EP1957816A1

EP1957816A1 - Clutch unit

Info

Publication number: EP1957816A1
Application number: EP06828498A
Authority: EP
Inventors: Mathieu Jordan; Karl-Ludwig Kimmig; Philippe Mih
Original assignee: LuK Lamellen und Kupplungsbau Beteiligungs KG; LuK Lamellen und Kupplungsbau GmbH
Current assignee: Schaeffler Buehl Verwaltungs GmbH; LuK Lamellen und Kupplungsbau GmbH
Priority date: 2005-11-29
Filing date: 2006-11-02
Publication date: 2008-08-20
Also published as: JP2009517609A; WO2007062615A1; US20080308379A1; CN101317021B; CN101317021A; BRPI0619390A2; DE112006002788B4; DE112006002788A5; KR20080071573A

Abstract

The invention relates to a clutch unit which consists of at least one friction clutch comprising a pressure disk, which is joined to the housing in a rotationally fixed manner but can be displaced in an axially limited manner. A lever system (5, 7), which can pivot in an axial direction, is arranged between the housing and the pressure disk and can be impinged upon by an actuation device in order to close the clutch. An adjusting device (13), which at least partially compensates at least the wear and tear of the friction lining (14) of the clutch device (13), engages between the lever system and the housing. Also, the lever system is axially supported on the housing by an adjusting ring (12) which can rotate in relation to the housing and can be impinged upon in an axial manner in the direction of the adjusting ring by spring elements (10, 21). Said spring elements produce an axially resulting supporting force which is in the opposite axial direction to the clutch closing pressure which can be applied to the lever system, and a force-path characteristic, which reduces at least in the working area wherein the spring elements are deformed for the at least partial wear and tear compensation, is produced.

Description

Kupplunqsaggreqat

The invention relates to coupling units, comprising at least one friction clutch with a pressure plate which is non-rotatably, but axially limited displaceable connected to a housing, wherein between the housing and thrust washer a pivotable in the axial direction lever assembly is provided, which can be acted upon by an actuator for closing the clutch is, between the lever assembly and the housing at least the wear of the friction linings of a clutch disc at least partially compensating adjusting device is effective, wherein further the lever assembly is axially supported via a relative to the housing rotatable adjusting ring on the housing and axially acted upon by spring means in the direction of Nachstellringes, wherein the spring means generate an axial resultant support force axially opposing the clutch closing force which can be introduced to the lever assembly.

Such clutch units with a single or two clutches have been proposed for example by DE 10 2004 018 377 A1.

Clutches with an automatic readjustment have been proposed, for example, by DE 29 16 755 A1 and DE 35 18 781 A1, wherein in these clutches a virtually constant application of force to the pressure plate to be effected by the pressure spring.

The present invention has for its object to make coupling units of the type mentioned in such a way that they require only a small space, at least in the axial direction. Another object underlying the present invention was to also keep the actuating travel of the actuating element acting on the lever arrangement and introducing the closing force into the coupling small or substantially constant over the service life of the coupling. Furthermore, a clutch unit designed according to the invention is intended to ensure optimized functioning and a long service life as well as cost-effective production.

The abovementioned objects and objectives are achieved, inter alia, by the fact that the lever arrangement has axial spring properties which cause it to be urged in the direction of a frustoconical position which corresponds to the open state of the tire. The clutch arrangement has an ascending force-displacement spring characteristic curve and the spring means acting axially on this lever arrangement generate a force-displacement characteristic which, at least in the working range, over which the spring means be deformed for the at least partial wear compensation, is sloping. It is expedient if the spring means applying an axial support force to the lever arrangement have a decreasing force-displacement characteristic curve over their entire working range necessary over the service life of the friction clutch. About the Ausrückweg the friction clutch thus decreases the force exerted by the spring means on the lever assembly axial spring force, so it is smaller.

The aforementioned spring characteristic of the lever arrangement can extend over the working area, which is necessary for the entire service life of the friction clutch, at least approximately linearly. However, the usable spring characteristics may also have a curvature at least in some areas.

