Pressure plate itself or other elements, such as the cover or pressure plate side supports, the plate spring or friction surface the flywheel - given is. By the proviso according to the invention about that guaranteed, that the Mass of the pressure plate by the adjuster is not increased. She is still housed in an area in which she Protected against the effects of disc abrasion and in which it is from the source of frictional heat is further away.

A particularly advantageous embodiment of a friction clutch with Adjustment between housing and diaphragm spring can thereby be achieved that the Disc spring on the housing between two editions - by those facing the pressure plate in the direction of the plate spring spring loaded - swiveling supported is, wherein the of the diaphragm spring when disengaging the clutch on the spring-loaded Pad force increases with pad wear and then increases as the acting on the spring-loaded pad counterforce or supporting force. The pressure plate spring has such a characteristic curve that, starting from their constructively defined mounting position in the friction clutch, at a caused by Reibbelagverschleiß relaxation direction the then applied force and thus the required release force first increases and at one opposite the defined installation position further deformed or strained position the force applied by it decreases during disengagement. By such Arrangement and design of the pressure plate spring is ensured that at occurring pad wear itself always a balance between that of the Anpreßtellerfeder on the pad when disengaging exerted Force and acting on the spring-loaded pad counterforce can stop, because when crossing the support force by the force exerted by the diaphragm spring on the support force the diaphragm spring displaced away the sensor spring from the cover-side pad and the adjusting device can be further rotated by the Force of the feed device. Thus, the support is displaced axially, until the pressure exerted by the sensor Force further rotation and a further axial displacement of the support prevented.

Especially Advantageously, it may be, as already mentioned, when the Anpreßtellerfeder is installed in the friction clutch so that they at least over one Part of the release area, preferably practically over the entire release area of the Friction clutch, a sloping force characteristic has. The installation position the contact plate spring can be such that in disengaged State of the friction clutch, the pressure plate spring practically the Minimum or the valley of their sinusoidal force-displacement curve reached or exceeded.

The Applied to the spring-loaded pad counterforce can in an advantageous Be generated by a power storage, which is essentially a constant force at least over the intended adjustment area applies. In particularly advantageous Way is suitable for this a trained and in the prestressed state in the friction clutch built-in plate spring.

The adjusting device according to the invention can be used in a particularly advantageous manner in friction clutches with a Anpreßtellerfeder which acts on the pressure plate with radially outer regions and radially further inward areas between two pivotal pads is mounted on the housing. In this design, the plate spring can act as a two-armed lever.

The However, the invention is not limited to friction clutches with disc springs, at the same time the release lever limited in the form of plate spring tongues, but limited also extends to other coupling assemblies where e.g. the diaphragm spring over additional Lever operated becomes.

Around a perfect adjustment of wear or an optimal contact force for the friction clutch to ensure, It may be particularly advantageous if the on the spring-loaded pad facing away from the Anpreßtellerfeder provided Counter-support is designed such that it axially in the direction of Pressure plate automatically or automatically displaced, in the opposite direction However, by a provision automatically or automatically locked is. The adjustment of the counter-pad, so the lid-side Edition, can be done by means of an energy storage, this counter-edition acted upon in the direction of pressure plate or against the Anpreßtellerfeder. It can therefore be the counter-pad according to the condition caused by the lining wear Automatically relocate the spring loaded support, whereby a play-free pivot bearing of the Anpreßtellerfeder guaranteed can be.

The Counter support can be provided by means of an adjustment plate spring and cover adjustment be axially displaceable. The adjusting device can be a ring-shaped, so in a coherent way Have component that, at least in the engaged state of the friction clutch from the pressure plate spring is acted upon axially. By rotation of the annular member in the event of wear and tear during the Ausrückvorganges can the swivel bearing adjusted according to the pad wear become. Therefor can in a particularly advantageous manner the Nachstellvorkehrung or the annular Component of this Nachstellvorkehrung in the axial direction rising Own adjustment ramps. Furthermore, it may be advantageous if the annular Component bears the counter-pad, the latter can be formed by a wire ring. This Wire ring can be added in a circumferential groove of the component and with this over Be connected positively. The positive connection can be designed as a snap connection.

The Casserole ramps can with cylindrical or ball-like Rolling bodies for Reconciliation interact. However, it can be particularly advantageous be when the ramps with corresponding counter-ramps work together, because then by appropriate choice of the angle of attack These ramps a self-locking in axial clamping of the ramps can be done. The counter-ramps can be of a ring-like Be worn between the component carrying the ramps Component and the lid can be arranged. A particularly simple Structure can, however, by introducing the counter-ramps in the casing guaranteed become. The latter can be done in a particularly simple manner in sheet metal housings, because the counter-ramps marked can be. The embossing can be done in radially extending areas of the housing.

Around a cheap To ensure production of the friction clutch, it can continue from Be beneficial if at least a part of the adjusting device made of plastic. Such plastic parts can through Syringes are made. As plastic are particularly suitable advantageously, thermoplastics, such as e.g. Polyamide. The use of plastics becomes possible because The adjuster itself in a heat only little exposed area. In addition, results due the lower weight and a lower moment of inertia.

The Nachstellvorkehrung may be designed such that they - in the disengaging direction the friction clutch considered - freilaufähnlich acts in the direction of disengagement opposite direction, however, is self-locking. For this purpose, the ramps and / or the Gegenauflauframpen be formed such that they are in axial direction have a pitch angle between 4 and 20 degrees, preferably of the order of 5 to 12 degrees. Advantageously, the ramps and / or counter runnels are so trained that one Self-locking takes place by frictional engagement. The self-inhibition can but also achieved by a positive connection or supports be replaced by e.g. one of the ramps soft and the other with one Profiling is designed, or in that both ramps have profilings. Through these measures is guaranteed that no additional Means are required to avoid an unwanted provision.

The adjusting device can be particularly advantageous and simple if the feed device which is effective in the circumferential direction is designed as a preloaded spring, which acts resiliently on at least one component carrying the ramps and / or a component carrying the counter-ramps or counter-ramps in the adjustment direction. The spring loading can be carried out in an advantageous manner such that the function of the other springs, such as in particular the actuator plate spring and the axially resilient pad acting spring not or practically not be is influenced.

For some use cases It may be advantageous if the Nachstellvorkehrung several relocatable Adjustment elements, such as in the radial and / or circumferential direction has displaceable adjusting wedges or rolling elements. Furthermore, can it may be advantageous if the Nachstellvorkehrung is speed-dependent. Thus, e.g. the effect on individual elements of the Nachstellvorkehrung einwir kende Centrifugal force for actuation and / or to lock the adjuster at certain operating conditions the internal combustion engine are used. In particular, the Adjustment by means of centrifugal force dependent means from a certain Speed, be blocked, which is e.g. at least approximate Idle speed or speed below the idle speed can, so that the wear adjustment only takes place at low speeds. This has the advantage that no unwanted adjustments caused by vibrations at high speeds could arise occur.

One particularly simple and reliable construction of the adjusting device can be guaranteed be that the displaceable relative to the housing Parts which have ramps and / or counter-ramps or counter-ramp areas, are resiliently loaded. If only a corresponding component with the corresponding ramps or areas is present, compared to the casing is displaceable, this is applied. Especially advantageous It can be there, when the spring load a force in the circumferential direction generated.

For the construction and the function of a friction clutch with adjuster between housing and Anpresstellerfeder it may also be advantageous if the sensor spring formed as a disc spring, like a diaphragm spring itself with its radially outer area on an axially fixed component, such as the housing is supported and with radially inward lying Areas applied to the turning off the cover Abwälzauflage. These Abroll pad can also be integrally formed with the sensor spring, so that so the Sensor plate spring also forms the pad. For holding the sensor spring in a strained position, the housing Wear support areas. These support areas can through individual, on the housing attached support elements be formed. However, it may also be advantageous if the support areas are integral with the housing, e.g. can on the housing embossings or cut and deformed areas are provided, which the sensor spring for support axially engage.

For the function of a friction clutch, in particular for minimizing Ausrückkraftverlaufes or the maximum required disengaging force, it may be particularly advantageous if the clutch plate einklemmbare between clutch plate has friction linings, between which a so-called pad suspension, as for example by the DE 36 31 863 A1 has become known, is provided. By using such a clutch disc actuation, in particular the disengagement of the friction clutch is supported. This is due to the fact that in the engaged state of the friction clutch, the tensioned lining suspension on the pressure plate exerts a reaction force, which is directed opposite to the force exerted by the Anpreßtellerfe- or actuator plate spring on this pressure plate. During disengagement during the axial displacement of the pressure plate, this initially pushed back by the resiliently tensioned lining suspension, wherein at the same time decreases the pressure exerted by this force on the pressure plate due to the present in the disengagement region relatively steeply sloping characteristic section of the pressure plate. As the force applied to the pressure plate by the pressure plate spring decreases, so does the restoring force exerted by the lining suspension on this pressure plate. The force required to disengage the friction clutch force results from the difference between the restoring force of the lining suspension and contact pressure of the Anpreßtellerfeder. After relaxation of the lining suspension, ie at Abhub the pressure plate of the friction linings or release of the clutch disc by the pressure plate, the required release force is mainly determined by the Anpreßtellerfeder. The force-displacement characteristics of the lining suspension and the force-travel characteristics of the Anpreßtellerfeder can be matched to one another in a particularly advantageous manner such that upon release of the clutch disc by the pressure plate for actuating the Anpreßtellerfeder required force is at a low level. It can therefore be required by targeted vote or even approximation of the pad spring characteristic of the Anpreßtellerfedercharakteristik until the release of the clutch disc by the pressure plate only a very small, in the extreme case virtually no operating force for the Anpreßtellerfeder to overcome the remaining output. Furthermore, the characteristic of the Anpreßtellerfeder be designed such that after released clutch disc then the force of the Anpreßtellerfeder pivoting force or required for pivoting the Anpreßtellerfeder force against the force applied by this Anpreßtellerfeder in the engaged state of the friction clutch contact pressure at a very low Level is. There are also interpretations possible in which when releasing the clutch disc by the pressure plate only a very small or virtually no force is required to the Anpreßtellerfeder to disengage the clutch. Such friction clutches can be designed so that the actuating forces are of the order of 0 to 200 N.

According to one Another idea, the friction clutch can be designed in such a way that at least nearly upon release of the clutch disc by the pressure plate of the contact plate spring applied axial force is in the zero range, with at Continuation of the disengagement process that of the pressure plate spring applied force can be negative, so a reversal of Force effect of the Anpreßtellerfeder takes place. This means that at Completely disengaged Frictional clutch this practically remains open by itself and only by external force the engagement process can be initiated again.

Further Advantages and appropriate training Self-adjusting friction clutches are related explained in more detail with the following description of the figures.

Mentioned first, that in the 1 to 27 Constructions of friction clutches are shown, which are not covered by the scope of claim 1, since in these the adjusting device between the clutch housing and the Anpresstellerfeder is effective. In principle, however, those features which are applicable to the design of the Anpresstellerfeder and the provision which cause a gradual build-up of the transferable from the clutch disc of the friction clutch moment during the engagement process, as well as their interaction in friction couplings according to the invention. The latter also applies to the features which relate to the design of a compensation component or the ramp design of an adjustment device. The diagrams according to 8th . 10 . 18 and 19 show characteristics of different spring elements, which can also be realized in the friction clutches according to the invention.

in the Individual shows:

1 a friction clutch in view,

2 a section according to the line II-II of 1 .

3 one in the friction clutch according to the 1 and 2 used adjusting ring,

4 a section along the line IV-IV of 3 .

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

6 a section according to the line VI-VI of 5 .

7 and 7a a spring which exerts a twisting force on the adjusting ring,

the 8th to 11 Diagrams with different characteristics, from which the interaction of the individual spring and adjusting elements of a friction clutch can be seen,

the 12 and 13 a further embodiment possibility of a friction clutch, wherein 13 a section according to the line XIII of 12 represents,

14 in the friction clutch according to the 12 and 13 used adjusting ring in view,

the 15 to 17 Details of another friction clutch with a compensation arrangement,

the 18 and 19 Diagrams with different characteristic curves from which the interaction of a pressure plate spring and a pad spring as well as the resulting effect on the Ausrückkraftverlauf a friction clutch can be seen,

20 another friction clutch in partial view,

20a a partial view in the direction of arrow A of 20 .

21 a section according to the line XXI the 20 .

22 a partial view of a friction clutch according to the 20 to 21 usable adjusting ring, the 23 and 24 further variants of friction clutches,

25 an adjusting ring in view, in a friction clutch according to the 12 and 13 or 20 to 21 could be used

the 26 and 27 additional variants of friction clutches,

28 an at least the claim 1 corresponding friction clutch in view,

29 a section along the line II-II of the 28 .

30 a section along the line III-III of 28 .

31 a partial section according to the line IV-IV of 28 .

32 one in the friction clutch according to the 28 and 29 used adjusting ring in view,

the 33 and 34 Details of further embodiments of friction clutches according to the invention,

the 35 a two-mass flywheel with torsional vibration damper and a friction clutch,

the 36 and 37 a torque transmitting device with a friction clutch.

The in the 1 and 2 illustrated friction clutch 1 has a housing 2 and a rotatably connected thereto, but axially limited displaceable thrust washer 3 , Axial between the thrust washer 3 and the lid 2 is a pressure plate spring 4 Tense, the one from the housing 2 worn ring-like pivot bearing 5 is pivotable and the pressure plate 3 in the direction of one over screws 6a with the housing 2 firmly connected counterpressure plate 6 , such as a flywheel, impinged, causing the friction linings 7 the clutch disc 8th between the friction surfaces of the thrust washer 3 and the counterpressure plate 6 be clamped.

The pressure disc 3 is with the case 2 over circumferentially or tangentially directed leaf springs 9 rotatably connected. In the illustrated embodiment has the clutch disc 8th so-called pad spring segments 10 , which, as is known, a progressive torque build-up when engaging the friction clutch 1 Ensure by having a limited axial displacement of the two friction linings 7 towards each other to a progressive increase in the friction linings 7 enable acting axial forces. However, it could also be used a clutch disc, in which the friction linings 7 axially practically rigidly applied to a carrier disk.

In the illustrated embodiment, the plate spring has 4 a contact pressure applying annular base body 4a , from the radially inwardly extending actuating tongues 4b out. The plate spring 4 is installed in such a way that it with radially outermost areas the pressure plate 3 acted upon and with radially inner areas around the pivot bearing 5 is tiltable.

