WO2010066225A1 - Unité d'embrayage - Google Patents

Unité d'embrayage Download PDF

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Publication number
WO2010066225A1
WO2010066225A1 PCT/DE2009/001618 DE2009001618W WO2010066225A1 WO 2010066225 A1 WO2010066225 A1 WO 2010066225A1 DE 2009001618 W DE2009001618 W DE 2009001618W WO 2010066225 A1 WO2010066225 A1 WO 2010066225A1
Authority
WO
WIPO (PCT)
Prior art keywords
intermediate flange
clutch
energy storage
input part
clutch assembly
Prior art date
Application number
PCT/DE2009/001618
Other languages
German (de)
English (en)
Other versions
WO2010066225A8 (fr
Inventor
Reinhold Reder
Original Assignee
Luk Lamellen Und Kupplungsbau Beteiligungs 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 Luk Lamellen Und Kupplungsbau Beteiligungs Kg filed Critical Luk Lamellen Und Kupplungsbau Beteiligungs Kg
Priority to DE112009003303.2T priority Critical patent/DE112009003303B4/de
Publication of WO2010066225A1 publication Critical patent/WO2010066225A1/fr
Publication of WO2010066225A8 publication Critical patent/WO2010066225A8/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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F16F15/13469—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F16F15/13476—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
    • F16F15/13484—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
    • F16F15/13492—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs the sets of springs being arranged at substantially the same radius
    • 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
    • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • F16D2013/703—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members the pressure plate on the flywheel side is combined with a damper
    • 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 with at least one clutch and at least one torsional vibration damper, which comprises a counter to the effect of at least one energy storage limited to an input part rotatable output device comprises the Beaufschlagungs Suitee for acting on the at least one energy storage.
  • Such torsional vibration dampers are known, for example as dual-mass flywheels with integrated friction clutch or as double clutches, which is preceded by a torsional vibration damper.
  • the torsional vibration damper usually have to be accommodated in limited space between a drive motor and a transmission of a motor vehicle.
  • the joining of a transmission side mounted dual clutch with a dual mass flywheel damper is often complex and takes place, for example via a spline between a damper flange and a driver plate of the double clutch.
  • the object of the invention is to optimize a clutch unit according to the preamble of claim 1 with respect to the assembly and / or noise occurring during operation.
  • a clutch unit with at least one clutch and with at least one torsional vibration damper, which comprises a limited against the action of at least one energy storage relative to an input part rotatable output device, the Beaufschlagungs Schemee for acting on the at least one energy storage, achieved in that the Beaufschlagungs Schemee engage in an axial direction in an intermediate flange, which is limitedly movable in the radial direction relative to the input part.
  • the terms axial, radial and in the circumferential direction relate to the axis of rotation of the torsional vibration damper.
  • Axial means in the direction or parallel to the axis of rotation of the torsional vibration damper.
  • the clutch unit is used for torque transmission between a drive unit, in particular an internal combustion engine, with an output shaft, in particular a crankshaft, and a transmission with at least one transmission input shaft.
  • the torsional vibration damper is connected between the output shaft of the drive unit and the clutch.
  • the clutch designed in particular as a friction clutch is preferably designed as a double clutch.
  • the output device of the Torsional vibration damper can be rotationally connected, also in one piece, to an input part of the coupling.
  • a preferred embodiment of the clutch assembly is characterized in that the intermediate flange has a first axial sealing surface for a first sealing device, which is arranged in the axial direction between the input part and the intermediate flange.
  • a further preferred embodiment of the clutch unit is characterized in that the first sealing device comprises a sealing ring.
  • the sealing ring is preferably made of plastic and may have a circular or substantially rectangular ring cross-section.
  • Another preferred embodiment of the clutch assembly is characterized in that the sealing ring, at least partially, is received in an annular space which is open radially inwardly and is limited by a cross-sectional step of the intermediate flange.
  • a further preferred embodiment of the coupling unit is characterized in that the intermediate flange has a second axial sealing surface for a second sealing device, which is attached to the input part and rests against the second axial sealing surface of the intermediate flange. This prevents unwanted leakage of grease between the second axial sealing surface of the intermediate flange and the input part without affecting the radial mobility of the intermediate flange.
  • a further preferred embodiment of the clutch assembly is characterized in that the second sealing means comprises a circular disk which overlaps a radial annular gap between the intermediate flange and the input part.
  • the annular disk is preferably formed from sheet metal and may, for example by a welded joint, be integrally connected to the input part.