The lever arrangement may be advantageously formed by a plurality of radially oriented in an annular array levers. In order to impart the necessary axial spring properties to such a lever arrangement, the individual levers can be coupled to one another, with connecting sections formed integrally with the levers being able to be provided for coupling. These connecting sections can form an annular energy store together with the levers. However, the provided between the adjacent levers connecting portions may also have a loop-shaped course in the radial direction. By appropriate configuration of existing between the individual levers connecting portions thus the desired spring characteristic for the lever assembly can be realized. In addition to or alternatively for the connecting portions, a ring-like z. B. plate spring-like spring element are used, which is at least axially connected to the individual levers.

The lever arrangement can be installed in an advantageous manner in the friction clutch such that it can be pivoted radially outward on a ring-shaped rolling support supported by the adjusting ring in the manner of a one-armed lever. For this purpose, the lever assembly is urged by the aforementioned spring means axially against the Abwälzauflage. The rolling support can be formed integrally with the adjusting ring. However, the Abwälzauflage can also by an additional z. B. annular member which is supported by the adjusting ring, be formed.

To form the adjusting device, it may be expedient if the adjusting ring is supported on the coupling housing via a ramp system provided in an annular arrangement. The ramp system advantageously has a plurality of ramps extending in the circumferential direction and rising in the axial direction. The pitch angle of the ramps is preferably designed such that a self-locking within the ramp system is present, so that slipping of the ramps can be avoided. If necessary, the ramps can be provided along their extent with a certain roughness or with low profilings, which allow in the direction of adjustment, a shift of the ramps, but prevent slipping thereof. The adjustment function of the ramp system can be ensured in a simple manner by means of at least one energy storage, which braces the ramp system in the adjustment direction.

The axial loading of the lever assembly in the direction of the pivot bearing by means of the spring means can be carried out radially within the pivot bearing bearing adjusting ring in an advantageous manner. The spring means applying the axial support force for the lever arrangement can be supported indirectly or directly on the lever arrangement. Advantageously, these spring means may comprise a plate spring-like element, which is operatively clamped between the housing and the lever assembly. Such a plate-spring-like element can be clamped axially between the housing bottom and lever arrangement. However, it may also be appropriate to provide such a plate-spring-like element on the housing bottom facing away from the lever assembly, wherein it may be useful if support means are provided which are connected to the housing, the lever assemblies penetrate axially and as an axial support for the serve plate spring-like element.

The spring means may further comprise spring elements which are clamped axially between the housing and the pressure plate. Such spring elements can be formed for example by so-called leaf springs. Such leaf springs are fixedly connected at one end to the housing and at the other end to the pressure disk. Such tensioned between housing and pressure washer spring elements (such as leaf springs) can on the one hand, the torque transmission between the housing and thrust washer and on the other hand, the axia- Ensure that the thrust washer is displaced during the clutch actuation. Preferably, these spring elements are installed braced so that they act on the thrust washer axially in the opening direction of the clutch or urge.

For the function of the clutch unit or the friction clutch, it may be particularly advantageous if there is a lining suspension between the back to back arranged friction linings of the clutch disc. Such a pad suspension causes an additional axial support force in the direction of the pivot bearing is exerted on the lever assembly, as soon as the friction linings are moved axially towards each other by the pressure plate, whereby the lining suspension is braced.

For the function of the adjusting device, it is particularly advantageous if at least approximately when the thrust washer abuts the adjacent friction lining of the clutch disc and in the absence of Reibbelagverschleiß the forces acting in the closing direction on the lever assembly forces are in equilibrium with the acting on the Habelanordnung axially against the closing direction resulting Spring force which urges the lever assembly in the direction of the rolling support supported by the housing. This resulting spring force is at least generated by at least one tensioned between the housing and lever assembly, plate spring-like component, further tensioned by the pressure plate and housing leaf springs and optionally by a result of the support of the thrust washer on the adjacent friction lining by means of the pad spring generated axial force.

Advantageously, the clutch unit may be constructed such that the wear compensation by means of the adjusting device takes place at least substantially during an opening phase of the clutch unit. The interpretation of the adjusting device and their vote on the other components of the clutch assembly and the friction clutch is preferably such that the wear adjustment is at least approximately at fully relaxed pad suspension during an opening phase of the clutch assembly and the friction clutch.

Further functional as well as structural advantages are explained in more detail in connection with the following description of the figures.