The pivot bearing 5 includes two swivel pads 11 . 12 which are formed here by wire rings and between which the plate spring 4 axially supported or clamped. The on the pressure plate 3 facing side of the plate spring 4 provided swivel pad 11 is axially in the direction of the housing 2 by means of an energy store 13 with force. The energy storage 13 is by a plate spring or by a plate spring-like component 13 formed, which is with its outer edge area 13a on the housing 2 supports and with radially inward sections the swivel pad 11 against the actuator spring 4 and thus also in the direction of the housing 2 acted upon axially. The between the pressure disc 3 and the actuator spring 4 provided plate spring 13 has an outer annular edge region 13b , from the inner edge radially inwardly extending tongues 13c go out, which is due to the swivel pad 11 support.

To support the plate-spring-like component 13 are in the illustrated embodiment, the housing 2 additional funds 14 attached, which is a swivel support for the plate spring-like component 13 form. These additional means can be achieved by attached or riveted segmental items 14 be formed, which can be evenly distributed over the circumference. The means 14 However, can also be formed by an annular, self-contained component. Furthermore, the support means 14 directly from the case 2 be formed out, for example, in the axial region of the housing 2 introduced stampings or by tongue-shaped cutouts, which after insertion and tensioning of the plate spring-like component 13 under the outer edge region of this component 13 be urged by material deformation. Furthermore, between the support means 14 and the plate spring-like component 13 a bayonet-type connection or locking be present, so that the plate-spring-like component 13 initially biased and its radially outer portions axially over the support means 14 can be brought. Thereafter, by a corresponding rotation of the plate spring-like component 13 opposite the housing 2 the support areas of the component 13 for contact with the support means 14 to be brought. The support areas of the plate spring-like component 13 can thereby by on the annular body 13b be formed radially outwardly protruding boom.

To prevent rotation of the actuator spring 4 and optionally the plate-spring-like component 13 and for centering the wire rings 11 . 12 are on the case 2 axially extending centering means in the form of rivet elements 15 attached. The rivet elements 15 each have an axially extending shaft 15a which extends axially through one between adjacent plate spring tongues 4b envisaged section extends and the on of him to parent tongue 13c the plate spring 13 molded areas 13d can be partially encompassed.

The plate spring-like component or the plate spring 13 is designed as a sensor spring which generates over a predetermined travel an at least substantially approximately constant force. About this sensor spring 13 which is on the tongue tips 4c intercepted acting Kupplungsausrückkraft, with always an at least approximate balance between by the release force on the swivel pad 11 generated force and by the sensor plate spring 13 on this swivel pad 11 applied counterforce prevails. By disengagement force is meant the force which occurs during the actuation of the friction clutch 1 on the tongue tips 4c or is exerted on the release lever of the diaphragm spring tongues.

The housing-side swivel pad 12 is about a Nachstellvorkehrung 16 on the housing 2 supported. This adjustment 16 ensures that at an axial displacement of the swivel pads 11 and 12 in the direction of the pressure disk 3 or in the direction of the counter-pressure plate 6 no unwanted play between the swivel pad 12 and the housing 2 or between the swivel pad 12 and the plate spring 4 can arise. This ensures that no unwanted dead or empty paths in the operation of the friction clutch 1 arise, resulting in optimum efficiency and thus proper operation of the friction clutch 1 given is. The axial displacement of the swivel pads 11 and 12 occurs at axial wear on the friction surfaces of the pressure plate 3 and the counterpressure plate 6 and the friction linings 7 , The operation of the automatic adjustment of the pivot bearing 5 is still in connection with the diagrams according to the 8th to 11 explained in more detail.

The Nachstellvorkehrung 16 comprises a spring-loaded adjusting element in the form of a ring-like component 17 that in the 3 and 4 is shown. The ring-like component 17 has circumferentially extending and axially rising ramps 18 that extend beyond the circumference of the component 17 are distributed. The adjusting element 17 is in the clutch 1 installed so that the ramps 18 the caseback 2a are facing. On the ramps 18 facing away from the adjusting element 17 is the swivel pad formed by a wire ring 12 in a groove-shaped receptacle 19 ( 2 ) centrically positioned. The recording 19 can be designed such that the swivel pad 12 on the adjusting element 17 is also secured in the axial direction. This can be z. B. take place in that at least partially to the recording 19 adjacent areas of the adjuster 17 the swivel pad 12 cling firmly hold or a snap connection for the swivel pad 12 form. When using different materials for the swivel support 12 and the adjusting element 17 It may be appropriate to compensate for the resulting in large temperature changes expansion differences when designed as a wire ring swivel pad 12 is open, so is separated over the circumference at least at one point, whereby a movement of the wire ring 12 opposite the recording 19 is made possible in the circumferential direction and thus the wire ring 12 to the diameter of the recording 19 can adapt.

In the illustrated embodiment, the adjusting element 17 made of plastic, such as made of a heat-resistant thermoplastic, which may additionally be fiber reinforced. This allows the adjusting element 17 produce in a simple manner as a molded part. The adjusting element 17 However, it can also be produced as a sheet metal part or by sintering. Furthermore, with appropriate choice of material, the swivel pad 12 with the adjusting element 17 be formed integrally. The swivel edition 11 can directly through the sensor spring 13 be formed. For this, the tips of the tongues 13c corresponding embossings or projections, such. B. have beads.

The adjusting ring 17 is through the axially extending areas 15a the evenly distributed over the circumference rivets 15 centered. For this purpose has the adjusting ring 17 Zentrierungskonturen 20 formed by circumferentially extending recesses 21 are formed, which radially within the pivotal support 11 lie. To form the recesses 21 owns the adjusting ring 17 at the inner edge region radially inwardly extending cams 22 , the radially inner contours of the recesses 21 limit.

How out 3 can be seen, are viewed in the circumferential direction, between the evenly spaced recesses 21 5 ramps each 18 intended. The recesses 21 are formed in the circumferential direction such that these at least one angle of rotation of the adjusting ring 17 opposite the housing 2 allow the over the life of the friction clutch 1 an adjustment of the friction surfaces of the thrust washer 3 and the counterpressure plate 6 and the friction linings 7 guaranteed wear guaranteed. Depending on the design of the ramps, this adjustment angle can be of the order of magnitude between 8 and 60 degrees, preferably of the order of magnitude of 10 to 30 degrees. In the illustrated embodiment, this twist angle is in the range of 12 degrees, wherein the installation angle 23 the ramps 18 also in the range of 12 degrees. This angle 23 is chosen such that the pressing together of the ramps 18 of the adjusting ring 17 and the counter-ramps 24 in the 5 and 6 shown support ring 25 resulting friction slipping between the ramps 18 and 24 prevented. Depending on the material pairing in the area of the casserole 18 and counter-ramps 24 can the angle 23 range between 4 and 20 degrees.

The adjusting ring 17 is spring-loaded in the circumferential direction, in Nachstelldrehrichtung, ie in the direction which by ramping the ramps 18 at the counter ramps 24 of the support ring 25 an axial displacement of the adjusting ring in the direction of thrust washer 3 That means in the axial direction of the radial housing section 2a away causes. In the in the 1 and 2 illustrated embodiment, the spring load of the adjusting ring 17 by at least one annular leg spring 26 ensures, for example, which may have two turns and at one of its ends a radially extending leg 27 own, the rotation with the adjusting ring 17 is, and at the other end an axially extending leg 28 has, the rotationally fixed to the housing 2 is mounted. The feather 27 is installed resiliently braced.

The in the 5 and 6 shown support ring 25 is also formed by an annular member, which counter-ramps 24 owns which complementary surfaces to those through the ramps 18 forming limited areas, passing through the ramps 18 and counter-ramps 24 limited areas may also be congruent. The angle of attack 29 the counter-ramp 24 corresponds to the angle 23 the ramps 18 , As by comparing the 3 and 5 it can be seen, are the ramps 18 and the counter ramps 24 similarly distributed in the circumferential direction. The support ring 25 is with the case 2 rotatably connected. For this purpose has the support ring 25 recesses distributed over the circumference 30 through which the riveting approaches of the rivet 15 therethrough.

In 2 is dashed another ring-shaped leg spring 26a hinted that, similar to the leg spring 26 may be bent at their end portions to a rotationally fixed connection with on the one hand the housing 2 and on the other hand the adjusting element 17 to ensure. This spring 26a is also installed resiliently braced so that they on the adjusting 17 exerts a twisting force. The use of two torsion springs 26 . 26a may be advantageous for some applications, as upon rotation of the friction clutch 1 as a result of the spring 26 respectively. 26a acting centrifugal forces a spring force amplification occurs. By using two torsion springs, for example, on the spring 26 occurring force amplification by that of the leg spring 26a applied force can be compensated. For this are the torsion springs 26 and 26a wound so that they at least under the influence of centrifugal force on the adjusting 17 Create forces that act in the circumferential direction opposite. The two thigh springs 26 . 26a can have one or more turns, furthermore, these leg springs can 26 . 26a have different winding diameters, as in 2 is shown, with the normally associated and on the springs 26 . 26a acting centrifugal forces, which vary in the circumferential forces on the adjusting 17 would produce, by appropriate interpretation of the wire size and / or the number of turns of the individual springs 26 . 26a can be at least approximately compensated. In 2 is the spring 26 radially inside the adjusting element 17 and the spring 26a radially outside of this adjusting element 17 arranged. Both springs could, however, by appropriate design also radially inside or radially outside of the adjusting 17 be arranged.

In 7 is the leg spring 26 shown in plan view. In relaxed condition, the leg spring 26 are the thighs 27 . 28 at an angle 31 offset, which may be on the order of 40 to 120 degrees. In the illustrated embodiment, this angle 31 in the order of 85 degrees. With 32 is the relative position of the thigh 27 opposite the thigh 28 shown, this with new friction linings 7 in the friction clutch 1 occupies. With 33 is the position of the thigh 27 shown, the maximum allowable wear on the friction linings 7 equivalent. The adjustment angle 34 is in the illustrated embodiment in the order of 12 degrees. The feather 26 is formed such that in the relaxed state of this spring 26 between the two thighs 27 . 28 just a wire turn 35 runs. In the remaining peripheral region are two wire turns axially superimposed. The feather 26a is similar to the spring 26 formed, however, has a larger winding diameter and a different clamping direction with respect to the adjusting element 17 according to 2 , The one by the spring 26 on the adjusting ring 17 However, applied force is greater than that of the spring 26a ,

In new condition of the friction clutch 1 grab the ramps 18 and counter-cushions groups 24 forming axial cams 18a . 24a the most axi al in each other, that means that the superimposed rings 17 and 25 need the least axial space.

In the embodiment according to the 1 and 2 are the counter-ramps 24 or the cam-shaped projections forming these 24a formed by a separate component. The counter-ramps 24 However, they can go directly through the case 2 be formed, for example by impressing cam-shaped lugs that can extend into the housing space. The embossing is particularly advantageous in sheet metal housings or lids, which are integrally formed.

To the adjusting ring 17 before mounting the friction clutch 1 in its retracted position, this has in the area of the cams 22 attack areas 36 for a twisting or retaining means, on the other hand, on the housing 2 can support. Such retaining means may be used in the manufacture or assembly of the friction clutch 1 be provided and after assembly of the friction clutch 1 on the flywheel 6 be removed, causing the readjustment 16 is activated. In the illustrated embodiment are for this purpose in the lid or housing 2 in the circumferential direction laid elongated recesses 37 and in the adjusting ring 17 a recess or a paragraph 38 intended. The elongated recesses in the circumferential direction 37 must have at least one such extent that the adjusting ring 17 can be rotated back according to the largest possible wear adjustment angle. It can also after the assembly of the friction clutch 1 a twisting tool axially through the slots 37 the lid passed and into the recesses 38 the adjusting ring 17 be introduced. After that, the ring can 17 be rotated back by means of the tool, so that this in the direction of the radial region 2a of the housing 2 is shifting and facing this area 2a its smallest axial distance occupies. In this position then the adjusting ring 17 secured, for example by a clip or a pin, in an aligned recess of the lid and the adjusting ring 17 engages and prevents twisting of these two components. This pin can after the assembly of the friction clutch 1 on the flywheel 6 be removed, so that, as already mentioned, the adjusting device 16 is released. The slots 37 in the case 2 are formed such that during disassembly or after disassembly of the friction clutch 1 from the flywheel 6 the adjusting ring 17 can be brought into its withdrawn position. This is the coupling 1 first disengaged so that the actuator spring 4 on the swivel pad 12 no axial force exerts and thus a perfect rotation of the adjusting ring 17 is guaranteed.

In connection with the in the diagrams according to the 8th to 11 Registered characteristics is now the operation of the above-described friction clutch 1 explained in more detail.

The line 40 in 8th shows the function of the Konizitätsveränderung the diaphragm spring 4 generated axial force, namely deformation of the diaphragm spring 4 between two supports whose radial distance from the radial distance between the pivot bearing 5 and the radially outer support diameter 3a at the pressure disk 3 equivalent. The abscissa represents the relative axial travel between the two supports and the ordinate shows the force generated by the diaphragm spring. The point 41 represents the installation position of the diaphragm spring 4 with the clutch closed 1 that is the position at which the diaphragm spring 4 for the corresponding mounting position, the maximum contact pressure on the thrust washer 3 exercises. The point 41 can by changing the conical mounting position of the plate spring 4 along the line 40 be moved up or down.

The line 42 represents the of the pad spring segments 10 applied axial spreading force, which between the two friction linings 7 acts, dar. This axial spreading force acts of the diaphragm spring 4 on the pressure disc 3 counteracted axial force. It is advantageous if the for the possible elastic deformation of the spring segments 10 required axial force at least that of the diaphragm spring 4 on the pressure disc 3 corresponds to the applied force. When disengaging the friction clutch 1 relax the spring segments 10 , over the way 43 , About this also a corresponding axial displacement of the pressure plate 3 appropriate way 43 becomes the disengagement process of the clutch 1 supports, that means that a lower maximum release force must be applied, than that which the installation point 41 in the absence of the pad spring segments 10 would correspond. When crossing the point 44 become the friction linings 7 released, due to the degressive curve of the diaphragm spring 4 the then still applied release force is significantly reduced compared to that which the point 41 would correspond. The release force for the clutch 1 decreases until the minimum or the valley point 45 the sinusoidal characteristic 40 is reached. When exceeding the minimum 45 increases the required release force again, the Ausrückweg in the tongue tips 4c is chosen so that even when exceeding the minimum 45 the release force is not the point 44 exceeds existing maximum release force, preferably below this remains. So it's the point 46 not be exceeded.

The spring serving as a force sensor 13 has a path-force course according to the line 47 of the 9 , This characteristic 47 corresponds to that which is generated when the plate spring-like component 13 is changed from the relaxed position in its conicity, between two pivot supports, which have a radial distance, the radial distance between the pivot supports 11 and 14 equivalent. Like the characteristic 47 shows, has the plate spring-like component 13 a spring travel 48 over which the axial force generated by her remains practically constant. The in this area 48 generated force is chosen such that these in the point 44 of the 8th Anste existing release force of the clutch corresponds at least approximately. The of the sensor spring 13 applied supporting force is opposite to the point 44 corresponding force of the diaphragm spring 4 according to the leverage of this disc spring 4 reduced. This ratio is in most cases in the range between 1: 3 to 1: 5, but may be larger or smaller for some applications.

