EP1957816A1 - Organe d'embrayage - Google Patents

Organe d'embrayage

Info

Publication number
EP1957816A1
EP1957816A1 EP06828498A EP06828498A EP1957816A1 EP 1957816 A1 EP1957816 A1 EP 1957816A1 EP 06828498 A EP06828498 A EP 06828498A EP 06828498 A EP06828498 A EP 06828498A EP 1957816 A1 EP1957816 A1 EP 1957816A1
Authority
EP
European Patent Office
Prior art keywords
clutch
lever
spring
housing
force
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP06828498A
Other languages
German (de)
English (en)
Inventor
Mathieu Jordan
Karl-Ludwig Kimmig
Philippe Mih
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Buehl Verwaltungs GmbH
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau Beteiligungs KG
LuK Lamellen und Kupplungsbau GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by LuK Lamellen und Kupplungsbau Beteiligungs KG, LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau Beteiligungs KG
Publication of EP1957816A1 publication Critical patent/EP1957816A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/75—Features relating to adjustment, e.g. slack adjusters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/75—Features relating to adjustment, e.g. slack adjusters
    • F16D13/757—Features relating to adjustment, e.g. slack adjusters the adjusting device being located on or inside the clutch cover, e.g. acting on the diaphragm or on the pressure plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0607—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0607—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate
    • F16D2021/0615—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate the central input plate is supported by bearings in-between the two clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0684—Mechanically actuated clutches with two clutch plates

Definitions

  • 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.
  • 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 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 Ausschweg 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.
  • 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.
  • 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.
  • the provided between the adjacent levers connecting portions may also have a loop-shaped course in the radial direction.
  • 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.
  • the lever assembly is urged by the aforementioned spring means axially against the Abicalzauflage.
  • the rolling support can be formed integrally with the adjusting ring.
  • the Abicalzauflage can also by an additional z.
  • 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.
  • 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.
  • 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.
  • 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.
  • leaf springs are fixedly connected at one end to the housing and at the other end to the pressure disk.
  • tensioned between housing and pressure washer spring elements 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.
  • these spring elements are installed braced so that they act on the thrust washer axially in the opening direction of the clutch or urge.
  • 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.
  • 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.
  • Figure 1 shows a half section through an inventively designed
  • 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
  • FIG. 1 A first figure.
  • 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 Konizticiansver selectedung 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.
  • the lever member 5 is disposed axially between the bottom 9 of the housing 3 and the pressure plate 4.
  • 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.
  • 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.
  • 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.
  • a so-called pad suspension 17 is preferably provided between the axially arranged back to back friction linings 14.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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, Federbeetzschla- supply and actuation zones.
  • 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.
  • the line 100 corresponds to the force exerted on the lever tips 6 axial force Konizticiansver selectedung 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 Beaufschlagungs Scheme 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 Einschweg 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 L predominantlyweg, 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.
  • 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.
  • 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.
  • 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.
  • the thrust washer 4 shifts with increasing wear on the friction
  • 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.
  • the leaf spring elements 10 When there is maximum wear, the leaf spring elements 10 have an operating point which corresponds to the point 142 in FIG. FIG.
  • FIG. 7 effects an adjustment in the adjusting device 13 or in the wear compensation device comprising it.
  • 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.
  • the adjustments take place in relatively small steps, with the operating or Nachstellin 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.
  • the lever member 5 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.
  • 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 Beaufschlagungs Kunststoffes 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 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 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 ,
  • 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 Reibbelagverschl foundedes.
  • Such a force profile section is substantially parallel to the abscissa.
  • 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.
  • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un organe d'embrayage composé d'au moins un embrayage à friction pourvu d'un disque de pression, relié à un carter de manière bloquée en rotation mais pouvant être déplacé de façon axialement limitée. Un ensemble de leviers (5, 7) pouvant pivoter dans le sens axial est prévu entre le carter et le disque de pression, lequel ensemble est soumis à l'action d'un dispositif d'actionnement pour fermer l'embrayage. Un dispositif de réglage (13) compensant au moins partiellement l'usure des garnitures de friction (14) du disque d'embrayage (15) agit entre l'ensemble de leviers et le carter. Cet ensemble de leviers est soutenu axialement sur le carter par l'intermédiaire d'une bague de réglage (12), pouvant tourner par rapport au carter, et soumis axialement à l'action de moyens à ressort (10, 21) en direction de la bague de réglage, ces moyens à ressort produisant une force de soutien résultante axiale, qui s'oppose axialement à la force de fermeture de l'embrayage pouvant être appliquée sur l'ensemble de leviers, et produisant une courbe caractéristique force-course descendante au moins dans la plage de travail sur laquelle les moyens à ressort permettant la compensation au moins partielle de l'usure sont déformés.
EP06828498A 2005-11-29 2006-11-02 Organe d'embrayage Withdrawn EP1957816A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005057233 2005-11-29
PCT/DE2006/001920 WO2007062615A1 (fr) 2005-11-29 2006-11-02 Organe d'embrayage

Publications (1)

Publication Number Publication Date
EP1957816A1 true EP1957816A1 (fr) 2008-08-20

Family

ID=37763883

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06828498A Withdrawn EP1957816A1 (fr) 2005-11-29 2006-11-02 Organe d'embrayage

Country Status (8)