Showing: Figure 1 shows a half section through an inventively designed

Friction clutch

FIG. 2 shows a detail of the adjusting device in FIG. 1,

Figures 3 to 7 are diagrams with different characteristics, from which the interaction of the individual spring and adjusting elements of a inventively designed friction clutch can be seen and

8 shows a dual clutch unit with a friction clutch according to

FIG. 1

The friction clutch 2 has a housing 3 and a rotationally fixed, but limited axially displaceable thrust washer 4. Between the pressure plate 4 and the housing 3, a lever element 5 is arranged , which is variable in its conicity and here has a suspension or elasticity in the sense of opening the clutch 2. To close the clutch 2, the radially inner tips 6 and the lever 7 forming the lever 7 are acted upon by means of at least substantially the closing force in the clutch 2 initiating actuator 8. The actuating element 8 advantageously comprises a roller bearing and forms part of an actuating system which may be designed as a pneumatic, hydraulic, electrical or mechanical actuating system or else has a combination of the mentioned actuating possibilities, that is, for example designed as an electrohydraulic actuating system. The lever element 5 is advantageously formed by a plurality of provided in an annular arrangement levers 7, which are connected to each other in the circumferential direction in an advantageous manner. The existing between the individual levers 7 compounds can be integrally formed with the levers or by an additional spring element, for. B. annular disc spring which is connected to the levers 7. The existing between the individual levers 7 compounds are expediently designed such that the lever member 5 has an axial elasticity, which ensures the possibility of a Konizitätsveränderung of the lever member 5. Such lever elements have been proposed for example by DE 103 40 665 A1, EP 09 92 700 B1, DE 199 05 373 A1 and EP 14 52 760 A1. In the illustrated embodiment, the lever member 5 is disposed axially between the bottom 9 of the housing 3 and the pressure plate 4.

Between the thrust washer 4 and the housing 3 spring elements 10 are provided, which are formed in the illustrated embodiment as so-called leaf springs. The spring elements 10 ensure the torque transmission between the housing 3 and the pressure plate 4. Furthermore, these designed as leaf springs spring elements 10 allow an axial displacement of the pressure plate 4 relative to the housing 3. The spring elements 10 have a defined axial bias, which ensures that the pressure plate 4th in the opening direction of the clutch 2 is acted upon. This ensures that the thrust washer 4 is always urged axially by means of the spring elements 10 in the direction of the lever element 5. By this action of the spring elements 10, the lever element 5 is urged against a supported by the housing 3, annular support 11 under normal operating conditions. The annular support 11 is supported or formed by an annular component 12, which is part of an adjusting device 13, by means of which at least the wear occurring on the friction linings 14 of a clutch disc 15 can be at least partially automatically compensated. The friction linings 14 are clamped between the thrust washer 4 and the counter-pressure plate 16 when closing the clutch 2. The housing 3 is firmly connected to the counter-pressure plate 16. The counter-pressure plate 16 may be part of a clutch unit, which has two clutches. Such coupling units can be used, for example, in conjunction with so-called powershift transmissions. However, the counter-pressure plate 16 may also be connected directly to the output shaft of an engine.

Between the axially arranged back to back friction linings 14, a so-called pad suspension 17 is preferably provided. Such pad springs have become known for example from DE 198 57 712 A1, DE 199 80 204 T1 or DE 29 51 573 A1.

As shown schematically in FIG. 2, the annular component 12 designed as an adjusting ring has ramps 18 extending in the circumferential direction and rising in the axial direction, which are supported on counter ramps 19 carried by the housing 3. In the circumferential direction of the adjusting ring 12 is acted upon by springs 20 which are braced between the housing 3 and the adjusting ring 12. The counter-ramps 19 can be imaged in an advantageous manner directly by integrally formed in the region of the housing bottom 9 ramps. Further details regarding the operation of an adjusting device 13, the design possibilities for the ramps 18 and counter ramps 19 and the design and arrangement of the springs 20 can be found in DE 42 39 291 A1, DE 42 39 289 A1, DE 43 22 677 A1 and DE 44 31 641 A1.

By using a pad spring 17, a progressive structure of the transmittable torque can be ensured when closing the friction clutch 2.