The aforementioned plate spring ratio corresponds to the ratio between the radial distance of the pivot bearing 5 for support 3a and the radial distance of the pivot bearing 5 to the plant diameter 4c , eg for a release bearing.

The installation position of the plate spring-like element 13 in the friction clutch 1 is chosen such that this in the region of the pivot bearing 5 an axial spring travel in the direction of the friction linings 7 can pass through, both at least the axial Nachstellweg the pressure plate 3 in the direction of the counter-pressure plate 6 corresponds, which arises as a result of Reibflächen- and Reibbelagverschleißes, as well as an at least approximately constant axial support force for the pivot bearing 5 guaranteed. That means the linear range 48 the characteristic 47 should at least have a length that corresponds to the mentioned wear path, preferably greater than this wear path, as this also installation tolerances can be at least partially compensated.

To a practically constant or defined release point 44 the friction linings 7 when disengaging the friction clutch 1 To obtain a so-called double-segment pad suspension between the friction linings 7 can be used, ie a pad spring, are provided in the pairwise individual spring segments back to back, wherein the individual pairs of segments may have a certain axial bias relative to each other, so that the total applied by the lining suspension axial force at not clamped clutch disc 8th at least the one with the point 44 corresponding release force on the diaphragm spring 4 corresponds, preferably slightly higher. By biasing the spring means provided between the pads can be achieved that the occurring over the operating time embedment losses of the segments in the back of the pads are at least substantially compensated or compensated. Embedding losses are to be understood as the losses which result from incorporation of the segments in the back of the linings. It is useful if the bias of the provided between the pads suspension in the order of 0.3 mm to 0.8 mm, preferably in the order of 0.5 mm. By a corresponding limitation of the axial spring travel between the two friction linings 7 and by a defined bias of effective between the friction linings suspension can be further achieved that at least when disengaging the friction clutch 1 the pressure plate 3 over a defined path 43 is pushed back by the provided between the coverings suspension. To a defined way 43 To obtain the axial path between the friction linings by appropriate stops both in the relaxation direction and in the direction of tension of the pad spring 10 be limited.

For optimal function of the friction clutch 1 or to ensure the automatic compensation of the lining wear ensuring adjusting device, it makes sense that on the Ausrückkraftverlauf 49 according to 10 considered first by the pad springing 10 and the sensor spring 13 on the plate spring 4 applied and adding forces and after lifting the pressure plate 3 from the friction linings 7 then only from the sensor spring 13 on the plate spring 4 applied force greater, but at least equal to or is, as in the area 4c the plate spring tongue tips attacking and correspondingly 10 over the Ausrückweg changing release force.

The previous consideration corresponds to a very specific installation position of the diaphragm spring 4 , and there was no wear on the friction linings 7 considered.

For axial wear, especially the friction linings 7 , the position of the thrust washer shifts 3 in the direction of the counter-pressure plate 6 , whereby a change of the conicity and thus also of the diaphragm spring in the engaged state of the friction clutch 1 applied contact force arises, in the sense of an increase. This change causes the point 41 towards the point 41 ' wanders, and the point 44 in the direction of the point 44 ' , This change will affect the disengagement of the clutch 1 originally existing equilibrium of forces in the area of the swivel pad 11 between the actuator spring 4 and the sensor spring 13 disturbed. The increase in Tellerfederanpreßkraft for the pressure plate caused by the lining wear 3 also causes a shift in the course of the release force in the sense of an increase. The resulting Ausrückkraftverlauf is in 10 through the dashed line 50 shown. By increasing the Ausrückkraftverlaufes is during the disengagement of the friction clutch 1 from the sensor spring 13 on the plate spring 4 applied axial force overcome, so that the sensor spring 13 in the area of pivoting bearings 5 to give way to an axial path, which is essentially the wear of the friction linings 7 equivalent. During this deflection phase of the sensor spring 13 the plate spring is supported 4 at the loading area 3a the pressure disk 3 off, so that this plate spring 4 their taper changed and thus also the energy stored in this or stored in this torque and consequently also by the diaphragm spring 4 on the swivel pad 11 or the sensor spring 13 and on the pressure disk 3 applied force. This change takes place as related to 8th can be seen in the sense of a reduction of the disc spring 4 applied forces. This change takes place as long as that of the diaphragm spring 4 in the range of the swivel edition 11 on the sensor leather 13 applied axial force is in equilibrium with that of the sensor spring 13 generated drag. This means that in the diagram according to 8th the points 41 ' and 44 ' again in the direction of the points 41 and 44 hike. After this balance is restored, the thrust washer can 3 again from the friction linings 7 take off. During this adjustment phase of wear during a disengagement of the friction clutch 1 becomes the adjuster 17 the adjusting device 16 through the preloaded spring 26 twisted, which also causes the swivel pad 12 according to the lining wear nachwandert, and thus a backlash-free pivot bearing 5 the plate spring 4 is guaranteed. After the adjustment, the Ausrückkraftverlauf corresponds again to the line 49 according to 10 , The lines 50 and 51 of the 10 represent the axial path of the thrust washer 3 at a Ausrückkraft-way course corresponding to the lines 49 . 50 ,

In the diagram according to 11 is the flow of forces during a disengaging operation on the housing 2 or on the plate spring 13 applied force, the extreme values were capped. Starting from the engaged position according to 1 acts on the housing 2 and thus also on the pressure disk 3 First, a force that is the installation point 41 ( 8th ) of the plate spring 4 equivalent. During the disengagement process, which takes through the diaphragm spring 4 on the case 2 or the swivel pad 12 applied axial force according to the line 52 of the 11 off, to the point 53 , When crossing the point 53 in the disengagement would in a conventional clutch, in which the plate spring is mounted axially fixed to the housing pivotally, so the swivel pad 11 axially unyielding with the housing 2 would be connected, an axial direction reversal of the force by the diaphragm spring 4 on the case 2 at the radial height of the pivot bearing 5 occur. When coupling is in the area of the pivot bearing 5 by the axial inversion of the through the diaphragm spring 4 in the area of pivoting bearings 5 generated force through the sensor spring 13 intercepted. Upon reaching the point 54 raises the diaphragm spring 4 from the loading area 3a the pressure disk 3 from. At least to this point 54 becomes the disengaging operation of the friction clutch 1 by the of the lining suspension 10 supported axial force supported. The of the pad suspension 10 applied force increases with increasing Ausrückweg in the area 4c the tongue tips or with increasing axial Ausrückhub the pressure plate 3 from. The line 52 So represents a resulting considered on the disengagement process, on the one hand in the tongue tip area 4c acting release force and on the other hand in the radial region 3a on the plate spring 4 through the padding suspension 10 exerted axial force. When the point is exceeded 54 in the disengagement direction is the of the diaphragm spring 4 on the swivel pad 11 applied axial force by that of the sensor disc spring 13 applied counterforce intercepted, these two forces, at least after relief of the friction linings 7 through the pressure disk 3 are in equilibrium and continuation of the disengagement of the sensor spring 13 in the area of pivoting bearings 5 applied axial force is preferably slightly larger than the upcoming release force. The subarea 55 the characteristic 52 according to the diagram 11 shows that with increasing Ausrückweg the disengagement force or by the plate spring 4 on the swivel pad 11 applied force is smaller than at the point 54 upcoming release force. The dashed line 56 corresponds to a state of the friction clutch 1 , in which in the field of friction linings 7 Wear has occurred, but still no adjustment in the area of the pivot bearing 5 is done. Again, it can be seen that the change caused by the wear of the mounting position of the plate spring 4 an increase in the case 2 and on the swivel pad 11 or on the sensor spring 13 exerted forces. This has in particular the consequence that the point 54 in the direction of the point 54 ' migrates, which causes the friction clutch when re-disengaging process 1 the one from the diaphragm spring 4 on the sensor leather 13 in the range of the swivel edition 11 applied axial force is greater than the opposing force of the sensor spring 13 , whereby the adjusting process already described by axial rebound of the sensor spring 13 he follows. By this adjustment process becomes the point 54 ' again in the direction of the point 54 shifted, whereby the desired state of equilibrium in the field of Schwenkauflagerung 5 between the plate spring 4 and the sensor spring 13 is restored.

In practice finds the described adjustment continuously or in very small steps, so that the better understanding of the Invention illustrated in the diagrams large point shifts and Characteristic shifts do not normally occur.

It can over the operating time of the friction clutch 1 some function parameters or operating points change. For example, by improper operation of the friction clutch 1 Overheating of the pad suspension 10 take place, the setting, so a reduction in the axial suspension of the pad suspension or lining segments 10 can result. By an appropriate interpretation of the characteristic 40 the plate spring 4 and corresponding adjustment of the course 47 the sensor spring 13 However, a reliable operation of the friction clutch can be ensured. An axial setting of the padding suspension 10 would only mean that the diaphragm spring 4 one opposite the in 1 position shown would take durchgedrücktere position, taking the disk spring 4 applied to the thrust washer pressing force would be slightly lower, as in connection with the characteristic 40 according to 8th is recognizable. Furthermore, a corresponding axial deformation of the sensor spring 13 and thus a corresponding axial displacement of the swivel pad 11 respectively.

According to another idea, the can on the actuator spring 4 acting resultant support force with increasing wear of the friction linings 7 increase. The increase may be to a portion of the total maximum permitted wear path of the friction linings 7 be limited. The increase in the support force for the actuator spring 4 can thereby by appropriate interpretation of the sensor spring 13 respectively. In 9 is dashed and with the reference numeral 47a characterized a corresponding characteristic curve over the area 48 shown. By an increase in the support force for the actuator spring 4 with increasing wear can be a contact pressure drop of the actuator spring 4 for the printing plate 3 , due to a decrease in the pad suspension, eg by embedding the segments in the pads, at least partially compensated. It may be particularly advantageous if the support force for the actuator plate spring 4 increases proportionally to the setting of the pad suspension or proportional to the segment embedding in the pads. This means that with decreasing the thickness of the disc in the region of the linings, ie reduction of the distance between the friction surfaces of the linings due to the segment embedding and / or setting the lining suspension and / or pad wear, the mentioned supporting force should increase. It is particularly advantageous if the increase in force takes place in such a way that it is greater over a first partial area than in a second partial area adjoining thereto, the two partial areas being within the area 48 according to 9 are located. The latter design is advantageous because most of the mentioned embedding between the spring segments and the linings takes place mainly within a small compared to the entire life of the friction clutch period and then stabilize the conditions between the spring segments and the friction linings practically. This means that, after a certain embedding, there is no longer any significant change in the embedding. An increase in the support force for the actuator spring can also be done over at least a portion of Abriebverschleißes the friction linings.

In the previous description of the readjustment process to compensate for the friction lining wear were by the leaf spring 9 possibly applied axial forces are not considered. At a bias of the leaf springs 9 in the sense of a lift off the thrust washer 3 from the corresponding friction lining 7 , ie in the sense of pressing the thrust washer 3 against the plate spring 4 there is a support of the disengagement process. It is superimposed by the leaf springs 9 applied axial force with that of the sensor spring 13 and the plate spring 4 applied forces and with the release force. This was for better understanding in the description of the diagrams according to the 8th to 11 not considered. The the actuator spring 4 in the disengaged state of the friction clutch 1 against the lid-side roller bearing 12 acting total force results from the addition of forces, which mainly by the leaf spring elements 9 , through the sensor leather 13 and by the existing release force on the actuator spring 4 be exercised. The leaf spring elements 9 can do so between the lid 2 and the printing plate 3 be installed that with increasing wear of the friction linings 7 through the leaf springs 9 on the actuator spring 4 applied axial force is greater. So, for example, over the way 48 according to 9 and thus also over the wear compensation path of Nachstellvorkehrung 16 those of the leaf springs 9 applied axial force a course along the line 47b exhibit. Out 9 can also be seen that with increasing spring deflection of the sensor spring 13 those of the leaf springs 9 on the printing plate 3 applied restoring force, which also on the actuator spring 4 works, increases. By Addition of the force curve according to the characteristics 47b and the plate spring characteristic results in the resulting force curve, which axially on the plate spring 4 acts, in the sense of pressing the diaphragm spring 4 against the cover-side swivel pad 12 , To a course according to the line 47a To obtain, it is expedient to interpret the sensor disc spring such that it has a characteristic curve corresponding to the line 47c of the 9 having. By adding the force curve according to line 47c and the force curve according to the line 47b then results in the force curve according to line 47a , It can therefore by a corresponding bias of the leaf springs 9 the applied by the sensor spring support force and the Abstützkraftverlauf be reduced. By appropriate design and arrangement of the leaf spring elements 9 can also be at least partially compensated for a decrease in the lining suspension and / or embedding the lining spring segments in the pads. It can therefore be ensured by the fact that the plate spring 4 maintains substantially the same operating point or the same operating range, so that the plate spring 4 over the life of the friction clutch essentially an at least approximately constant contact pressure on the pressure plate 3 exercises. Furthermore, in the design of the friction clutch, in particular the sensor spring 13 and / or the leaf springs 9 passing through the on the adjusting element 17 acting Nachstellfedern 26 and or 26a generated resultant axial force, which is the sensor spring 13 and / or the leaf springs 9 counteracts.

In a design of the friction clutch 1 with preloaded leaf springs 9 must still be taken into account that by the bias of the leaf springs 9 the of the pressure plate 3 on the friction linings 7 applied axial force is affected. This means that at a bias of the leaf springs 9 in the direction of the actuator spring 4 the one from the diaphragm spring 4 applied contact pressure about the biasing force of the leaf springs 9 is reduced. It thus forms in such a friction clutch 1 a resulting pressure force for the pressure plate 3 or for the friction linings 7 , which is due to superposition of the Anpreßkraftverlaufes the diaphragm spring 4 with the tension of the leaf springs 9 results. Assuming that - over the operating range of the friction clutch 1 considered - the characteristic 40 according to 8th the resulting force curve from actuator spring 4 and preloaded leaf springs 9 in the new condition of the friction clutch 1 represents, would reduce the distance between the pressure plate 3 and the counterpressure plate 6 as a result of lining wear, a shift of the resulting course in terms of a reduction result. In 8th is a dashed line 40a represented, for example, a total lining wear of 1.5 mm. Through this over the life of the friction clutch occurring shift of the line 40 in the direction of the line 40a decreases when disengaging the friction clutch 1 through the plate spring 4 on the sensor leather 13 applied axial force, due to the increasing wear by the leaf springs 9 on the plate spring 4 applied counter-moment. This counter-moment is due to the radial distance between the pivot bearing 5 and the loading diameter 3a between actuator spring 4 and pressure plate 3 available. When designing the friction clutch 1 it is particularly important that the increase in the tension of the leaf springs due to lining wear 9 smaller than the Ausrückkraftzunahme taking place as a result of the same lining wear, which requires the necessary pivoting of the sensor spring for adjustment 13 causes. Otherwise, the contact pressure of the pressure plate 3 for the friction linings 7 fall in the engaged state of the friction clutch, and there could be no adjustment at all.