  • the size of the annular gap, the mobility of the intermediate flange is limited in the radial direction relative to the input part.
  • the second sealing device may be an additional sealing element, for example a Plastic sealing ring, which is or which is arranged in the axial direction between the annular disc and the second axial sealing surface of the intermediate flange.
  • Another preferred embodiment of the clutch assembly is characterized in that the two axial sealing surfaces are flat and / or smooth. As a result, the sealing effect is improved.
  • a further preferred embodiment of the clutch unit is characterized in that the at least one energy store is arranged in an energy storage receiving space which is bounded by the input part and the intermediate flange.
  • the energy storage receiving space is designed as an annular space and serves, for example, to accommodate a plurality of bow springs and grease.
  • Another preferred embodiment of the clutch unit is characterized in that extending input stops for the energy storage of the input part in the axial direction in the energy storage storage space.
  • the input stops are preferably produced by forming the input part, which is preferably formed from sheet metal.
  • a further preferred exemplary embodiment of the clutch unit is characterized in that intermediate stops for the energy store extend from the intermediate flange in the axial direction into the energy storage receiving space.
  • the intermediate stops are preferably produced by forming the intermediate flange, which is preferably formed from sheet metal.
  • Another preferred embodiment of the clutch assembly is characterized in that the loading regions of the output device are formed on a first and on a second output part, which are coupled to the intermediate flange.
  • the two output parts are preferably formed from sheet metal and can be firmly connected by means of rivet connection elements, for example with a counter-pressure plate of a double clutch.
  • a further preferred embodiment of the clutch unit is characterized in that the first output part radially outside the second output part in the Zwi - A - engages flange.
  • the engagement of the output parts in the intermediate flange is preferably carried out positively, wherein in one or more directions, if necessary, a certain amount of play can be provided. Due to the interlocking interventions of the two output parts in the intermediate flange, a rotationally fixed connection between at least one of the output parts and the intermediate flange is provided.
  • a further preferred embodiment of the coupling unit is characterized in that the first output part has tongues which engage in the axial direction in the intermediate flange.
  • the tongues preferably engage in the intermediate flange in the region of the intermediate stops for the energy store in the axial direction.
  • a further preferred embodiment of the clutch assembly is characterized in that the tongues of the first output part engage with clearance in the circumferential direction in recesses of the intermediate flange.
  • the recesses are preferably formed by deformed areas of the intermediate flange.
  • the deformed areas of the intermediate flange simultaneously constitute the intermediate stops for the energy store.
  • a further preferred embodiment of the clutch unit is characterized in that between the first output part and the intermediate flange sufficient for pre-centering between the torsional vibration damper and the clutch clearance is present.
  • the game is preferably provided in the radial direction and / or in the axial direction.
  • the first output part is used in particular for transmitting large torques between the intermediate flange and the coupling.
  • a further preferred embodiment of the clutch unit is characterized in that the second output part has fingers which engage in the axial direction in the intermediate flange.
  • the fingers preferably engage radially inwards and in the circumferential direction outside of the intermediate stops for the energy store in the axial direction in the intermediate flange.
  • a further preferred embodiment of the clutch unit is characterized in that the fingers engage in tooth-like recesses which are formed radially inwardly on the intermediate flange.
  • the fingers and the tooth-like recesses extend in the circumferential direction at the second output part or the intermediate rule and are only in the range of intermediate stops for the energy storage not available or interrupted.
  • Another preferred embodiment of the clutch assembly is characterized in that the fingers are biased against the intermediate flange.
  • the fingers are biased against the intermediate flange.
  • FIG. 1 shows a coupling unit according to the invention with a double clutch and a torsional vibration damper in longitudinal section
  • FIG. 2 shows the torsional vibration damper from FIG. 1 alone
  • FIG. 3 shows an enlarged detail from FIG. 2,
  • FIG. 4 shows the same illustration as in FIG. 3 with a pre-stressed finger
  • FIG. 6 shows the view of a section along the line VI in FIG. 2, FIG.
  • FIG. 7 shows an enlarged section of FIG. 6 when introducing torque pulses
  • FIG. 8 shows a representation similar to FIG. 6 shortly before assembly
  • FIG. 9 shows a representation similar to that in FIG. 3 with an additional input stop element
  • Figure 10 is a similar view as in Figure 9 with an alternative additional
  • FIG. 12 shows a similar energy store as in FIG. 11 with a modified end turn of an outer spring.
  • FIG. 1 shows a part of a drive train 1 of a motor vehicle is shown in longitudinal section.