The lever element 5 is additionally acted upon in the opening direction of the clutch 2 by a spring element 21, which is operatively axially clamped between the housing 3 and the lever element 5. In the illustrated embodiment, this spring element 21 is formed by a plate spring having an annular base body 22, which is supported in the embodiment shown in Figure 1 radially inwardly over boom 23 on standoffs 25 and radially outward on boom 24 on the lever element 5. The spacer bolts 25 are connected to the housing 3 and extend axially between adjacent levers 7. The pressure disk 4 has circumferentially distributed, individual cams 26, between which the boom 24 are received circumferentially. The cams 26 are acted upon by the lever element 5 at least when closing the clutch 2.

As can be seen from Figure 1, the lever 7 are pivoted in the closing direction 27 in the manner of a one-armed lever to the annular support 11 during pivoting of the lever member 5. This pivoting about the annular support 11 is ensured by the fact that the at least of the leaf springs 10 and the plate spring-like spring element 21 axially exerted on the lever member 5, resulting support force is greater than that for closing the clutch 2 in the region of the lever tips 6 via the actuator. 8 In the case of the above-mentioned balance of forces, the axial force generated by the springs 20 via the ramp system 18 and 19 must also be taken into account, which is exerted on the lever element 5 via the annular component 12.

The individual axial forces acting on the lever element 5 are matched with respect to one another such that an adjustment of the adjusting device 13 is impossible, provided that no wear occurs at least on the friction linings 14. The relationship between the individual spring and actuating forces will be described in more detail below. From Figure 1 is still removed that, as soon as during a closing phase of the clutch 2, the friction linings 14 between the thrust washer 4 and the reaction plate 16 to be clamped, the axial force generated by the pad spring 17 then additionally axially acting on the lever member 5.

Due to the above-mentioned balance of forces or force designs ensures that, as already mentioned, during pivoting of the lever member 5, this remains in contact with the annular support 11 and is pivoted in the manner of a one-armed lever to this annular support 11. Thus, the pressure plate 4 is acted upon by the cam 26 in the closing direction, wherein at the same time the plate spring-like spring element 21 is acted upon and elastically deformed according to the existing lever ratios between the Abstütz- or Beaufschlagungsdurchmessem. During the elastic deformation takes place here, the pivoting of the spring element 21 in the region of the tips of the boom 23, which are supported on the pin 25. As already mentioned, in the absence of wear against the closing direction 27 axially acting on the lever member 5, resulting spring force during the entire closing path of the clutch 2 is always greater than the initiated in the lever tips 6 closing force. This ensures that the lever element 5 always exerts a certain axial force on the annular component 12. As a result, an unintentional rotation and thus adjustment in the area of the adjusting device 13 is avoided.

By the interaction of the adjusting device 13 with at least the spring element 21 and the leaf spring elements 10, a wear compensation device is formed, which causes at least on the friction linings 14 at least a partial compensation of this wear by axial tracking of the annular support 11 when wear occurs. The balance of power between the various acting on the lever member 5 spring elements and the lever element 5 itself are preferably coordinated so that the required to close the clutch 2 in the region of the lever tips 6 actuating travel in the direction of the arrow 27 remains practically constant, with open and closed friction clutch 2, the axial position of the lever tips 6 remains practically constant. This ensures that also the actuating element 8 operates over the entire life of the friction clutch practically via the same axial actuating travel. This operation of the wear compensation device is determined by appropriate design of the force acting on the lever member 5 spring elements and the spring characteristics of the lever member 5 and the lever ratios, the are present on the lever element 5 between the annular support, Federbeaufschla- supply and actuation zones.

As can be seen from FIG. 1, the lever element 5 can have a plate spring-like, circumferentially closed base region 28, from which radially outwardly and inwardly extending arms 29, 30 extend.

In connection with the characteristic curves entered into the diagrams according to FIGS. 3 to 7, the mode of operation of the above-described friction clutch 2 will now be explained in more detail.

The ratios shown in Figure 3 correspond to the new state of the mounted friction clutch 2 after the first operation, ie without any wear has occurred.