The in the 12 and 13 illustrated friction clutch 101 differs essentially from that in the 1 and 2 shown friction clutch 1 in that the adjusting ring 117 by coil springs 126 is loaded in the circumferential direction. With regard to its function and mode of action with respect to the wear compensation of the friction linings corresponds to the adjusting ring 117 the adjusting ring 17 according to the 2 to 4 , In the embodiment shown are three coil springs 126 provided, which is evenly distributed over the circumference and between clutch housing 2 and adjusting ring 117 are biased.

As in particular from 14 shows, has the adjusting ring 117 on the inner circumference radial projections or gradations 127 , in which the arcuately arranged coil springs 126 with one of its ends for acting on the adjusting ring 117 can support in the circumferential direction. The other end areas of the springs 126 are based on the clutch housing 2 worn attacks 128 from. In the illustrated embodiment, these attacks 128 formed by screw-like fasteners, which with the lid 2 are connected. These attacks 128 However, by axial projections, which are integral with the coupling housing 2 are formed, be formed. For example, the attacks 128 through out of a sheet metal housing 2 axially formed embossments or tabs may be formed. As in particular from the 13 and 14 it can be seen, the ring 117 be formed on the inner circumference such that at least substantially in the region of the extension of the springs 126 and preferably also about the Ver required for adjustment of wear Ver angle of rotation of the ring 117 or via the relaxation path of the springs 126 a guide 129 There is an axial support and radial support of the springs 126 guaranteed. The spring guides 129 are formed in the illustrated embodiment by, viewed in cross-section, formed substantially semicircular depressions whose boundary surfaces substantially to the cross section of the coil springs 126 are adapted.

Such a configuration has the advantage that when rotating friction clutch proper guidance of the springs 126 is given, so that they can not dodge axially. For additional protection of the coil springs 126 can, like this in 13 is shown, the lid 2 at its radially inner edge region axial projections 130 own the feathers 126 overlap in the axial direction. Instead of individual formations 130 can the lid 2 also an over the circumference continuous and axial inner edge 130 have. The inner edge 130 can limit the relaxation of the diaphragm spring 4 serve.

A guide of the Nachstellfedern 126 according to the 12 to 14 has the advantage that when rotating coupling unit 1 the individual turns of the springs 126 under centrifugal force on the adjusting ring 117 can support radially, wherein the springs 126 in the circumferential direction applied adjusting forces due to the between the spring coils and the adjusting ring 117 frictional resistances are reduced or even completely eliminated. The feathers 126 So can with rotation of the friction clutch 101 (Due to the spring effect suppressing frictional forces) practically rigid behavior. It can thereby be achieved that, at least at speeds above the idling speed of the internal combustion engine, the adjusting ring 117 not by the springs 126 can be twisted. This can be achieved that a compensation of Reibbelagverschleißes only when the friction clutch 101 takes place at idle speed or at least approximately at idle speed. The blocking of the adjusting ring 117 However, it can also be such that only when the internal combustion engine, so not rotating friction clutch 101 an adjustment can take place due to the pad wear.

A blocking of the readjustment process during rotation of the friction clutch 1 or when exceeding a certain speed can also in one embodiment according to the 1 and 2 be beneficial. For this example, on the housing 2 Means are provided, the centrifugal force on the adjusting element 17 cause an anti-rotation, against the by the leg spring 26 and or 26a generated adjusting force. The blocking means may be formed by at least one under centrifugal force radially outwardly drängbares weight, for example, on the inner edge of the ring 17 supports and there he can witness a friction, the ring 17 causes a holding torque that is greater than that of the adjusting springs on the ring 17 applied twisting moment.

For the radial support of at least a portion of the extension of the springs 126 can also from the housing 2 worn support means are provided. These support means may in the embodiment according to the 12 and 13 with the stops 128 be formed in one piece. For this purpose, the attacks 128 be formed angularly, so that they each have a circumferentially extending region, at least over a portion of the extension of a spring 126 into it. As a result, at least a part of the spring coils can be guided and supported at least in the radial direction.

How out 13 it can be seen, the in 2 provided wire ring 11 omitted and through the tongue tip area of the sensor spring 113 attached formations 111 been replaced. This is what the tongues are for 113c in the area of their tips on their the actuator spring 4 facing side formed convex.

In the 15 to 17 a further embodiment of a wear adjustment is shown, in which instead of an annular adjusting ring individual adjusting elements 217 are used. These adjusters are over the circumference of the lid 202 equally distributed. The adjusting elements 217 are formed by button-shaped or disc-shaped components, which has a circumferentially extending and axially rising ramp 218 have. The annular adjusting elements 217 have a central recess or bore 219 through which the lid-worn axial pin-like projections 215a extend, so that the annular adjusting elements 218 rotatable on these approaches 215a are stored. On the lid 202 are markings 225 provided, which counter ramps 224 for the ramps 218 form. Between an adjusting element 217 and the lid 202 is a spring element 226 clamped, which is the adjusting element 217 acted on in the adjustment effecting direction of rotation. The spring element 226 can look like 15 indicates an axial approach 215a extend, so be trained helical spring. At the end of a spring 226 are projections, such as bends or legs provided for supporting the one spring end on the housing 202 and the other end of the spring on the correspond the adjusting element 217 , At an axial displacement of the plate spring 204 or the sensor spring 213 in the range of the swivel edition 205 become the adjusting elements 218 twisted and the shift by ramping up the ramps 218 at the ramps 224 balanced.

The axial support of the sensor plate spring 213 on the housing 202 done by means of tabs 214 coming from the axially extending area of the housing 202 shaped out and radially inward under the outer portions of the sensor spring 213 were urged.

The annular adjusting elements 218 have the advantage that they can be largely independent of centrifugal force with respect to their Nachstellwirkung can be formed.

Instead of in 14 shown rotating or twisting adjusting elements 217 could also be used individual wedge-like adjusting elements, which are displaceable in the radial and / or circumferential direction for wear adjustment. These wedge-like adjusting elements can have an elongate recess through which an axial projection 215a can extend to guide the corresponding adjusting element. The wedge-shaped adjusting elements can act adjusting due to the centrifugal force acting on them. However, it can also be provided energy storage, which act on the wedge-shaped adjusting in Nachstellrichtung. For proper guidance of the wedge-like adjusting the housing 202 Have moldings. The opposite to a plane perpendicular to the axis of rotation of the friction clutch plane extending with a certain ramp angle wedge surfaces of the adjusting can be provided on the housing side and / or on the side of the actuator plate spring. When using such wedge-shaped Einzelelemen th it is expedient to make them from a lightweight material in order to reduce the centrifugal forces acting on them to a minimum.

The Material pairing between the components forming the adjustment ramps is preferably chosen such that about the Operating life of the friction clutch none, an adjustment preventing Adhesion between the ramps and counter-ramps occur can. To avoid such liability, at least one these components with a coating at least in the field of Ramps or counter ramps be provided. By such coatings especially corrosion when using two metallic components be avoided. Sticking or sticking between the adjusting ramps forming components can be further avoided by the supporting one another and the ramps and counter ramps forming components of a material are produced with different coefficients of expansion, so that as a result of while the operation of the friction clutch occurring temperature fluctuations the surfaces in contact, which adjustment ramps form, relative to each other perform a movement. This will be the the Ramps and counter-ramps forming components relative always kept moving to each other. So it can be a liability or Sticking between these parts does not take place because of the different Extensions these parts always broke away from each other or solved become. A release the Nachstellrampen can also be achieved by virtue of difference Licher strength and / or training of the parts on these centrifugal forces acting on these parts cause different strains or movements, which in turn avoid sticking or sticking of the parts.

To avoid an adhesive bond between ramps and counter-ramps, at least one provision can be provided which exerts an axial force on the or the adjusting elements when disengaging the friction clutch or wear adjustment. For this purpose, the adjusting element 17 . 117 be axially coupled with a component having areas that move axially when wear occurs. This coupling can in particular in the field of pivotal mounting 5 done, with the actuator spring 4 and / or the sensor spring 13 ,

In the diagram according to 18 is a pressure plate spring characteristic 340 represented, which is a valley point or a minimum 345 has, in which the force applied by the Anpreßtellerfeder force is relatively low (about 450 Nm). The maximum of the diaphragm spring with the displacement-force characteristic 340 is on the order of 7 600 Nm. The characteristic 340 is generated by deformation of a plate spring between two radially spaced supports, and indeed, as in connection with the characteristic 40 according to 8th and in connection with the diaphragm spring 4 has been described.

The diaphragm spring characteristic 340 can with a pad spring characteristic 342 be combined. How out 18 can be seen, is the path-force curve of the pad spring characteristic curve 342 to the contact plate spring characteristic 340 Approximated or the two curves are only at a small distance from each other, so that the corresponding friction clutch can be operated with a very small force. In the effective range of the pad springing, the theoretical release force results from the difference between two vertically superposed points of the lines 340 and 342 , Such a difference is with 360 characterized. The actually required release force is reduced by the corresponding leverage of the actuators, such as disc spring tongues. This was also in connection with the embodiment according to the 1 and 2 and the diagrams according to the 8th to 11 described.

In 18 is dashed another actuator plate spring characteristic 440 represented which a minimum or a valley point 445 has, in which the force applied by the plate spring force is negative, that is not acting in the direction of engagement of the corresponding friction clutch, but in the release direction. This means that when the point is exceeded 461 during the Ausrückphase the friction clutch remains open automatically. The diaphragm spring characteristic 440 can be a pad spring characteristic according to the line 442 be assigned.

In 19 is the Ausrückkraftverlauf applied to disengage the corresponding friction clutch on the actuating lever, such as the diaphragm spring tongues for the associated characteristics 340 and 342 respectively. 440 and 442 shown. As can be seen, the Ausrückkraftverlauf 349 that the characteristics 340 . 342 is assigned, always in the positive force range, that is, in order to keep the clutch in the disengaged state, always a force in the release direction is required. The release force curve 449 that the characteristics 440 and 442 is assigned has a subarea 449a , in which the release force first decreases and then passes from the positive to the negative force range, so that the corresponding friction clutch in the disengaged state requires no holding force.

In the in the 20 . 20a and 21 illustrated embodiment of a friction clutch 501 is the sensor plate spring 513 on the clutch cover 502 axially via a bayonet connection 514 supported. For this the sensor spring possesses 513 radially from the outer periphery of the annular body 513b extending tabs 513d that attach to radial areas 502a , in the form of shaped out of the lid material tabs, axially supported. The lid flaps 502a are from the substantially axially extending edge region 502b formed out of the lid, it being useful if this is the tabs 502a at least partially by a free cut 502c or 502d are first formed out of the lid material. By at least partially cutting the tabs 502a These can be easily deformed into their desired position. As in particular from 21 it can be seen, are the tabs 502a and the arms or tongues 513d coordinated so that a centering of the sensor spring 513 opposite the lid 502 can be done. In the illustrated embodiment, the tabs 502a For this a small axial gradation 502e ,

To ensure proper positioning of the sensor spring 513 opposite the housing 502 during manufacture of the bayonet-type locking connection 514 to ensure at least three, preferably over the circumference of the lid 502 evenly distributed tabs 502a matched in relation to the other lid areas such that after a defined relative rotation between the sensor spring 513 and the lid 502 the corresponding booms 513d at a circumferential stop 502f come to rest and thus a further relative rotation between sensor spring 513 and lid 502 is avoided. The stop 502f is in the illustrated embodiment, as this particular 20a shows, by an axial shoulder of the lid 502 educated. Out 20a goes on to show that at least single, preferably three tabs 502a another Verdrehbegrenzung 502g between the lid 502 and the tongues 513d the sensor spring 513 form. In the illustrated example, the same tabs form 502a the anti-rotation devices 502f and 502g for both directions of rotation. The one release between the sensor spring 513 and the lid 502 avoiding stops 502g are axial, in the radial direction duri Fende bends of the tongues 502a educated. By the circumferential stops 502f and 502g is a defined positioning in the circumferential direction of the sensor spring 513 opposite the lid 502 given. For producing the locking connection 514 becomes the sensor spring 513 axially in the direction of the lid 502 strained, so that the tongues 513d axially in the free cuts 502c and 502d dive in and axially over the lid supports 502a to come to rest. After that, the lid can 502 and the sensor spring 513 be twisted relative to each other until some of the tongues 513d at the Verdrehbegrenzungen 502f come to the plant. This is followed by a partial relaxation of the sensor spring 513 so that some of the tongues 513d , viewed in the circumferential direction, between the corresponding stops 502f and 502g to come to rest and all tongues 513d on the lid-side supports 502a supports. Due to the design of the bayonet-type locking 514 ensures that during assembly of the friction clutch 1 the tongues 513d not next to the cover-side pads 502a to come to rest.

In the embodiments shown so far, the actual spring force of the sensor spring 513 applying annular base body, eg 513b , Provided radially outside the Beaufschlagungsbereiches or support region between the pressure plate and actuator plate spring. For some applications, however, it may also be expedient if the annular main body of the sensor disc spring radially within Be aufschlagungsdurchmessers between pressure plate and actuator spring is vorgese hen. So that means for an embodiment according to the 1 and 2 in that the axial tensioning force of the sensor spring 13 applying basic body 13b radially within the loading area 3a between actuator spring 4 and pressure plate 3 is provided.

In the embodiment according to the 20 to 21 are the cover-side counter-ramps 524 by cam-shaped stampings, which in the sheet metal housing 502 are formed, formed. Furthermore, in this embodiment, the between the housing 502 and the adjusting ring 517 tensioned coil springs 526 through guide pins 528 , which are integral with the adjusting ring 517 are formed and extend in the circumferential direction, guided. These guide thorns 528 can, as this particular out 21 shows, in the axial direction have an elongated cross-section, the inner diameter of the springs 526 is adapted. The guides 528 extend over at least a portion of the longitudinal extent of the springs 526 into this. As a result, at least a part of the spring coils can be guided and supported at least in the radial direction. Furthermore, a buckling or jumping out of the springs 526 be avoided in the axial direction. Through the spines 548 the assembly of the friction clutch can be significantly facilitated.

