WO2011057600A1 - Unité d'embrayage - Google Patents

Unité d'embrayage Download PDF

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Publication number
WO2011057600A1
WO2011057600A1 PCT/DE2010/001267 DE2010001267W WO2011057600A1 WO 2011057600 A1 WO2011057600 A1 WO 2011057600A1 DE 2010001267 W DE2010001267 W DE 2010001267W WO 2011057600 A1 WO2011057600 A1 WO 2011057600A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring
ramp
tension spring
helical tension
clutch
Prior art date
Application number
PCT/DE2010/001267
Other languages
German (de)
English (en)
Inventor
Florian Krebs
Original Assignee
Schaeffler Technologies Gmbh & Co. Kg
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 Schaeffler Technologies Gmbh & Co. Kg filed Critical Schaeffler Technologies Gmbh & Co. Kg
Priority to DE112010004396T priority Critical patent/DE112010004396A5/de
Publication of WO2011057600A1 publication Critical patent/WO2011057600A1/fr

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
    • 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
    • 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
    • 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

Definitions

  • the invention relates to a clutch unit having at least one friction clutch, which comprises a wear adjustment device with a first ramp device, which cooperates with a second ramp device, which is braced by at least one spring device with the first ramp device and a spring device for use in such a clutch unit.
  • the object of the invention is to optimize a clutch unit with regard to the space for the spring device.
  • a clutch unit having at least one friction clutch, which comprises a wear adjustment device with a first ramp device, which cooperates with a second ramp device, which is braced by at least one spring device with the first ramp device, wherein the spring device at least one coil spring, preferably coil spring, comprising over its length variable winding diameter.
  • the winding diameter is in particular the diameter of a sectional surface perpendicular to the spring axis.
  • the spring device in particular its helical spring, can thus be optimally adapted to the space available in the area of the ramps.
  • the helical tension spring is preferably a conical helical tension spring, more preferably a frustoconical helical tension spring.
  • the enveloping contour of the helical tension spring can thus be adapted to substantially triangular or sawtooth ramps in the case of a spring axis which lies substantially in a plane perpendicular to the axis of rotation of the coupling.
  • an enveloping contour of the helical tension spring corresponds to the contour of a ramp of the ramp device.
  • a slope of a straight line applied to the outside of the spring windings in the direction of the spring axis relative to the spring axis corresponds to the gradient of the ramp with respect to a radial reference surface.
  • the coil spring preferably comprises at the spring end with the lower
  • Winding diameter between the spring end and a hook a wire preferably corresponds to the length of the unstressed helical tension spring.
  • the spring coils of the helical tension spring preferably have a winding spacing in the unstressed state. The spring coils are therefore not directly on each other.
  • a clutch assembly having at least one friction clutch comprising a wear adjustment device with a first ramp device cooperating with a second ramp device braced by at least one spring device with the first ramp device, the spring device comprising a helical tension spring having a variable length over its length Windungs trimmesser has.
  • the helical tension spring is a conical helical tension spring, more preferably a frusto-conical helical tension spring.
  • the spring device preferably comprises at the spring end with the lower
  • Winding diameter between the spring end and a hook a wire preferably corresponds to the length of the unstressed helical tension spring.
  • the spring coils of the helical tension spring have a winding spacing in the unstressed state.
  • Figure 1 shows a half section through a clutch unit with two ramp means which are clamped together by a plurality of tension spring means;
  • Figure 2 parts of the wear adjustment with tension springs according to the invention;
  • FIG. 4 is a perspective view of the tension spring device from FIG. 3.
  • the clutch unit 1 shown in Figure 1 comprises two friction clutches 2, 3, which are shown in the disengaged, ie open state.
  • the clutch unit thus forms a double clutch, which comprises two clutch plates 4, 5, which are connectable to different transmission input shafts, said gear having these waves can advantageously form a so-called power shift transmission, which may have two partial transmissions.
  • the clutch discs 4, 5 bear radially outside friction linings 6, 7, which are axially clamped between one of the two friction clutches 2 and 3 common counter-pressure plate 8 and a respective friction clutch 2 and 3 associated pressure plate 9, 10.