The line 100 corresponds to the force exerted on the lever tips 6 axial force Konizitätsveränderung the resilient lever element 5, in this deformation of the lever element 5 between two annular supports whose radial distance from the radial distance between the formed by the spring element 21, annular support 31 and the annular Beaufschlagungsbereich 32 corresponds to the tongue tips 6 for the actuator 8. The operating point assumed by the lever element 5 when new and after the first actuation of the friction clutch 2 corresponds to the point 101. Through this operating point 101, the angular installation position of the lever element 5 is determined when the new friction clutch 2 is ready for operation. It can be seen from FIG. 3 that the lever element 5 has a spring characteristic which increases over the closing path 102, ie is progressive. The force curve 103 via the Einrückweg 102 can be adjusted by appropriate design of the resilient lever member 5 to the respective application.

The dashed line 104 represents the applied by the pad spring segments 17 axial spreading force, which acts between the two friction linings 14. This axial spreading force counteracts the axial closing force introduced via the lever element 5 onto the pressure plate 4. This effect occurs as soon as the friction linings 14 between the friction surfaces of the pressure plate 4 and the counter-pressure plate 16 begin to be clamped. The latter is the case after the partial region 105 of the engagement path 102 has been covered by the pressure plate 4 in the direction of engagement 27. The portion 105 corresponds to the Lüftweg, which is required to a certain axial clearance for the friction linings 14 between the friction surfaces to ensure the thrust washer 4 and the platen 16. Such a game is necessary to avoid the transmission of a too large drag torque on the clutch plate 15 with disengaged clutch 2, since such a drag torque would affect at least the switchability of the transmission.

The line 106, which is extended beyond the control point 107 also dashed, represents the resulting force curve, which is generated by the superimposition or addition of at least the force curves of the leaf springs 10 and here plate spring-like spring element 21. The at least of the leaf spring elements 10 and the spring element 21 generated forces acting on the lever member 5 in the region of the lever tips 6 introduced by means of the actuating element 8 closing force axially counteract.

From Figure 3 it can be seen that the resulting force curve according to the line 106 has a decreasing with increasing tension or deformation of the spring elements 10 and 21 characteristic curve. It can be seen that due to the selected courses of the lines 100 and 106, these intersect in the region of the control point 107 and the balance of forces between the two lines 100 and 106 reverses, with the result that after exceeding the control point 107, the at least of The axial support force exerted on the lever element 5 by the spring elements 10 and 21 becomes smaller than the closing force introduced for deforming the lever element 5 in the region of the lever tips 6.

As already mentioned, the covering spring 17 also acts after exceeding the partial region 105, whereby when the partial region 105 is exceeded in the direction of engagement 27, the actuating force required for pivoting the lever element 5 increases until the end of the engagement path 102. This increase is represented by the line section 109 extending over the second subregion 108 of the engagement path 102.

Based on the characteristics shown in Figure 3 it can be seen that on both sides of the control point the forces acting axially on the lever member 5, opposite to the arrow 27 are greater than the forces represented by the force curve 103, the closing of the friction clutch 2 in the region of the lever tips. 6 in the direction of arrow 27. This ensures that the lever member 5 always exerts an axial force on the annular support 11 and the annular member 12, whereby a rotation of the annular member is prevented. In the region of the control point 107, if there is no wear, there is at least one axial balance between the aforementioned forces. Hand, so that no unwanted adjustment within the friction clutch 2 can take place.

In connection with Figure 1 is also understood that when engaging, so closing the friction clutch 2, the spring elements 10 and 21 are elastically or resiliently deformed, this deformation is dependent on the axial displacement of the pressure plate 4 and the pivoting movement of the lever element 5 in With respect to the annular support 11.

The basic development of the resulting force curve according to the lines 106 and 109 of FIG. 3 will now be briefly explained with reference to FIGS. 4 to 6.

FIG. 4 shows a possible spring characteristic 120 of a plate spring-like spring element corresponding to the spring element 21. The illustrated characteristic 120 has in the illustrated embodiment, a typical plate spring characteristic with a maximum force 121 and a minimum force 122. The characteristic 120 shown here has between the maximum force 121 and the minimum force 122 a practically linear region 123. However, this area 123 could also have a different course own, such. B. a slightly curved course.