In 22 is the adjusting ring 517 partially shown. The adjusting ring 517 has radially inwardly extending projections 527 that the dornarti conditions, circumferentially extending guide areas 528 for the coil springs 526 wear. In the illustrated embodiment, the spring receiving areas 528 in one piece with the plastic ring produced as a molded part 517 educated. The spring guide areas or spring receiving areas 528 However, can also be formed by individual components or all together by a single component, which or which with the adjusting ring 517 , eg via a snap-lock, be connected or is. So can all leadership areas 528 be formed by an optionally open around the circumference of the ring with the adjusting ring 517 via at least three connection points, preferably designed as a snap lock is coupled.

Similar as in connection with the 12 and 13 described, the coil springs can 526 in addition, for example, due to centrifugal force, at correspondingly formed areas of the lid 502 and / or the adjusting ring 517 support radially.

The cover-side supports for the coil springs 526 are formed by out of the lid material and extending in the axial direction wings or by axial walls forming embossments 526 educated. These support areas 526a for the springs 526 are expediently designed such that the corresponding ends of the springs are guided and thus secured against an impermissible displacement in the axial and / or radial direction.

At the in 23 illustrated embodiment of a coupling 601 is the sensor spring 613 on the pressure plate 603 facing away from the case 602 intended. By arranging the sensor spring 613 outside the housing interior, which the pressure plate 603 absorbs the thermal stress of the sensor spring 613 be reduced, thereby reducing the risk of setting this spring 613 due to thermal overload is avoided. Also done on the outside of the case 602 a better cooling of the spring 613 ,

The support of the side facing away from the lid of the actuator spring 604 provided swivel pad 611 via spacer rivets 615 extending axially through corresponding recesses of the plate spring 604 and the housing 602 extend and with the sensor spring 613 are axially connected. In the illustrated embodiment, the spacer rivets 615 with the sensor spring 613 riveted. Instead of spacer rivets 615 Other means may be used which provide a connection between the rolling surface 611 and the sensor spring 613 produce. For example, the sensor spring could 613 have in the radially inner region axially extending tabs which the Abwälzauflage 611 be supported with appropriate radial preparation chen or even this Abwälzauflage 611 form directly by appropriate formations.

In the embodiment according to 24 extends the sensor spring 713 radially within the pivot bearing 715 for the actuator spring 704 , The sensor spring 713 is at its radially inner regions on the lid 702 supported for this purpose has the lid 702 axially through corresponding slots or recesses of the plate spring 704 extending tabs 715 which the sensor plate spring 713 support axially. According to another embodiment, the sensor spring could also 713 Have at their inner edge region tabs extending in the axial direction through corresponding openings of the plate spring 704 extend axially and support the lid side.

The in 25 illustrated adjusting ring 817 can in a friction clutch according to the 20 to 21 be used. The adjusting ring 817 has radially inward projections 827 which extend radially. The formations 827 own radial approaches 827a , The support areas for the circumferentially between the clutch cover and adjusting ring 817 tensioned coil springs 826 form. To guide and facilitate the assembly of the coil springs 826 is a ring 528 provided, which is interrupted or open at the outer periphery. The ring 528 is with the radial formations 827a connected. For this purpose, the formations 827a circumferentially extending recesses or grooves formed to communicate with the ring 828 form a snap connection. The cover-side supports for the Nachstellfedern 826 are by axial tabs 826a formed of the clutch cover. The axial tabs 826a each have an axial cut 826b for receiving the ring 828 , The cuts 826b are designed such that the ring 828 opposite the tabs 826a an axial displacement possibility, at least according to the wear path of the friction clutch has. For this purpose, it is particularly useful when in the radial projections 827a introduced recesses for receiving the ring 828 and the cutouts 826b , viewed in the axial direction, are formed in opposite directions, or in other words that the recesses in the projections 827a in the one axial direction and the cutouts 826b in the other axial direction are open.

At the in 26 illustrated embodiment of a friction clutch 901 finds the support of the actuator spring 904 in the disengagement in a central region of the body 904 the plate spring 904 instead of. Radially on the outside, the body is supported 904 on the pressure plate 903 from and extends radially inwardly over the pivot bearing 905 out. This means that the swivel bearing 905 from the inner edge of the body 904 the plate spring 905 or the slot ends, which are the tongues of the diaphragm spring 904 form, compared to the previously known disc spring clutches, is relatively far away. In the illustrated embodiment, the radial width ratio is radially within the pivot bearing 905 provided body portions to the radially outside of the pivot bearing 905 It is expedient for this ratio to be between 1: 6 and 1: 2. By such a support of the actuator spring 904 can damage or overuse of the plate spring main body 904 in the area of pivoting bearings 905 be avoided.

In 26 is still dashed an axial Anformung 903a , which on the pressure plate 903 is provided, indicated. About such on the pressure plate 903 , in particular in the field of support cams 903b , intended formations 903a can the actuator spring 904 opposite the clutch 901 be centered. So it can be the actuator spring 904 about a Außendurchmesserzentrierung in the radial direction relative to the lid 902 be held so that the in 26 also shown centering rivets or bolts 915 can be omitted. Although not shown, the outer diameter centering can also be over from the material of the lid 902 shaped tabs or stampings done.

At the friction clutch 901 is the sensor spring 913 designed such that the force applying body 913a radially inside the cams 903b is provided. To support the actuator spring 904 on the one hand and for your own support on the lid 902 on the other hand has the sensor spring 913 radial arms or tongues, on the one hand from the main body 913a extend radially inwardly and on the other hand from the main body 913a proceed radially outwards.

At the in 27 illustrated embodiment of a friction clutch 1001 is the release force of the friction clutch or the pivoting force of the Betätigungsstellerfeder 1004 opposite force through a sensor spring 1013 applied, which between the housing 1002 and the printing plate 1003 axially braced. In such an embodiment, the actuator spring becomes 104 in the swivel or tilt area 1005 not supported by a pivot bearing in the release direction. The plant of the plate spring 1004 on the cover-side swivel support or Abstützauflage 1012 is due to the biasing force of the sensor spring 1013 guaranteed. This sensor spring is designed such that during the disengagement of the friction clutch 1001 the ones from this sensor spring 1013 applied axial force on the plate spring 1004 is greater than the release force of the friction clutch 1001 , It must be ensured that if there is no wear on the friction linings, the diaphragm spring 1004 always on the cover-side support or the pivoting supports 1012 remains in investment. For this purpose, in a similar manner as has been described in connection with the previous embodiments, a coordination between the individual forces acting in the axial direction and overlapping forces must take place. These forces caused by the sensor spring 1013 , by the pad suspension by the between the pressure plate 1003 and the housing 1002 possibly provided leaf spring elements, by the actuator plate spring 1004 , by the disengagement force for the friction clutch 1001 and through the on the adjusting ring 1017 acting Nachstellfederelemente be generated must be matched accordingly.

The in the 28 and 29 illustrated friction clutch 1101 has a housing 1102 and a rotatably connected thereto, but axially limited displaceable thrust washer 1103 , Axial between the thrust washer 1103 and the lid 1102 is a pressure plate spring 1104 Tense, the one from the housing 1102 worn ring-like pivot bearing 1105 is pivotable and the pressure plate 1103 in the direction of one with the housing 1102 firmly connected counterpressure plate 1106 , such as a flywheel, impinged, causing the friction linings 1107 the clutch disc 1108 between the friction surfaces of the thrust washer 1103 and the counterpressure plate 1106 be clamped.

The pressure disc 1103 is with the case 1102 in the circumferential direction or tangentially directed hinge means in the form of leaf springs 1109 rotatably connected. In the illustrated embodiment has the clutch disc 1108 so-called pad spring segments 1110 , which ensure a progressive torque build-up when engaging the friction clutch, by having a limited axial displacement of the two friction linings 1107 towards each other to a progressive increase in the friction linings 1107 enable acting axial forces. However, it could also be used a clutch disc, in which the friction linings 1107 axially practically rigidly applied to at least one carrier disc and a replacement elsewhere for the pad spring segments 1110 be provided, for example: between disc spring 1104 and thrust washer 1103 ,

In the illustrated embodiment, the plate spring has 1104 a contact pressure applying annular base body 1104a , from the radially inwardly extending actuating tongues 1104b out. The plate spring 1104 is installed in such a way that it with radially outermost areas the pressure plate 1103 apply and with radially inward areas around the pivot bearing 1105 is tiltable. The pivot bearing 1105 includes two swivel pads 1111 . 1112 , which are formed here by wire rings and between which the plate spring is axially supported or clamped. To prevent rotation of the actuator spring 1104 and for centering and holding the wire rings 1111 . 1112 opposite the housing 1102 are holding means in the form of rivet elements 1115 attached to the lid, each with an axially extending shaft 1115a through one between adjacent plate spring tongues 1104b extending cutout extend.

The coupling 1101 has an axial wear on the friction surfaces of the pressure plate 1103 and the counterpressure plate 1106 and the friction linings 1107 compensating Nachstellvorkehrung, consisting of a between Anpreßtellerfeder 1104 and thrust washer 1103 provided wear compensation device 1116 and from the Ausrückweg the pressure plate 1103 limiting limits 1117 , which are designed as a displacement sensor consists.

The effective as wear sensor limiting means 1117 each have a socket 1118 that in a hole 1120 the pressure disk 1103 is received rotatably. The socket 1118 forms a slot 1121 , through which axially two leaf spring elements 1122 extend. The leaf spring elements 1122 are supported on each other, wherein at least one leaf spring elements is curved, preferably both leaf spring elements are curved in opposite directions. The leaf spring elements 1122 are received in the socket with a defined bias and are thus contrary to a predetermined frictional resistance to the socket 1118 in the axial direction of the coupling 1101 displaced. The axial length of the leaf spring elements 1122 is chosen such that when engaged friction clutch 1101 these leaf spring elements with respect to an axially fixed coupling component - in the illustrated embodiment with respect to the outer edge region 1123 of the housing 1102 - a defined game 1124 have, that the predetermined Ausrückweg the thrust washer 1103 equivalent. When the friction clutch is engaged, the leaf spring elements come 1122 with her the housing 1102 opposite end 1122a at the counterpressure plate 1106 to the plant, whereby it is ensured that in case of wear of the friction linings 1107 the pressure disk 1103 according to this pad wear against the leaf spring elements 1122 is axially displaced, against the action of the frictional engagement between the leaf spring elements 1122 and the socket 1118 , which preferably consists of plastic or of a friction material.

In the illustrated embodiment, the bore 1120 into which the socket 1118 is determined by pressing both in the axial and in the circumferential direction, in a pressure plate cam 1125 provided, which extends radially outwardly and to the respective one leaf spring element 1109 via a riveted joint 1109a is articulated. Moving the socket 1118 in the direction of the counter-pressure plate 1106 can also be avoided by the fact that the socket 1118 at her the housing 1102 facing the end of a covenant 1118a possesses, over which they are at the pressure disk 1103 can support. An emigration of the bush 1118 out of the hole 1120 in the direction of the housing or clutch cover 1102 can be avoided by, as in 28 dash-dotted lines, the leaf springs 1109 the socket 1118 partially radially overlaps and optionally additionally firmly into the bore 1120 axially braced. An Ver rotate the sleeve can be further prevented by the fact that the socket has a profiling, in particular a paragraph, which the cross-section of the bushing areas 1119 the leaf springs 1109 receives.

The wear compensation device 1116 owns one from the plate spring 1104 acted compensation component in the form of a U-shaped in cross-section sheet metal ring 1126 who in 32 is shown in plan view. The compensation component 1126 owns on the plate spring 1104 facing side of the floor 1127 at least one annular axial projection 1128 or more protrusions 1128 , which are preferably uniformly distributed over the circumference and are formed by embossed into the sheet material beads. Segmented projections 1128 ensure that in the area between circumferentially adjacent projections 1128 radial passages between the plate spring main body 1104a and the compensation ring 1126 are formed, which allow an air passage for cooling. As in particular from 29 can be seen, is the compensation ring 1126 opposite the pressure disc 1103 centered. For this purpose has the pressure plate 1103 at least one gradation 1129 that the radially inner, axially extending wall 1130 of the compensation ring 1126 centric to the thrust washer 1103 positioned. The gradation 1129 may be formed by a circumferentially extending closed surface, or even by over the circumference at a distance from each other provided segmental surfaces. The compensation ring 1126 also has a radially outer axially extending wall 1131 that work together with the inner wall 1130 and the floor 1127 an annular space 1126a forms. Radial outside has the compensation ring 1126 radial boom or cam 1132 who make stops, which with counter-strokes 1133 the axially displaceable components in the form of leaf spring elements 1122 the wear sensor 1117 interact. The counter-attacks 1133 are through to the leaf spring elements 1122 molded nose, which point radially inward and the boom 1132 spread. This will cause the axial displacement of the compensation ring 1126 in the direction of the pressure disk 1103 away, so in the direction of the housing, through the counter-attacks 1133 limited.

Between the compensation ring 1126 and the pressure disc 1103 is a balancing device 1134 provided when disengaging the friction clutch 1101 and presence of pad wear an automatic adjustment of the compensation ring 1126 allows and when engaging the clutch self-locking, so blocking, acts, thereby ensuring that during the engagement phase of the friction clutch 1101 the combination ring 1126 a defined axial position relative to the pressure plate 1103 maintains. This defined position can only change during a disengaging process and in accordance with the lining wear that occurs.

The adjusting device 1134 comprises a plurality of pairs of wedges, preferably uniformly distributed over the circumference 1135 . 1136 in the annular space 1126a of the sheet metal ring 1126 are included. Which is attached to an annular surface 1137 the pressure disk 1103 supporting wedges 1136 are with the metal ring 1126 rotationally fixed, but connected axially displaceable. For this has the metal ring 1126 in the region of its axially extending walls 1130 . 1131 Formations in the form of beads 1138 . 1139 in the area of open space 1126a Form projections, which in correspondingly adapted depressions or grooves 1140 . 1141 the wedges 1136 intervention. The grooves 1140 . 1141 or the formations 1138 . 1139 run in the axial direction of the coupling 1101 , As well as out 30 can be seen, are the wedges 1135 essentially axially between the ground 1127 of the sheet metal ring 1126 and the wedges 1136 added. The wedges 1135 and 1136 Form in the circumferential direction extending and axially rising ramps 1142 . 1143 about which the wedges associated with a pair 1135 . 1136 support each other. The wedges 1135 On the other hand, they are based on the ground 1127 of the ring 1126 off and are opposite this ring 1126 displaced in the circumferential direction. The ramps 1142 . 1143 are braced against each other. For this are power storage in the form of coil springs 1144 in the annulus 1126a taken up, which end with one at the ring 1126 non-rotating wedge 1136 and with its other end on a circumferentially displaceable wedge 1135 support. To hold the energy storage 1144 own the wedges 1135 . 1136 at their the corresponding energy storage end facing projections 1145 . 1146 , which engage in the spring coils and thus hold the spring ends. The feathers 1144 will continue through the wall areas 1130 . 1131 and the floor 1127 of the ring 1126 guided.