  • a drive unit 3 in particular an internal combustion engine, from which a crankshaft originates, and a transmission 5
  • a clutch unit 8 with a torsional vibration damper 10 and two friction clutches 11, 12 is arranged.
  • the torsional vibration damper 10 is connected between the drive unit 3 and the double clutch.
  • the two friction clutches 11, 12 each include a clutch disc 13, 14 which is non-rotatably connected to a transmission input shaft.
  • friction linings are mounted in a known manner, which can be clamped between each of a pressure plate 15, 16 and a counter-pressure plate 18 of the double clutch.
  • the counterpressure plate 18 is coupled to the torsional vibration damper 10, which includes a starter ring gear 20.
  • the torsional vibration damper 10 includes an input part 21 to which the starter ring gear 20 is fixed.
  • the input part 21 of the torsional vibration damper 10 is rotatably connected via screw with the crankshaft of the drive unit 3 connectable.
  • an output device 22 of the torsional vibration damper 10 is fixed, which is rotatable relative to the input part 21 of the torsional vibration damper 10 and against the action of an energy storage device 24 limited.
  • the energy storage device 24 comprises an arc outer spring 25 and an arc inner spring 26.
  • a plurality of energy storage devices 24 or spring springs 25, 26 are arranged distributed over the circumference of the torsional vibration damper 10.
  • the torsional vibration damper 10 shown alone in Figure 2 is also referred to as a dual mass flywheel, wherein the input part 21 is also referred to as primary flywheel or primary flywheel.
  • the output device 22 is also referred to as secondary flywheel or secondary flywheel.
  • the output device 22 comprises a first output part 31 and a second output part 32.
  • the two output parts 31 and 32 are fastened by means of rivet connection elements to the counter-pressure plate of the double clutch.
  • the first output part 31 engages radially outside the second output part 32 in the intermediate flange 35 a.
  • the engagement of the two output parts 31, 32 in the intermediate flange 35 takes place in the axial direction, that is parallel to a rotational axis 36 of the torsional vibration damper 10th
  • the intermediate flange 35 comprises, viewed in cross section, a first leg 37 which extends in the radial direction and from which a second leg 38 is angled, which extends in the axial direction. From the free end of the second leg 38, in turn, a collar 39 is bent radially inwardly.
  • the collar 39 of the intermediate flange 35 faces a first axial sealing surface 41, which is provided on the input part 21.
  • a second axial sealing surface 42 is provided on the first leg 37, on the side facing away from the energy storage 24 side.
  • a sealing ring 45 with a substantially rectangular ring cross-section is arranged in the region of a cross-sectional step 46 of the collar 39 of the intermediate flange 35 so that the sealing ring 45 bears sealingly against the first axial sealing surface 41 of the input part 21.
  • the sealing between the first axial sealing surface 41 of the input part 21 and the cross-sectional step 46 of the collar 39 of the intermediate flange 35 arranged sealing ring 45 is a first sealing means 51 of the torsional vibration damper 10.
  • a second sealing device 52 of the torsional vibration damper 10 comprises a circular disk 53, which is fixed radially within a peripheral edge web 54 of the input part 21 by means of a weld 55 on the input part 21.
  • the annular disk 53 extends radially inwardly from the peripheral edge web 54 of the input part 21 of the torsional vibration damper 10 and overlaps or overlaps an annular gap 56 which is formed in the radial direction between the intermediate flange 35 and the input part 21 of the torsional vibration damper 10.
  • the annular gap 56 allows movement of the intermediate flange 35 relative to the input part 21 of the torsional vibration damper 10 in the radial direction.
  • a sealing portion 58 is formed radially inwardly of the annular disk 53 of the second sealing means 52, which sealingly bears against the second axial sealing surface 42 on the intermediate flange 35.
  • a straight line 59 is indicated in Figure 3, that an energy storage receiving space 60, which serves to receive the energy storage device 24 and is limited by the input part 21 and the intermediate flange 35, partially filled with a lubricating and / or damping medium, such as grease , Therefore, the energy storage accommodating space 60 is also referred to as the grease space.
  • the sealing means 51, 52 ensures that the two axial sealing surfaces 41, 42 do not come into contact with grease from the grease chamber 60.
  • a bias of the sealing portion 58 of the annular disk 53 of the second sealing means 52 against the second axial sealing surface 42 a basic hysteresis can be adjusted together with the coefficients of friction on the two sealing surfaces 41, 42.
  • the application or activation of the energy storage device 24 is divided axially.
  • the energy store 24 is driven by input stops 61, of which only one is visible in FIG.
  • the input strikes 61 are formed by bending or deforming portions of the input part 21.
  • the transmission-side control or charging of the energy accumulator 24 takes place by intermediate stops 62, which are formed by deforming or bending individual regions of the intermediate flange 35.
  • Both the input stops 61 and the intermediate stops 62 for the energy storage device 24 extend from the input part 21 or the intermediate flange 35 into the energy storage receiving space 60 in the axial direction.