4, since the friction linings 14 are subject to wear over the life of the friction clutch 2 (for example of the order of a total of 2 to 3 mm), In the case of maximum wear, the spring element 21 should have a bracing state, which corresponds to point 125, in the case of maximum wear. It can thus be seen from FIG. 4 that, viewed over the service life of the friction clutch 2, the axial force exerted on the lever element 5 by the spring element 21 decreases.

FIG. 5 shows the spring characteristic 140, which is generated by the leaf spring elements 10 in the illustrated embodiment. The leaf springs are here designed such that they produce a virtually linear force characteristic. The leaf spring elements 10 are installed in such a way that they exert an axial force on the thrust washer 4 when the friction clutch 2 is mounted, ready for use, which corresponds to the point 141. As can be seen in connection with FIG. 1, the thrust washer 4 shifts with increasing wear on the friction By this displacement, the leaf spring elements 10 are additionally braced so that they exert an increasing axial force on the thrust washer 4 and thus on this also on the lever member 5 over the life of the friction clutch 2. When there is maximum wear, the leaf spring elements 10 have an operating point which corresponds to the point 142 in FIG. FIG. 6 shows the resulting line of force curve 150 which is produced by superimposition, that is to say addition, of the linear course 123 of the characteristic curve 120 and the spring characteristic curve 140. It can be seen that this resulting force curve 150 over the life of the friction clutch 2 has a sloping course. The characteristic points corresponding to the restart and the worn state of the friction clutch 2 are indicated by 151 and 152.

The operating points 124, 125,... Contained in FIGS. 4, 5 and 6. 141, 142, 151 and 152 respectively correspond to those operating points of the various spring elements 10 and 21, which are present at mounted, ready to operate, open clutch 2.

6 shows still increasing characteristic regions 153, 154, which take into account the effect of the pad suspension 17 which becomes effective after a defined engagement path (eg 105 according to FIG.

The principle will now be explained with reference to FIG. 7, which effects an adjustment in the adjusting device 13 or in the wear compensation device comprising it. It should be noted in advance that the distance ranges used or changes in these path areas for explaining the mode of operation of a readjustment cycle as well as the occurring force changes are shown excessively for better understanding. In fact, the adjustments take place in relatively small steps, with the operating or Nachstellpunkte due to existing in the overall system clutch hysteresis and disturbance forces, z. B. due to vibrations, subject to certain variations, ie within a certain range are available.

The diagram according to FIG. 7 is based on the assumption that a certain amount of wear on the friction linings 14 has taken place when the friction clutch 2 is closed. As a result, the pivoting angle of the lever element 5 increases by an amount that is dependent on this wear. This is evident from the fact that, in FIG. 7, the engagement path 102a is greater in relation to the engagement path 102 according to FIG. 3, in the ideal case around the wear occurring at least on the friction linings 14. Assuming that the Fed's If the characteristics of the pad spring 17 have remained the same, the portion 108 a, via which this pad spring 17 is effective, is identical to the portion 108 in terms of its size. Due to the wear, however, the portion 105a between the path 110, from which the effect of the pad spring 17 when opening the clutch 2 is no longer present on the pressure plate 4 and the path 111, which corresponds to the installation position of the lever member 5 with the clutch 2 is open, been enlarged. As can be seen in connection with FIGS. 3 and 7, this increase in the distance 105a causes the holding force to be introduced for pivoting the lever element 5 in the region of the lever tips 6 to be larger when opening the clutch 2 by a certain distance 112a than that over this distance 112a then existing resulting force (or the force curve), which acts on the lever member 5 axially in the direction of the annular support 11. The area resulting from the intersection of the two characteristic curves 106 and 100 is hatched in FIG.

Due to the force relationships occurring during wear on the friction linings 14 when opening the friction clutch 2, the lever member 5 is first pivoted about the annular support 11 in the manner of a one-armed lever against the direction of arrow 27 in Figure 1, and that until, in Figure 7 with 113 indicated point is reached. Upon continuation of the pivotal movement of the lever member 5 in the opening direction, the lever member 5 pivots now in the manner of a two-armed lever to the annular support 31. This pivoting is due to the fact that acting in the direction of arrow 27 on the lever member 5 axial force, which in particular the introduced in the region of the lever tongues 6 actuating force is generated, is greater than the resultant supporting force for the lever member 5, which is opposite to the arrow 27. This pivoting of the lever member 5 to the annular support 31 stops at least approximately until until the point 114, the resulting, acting on the lever member 5, axial support force against the arrow 27 is greater than that for deforming or supporting the lever element. 5 required force in the area of the levers 6.