  • the counter-pressure plate 8 forms part of a flywheel which is connected to a drive motor.
  • the counter-pressure disk 8 is connected via axially extending regions, which are not shown here in detail, to a drive plate or a drive cage 11.
  • the drive plate 11 is formed as it protagonistring.
  • the axially extending portions which produce a connection between the back area 8 and the drive plate 11, can either be formed on the counter-pressure plate 8 or on the drive plate 11 or at least partially provided on both parts 8, 11.
  • the drive plate 11 may be screwed either in the manner of a torque converter with a provided for example on the crankshaft of the drive motor drive plate or be connectable to a motor side arranged drive element via an axial connector.
  • a torque converter with a provided for example on the crankshaft of the drive motor drive plate
  • a motor side arranged drive element via an axial connector.
  • the counter-pressure disk 8 is mounted on the transmission side via a bearing 12 and fixed at least in an axial direction in order to axially intercept the closing forces required for at least one of the friction clutches.
  • the GE- 8 can thus be stored or axially supported according to the teaching of this document on a transmission input shaft. However, it can also be accommodated in a modification of this doctrine on a fixedly connected to the transmission housing support stub or support tube and axially supported.
  • the pressure plate 9 is indirectly or directly preferably via leaf spring-like elements with the counter-pressure plate 8 rotatably, but limited axially displaceable connected.
  • the pressure plate 10 of the friction clutch 3 is drivingly coupled to the reaction plate 8 in a similar manner.
  • a housing-like component 12 is attached, which is designed here as a sheet metal lid. Axial on both sides of this component 12 provided in an annular arrangement lever elements 13, 14 are provided, by means of which the respectively associated friction clutch 2, 3 can be actuated.
  • the lever elements 13, 14 can each form a ring-like component which has dish spring-like properties, that is to say that its conicity is resiliently variable.
  • the lever elements 13, 14 combined to form a ring-like component are referred to as lever springs 15 and 16, respectively.
  • These lever springs 15, 16 preferably each have a spring property, which ensures that they tend to set up in a frustoconical position, which corresponds to an open state of the friction clutches 2 and 3.
  • the pressure plate 10 carries traction means 17 which extend axially and at its end facing away from the pressure plate 10 end 18 carry a pivot bearing or Abisselzauflage 19, on which the lever spring 16 is tiltably or pivotally supported.
  • the Abisselzauflage 19 is integral with the traction means 17 formed and formed by a radially inwardly directed annular area.
  • the traction means 17 may be formed by individual distributed over the circumference hook-like components. In an advantageous manner, however, these traction means 17 can also be combined to form a preferably made of sheet metal component, which has a preferably closed annular region, from which a plurality of axial legs can go out, which are firmly connected to the pressure plate 10.
  • the lever spring 16 Radially within the rolling support 19, the lever spring 16 is supported on an annular support ring 20.
  • the annular support ring 20 is clamped axially between the housing-like component 12 and the lever spring 16 and forms part of an adjusting device 21, by means of which at least the wear occurring on the friction linings 7 can be compensated for at least partially automatically.
  • the radially inner tips 22 of the lever spring 16 are acted upon in the left direction.
  • a closing force is at least substantially in the friction clutch 3 initiating actuating element, such as an actuating bearing provided, which is not shown in detail.
  • Such an actuator forms part of an actuating system, which may be formed as a pneumatic, hydraulic, electrical or mechanically actuated actuating system or has a combination of the aforementioned actuation options, that is, for example, designed as an electro-hydraulic actuation system.
  • Lever elements 13, 14 or lever springs 15, 16 have been proposed for example by DE 10340 665 A1, DE 199 05 373 A1, EP 0 992 700 B1 and EP 1 452 760 A1.
  • the torque transmission and the axial displaceability of the pressure plate 10 ensuring spring means, in particular leaf springs which connect the components 8 and 10 in a conventional manner, preferably have a defined axial bias, which ensures that the pressure plate 10 in the opening direction of the friction clutch 3rd is charged.
  • spring means in particular leaf springs which connect the components 8 and 10 in a conventional manner