In the illustrated embodiment, the balancing ring 1126 opposite the pressure disc 1103 secured against rotation. For this are how out 31 it can be seen on the pressure plate 1103 axial projections in the form of pins 1147 provided axially through recesses 1148 that are in the area of the outriggers 1132 are provided extend. This rotation ensures that during the operation of the friction clutch, the stop areas of the tabs 1132 always below the limit noses 1133 the leaf spring elements 1122 stay positioned.

In the illustrated embodiment, the wedges 1135 . 1136 made of a heat-resistant plastic, such as, for example, a thermosetting plastic or thermoplastic, which may additionally be fiber-reinforced. This allows the wedges acting as adjusting elements 1135 . 1136 produce in a simple manner as molded parts. However, it may also be advantageous if at least one of the wedges 1135 . 1136 a pair of friction material, such as covering material, is made. The wedges or adjusting elements 1135 . 1136 However, they can also be produced as a sheet metal part or as a sintered part. The pitch angle as well as the extension and the ramps 1142 . 1143 are designed so that over the entire life of the friction clutch 1101 an adjustment of the friction surfaces of the thrust washer 1103 and the counterpressure plate 1106 and the friction linings 1107 occurring wear is guaranteed. The wedge angle 1149 or the pitch angle 1149 the ramps 1142 . 1143 opposite a plane perpendicular to the Rotationsach the friction clutch plane is chosen such that the pressing together of the ramps 1142 . 1143 resulting friction prevents slipping between these ramps. Depending on the material pairing in the area of the ramps 1142 . 1143 can the angle 1149 range between 5 and 20 degrees, preferably on the order of 10 degrees. The circumferentially displaceable wedges 1135 are arranged so that these with their wedge tip in the direction of rotation 1150 demonstrate.

The tension through the energy storage 1144 the ramps 1142 . 1143 and the pitch angle 1149 are designed so that the on the adjusting ring 1126 acting axial force is less than the required Verchiebekraft wear sensors 1122 the limiting means 1117 ,

Furthermore, in the design of the diaphragm spring 1104 Be taken into account that the applied by this pressure force for the pressure disk 1103 the required displacement force for the wear sensors 1122 and the clamping force of the between lids 1102 and thrust washer 1103 strained leaf springs 1109 must be increased. Furthermore, the individual components must be designed so that the bearing wear between disc spring 1104 and support ring 1126 as well as the system wear between the wear sensors 1122 and the counterpressure plate 1106 or between the wear probes and the housing 1102 in relation to the wear on the coverings 1107 stay low.

To an unwanted adjustment between the ramps 1142 . 1143 or the adjusting elements 1135 . 1136 in 30 To avoid, in the area of at least one of the ramps 1142 . 1143 small projections may be provided which hook on the other ramp. The projections can be designed such that an adjustment is made possible for wear compensation, slipping of the ramps relative to each other, however, is prevented. It may also be particularly useful if both ramps 1142 . 1143 Have projections that interlock. These projections may be formed, for example, by a sawtooth-like profiling having a very small height, which is a relative displacement of the ramps 1142 . 1143 only possible in Verschleißnachstellrichtung. Such a profiling is in 3 over a partial area of the extension of the ramps 1142 . 1143 shown schematically and with 1143a characterized. In applications where only one of the ramps 1142 . 1143 Having projections, they may be formed such that they have a higher hardness than the material forming the other ramp, so that at least a small penetration or clinging of the protrusions on the support ramp can be carried out.

To prevent the curved or wavy leaf springs 1122 as a result of the engagement on the pressure disk 1103 The resulting very high temperatures lose their tension, are the sockets 1118 Before preferably made of a material with low thermal conductivity and high coefficient of friction. The wedges 1135 . 1136 can be made of the same material.

To better cool the clutch; in particular the pressure disk 1103 , to allow, in the pressure washer 1103 radially extending and circumferentially distributed grooves, of which in 29 a dashed line and with 1151 is provided, be provided. These radial grooves 1151 are, viewed in the circumferential direction, provided between each two adjacent pairs of wedges and extend between the ring 1126 and the pressure disc 1103 , It could also be in the area of feathers 1144 the ring 1126 from the ground 1127 have outgoing axial cutouts, whereby between the plate spring 1104 and the ring 1126 radial passages would be formed.

To increase the wear resistance at the various support points, the corresponding areas can be provided with a wear-resistant layer, such as hard chrome plating, molybdenum coating or else special wear-resistant components can be provided in the area of the contact points. For example, on the wear probes 1122 Plastic shoes in the contact area with the counterpressure plate 1106 and the case 1102 be provided.

The torque on the pressure plate 1103 transmitting leaf springs 1109 are between the pressure plate 1103 and the housing 1102 biased so that they upon disengagement of the friction clutch 1101 the pressure disk 1103 in the direction of the housing 1102 relocate. This ensures that virtually over the entire disengagement phase or until the effectiveness of the limiting means 1117 the ring 1126 on the plate spring 1104 remains in investment.

The release travel of the clutch in the area of the tongue tips 1104c is preferably chosen such that when disengaged clutch the outer edge of the plate spring 1104 by a small amount from the ring 1126 takes off. This means that when disengaging the friction clutch 1101 the plate spring travel in the diameter range of Druckscheibenbeaufschlagung by the plate spring 1104 greater than that by the Wegbegrenzungsmittel 1122 fixed departure route 1124 the pressure disk 1103 ,

In the 29 shown relative position of the individual components corresponds to the new condition of the friction clutch. For axial wear, especially the friction linings 1107 , the position of the thrust washer shifts 1103 in the direction of the counter-pressure plate 1106 , whereby initially a change in the taper and thus also of the plate spring in the engaged state of the friction clutch 1101 applied contact force arises, preferably in the sense of an increase. This change causes the thrust washer 1103 their axial position with respect to the counter-pressure plate 1106 axially supporting wear sensors 1122 changes. As a result of the ring 1126 acting cup spring force follows this ring 1126 the axial displacement of the counterpressure plate caused by lining wear 1103 , whereby the stop areas 1132 of the ring 1126 axially from the counter-abutting areas in the form of noses 1133 the wear sensor 1122 withdraw, by an amount; which essentially corresponds to the lining wear. The balancing ring 1126 maintains its axial position during a coupling operation with respect to the pressure plate 1103 because he's through the plate spring 1104 in the direction of the pressure disk 1103 is applied and the wear compensation device 1134 is self-locking during the coupling process, so acts as an axial lock. When disengaging the friction clutch 1101 The thrust washer is replaced by the leaf springs 1109 in the direction of the housing 1102 applied and shifted until the wear sensor 1122 on the housing 1102 or at the housing stop areas 1123 come to the plant. Up to this Ausrückweg, the Abhubweg the thrust washer 1103 corresponds, the axial position of the ring remains 1126 opposite the pressure disc 1103 receive. If the disengagement process continues, the thrust washer remains 1103 axially, whereas the ring 1126 axially follows the disengagement of the plate spring in the region of the loading diameter, and that until the stop areas 1132 of the ring 1126 at the counter-attack areas 1133 the wear sensor 1122 come back to the plant. The axial displacement of the compensation ring 1126 gets through the wedges 1135 caused by the springs 1144 are charged. These wedges 1135 will be facing the wedges for so long 1136 shifted in the circumferential direction until the ring 1126 against the counter-attacks 1133 the wear sensor 1122 is tense. The lift of the pressure disc 1103 is in the illustrated embodiment on the leaf springs 1109 ensures that between housings 1102 and pressure-washer 1103 are installed, that they have an axial bias, which the thrust washer 1103 in the direction of the housing 1102 urges. Will the plate spring 1104 further pivoted in the disengagement, so this lifts with its radially outer region of the adjusting ring 1126 from, since the latter, as already described, by the wear sensor 1122 opposite the pressure disc 1103 is retained axially. Such, at least slight Abhub the diaphragm spring 1104 opposite the adjusting ring 1126 during a disengaging process is for the function of the adjustment system 1117 + 1134 especially advantageous.

The Nachstellvorkehrung invention 1117 + 1134 ensures that the adjustment on Auflagering 1126 through the adjusting wedges 1135 . 1136 always according to the lining wear amount. This is due to the fact that the adjusting ring 1126 between the adjusting means in the form of wedges 1135 . 1136 and the wear sensors 1122 is axially clamped, thereby preventing the compensation member in the form of the ring 1126 adjusted by a larger amount than the corresponding lining wear. Furthermore, it is ensured by the inventive design of Nachstellvorkehrung that even when over-travel in the region of the release means, such as the diaphragm spring tongues 1104b , or in Axialschwingungen the pressure plate no adjustment of Nachstellvorkehrung 1117 + 1134 can follow, since the wear sensor 1121 even with a hard impact on the case 1102 opposite the pressure disc 1103 by the self-locking wear compensation device 1134 is axially supported, via the counter stops 1132 , It can therefore in the disengaged state of the friction clutch on the wear sensor 1122 axial forces in the direction of the counter-pressure plate 1106 acting, which are greater than the non-positive connection between the wear probes 1122 and the pressure disc 1103 , without the wear sensor against this pressure plate 1103 be moved axially.

With the Nachstellvorkehrung invention ensures that over the entire life of the clutch, the plate spring operates practically over the same range of characteristics and in the engaged state of the friction clutch 1101 has a practically constant tensioning and thus also a virtually constant contact pressure on the pressure plate 1103 applies. This makes it possible to use a diaphragm spring with a degressive force characteristic across the Ausrückweg, preferably in combination with a clutch disc whose linings 1107 via spring segments 1110 are cushioned against each other, whereby the effective aufzu to bring Ausrückkraft can be brought to a relatively low level and over the life of the clutch, provided that the pad spring characteristic does not change significantly over the life of the clutch, can be kept practically constant. When disengaging such a clutch, the plate spring 1104 around their lid storage 1105 pivoted, wherein over a predetermined portion of the axial Ausrückweges the pressure plate 1103 the spring segments 1110 relax and thus the of the spring segments 1110 applied axial force the disengagement of the friction clutch 1101 supported. This means that a lower maximum release force must be applied than that which in the engaged position of the clutch 1101 theoretically results from the installation position of the plate spring 1104 and the leaf springs 1109 , As soon as the spring or relaxation area of the segments 1110 is exceeded, the friction linings 1107 released, due to the degressive curve range in which the diaphragm spring 1104 works, the then still applied release force is already significantly reduced compared to what the installation point or the installation position according to 29 would correspond. Upon continuation of the disengagement process, the release force continues to decrease, at least until the minimum or the valley point of the preferably sinusoidal characteristic of the diaphragm spring 1104 is reached.

The in the 28 and 29 illustrated Nachstellvorkehrung 1117 + 1134 can be designed in an advantageous manner so that when rotating Rei friction clutch 1101 the individual spring coils of the Nachstellfedern 1144 on the outside wall 1131 of the adjusting ring 1126 support and the springs 1144 in the circumferential direction applied adjusting forces due to the between the spring coils and the adjusting ring 1126 frictional resistances are reduced or even completely eliminated. The feathers 1144 So can with rotation of the friction clutch 1101 due to the spring effect suppressing frictional forces practically rigid behavior. Furthermore, the adjusting wedges 1135 due to the centrifugal forces acting on them also on the wall 1131 of the adjusting ring 1126 radially support and by the between the wedges 1135 and the adjusting ring 1126 frictional forces generated against rotation are secured. It can thereby be achieved that at least at speed ranges above the idling speed of the internal combustion engine, the wear compensation device 1134 not by the springs 1144 to be twisted. So it can be the friction clutch 1101 be designed so that a compensation of the friction lining wear only upon actuation of the friction clutch 1101 takes place at idle speed or at least approximately at idle speed. The blocking of the adjusting ring 1126 can by appropriate design of the wear compensation device 1134 However, also be such that only when the internal combustion engine, so at not rotating friction clutch 1101 or at very low speeds an adjustment of the lining wear can take place.

The material combination between the components forming the adjustment ramps 1135 . 1136 as well as the material of the components cooperating with these components is preferably selected such that over the operating life of the friction clutch no, an adjustment preventing, adhesion between the ramps and the components interacting with these can occur. In order to avoid such adhesion, at least one of these components may be provided with a coating at least in the region of the ramps or supporting surfaces.

Around an adhesive connection between ramps and counter-ramps At least one precaution can be provided for when you move out the friction clutch or wear adjustment an axial force on the or the adjusting exercises, the separation or tearing of the Ramps effected.

In new condition of the friction clutch 1101 that is, in the state that the clutch has before it intervening with the clutch disc 1108 at the counterpressure plate 1106 is attached, are the wedges 1135 opposite to the 30 shown position in a more retracted position relative to the wedges 1136 , so that the adjusting ring 1126 his in the direction of the pressure disk 1103 has the most retracted position and thus the unit thrust washer 1103 / adjusting ring 1126 need the least axial space. To the wedges 1135 before mounting the friction clutch 1101 to keep in their withdrawn position, own the wedges 1135 Attack areas in the form of recesses 1152 for a twisting or retaining means. Such retention means may be used in the manufacture or assembly of the friction clutch 1101 be provided and after assembly of the friction clutch 1101 on the flywheel 1106 be removed, causing the readjustment 1134 is activated. In the illustrated embodiment, as shown in FIGS 30 and 32 appears in the adjusting ring 1126 elongated slots extending in the circumferential direction 1153 provided by which the engagement areas of the retaining means or the turning tool for engagement in the recesses 1152 can be passed. The elongated recesses in the circumferential direction 1153 must have at least one extension, the rotation corresponding to the largest possible wear adjustment angle of the wedges 1135 in the circumferential direction corresponds. The keys held in new condition of the friction clutch in the circumferential direction in its retracted position wedges 1135 can in this position through the wear sensor 1122 , which the adjusting ring 1126 secure in its withdrawn position. The self-adjusting connections between the wear probes 1122 and the pressure disc 1103 must be designed such that the required displacement force to shift the wear sensor 1122 opposite the pressure disc 1103 bigger than the one on the ring 1126 acting resultant force generated by the wedges 1135 acting on springs 1144 ,

In the embodiment according to the 28 and 29 can the ramps 1143 also directly through the ring 1126 be formed, for example by embossing oblique surfaces 1143 , where the ring 1126 then through the springs 1144 opposite the pressure disc 1103 must be rotatable. The wedges 1136 are in such an embodiment with the pressure disk 1103 rotatably or directly formed on this. Furthermore, in such an embodiment as the boom 1132 trained stops in the circumferential direction corresponding to the required Nachstellverdrehwinkel the ring 1126 be extended to ensure that an axial boundary between the wear probes 1122 and the ring 1126 maintained over the life of the friction clutch. In the last-described embodiment, the adjusting ring 1126 also with mounted friction clutch 1101 be rotated in a simple manner from radially outward, in particular on the circumferentially extending stop tabs 1132 that over on the outer jacket of the clutch housing 1102 provided radial passages are accessible. These radial passages can in particular also the torque transmission cams 1125 the pressure disk 1103 as well as the leaf springs 1109 take up. The Nachstellvorkehrung invention also has the advantage that the principle can also be used in so-called drawn friction clutches in which the plate spring is pivotally supported with a radially outer edge region on a lid and surfaces with radially further edge Randberei applied to the thrust washer. Such a coupling is in 33 shown. Between plate spring 1204 and thrust washer 1203 is a wear compensation device 1234 provided, which may be similar, as related to the 28 and 29 has been described. The adjusting ring 1226 in turn acts via sensor elements 1217 with wear sensor 1222 together. The adjustment of the wear sensor 1222 opposite the pressure disc 1203 done by planting the stop areas 1222a on the housing or lid 1202 , The wear sensors 1222 again carry attacks 1233 representing the axial path of the thrust washer 1203 at a disengagement limit. To ensure proper functioning of the adjustment according to 33 to allow possesses the ring 1226 at least a slight axial movement possibility compared to the wear probes 1222 , This can be done by a corresponding stop connection 1233a with play between the wear probes 1222 and the ring 1226 is present or else in that the ring 1226 radial areas 1226a has, which are resiliently deformable in the axial direction, so have an elastic compliance.