During the aforementioned operating phase, in which the lever element 5 is pivoted about the annular support 31 in the manner of a two-armed lever, the adjusting ring 13 is relieved, so that it can follow the pivoting movement of the outer arm 29 and the outer region of the lever element 5. This results in at least a certain adjustment of the wear occurring on the friction linings 14. The size of the adjustment depends on the lever element 5 existing lever ratios, the are predetermined by the diameter of the annular support 11, the annular support 31 and the annular Beaufschlagungsbereiches 32. The axial adjustment of the support 11 may be greater than the occurred axial wear on the friction linings fourteenth

The aforementioned leverage ratios and acting on the lever member 5, the pivoting and displacement of the same determining forces and the spring properties of the lever element 5 are preferably coordinated such that over the life of the friction clutch 2, in the open state thereof, the tongue tips 6 a practically constant have axial position. This implies that, although the tongue tips 6 maintain a practically constant axial position with respect to the coupling housing 3, the outer region (in the region of the annular support 11) of the lever element 5 must be axially displaced. This is necessary in order to ensure that despite the wear occurring on the friction linings 14 and the associated axial displacement of the pressure disk 4, the actuating travel necessary for closing the friction clutch in the area of the lever tips 6 remains at least approximately constant. Due to the existing in the construction of Figure 1 kinematics or Verschwenkverhältnisse for the lever member 5 of the required axial adjustment path in the region of the annular support 11 is greater than the axial amount of wear on the friction linings 14, in accordance with the existing leverage ratios. These leverage ratios are mainly determined by the distance between the annular support 11 and the loading diameter 32 on the one hand and the radial distance between the annular support 31 and the loading diameter 32 on the other hand. The requirement according to which the lever tips 6 are to maintain an at least constant axial position over the life of the friction clutch causes the lever element 5 to change its tension state at least when the friction clutch 2 is open, which is done by corresponding adjustment of the annular support 11. This change also causes a change in the state of tension of the spring elements 10 and 21 when the friction clutch is open. This is due to the fact that these spring elements 10 and 21 are supported either axially or indirectly on the lever element 5, which in turn assumes a, over the life of the friction clutch changing, strained position.

The aforementioned changes in the tension state of at least the spring elements 10 and 21 and the lever element 5 require that the lever element 5 on the Le Bensdauer the friction clutch relaxed by a certain amount, whereas the spring elements 10 and 21 experience an increase in their tension. The latter means that, as can be seen in connection with the various diagrams according to FIGS. 3 to 7, the resulting supporting force for the lever element 5 produced by the spring elements 10 and 21 decreases with increasing wear on the friction linings 14. Also, the force curve required for pivoting the lever element 5 in the region of the lever tips 6 decreases due to the mentioned relaxation of the lever element 5.

The spring characteristics of the individual elements, in particular of the components 5, 10 and 21 are designed such that despite the aforementioned displacements or changes in the operating points or the working areas of these spring elements, which remains pre-described adjustment principle due to the existing balance of power over the life of the friction clutch ,

By appropriate design, at least the spring elements 10 and 21, a resultant force curve can be generated, which has a substantially constant force at least over the axial adjustment path of the pressure plate 4 to compensate for Reibbelagverschleißes. Such a force profile section is substantially parallel to the abscissa. In such a design, the then taking place axial displacement of the lever element 5 take place such that the lever element 5, at least in the engaged state of the clutch 2 and possibly also in the disengaged state of the clutch 2, each having a constant taper.