Country Link
US (1) US20080308379A1 (fr)
EP (1) EP1957816A1 (fr)
JP (1) JP2009517609A (fr)
KR (1) KR20080071573A (fr)
CN (1) CN101317021B (fr)
BR (1) BRPI0619390A2 (fr)
DE (1) DE112006002788B4 (fr)
WO (1) WO2007062615A1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112008003201A5 (de) * 2007-09-24 2010-09-02 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Reibungskupplung
DE102010034823B4 (de) * 2009-09-03 2019-12-19 Schaeffler Technologies AG & Co. KG Reibungskupplung mit Nachstelleinrichtung
DE102011085845A1 (de) * 2010-11-19 2012-05-24 Schaeffler Technologies Gmbh & Co. Kg Kupplungsvorrichtung
WO2012130198A1 (fr) * 2011-03-31 2012-10-04 Schaeffler Technologies AG & Co. KG Bague de rampe et support pour un système de post-réglage d'un accouplement à friction
DE102012217502A1 (de) * 2011-10-24 2013-04-25 Schaeffler Technologies AG & Co. KG Reibungskupplung und Verfahren zu deren Herstellung
DE102013200552B4 (de) * 2012-01-30 2019-10-10 Schaeffler Technologies AG & Co. KG Doppelkupplung mit Verschleißnachstelleinrichtungen
FR3000152B1 (fr) * 2012-12-20 2015-01-16 Valeo Embrayages Embrayage a rattrapage d'usure, notamment pour vehicule automobile
DE102015201917A1 (de) * 2014-02-13 2015-08-13 Schaeffler Technologies AG & Co. KG Selbstnachstellende Kupplung mit modifizierter Sensorkraft
JP6322619B2 (ja) * 2015-12-15 2018-05-09 本田技研工業株式会社 クラッチ装置
DE102016124812A1 (de) 2016-12-19 2018-06-21 Schaeffler Technologies AG & Co. KG Reibungskupplungseinrichtung und Antriebsstrang
CN109114126A (zh) * 2017-06-23 2019-01-01 舍弗勒技术股份两合公司 自调式离合器及汽车
DE102017123709B4 (de) * 2017-10-12 2021-05-20 Schaeffler Technologies AG & Co. KG Doppelkupplungsvorrichtung und Antriebsanordnung für ein Kraftfahrzeug
WO2023077265A1 (fr) * 2021-11-02 2023-05-11 舍弗勒技术股份两合公司 Embrayage et système d'énergie hybride
DE102021129006B3 (de) 2021-11-08 2022-12-22 Schaeffler Technologies AG & Co. KG Verfahren zur Herstellung eines Reibbelags und eine Reibungskupplung mit imprägnierten Reibbelägen

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4228883A (en) * 1978-04-27 1980-10-21 Borg-Warner Corporation Automatic wear adjuster for Belleville spring clutches
DE2951573A1 (de) * 1979-12-21 1981-07-02 Fichtel & Sachs Ag, 8720 Schweinfurt Federnde reibbelagbefestigung
DE3518781A1 (de) * 1985-05-24 1986-11-27 Fichtel & Sachs Ag, 8720 Schweinfurt Selbstnachstellende kupplung
SE512438C2 (sv) * 1991-11-26 2000-03-20 Luk Lamellen & Kupplungsbau Friktionskoppling
DE4322677B4 (de) * 1992-07-11 2005-05-12 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Reibungskupplung
CN1103140A (zh) * 1993-09-13 1995-05-31 卢克摩擦片和离合器有限公司 分离装置
DE19510905A1 (de) * 1994-03-29 1995-10-05 Luk Lamellen & Kupplungsbau Reibungskupplung
WO1999032797A1 (fr) 1997-12-18 1999-07-01 Luk Lamellen Und Kupplungsbau Gmbh Disque d'embrayage
US6267216B1 (en) 1998-01-28 2001-07-31 Valeo Friction plate, in particular for motor vehicle clutch
EP0992700B1 (fr) 1998-10-05 2004-08-25 Aisin Seiki Kabushiki Kaisha Embrayage à friction pour véhicules
DE19905373A1 (de) * 1999-02-10 2000-08-31 Sachs Race Eng Gmbh Reibungskupplung und Anpreßhebelanordnung für eine Reibungskupplung
JP5023372B2 (ja) * 2000-11-22 2012-09-12 シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト クラッチ装置
FR2838488A1 (fr) * 2002-04-10 2003-10-17 Luk Lamellen & Kupplungsbau Agregat d'accouplement
EP1452760B1 (fr) 2003-02-25 2006-04-12 ZF Sachs AG Dispositif de transmission de force pour un embrayage à friction
DE10308994A1 (de) * 2003-03-01 2004-09-09 Zf Sachs Ag Reibungskupplung
US7066313B2 (en) * 2003-04-17 2006-06-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Self-adjusting clutch
DE10340665A1 (de) 2003-09-04 2005-03-31 Zf Friedrichshafen Ag Kraftspeicher für eine Reibungskupplung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007062615A1 *

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CN101317021A (zh) 2008-12-03
DE112006002788A5 (de) 2008-09-04
DE112006002788B4 (de) 2019-07-25
WO2007062615A1 (fr) 2007-06-07
US20080308379A1 (en) 2008-12-18
KR20080071573A (ko) 2008-08-04
JP2009517609A (ja) 2009-04-30
BRPI0619390A2 (pt) 2011-10-04
CN101317021B (zh) 2011-05-11

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