At the in 34 illustrated embodiment, the wear sensor elements 1317 directly in the main body of the pressure disk 1303 added. The wear sensors 1322 own stop areas 1322a covered with lid areas 1323 which counter-attacks form, cooperate. The lid areas 1323 are one-piece with fasteners 1302a about which the diaphragm spring 1304 on the lid 1302 is pivotally mounted. In the illustrated embodiment, the fastening or holding means 1302a by lugs formed integrally from the lid material, which axially through the plate spring 1304 pass through, formed. Radially outside the in the radial region of the plate spring main body 1304a provided wear sensors 1317 is the wear compensation device 1334 intended.

Due to the inventive design of a friction clutch not only an increase in the clutch life by using thicker friction linings, ie by increasing the axial lining wear volume can be achieved, but also in particular a reduction of Ausrückkräfte, by using a force accumulator over the Ausrückweg the friction clutch degressiver Force-displacement characteristic in combination with at least one of the pressure acting on the pressure plate acting force storage spring means which upon engagement and disengagement of Rei tion clutch causes a gradual buildup or degradation of the transmittable by the friction clutch torque over at least a portion of the clutch actuation path or the Druckplattenweges. This spring means is suitably in series with the pressure spring, such as. B. disc spring, the friction clutch connected. It can therefore be achieved by the inventive design of a friction clutch a very substantial Ausrückkraftsenkung and this reduction is maintained over the life of the friction clutch or unchanged, that means in a ratio tively narrow tolerance band. Furthermore, in friction clutches according to the present invention, disc springs can be used with a relatively steeper force-displacement identifier in the working range. Such disc springs would result in conventional clutches to a very strong increase in the release force with pad wear.

In clutches without the adjustment of the invention moves with increasing pad wear first of the engaged state of the friction clutch corresponding point 41 ( 8th ) along the line 40 in the direction of the maximum 41a , Up to this point 41a takes place during a disengagement a drop in the release force, but overall, the level of Ausrückkraftverlaufes over the Ausrückkraftverlauf in the new condition of the friction clutch increases. So that means that the area 43 wanders to the left until the point 41 with the maximum 41a matches. Point 44 shifts accordingly along the characteristic curve 40 , With further lining wear of the engaged state of the friction clutch corresponding installation point of the actuator spring moves from the maximum 41a gradually towards the point 41b , so that the force applied by the plate spring contact pressure gradually decreases. The in point 41b applied by the actuator spring pressure corresponds to the in point 41 in the new state of the friction clutch applied contact pressure. Once the maximum 41a is exceeded, the release force increases during the disengagement at least over a portion of the clutch actuation path. He reach the maximum allowable wear path or wear point 41b is over the entire Ausrückweg 43a an increase in the release force exists. This release force increase is maintained even if, as in 8th is shown, a pad suspension or a pad spring replacement 42a is available.

In the interpretation of the friction clutch and in particular their Nachstellvorkehrung must be considered that the crankshaft of the engine thrusts axial and tumbling vibrations on the flywheel, which are also transmitted to the friction clutch attached to the flywheel. Thus, the friction clutch or Nachstellvorkehrung can work properly, that is, no unwanted adjustment takes place due to such vibrations, must in embodiment according to the 1 to 27 , So quite generally in embodiments with a Nachstellvorkehrung with force sensor, the adjusting force of this force sensor to be greater than the inertial forces which can act on the force sensor. These forces result in particular by the masses of the main plate spring, the adjusting ring and the adjusting elements, a corresponding mass fraction of the force sensor and optionally by the mass of other components multiplied by the maximum possible axial acceleration of these components or elements, which from the axial and bending oscillations of the flywheel results. For example, in one embodiment according to 27 in which the sensor plate spring 1013 at the clutch pressure plate 1003 also supports the inertia of this clutch pressure plate 1003 be taken into account. It must therefore always be ensured that the force applied by the sensor spring force is greater than the forces acting on these, which are formed by the multiplied by the maximum possible axial acceleration mass of the components which act on the sensor spring due to their inertia. These inertial forces can have an adverse effect, in particular during the actuation of the friction clutch and in particular in the disengaged state of the friction clutch.

In embodiments according to the 29 to 34 When designing the wear sensors and the wear compensation devices, the forces resulting from the inertia of the individual components and the axial and torsional vibrations acting on them must also be taken into account.

In general, therefore, in the design of a friction clutch with integrated wear compensation means, the masses of the elements are to be considered, can be transmitted to the axial and or torsional vibrations and acting on the compensating means. In the embodiments according to the 28 to 34 In particular, the components that affect the function of the ramp mechanism should be considered.

In 35 is a split flywheel 1401 shown, one, attachable to a crankshaft, not shown, of an internal combustion engine, first or primary flywheel 1402 owns and a second or secondary flywheel 1403 , On the second flywheel 1403 is a friction clutch 1404 with the interposition of a clutch disc 1405 fastened, via which a likewise not signed gear can be connected and disconnected. The momentum 1402 and 1403 are about a storage 1406 rotatably mounted to each other, the radially within the holes 1407 for the implementation of fastening screws 1408 for the assembly of the first flywheel 1402 is arranged on the output shaft of the internal combustion engine. Between the two momentum masses 1402 and 1403 is the damping device 1409 effective, the helical compression springs 1410 owns that in an annular space 1411 , which is a toroidal area 1412 forms, are housed. The annular space 1411 is at least partially filled with a viscous medium such as oil or fat.

The primary flywheel 1402 is mainly due to a component 1413 formed from sheet metal material. The component 1413 has a substantially radially extending flange-like area 1414 , the radially inwardly integrally formed, axial approach 1415 carries, which of the holes or holes 1407 is surrounded. The single row rolling bearing 1406a the rolling bearing 1406 is with his inner ring 1416 radially outward on the end portion of the axial extension 1415 added. The outer ring 1417 of the rolling bearing 1406a carries the trained essentially as a flat, disk-shaped body second flywheel 1403 , For this has the flywheel 1403 a central recess in which the bearing 1406a is included. The substantially radially extending region 1414 goes radially outward in a bowl-like area 1418 over, the energy storage 1410 at least partially surrounds and guides or supports at least over the outer periphery. The at the area 1418 attached, shell-like body 1419 partially surrounds the scope of the energy storage 1410 , The body 1419 is with the sheet metal body 1413 welded (at 1420 ). The toroidal area 1412 is, viewed in the circumferential direction, divided into individual images in which the energy storage 1410 are provided. The individual recordings are, viewed in the circumferential direction, separated from each other by loading areas for the energy storage 1410 which pass through into the sheet metal part 1413 and the bowl-like body 1419 embossed pockets can be formed. The second flywheel 1403 associated admission areas 1421 for the energy storage 1410 are from the clutch cover 1422 carried.

The admission areas 1421 are by radial arms 1421 formed in the illustrated embodiment, the axial region 1423 the clutch cover 1422 are placed on and in the annulus 1412 radially engage, between the ends of circumferentially adjacent force accumulators 1410 , The axially extending lid area 1423 envelops or surrounds with a section 1423a the second flywheel 1403 and is with this z. B. over in the section 1423a introduced stampings, which are in corresponding recesses of the flywheel 1403 engage, or firmly connected by another type of fastening.

The on the outer contour of the flywheel 1403 centered clutch cover 1422 owns at its the loading areas 1421 opposite end a substantially radially inwardly extending, annular region 1426 , on which an effective as two-armed lever disc spring 1427 is held pivotally. With radially outward areas applied to the plate spring 1427 a printing plate 1428 , whereby the friction linings 1429 the clutch disc 1405 between the second flywheel 1403 and the printing plate 1428 be clamped axially. Between the friction linings 1429 is a lining suspension 1465 intended.

Like from the 35 it can be seen, is the annular space 1411 or its torus-like region 1412 predominantly radially outside the outermost contours of the second flywheel 1403 arranged. This can be used for articulation of the first flywheel 1402 serving on the output shaft of the internal combustion engine and the toroidal region 1412 bearing component 1413 , which is adjacent to the internal combustion engine, and the second flywheel 1403 radially within the annular space 1411 over a relatively large radial extent, forming an intermediate space or air gap 1430 , Virtually immediately opposite, so be practically adjacent to a small distance, creating a very compact in the axial direction of the flywheel 1401 , Clutch 1404 and clutch disc 1405 existing aggregate is made possible. The sealing of the annular space 1411 is through a seal 1431 ensures that between the inner areas of the radial wall 1419 and the outer surface of the lid 1422 is effective.

Advantageously, this gap 1430 for cooling the flywheel 1401 serve, namely by passing through this gap 1430 a cooling air flow is passed. To generate such a cooling air circulation has the second flywheel 1403 radially within the friction surface 1432 axial recesses 1433 extending in the direction of the engine-side component 1413 extend and into the gap 1430 open out. To improve cooling, the second flywheel can 1403 further axial passages 1435 have, which lie radially outward and on the friction surface 1432 opposite side with the gap 1430 communicate and on the clutch 1404 facing side of the flywheel 1403 radially outside the Reibflä che 1432 open out. Radial within the passages or recesses 1433 owns the flywheel 1403 further passages 1434 , in particular for receiving or carrying out the fastening screws 1408 serve.

For sealing the partially filled with viscous medium annular chamber 1411 is another seal 1436 provided, which is formed by a diaphragm-like or plate spring-shaped component, which extends radially in the intermediate space 1430 extends.

The shell-like body 1419 carries a starter sprocket 1439 which is connected to it via a welded joint.

Together with the clutch unit, consisting of clutch 1404 and clutch disc 1405 , that forms in 35 illustrated two-mass flywheel 1402 + 1403 a structural unit A, which is pre-assembled as such, so shipped and stored and can be screwed onto the crankshaft of an internal combustion engine in a particularly simple and efficient manner. For the assembly of the unit A, the first coupling 1404 and the second flywheel 1403 , with interposition of the clutch disc 1405 , connected with each other. Thereafter, the subunit consisting of coupling 1404 , Flywheel 1403 and clutch disc 1405 with the component 1413 axially merged, whereupon the shell-like body 1419 on the outer edge 1423 the clutch cover 1422 is received, to rest against the outer regions of the component 1413 brought and with this (at 1420 ) can be welded. Before the axial merging of the two components 1413 and 1419 became the feathers 1410 in the toroidal area 1412 inserted. The unit A further has already integrated the camp 1406 which is on the axial neck 1415 is applied. In the holes 1407 of the flange area 1414 are also still the mounting screws 1408 already pre-assembled or contained, in the form of Allen screws 1408 , Here are the screws 1408 in a position corresponding to the lower half of the 35 , The screws are held captive in this position in the unit or the unit A.

The clutch disc 1405 is in a pre-centered to the axis of rotation of the crankshaft position between pressure plate 1428 and friction surface 1432 the second flywheel 1403 clamped and beyond in such a position that the openings provided in the clutch disc 1443 are in such a situation that during the assembly process of the unit A on the output shaft of the internal combustion engine, a screwing tool can be moved through. It can be seen that the openings 1443 are smaller than the heads 1440 the screws 1408 , so that thereby a perfect and captive mounting of the screws 1408 in the unit A is guaranteed.

Also in the plate spring 1427 , in the area of their tongues 1427A , are openings or cutouts 1444 provided for the passage of the screwing tool. The cutouts 1444 may be provided such that they widenings or extensions of between the tongues 1427A form existing slots. The openings 1444 in the plate spring 1427 . 1443 in the clutch disc 1405 and 1434 in the flywheel 1403 cover each other while in the axial direction, in such a way that even with a due to be positioned to be successful assembly of the unit A on the crankshaft required asymmetrical arrangement of the holes 1407 an assembly tool, such as an Allen key, properly through the openings 1444 . 1427 and 1443 pass through and into the recesses of the heads 1440 the screws 1408 can intervene.

One Such complete unit A facilitates the assembly of the flywheel considerably, because it eliminates various operations, such as the otherwise required centering for the clutch disc, the Operation for the insertion of the clutch disc, the attachment of the clutch, the Introduce the centering mandrel, centering the clutch disc itself, the insertion of the screws and the screwing of the clutch and the removal of the centering mandrel.

The friction clutch 1404 has a readjustment 1445 in a similar way as this in conjunction with the 1 to 27 was described by means of a sensor spring 1446 and an adjusting ring 1447 ensures wear compensation.

In the 36 illustrated torque transmitting device 1501 has a rotatably connectable to the crankshaft K of an internal combustion Ge gendruckplatte 1503 at which a friction clutch 1504 with the interposition of a clutch disc 1505 is attached. The clutch disc 1505 is receivable on the input shaft of a transmission, not shown.

The clutch cover 1522 has an axially extending area 1523 who has the printing plate 1528 and the friction linings 1529 the clutch disc 1505 radially overlaps axially outside. The end section 1523a of the sleeve or tubular cover area 1523 surrounds or surrounds the counter-pressure plate 1503 and is with this over in the section 1523a introduced stampings 1524 that is in on the outer circumference of the platen 1504 in front engage wells seen firmly connected. The lid 1522 and the counterpressure plate 1503 However, they can also be connected in other ways, eg. B. via welded joints, by connections by means of screws or pins, which are also preferably introduced in the radial direction.