FIG. 8 shows a dual-clutch unit 201 which has two friction clutches 202 and 203, which are arranged on both sides of a plate 204 designed as a counterpressure disk. In the illustrated embodiment, the friction clutch 203 is formed with respect to the functional arrangement of the individual components, as described in connection with the preceding figures, LIST OF REFERENCES

1 clutch unit

2 friction clutch

3 housing

4 pressure disc

5 lever element

6 inside tips

7 lever

8 actuator

9 caseback

10 spring elements

11 annular support

12 adjusting ring

13 adjusting device

14 friction linings

15 clutch disc

16 counter pressure plate

17 lining suspension

18 ramps

19 counter ramps

20 springs

21 spring element

22 annular body

23 outriggers

24 outriggers

25 spacers

26 cams

27 arrow

28 closed base area

29 outriggers

30 outriggers

31 annular support

32 annular loading area 100 line - axial force to change the conicity

101 operating point

102 closing path 102a Einrückweg

103 Force progression

104 dotted line - axial spreading force

105 subarea 105a subarea

106 line - resulting force curve

107 control point

108 second subsection 108a subarea

109 line section

110 way

111 way

112

112a route

113 pivoting

114 point

120 spring characteristic

121 maximum force

122 power minimum

123 linear range

124 stress state

125 tension condition

140 spring characteristic

141 operating point

142 operating point

151 characteristic point

152 characteristic point

153 rising characteristic point 154 rising characteristic point

Claims

claims

1. Clutch assembly consisting of at least one friction clutch with a pressure plate which is rotationally fixed, but axially limited displaceable connected to a housing, wherein between housing and thrust washer a pivotable in the axial direction lever assembly is provided which can be acted upon by an actuator for closing the clutch , wherein between Hebelandordnung and housing at least the wear of the friction linings of the clutch disc at least partially compensating adjusting device is effective, the Hebelandordnung is axially supported by a relative to the housing rotatable adjusting ring on the housing and is acted upon by spring means axially in the direction of Nachstellringes, wherein the spring means generate an axial resultant supporting force, which is directed axially opposite to the clutch closing force which can be introduced onto the lever arrangement, characterized in that the lever arrangement has an axial spring property s which cause the lever assembly to be urged toward a tapered step corresponding to the open state of the friction clutch, the lever assembly having an increasing force-displacement spring characteristic across the pivoting path necessary to close the friction clutch and axially engaging the lever assembly acting spring means generate a force-displacement curve, which, at least in the work area over which the spring means for the at least partial wear compensation are deformed, is sloping.

2. Clutch assembly according to claim 1, characterized in that the lever arrangement is pivotable radially outwardly in the manner of a one-armed lever to a ring carried by Nachstellring, annular Abwälzauflage.

3. Clutch assembly according to claim 1 or 2, characterized in that the adjusting ring is supported on the clutch housing via a ramp system provided in an annular arrangement.

4. Clutch assembly according to claim 3, characterized in that the ramp system is braced over at least one energy storage in the sense of an axial wear adjustment.

5. Clutch assembly according to one of claims 1 to 4, characterized in that the lever arrangement radially within the bearing of a pivot bearing Nachstellringes is acted upon by the spring means indirectly or directly axially in the direction of the pivot bearing.

6. clutch unit according to one of claims 1 to 5, characterized in that the spring means comprise a plate-spring-like element which is operatively clamped between the housing and the lever arrangement.

7. Clutch assembly according to one of claims 1 to 6, characterized in that the spring means comprise spring elements which are clamped axially between the housing and the pressure plate.

8. Clutch assembly according to claim 7, characterized in that the spring elements are formed by leaf springs.

9. Clutch assembly according to claim 1, characterized in that between the friction linings of the clutch disc a lining suspension is present.

10. Clutch assembly according to one of claims 1 to 9, characterized in that at least approximately, in contact with the thrust washer on the adjacent friction lining of the clutch disc and in the absence of Reibbelagverschleiß, the forces acting in the closing direction on the lever assembly axial forces in equilibrium with the on the lever assembly axial, counter to the closing direction acting, resulting spring force.

11. Clutch assembly according to claim 10, characterized in that the resulting spring force at least by at least one braced between housing and lever assembly plate spring-like component, further tensioned by between thrust washer and housing leaf springs and possibly by a result of the support of the thrust washer on the adjacent friction lining means of Pad spring generated axial support force is formed.

12. Clutch assembly according to one of claims 1 to 11, characterized in that the wear compensation by means of the adjusting device takes place during an opening phase of the clutch unit.

13. Clutch assembly according to one of claims 1 to 12, characterized in that the wear adjustment by means of the adjusting device is at least approximately at fully relaxed pad suspension during an opening phase of the clutch unit.