  • the intermediate stops 62 are preferably formed by deforming a radially inner region of the intermediate flange 35. Radially outwardly, intermediate stop fingers 64 can additionally be bent into the energy storage receiving space 60 in the axial direction at the intermediate flange 35.
  • the intermediate stops 62 and the additional intermediate stop fingers 64 are designed so that the second axial sealing surface 42 is not interrupted at the intermediate flange 35.
  • the intermediate flange 35 is pre-centered radially outside during assembly of the torsional vibration damper 10. In this case, the radial mobility or mobility of the intermediate flange 35 is made possible by the radial annular gap 56.
  • the extent of the second sealing device 52 radially inward is dimensioned so that the output device 22 can be brought with its two output parts 31 and 32 into engagement with the intermediate flange 35 in order to allow a torque transmission between the intermediate flange 35 and the output device 22.
  • Tongues 65 extend from the first output part 31, which tongues extend in the axial direction and engage in a recess 67 which is radially inward at the intermediate stop 62 is formed.
  • the first output part 31 so to speak dips into the intermediate stops 62 of the intermediate flange 35 and serves, on the one hand, to pre-center the double clutch during assembly relative to the torsional vibration damper 10.
  • the first output part 31 with the tongues 65 serves to transmit particularly large torques between the drive unit 3 and the double clutch.
  • the second output part 32 of the output device 22 comprises fingers 68 which engage radially inside the tongues 65 of the first output part 31 in the axial direction in tooth-like recesses 69, which are formed radially inwardly on the second leg 38 of the intermediate flange 35.
  • the depressions 69 form at an inner diameter of the intermediate flange 35 a tooth structure into which the preferably elastically formed fingers 68 of the second output part 32 engage.
  • the fingers 68 take over the transmission of the torque of the drive unit in the usual driving range. In this case, the fingers 68 take over the engine torque, in particular into a torque range, in which a contact between the tongues 65 of the first output part 31 and the intermediate flange 35 no longer causes audible noises.
  • a radial compensation of the design-related play which is to be compensated during installation and / or operation between the dual clutch and the torsional vibration damper 10, takes place between the intermediate flange 35 and the input part 21 of the torsional vibration damper 10.
  • a further energy storage 74 is shown in addition to the energy storage 24, in addition to the energy storage 24, a further energy storage 74 is shown.
  • the fingers 68, 78 are elastically deformable so that they survive deformations that occur during insertion of the fingers 68, 78 in the tooth structure of the intermediate flange 35 without damage. Moreover, it is indicated in FIG. 7 that the fingers 78 can even absorb over torques of the drive train, which are also referred to as impacts, until the more robustly executed tongue 65 comes into contact with the intermediate flange 35 in the recess 67.
  • FIGS. 9 and 10 show similar sections as in FIGS. 3 and 4. To designate the same parts, the same reference numerals are used. To avoid repetition, reference is made to the preceding description of Figures 3 and 4. In the following, the differences between the individual embodiments will be discussed.
  • FIGS. 9 and 10 it can be seen that the input stops 61 on the input part 21 are replaced by additional input stop elements 82; 93 can be supplemented.
  • the additional input stop members 82; 93 may be connected by connection areas 81; 91, 92 may be connected to the input stop 61 of the input part 21.
  • an asymmetric load on the energy storage 24 can be reduced. As a result, the life of the bow springs 25, 26 can be extended.
  • FIG. 11 shows the energy storage device 24 with the bow outer spring 25 and the bow inner spring 26 in plan view.
  • the inner bow spring 26 is disposed radially inside the bow outer spring 25.
  • an energy storage device 124 with an outer bow spring 125 and an inner bow spring 126 shows that an end turn of the bow outer spring 125 can be modified so that a bent end 127 of this end turn is arranged centrally on a diameter line.
  • the end 127 of the end turn of the bow outer spring 125 is arranged so that the introduction of force by a stop which does not strike symmetrically, but the axial center of the energy storage device 124 meets evenly into the energy storage device 124.
  • the inner bow spring 126 is always centrally applied by the center bent end 127 of the bow outer spring 125, in contrast to the arc inner spring 26 shown in Figure 11.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne une unité d'embrayage munie d'au moins un embrayage et d'au moins un amortisseur de vibrations torsionnelles (10) qui comprend un dispositif de sortie (22) qui peut tourner de manière limitée par rapport à une partie d'entrée (21) en s'opposant à l'action d'au moins un accumulateur d'énergie (24) et qui présente des zones de sollicitation pour solliciter le ou les accumulateurs d'énergie. L'invention est caractérisée en ce que les zones de sollicitation s'engagent dans la direction axiale dans un flasque intermédiaire (35) qui peut être mû de manière limitée dans la direction radiale par rapport à la partie d'entrée (21).
PCT/DE2009/001618 2008-12-08 2009-11-12 Unité d'embrayage WO2010066225A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112009003303.2T DE112009003303B4 (de) 2008-12-08 2009-11-12 Kupplungsaggregat