The on the outer contour of the counter pressure plate 1503 centered clutch cover 1522 has a substantially radially inwardly extending annular region 1526 , on which an effective as two-armed lever disc spring 1527 is pivotally mounted. With radially outward areas the plate spring acts 1527 the pressure plate 1528 , whereby the friction linings 1529 between the counter-pressure plate 1503 and the printing plate 1528 be clamped axially. The plate spring 1527 has radial tongues 1527a for actuation of the clutch 1504 via a release system. For torque transmission between the pressure plate 1528 and the lid 1522 are torque transmitting means, preferably in the form of leaf springs 1521 provided with one end with the lid 1522 , preferably via riveted joints 1521a , are firmly connected and with their other end also via a riveted connection to the pressure plate 1528 , Preferably, the connection between the pressure plate 1528 and the leaf spring elements 1521 via a so-called Blindnietverbindung, as in the radial extent of the friction linings in the upper half of 35 is shown.

The friction clutch 1504 or the torque transmission device 1501 has a readjustment 1545 in a similar way as this in conjunction with the 1 to 27 was described by means of a sensor spring 1546 and an adjusting ring 1547 ensures wear compensation.

at 35 and 36 are stamped directly into the lid material Gegenauflauframpen designed such that in the direction of rotation of the friction clutch in each case an air passage opening ( 1547a in 36 ) form. By such a configuration, a better cooling of the same by a forced air circulation is achieved upon rotation of the corresponding friction clutch. In particular, this is also made of plastic Herge adjusting ring 1447 respectively. 1547 cooled, whereby the thermal load of this ring can be substantially reduced.

The friction clutch 1504 or the counterpressure plate 1503 is on the output shaft K via an elastic or resilient member 1550 rotatably, but axially limited displacement, attached. In the illustrated embodiment, this component 1550 disc-shaped and its stiffness dimensioned such that the on the output shaft K to the friction clutch 1504 excited axial and wobble or bending vibrations by the elastic member 1550 be attenuated or suppressed to a degree that a proper function of the friction clutch 1504 and in particular their readjustment 1545 guaranteed. It should therefore on the axially compliant component 1550 the greatest possible decoupling of the coupling unit 1504 relative to the axial and bending vibrations of the output shaft of the internal combustion engine, such as the crankshaft, take place. This can be avoided that the coupling unit 1504 or their Nachstellvorkehrung 1545 be impaired in their function. Without the aforementioned decoupling of the coupling unit 1504 relative to the crankshaft K could be an undesirable adjustment of the wear compensation 1545 due to the mass of the components and due to vibrations acting on these accelerations. It would have to be without the component filtering the vibrations 1550 , in particular in the interpretation of Nachstellvorkehrung 1545 , which are particularly taken into account by the inertial forces generated by the components forming this adjustment, whereby a complex tuning would be required and / or additional means to a non-attributable to a lining wear adjustment of the wear compensation arrangement 1545 to avoid.

In the torque transmission device 1501 according to 36 is the wear compensation precaution 1545 between the clutch cover 1522 and the plate spring 1527 effective. The torque transmitting device 1501 However, could also with a friction clutch according to the 28 to 34 be equipped, ie with a friction clutch in which the Verschleißnachstellvorkehrung between the diaphragm spring and acted upon by this pressure plate is effective.

The counterpressure plate 1503 is radially outside via screw connections 1551 with the axially elastic, disc-shaped component 1550 firmly connected. Instead of screw connections 1551 could also Blindnietverbindungen, like those in the upper half of the 35 in connection with the attachment of leaf springs to the pressure plate 1428 shown, use find. Radial within the articulation points 1551 between the disc-like component 1550 and the counterpressure plate 1503 is between these two components 1550 and 1503 an axial gap 1552 present the maximum amplitude of the axial oscillations between the two components 1550 and 1503 determined in the one axial direction. By abutment of the radially inner regions of the counter-pressure plate 1503 on the disk-shaped component 1550 can be the maximum axial displacement of the friction clutch 1504 in the direction of Output shaft K of the internal combustion engine to be limited. However, under normal operating conditions, in particular when the internal combustion engine is functioning properly, such a system does not take place. The annular counter pressure plate 1503 encompasses an axial projection 1553 , the part of a ring-shaped or disc-shaped component 1554 is. This disc-shaped component 1554 can with the radially inner areas of the elastic disc 1550 be firmly connected. The elastic disc 1550 and the disc-shaped member 1554 are on an annular ledge 1555 the shaft K centered and with this via screw 1556 firmly connected. The radially inner regions of the disk-shaped component 1550 are axially between an end face 1557 the shaft K and the annular member 1554 trapped.

The axial approach 1553 of the component 1554 has at its the elastic member 1550 remote end radial areas 1558 showing the axial displacement of the friction clutch 1504 or the counter-pressure plate 1503 in the other axial direction limit. Between the areas 1558 and the counterpressure plate 1503 is at unclaimed elastic component 1550 an axial gap 1559 available. This gap 1559 is similarly dimensioned in the axial direction as the gap 1552 , The counterpressure plate 1503 can over its inner circumferential surface on the axial projection or projection 1553 be taken virtually free of play, so that thereby an axial guidance of Ge gendruckplatte 1503 can be guaranteed. It may be useful, however, if between the inner circumferential surface of the counter-pressure plate 1503 and the axial approach 1553 At least a small air gap is present, so there is no contact between these two components in normal operating conditions.

According to a development, for damping, in spite of the elastic member 1550 still transferred vibrations are provided for the vibration energy destroying precaution. Such a provision may be formed by a frictional connection, such as in 37 is shown. At the in 37 illustrated embodiment is between the inner regions of the platen 1503 and the outer surface of the neck 1553 a damping agent 1560 provided, which z. B. by a corrugated ring in the circumferential direction, the corrugations may extend radially, may be formed. This ring 1560 is installed braced in the radial direction, causing friction, z. B. between this ring 1560 and the inner circumferential surface of the counter-pressure plate 1503 is generated in the presence of axial vibrations. So there is a damped storage of the platen 1503 on the approach 1553 , The wavy ring 1560 can be separated over its circumference, so open.

Radial outside carries the disc-like, elastic component 1550 a starter ring gear 1561 ,

The disk-shaped component 1550 , the counterpressure plate 1503 , the clutch disc 1505 and the friction clutch 1504 Form a unit that is pre-assembled as such, so shipped, stored and can be screwed onto the crankshaft K of an internal combustion engine in a particularly simple and efficient manner. The fixing screws 1556 in the form of Allen screws are also already pre-assembled; So included in the assembly, and indeed captive.

The clutch disc 1505 is in a pre-centered to the axis of rotation of the crankshaft position between pressure plate 1528 and counter pressure plate 1503 clamped and beyond in such a position that the openings provided in this 1562 which radially inside the spring damper of the clutch disc 1505 are provided, are in such a situation that during the assembly process of the unit on the shaft K a screwing tool 1563 can be moved through. Also the plate spring 1527 has, if necessary, openings or cutouts 1564 for carrying out the screwing tool 1563 , The openings or cutouts 1564 the plate spring 1527 overlap with the openings 1562 the clutch disc 1505 so that the assembly tool, such as an Allen key 1563 , perfectly in the screw profiling of the heads of the screws 1556 can intervene.

As already described in connection with the other embodiments, by the use of a friction clutch 1504 with a precaution 1545 , which compensates at least the pad wear, an optimization in the design of the friction clutch, in particular of the tensioning force for the clutch disc applying force accumulator 1527 , respectively. This energy storage device can be designed so that it practically applies only the necessary for transmitting the desired torque clamping force for the clutch disc. By the Nachstellvorkehrung 1545 is ensured that the energy storage 1527 in the engaged state of the coupling unit 1501 practically the same installation position over the entire lifetime. Furthermore, by the likewise in the coupling unit 1501 Existing provision in the form of pad suspension 1565 which when disengaging and engaging the unit 1501 over at least a portion of the actuating travel of the printing plate 1528 causing a gradual degradation of the unit transmissible torque, a reduction the disengagement forces or the Ausrückkraftverlaufes be achieved. It can therefore be determined by appropriate coordination between the force applied by the precaution, such as a pad spring, and by the force acting on the pressure plate force storage forces or the force-displacement identifiers of the desired Ausrückkraftverlauf. This also makes it possible, the elastic component 1550 optimal interpreted with respect to the desired damping function for axial, bending or tumbling oscillations, since the force acting on this elastic member reduced Ausrückkräfte are of subordinate importance. It can therefore be required without significant axial displacement of the coupling unit Duch the component to be supported for disengaging the clutch actuating forces.

The Invention is not limited to the illustrated and described embodiments limited, but includes also variants, by combination of individual in connection with the different embodiments described features or elements can be formed. Farther can individual features described in connection with the figures or Functions for taken alone represent an independent invention.

Claims (21)

Friction clutch, in particular for motor vehicles, with a pressure plate, which is non-rotatably, but axially limited displaceable connected to a housing, wherein between housing and pressure plate at least one pressure spring in the form of a plate spring ( 1104 ) is effective, which acts on the pressure plate in the direction of a between this and a counter-pressure plate, such as a flywheel, clamped clutch disc, wherein the wear of the friction linings of the clutch disc compensating adjusting device ( 1116 . 1117 ) is present and the friction clutch actuating means ( 1104b ) has to move in and out and a precaution ( 1110 ), which during the engagement process causes a gradual build-up of the transmittable by the clutch disc of the friction clutch torque and wherein the adjusting device ( 1116 . 1117 ) is characterized in that between pressure plate ( 1103 ) and disc spring ( 1104 ) a displaceable in the axial direction compensation component ( 1126 ) is provided on the pressure plate ( 1103 ) at least one wear sensor ( 1122 ) provided with a counter-abutment area ( 1133 ) on the compensation component ( 1126 ) and in a pa r parallel to the axis of rotation of the pressure plate ( 1103 ) arranged opening ( 1120 ) is mounted such that it when engaging the friction clutch ( 1101 ) by a on the wear sensor ( 1122 ) acting force of an axially fixed component ( 1106 ) according to the respective wear of the friction linings ( 1107 ) axially opposite the pressure plate ( 1103 ) is displaceable and the counter-stop area ( 1133 ) of the compensation component ( 1126 ) takes off. Friction clutch according to claim 1, characterized in that the friction clutch is a precaution ( 1110 ), which during the disengagement process over a portion of the axial displacement path of the by the pressure spring ( 1104 ) acted upon pressure plate ( 1103 ) causes a gradual reduction of the transmissible by the friction clutch torque. Friction clutch according to claim 1 or 2, characterized in that the gradual construction of the transmittable by the clutch disc of the friction clutch torque effecting provision in the power flow between the actuating means ( 1104b ) and the mounting portions of the housing is provided on the counter-pressure plate. Friction clutch according to one of claims 1 to 3, characterized in that the provision ( 1110 ) in the power flow between the press spring ( 1104 ) and the friction surface of the pressure plate ( 1103 ) is provided. Friction clutch according to one of the preceding claims, characterized in that the provision ( 1110 ) axially between the friction linings ( 1107 ) of the clutch disc is provided. Friction clutch according to one of claims 1 to 5, characterized in that the provision ( 1110 ) provides an axial, resilient compliance between coupling components, wherein the arrangement is arranged such that when the clutch is opened, the force acting on the precaution is smallest and when closing the clutch, the force acting on the precaution gradually increases to the maximum, said increase takes place over at least a portion of the closing path. Friction clutch according to one of claims 1 to 6, characterized in that the provision ( 1110 ) the gradual reduction or the gradual increase of the transmittable by the friction clutch torque over at least approximately 40 to 70% of the actuating travel of the actuating means ( 1104b ) causes. Friction clutch according to one of claims 1 to 7, characterized in that the pressure spring ( 1104 ) has a degressive force-displacement curve over at least part of the Ausrückweges the friction clutch. Friction clutch according to one of vorherge existing claims, characterized in that the pressure spring ( 1104 ) on the one hand to a supported by the housing ring-like pivot bearing ( 1111 . 1112 ) is pivotable and on the other hand, the pressure plate applied. Friction clutch according to claim 9, characterized in that the disc spring ( 1104 ) a ring body ( 1104a ) emanating from the radially inwardly directed tongues, which the actuating means ( 1104b ) form. Friction clutch according to claim 9 or 10, characterized in that the disc spring ( 1104 ) on the housing ( 1102 ) between two editions ( 1111 . 1112 ) is pivotally supported. Friction clutch according to one of claims 8 to 11, characterized in that the disc spring ( 1104 Has a sinusoidal force-displacement curve and in the engaged state of the friction clutch, the operating point of the plate spring on the first maximum force fol lowing degressive characteristic area is provided and the plate spring is a force ratio of about 1: 0.4 to 1: 0.7 between the first maximum force and the following minimum. Friction clutch according to one of claims 1 to 12, characterized in that the provision ( 1110 ) at least one with the pressure spring ( 1104 ) in series arranged spring means, which during the engagement process over a portion of the actuating travel of the actuating means ( 1104b ) causes a gradual build up of the transferable via the clutch disc torque. Friction clutch according to one of claims 1 to 13, characterized in that it is part of a clutch unit, wherein the counter-pressure plate ( 1106 ) Part of a mass of a dual mass flywheel ( 1402 . 1403 ), whose masses against the action of a torsional vibration damper ( 1409 ) are rotatable relative to each other, wherein the other of the masses with the output shaft of an internal combustion engine is connectable. Friction clutch according to claim 14, characterized in that the housing ( 1102 ) with the through the counter-pressure plate ( 1106 ) inertia mass is rotationally fixed about a not releasable without destruction connection. Friction clutch according to claim 14 or 15, characterized in that the torsional vibration damper ( 1409 ) is provided radially outside the outermost friction diameter of the clutch disc. Friction clutch according to one of claims 1 to 16, characterized in that it is part of a clutch unit, which via an axially elastic component ( 1550 ) is connectable to the output shaft of an internal combustion engine whose stiffness is dimensioned such that the excited via the output shaft to the friction clutch axial, wobble and bending oscillations by the elastic member ( 1550 ) are damped to a level that ensures proper operation of the friction clutch. Friction clutch according to claim 17, characterized in that the rigidity of the component ( 1550 ) is dimensioned such that the actuating forces required for disengaging the clutch without significant axial displacement of the clutch assembly by the component ( 1550 ) are supported. Friction clutch according to claim 17 or 18, characterized in that the provision ( 1110 ) has a spring means in series with the pressure spring ( 1104 ) is arranged. Friction clutch according to one of claims 17 to 19, characterized in that the counter-pressure plate via a torsional vibration damper ( 1409 ) Is connectable to the output shaft of the internal combustion engine. Friction clutch according to one of claims 1 to 17, characterized in that it is part of a drive unit is, consisting of an automatic or semi-automatic transmission and a drive motor, wherein between the transmission and the drive motor arranged friction clutch at least in response to the actuation of the Transmission is controlled or regulated actuated.