  • the pressure plate 10 is urged away axially in the direction to the left by the counter-pressure plate 8 by the mentioned prestressed leaf springs.
  • the bias of the corresponding spring means, in particular leaf springs should continue ensure that the rolling support 129 is always urged axially in the direction of the radially outer regions of the lever spring 16.
  • the support ring 20 forms a so-called adjusting ring 20 which is axially supported via a ramp system on the housing-like component 12.
  • the ramp system has ramps extending in the circumferential direction and rising in the axial direction.
  • corresponding ramps can be formed directly on the adjusting ring 20 and the cooperating counter-ramps advantageously be introduced directly in the region of the housing bottom of the housing-like component 12 in an advantageous manner.
  • In the circumferential direction of the adjusting ring 20 is acted upon by at least one spring not shown in the circumferential direction or adjustment.
  • the adjusting device 21 further comprises a sensor device 23 which has a sensor ring 24, which is supported in a similar manner as described in connection with the adjusting ring 20 via a ramp system on the housing bottom of the housing-like member 12 and circumferentially acted upon in the adjustment direction by a spring becomes.
  • the sensor ring 24 is arranged axially between the housing-like component 12 and the outer regions of the lever spring 16, in this case at the radial height of the rolling support 19.
  • the sensor device 23 further has a sensor element 25, which preferably has axially resilient regions.
  • the sensor element 25 clamps, if no wear has occurred, the sensor ring 24 axially, so that it is then held non-rotatably.
  • the sensor element 25 has abutment regions 26 which can cooperate with counter-abutment regions 27 carried by the traction means, in particular when wear on the friction linings 7 occurs.
  • the axial arrangement of the abutment regions 26 and abutment regions 27 and between these upon actuation of the friction clutch 3 occurring axial paths are coordinated so that at a closure of the friction clutch 3 and lack of wear a maximum of only one touch between the Stop areas 26 and the counterstop areas 27 can take place.
  • the sensor element comprising the abutment regions 26 may be formed by an annular component which, viewed over the circumference, has individual, preferably evenly distributed, fastenings with the housing-like component 12.
  • the existing between these fasteners areas of the annular sensor element 25 carry the stop portions 26.
  • the provided in the circumferential direction between the fasteners areas of the sensor element 25 are elastically or resiliently deformable in the axial direction. For some applications, it may be expedient if these areas are also exposed to a torsional stress causing at least a slight twisting of at least the laterally of the abutment portions 26 circumferentially extending regions of lesser radial width.
  • the lever spring 15 of the friction clutch 2 is provided with respect to the lever spring 16 axially on the other side of the radial portions of the box-like member 12.
  • the lever spring 16 is supported by a radially outer region on a support ring or adjusting ring 28.
  • the adjusting ring 28 is in a similar manner as described in connection with the adjusting ring 20, relative to the housing-like member 12 rotatable and axially supported on this via a ramp system.
  • the adjusting ring 28 forms part of an adjusting device 29, which is effective between the radial regions of the housing-like member 12 and the lever spring 15.
  • torque transmission means are provided, which are preferably formed by known leaf springs, which are axially biased such that the pressure plate 9 is pressed axially against the lever spring 15.
  • the total axial force which acts on the lever spring 15 in the direction of the right, is dimensioned such that during operation of the clutch unit 1, an axial displacement or pivoting of the lever spring 16 due to at least resonance phenomena and / or axial vibrations or tumbling oscillations of at least individual components Clutch unit is prevented.
  • further energy storage or spring elements may be provided which act on the pressure plate 9 or directly on the lever spring 15.
  • the adjusting device 29 comprises a sensor device 30, which is arranged radially inside and spaced from the adjusting ring 28 here.
  • the sensor device 30 comprises a sensor ring 31, which is similar to the sensor ring 24 against the housing-like component 12 rotatable and supported by a ramp system.
  • the sensor device 30 has a sensor element 32, which is supported either directly or indirectly by the housing-like component 12.
  • the sensor element 32 has at least one, preferably a plurality of stop regions 33 distributed over the circumference, which interact with counterstop regions 34 at least when wear occurs on the friction linings 6 of the clutch disk 4.