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102008060693 2008-12-08
DE102008060693.6 2008-12-08
DE102009010134.9 2009-02-23
DE102009010134 2009-02-23

Publications (2)

Publication Number Publication Date
WO2010066225A1 true WO2010066225A1 (fr) 2010-06-17
WO2010066225A8 WO2010066225A8 (fr) 2010-12-02

Family

ID=42101703

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2009/001618 WO2010066225A1 (fr) 2008-12-08 2009-11-12 Unité d'embrayage

Country Status (2)

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DE (2) DE102009053033A1 (fr)
WO (1) WO2010066225A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014213331A1 (de) 2014-07-09 2016-01-14 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer
DE102021100644A1 (de) 2020-02-12 2021-08-12 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer für ein Kupplungsaggregat, sowie Kupplungsaggregat zum Ankoppeln einer Brennkraftmaschine
DE102020107935A1 (de) 2020-03-23 2021-09-23 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer für ein Kupplungsaggregat, sowie Kupplungsaggregat zum Ankoppeln einer Brennkraftmaschine

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0270980A2 (fr) * 1986-12-06 1988-06-15 Volkswagen Aktiengesellschaft Disposition de volants d'inertie
GB2231937A (en) * 1989-05-22 1990-11-28 Luk Lamellen & Kupplungsbau Device for clamping vibrations
DE19857110A1 (de) * 1997-12-12 1999-06-24 Exedy Corp Dämpfungsscheibenanordnung

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2640013A2 (fr) * 1988-06-30 1990-06-08 Valeo Dispositif amortisseur de torsion, notamment pour disque de friction d'embrayage de vehicules automobiles
DE102004016760A1 (de) * 2004-04-01 2005-10-20 Zahnradfabrik Friedrichshafen Torsionsschwingungsdämpfer
DE102004024747A1 (de) * 2004-05-19 2005-12-15 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0270980A2 (fr) * 1986-12-06 1988-06-15 Volkswagen Aktiengesellschaft Disposition de volants d'inertie
GB2231937A (en) * 1989-05-22 1990-11-28 Luk Lamellen & Kupplungsbau Device for clamping vibrations
DE19857110A1 (de) * 1997-12-12 1999-06-24 Exedy Corp Dämpfungsscheibenanordnung

Also Published As

Publication number Publication date
DE102009053033A1 (de) 2010-08-19
DE112009003303B4 (de) 2021-02-04
DE112009003303A5 (de) 2012-05-24
WO2010066225A8 (fr) 2010-12-02

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