  • the counter-abutment portions 34 may be formed by elements connected to the lever spring 15. It is particularly advantageous if these counter-abutment regions 34 are formed by tongues formed integrally with the lever spring 15.
  • the sensor element 32 has regions 35 which cooperate with axial prestressing at regions 36 of the sensor ring 31. Due to the axial prestressing of at least the regions 35, the sensor ring 31 is clamped axially, so that a rotation of the same at least in the absence of wear on the friction linings 6 is avoided. This will cause an uncontrolled te, not attributable to wear adjustment of the adjusting device 29 avoided.
  • the sensor element 32 may also be formed by an annular member which is similarly connected to the box-like member 12 and effective, as described in connection with the sensor element 25.
  • the housing-like component 12 is shown in a plan view together with the sensor ring 24, which is also referred to as a sensing ring, as well as tension spring devices 64 to 66.
  • the housing-like component 12 comprises an annular disk-like base body 40, which has nine ramps provided with elevations 41 to 49, which are also referred to as Rampenberge.
  • the ramp peaks 41 to 49 are arranged on a circumference such that a ramp valley 51 to 59 results in each case between two ramp peaks 41 to 49.
  • the ramps on the ramp peaks 41 to 49 cooperate with complementary shaped ramps which are formed on the sensor ring 24.
  • Each ramp part 51 to 59 of the housing-like component 12 is associated with a Rampenberg 61, 62 of the sensor ring 24.
  • the housing-like component 12 is also referred to as the first ramp device.
  • the sensor ring 24 is referred to as a second ramp device. The two ramp devices 12, 24 are braced against each other with the aid of three tension spring devices 64 to 66.
  • the sensor element 25 is attached by means of three rivet elements 71 to 73, which is also referred to as a clamping spring.
  • the clamping spring 25 has three inwardly projecting spring tongues, which serve to bias the sensor ring 24 in the axial direction against the housing-like component 12.
  • Figure 3 shows a perspective view of a section of the housing-like component 12 with the support ring 20 and the sensor ring 24. Also shown is one of the tension spring devices, this is denoted by the reference numeral 64.
  • the sensor element 25 is not shown, so that the view of the support ring 20 and the sensor ring 24 and the tension spring device 64 is free.
  • the tension spring device 64 is suspended between the sensor ring 24 and the sensor element 25 by means of hooks explained in greater detail below.
  • both the support ring 20 and the sensor element 25 each have recesses or holes into which the hooks can each be hung.
  • FIG. 4 shows an exemplary embodiment of the tension spring devices 64 to 66 in a three-dimensional view.
  • the tension spring device comprises a helical spring 80, which has a variable winding diameter D over its spring length L. This reduces conically or frustoconically from a maximum diameter Di to a minimum diameter D 2 .
  • a hook 82 is formed on the spring. The hook 82 protrudes beyond an enveloping conical surface, which is applied to the turns of the tension spring 80 from the outside, so that the hook 82 is outside an intellectual extension of the spring coils along the spring axis.
  • a wire 84 is formed, the end of which has a hook 85.
  • the spring device according to FIG. 4 is unloaded Tension spring 80 shown, while this is not acted upon by a tensile force or compressive force.
  • a spring axis 86 of the tension spring 80 has a curved course.
  • the wire 84 has a curved course.
  • the curvature corresponds approximately to the circular curvature of the sensor ring 24 or sensor element 25 at the installation location of the respective tension spring device.
  • the spring windings In the unstressed state of the helical tension spring 80 shown in FIG. 4, the spring windings have a constant or variable winding spacing A, that is to say that the spring windings are not in contact with one another.
  • the conical or frustoconical shape of the helical tension spring 80 is dimensioned so that the spring rests in the installed position on one of the ramps over the length of the helical tension spring 80.
  • the ramps each have an axial slope, viewed in the circumferential direction, which corresponds to the pitch of the outer contour of the spring coils in the installed position. The available space can be optimally utilized in this way, without the fferenzugfeder 80 rests with spring coils on the ramp device.
  • the slope of a line applied to the outside of the spring coils in the direction of the spring axis with respect to the spring axis corresponds to the slope of the ramp relative to a radial reference surface.

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

Abstract

L'invention concerne une unité d'embrayage (1) comprenant au moins un embrayage à friction (2, 3) qui comprend un dispositif de rattrapage d'usure avec un premier dispositif de rampe (12) qui coopère avec un deuxième dispositif de rampe (24) qui est tendu avec le premier dispositif de rampe par au moins un dispositif de ressort (64, 65, 66). Selon l'invention, l'espace de montage nécessaire est optimisé en ce sens que le dispositif de ressort comprend au moins un ressort à boudin (80), de préférence un ressort de traction à boudin, avec un diamètre d'enroulement (D) variable sur sa longueur (L).
PCT/DE2010/001267 2009-11-12 2010-10-29 Unité d'embrayage WO2011057600A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112010004396T DE112010004396A5 (de) 2009-11-12 2010-10-29 Kupplungsaggregat

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009053020 2009-11-12
DE102009053020.7 2009-11-12

Publications (1)

Publication Number Publication Date
WO2011057600A1 true WO2011057600A1 (fr) 2011-05-19

Family

ID=43629138

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2010/001267 WO2011057600A1 (fr) 2009-11-12 2010-10-29 Unité d'embrayage

Country Status (2)

Country Link
DE (2) DE102010050069A1 (fr)
WO (1) WO2011057600A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012142994A1 (fr) * 2011-04-20 2012-10-26 Schaeffler Technologies AG & Co. KG Dispositif d'embrayage
FR3046642B1 (fr) * 2016-01-08 2019-05-24 Valeo Embrayages Dispositif d'embrayage a rattrapage d'usure, notamment pour vehicule automobile

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4239289A1 (fr) 1991-11-26 1993-05-27 Luk Lamellen & Kupplungsbau
DE4412107A1 (de) * 1993-04-29 1994-11-03 Fichtel & Sachs Ag Reibungskupplung mit automatischem Verschleißausgleich und zwei Nachstellringen
DE4431641A1 (de) 1993-09-13 1995-03-16 Luk Lamellen & Kupplungsbau Ausrückvorrichtung
DE4322667A1 (de) 1992-04-17 1995-05-24 Erich Mundhenke Behälter zur Materialtrennung
DE19905373A1 (de) 1999-02-10 2000-08-31 Sachs Race Eng Gmbh Reibungskupplung und Anpreßhebelanordnung für eine Reibungskupplung
DE10011412A1 (de) * 1999-03-12 2000-09-14 Luk Lamellen & Kupplungsbau Kupplungsaggregat
US20020074203A1 (en) * 2000-12-19 2002-06-20 Blessinger Jeffrey S. Spring ferrule for friction clutch with automatic adjustment feature
EP0992700B1 (fr) 1998-10-05 2004-08-25 Aisin Seiki Kabushiki Kaisha Embrayage à friction pour véhicules
EP1452760A1 (fr) 2003-02-25 2004-09-01 ZF Sachs AG Dispositif de transmission de force pour un embrayage à friction
DE10340665A1 (de) 2003-09-04 2005-03-31 Zf Friedrichshafen Ag Kraftspeicher für eine Reibungskupplung
DE102005037514A1 (de) 2004-09-03 2006-03-09 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Drehmomentübertragungseinrichtung
EP2028385A2 (fr) * 2007-08-20 2009-02-25 LuK Lamellen und Kupplungsbau Beteiligungs KG Embrayage

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112006001361A5 (de) 2005-06-28 2008-03-06 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Kupplungssystem
KR101438525B1 (ko) 2005-06-28 2014-09-11 섀플러 테크놀로지스 아게 운트 코. 카게 클러치 시스템
EP1902226B1 (fr) 2005-06-28 2016-09-28 Schaeffler Technologies AG & Co. KG Unite d'accouplement
DE112006002807A5 (de) 2005-12-03 2008-09-04 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Drehmomentübertragungseinrichtung

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4239291A1 (fr) 1991-11-26 1993-05-27 Luk Lamellen & Kupplungsbau
DE4239289A1 (fr) 1991-11-26 1993-05-27 Luk Lamellen & Kupplungsbau
DE4322667A1 (de) 1992-04-17 1995-05-24 Erich Mundhenke Behälter zur Materialtrennung
DE4412107A1 (de) * 1993-04-29 1994-11-03 Fichtel & Sachs Ag Reibungskupplung mit automatischem Verschleißausgleich und zwei Nachstellringen
DE4431641A1 (de) 1993-09-13 1995-03-16 Luk Lamellen & Kupplungsbau Ausrückvorrichtung
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
DE10011412A1 (de) * 1999-03-12 2000-09-14 Luk Lamellen & Kupplungsbau Kupplungsaggregat
US20020074203A1 (en) * 2000-12-19 2002-06-20 Blessinger Jeffrey S. Spring ferrule for friction clutch with automatic adjustment feature
EP1452760A1 (fr) 2003-02-25 2004-09-01 ZF Sachs AG Dispositif de transmission de force pour un embrayage à friction
DE10340665A1 (de) 2003-09-04 2005-03-31 Zf Friedrichshafen Ag Kraftspeicher für eine Reibungskupplung
DE102005037514A1 (de) 2004-09-03 2006-03-09 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Drehmomentübertragungseinrichtung
EP2028385A2 (fr) * 2007-08-20 2009-02-25 LuK Lamellen und Kupplungsbau Beteiligungs KG Embrayage

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Publication number Publication date
DE112010004396A5 (de) 2013-01-10
DE102010050069A1 (de) 2011-05-19

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