FR2724995A1 - Rigid friction plate clutch - Google Patents

Rigid friction plate clutch Download PDF

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Publication number
FR2724995A1
FR2724995A1 FR9411500A FR9411500A FR2724995A1 FR 2724995 A1 FR2724995 A1 FR 2724995A1 FR 9411500 A FR9411500 A FR 9411500A FR 9411500 A FR9411500 A FR 9411500A FR 2724995 A1 FR2724995 A1 FR 2724995A1
Authority
FR
France
Prior art keywords
web
clutch
elastic
disc
hub
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.)
Granted
Application number
FR9411500A
Other languages
French (fr)
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FR2724995B1 (en
Inventor
Gilles Lebas
Fabrice Tauvron
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.)
Valeo SA
Original Assignee
Valeo SA
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 Valeo SA filed Critical Valeo SA
Priority to FR9411500A priority Critical patent/FR2724995B1/en
Publication of FR2724995A1 publication Critical patent/FR2724995A1/en
Application granted granted Critical
Publication of FR2724995B1 publication Critical patent/FR2724995B1/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00Friction clutches
    • F16D13/58Details
    • F16D13/60Clutching elements
    • F16D13/64Clutch-plates; Clutch-lamellae
    • F16D13/68Attachments of plates or lamellae to their supports
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00Friction clutches
    • F16D13/58Details
    • F16D13/60Clutching elements
    • F16D13/64Clutch-plates; Clutch-lamellae
    • F16D13/644Hub construction
    • F16D13/646Mounting of the discs on the hub

Abstract

The rigid friction clutch for association with a flywheel damper contains a friction pad disc (13) fixed to a web (15) carried by a hub. It has resilient rings between the disc (13) and the hub (16) for a predetermined play which relates to the misalignment tolerances between the engine/gearbox. This arrangement is inserted in the contact area of the fixing rivets (14) and the web (15) in the form of an elastic ring (21,24) associated with each rivet to take up this play (A,R).

Description

 The present invention relates to clutches of the type known as rigid friction which are usually associated in motor vehicles with a damping flywheel of the type comprising two coaxial masses mounted movable relative to each other against an elastic device depreciation. Since such a flywheel is capable of absorbing the undesirable vibrations of the engine upstream of the friction, that is to say of the lining support disc itself coupled to the clutch hub, it has been possible to dispense with the incorporation of elastic vibration damping means in this coupling, which has led to the adoption of rigid friction.

 However, the fact remains that misalignments or offsets of the gearbox shaft with respect to the engine shaft create noise and wear problems on vehicles. This problem has been able to find solutions in the context of friction fitted with damping means (tapered bearings, elastic bearings, etc.) but does not seem to have been tackled in the case of rigid friction.

 The object of the present invention is to provide a means of solving, in rigid friction, these problems resulting from the inevitable tolerances as regards misalignment between gearbox shaft and motor shaft in motor vehicles.

 To this end, the invention proposes, in a rigid friction clutch of the kind comprising a lining carrier disc secured to a web carried by a hub, the arrangement between disc and hub of a predetermined clearance as a function of the engine misalignment tolerances. box and an elastic system for controlling the take-up of this play by the development of damping forces in the axial direction and in the radial direction with hysteresis effect until the misalignment is eliminated.

The development of the game may take place, for example, in the attachment of the disc to the hub web or in the coupling of the web to the hub, and this elastic system for controlling the conditions for taking up this game may take various forms, provided that they are insured.
- radial damping;
- axial damping
- hysteresis; and
- torque transmission.

The characteristics and advantages of the invention will become apparent from the following description of various embodiments with reference to the accompanying drawings in which
- Figure 1 is a partial schematic view in axial section of a clutch according to the invention associated with a damping flywheel
- Figures 2 to 4 are sectional views of disc-sail riveting according to three exemplary embodiments;
- Figures 5A and 5B are similar views of alternating riveting of a fourth embodiment;
- Figures 6A, 6B, 6C illustrate a fifth embodiment, respectively showing a partial front view in 6A and sections along lines BB and
CC of Figure 6A
- Figures 7A and 7B show, in partial front views and in section respectively, a sixth embodiment
- Figures 8A and 8B are views respectively from the front and in axial section of a seventh embodiment;
- Figures 9A and 9B are partial views, respectively from the front and in section along a plane IX-IX, of an eighth embodiment.

 According to the embodiment chosen and shown in Figure 1, the invention is applied to a clutch associated with a damping flywheel comprising two coaxial parts 1, 2 mounted movable relative to each other against means elastic 3 belonging to an elastic damping device.

 Part 1 is a plate fixed by means of screws 4 at the end of a crankshaft (not detailed). The annular part 2 constituting the clutch reaction plate is mounted for rotation on a tubular hub 5 of the first part 1 by means of a bearing 6.

The reaction plate 2 carries the clutch cover 8, which in turn carries, in its usual manner, by means of tabs 9 a pressure plate 10, as well as, by means of columns 11, a diaphragm 12 .

 The diaphragm bears on the bottom of the cover to urge the pressure plate 10 towards the reaction plate 2 by enclosing a friction disc 13 which is fixed by means of rivets 14 to the web 15 carried by a hub 16 fixed in rotation by a spline mounting on the input shaft of axis XX of the vehicle gearbox (not detailed). A series of lights 40 formed in the web 15 around the hub 16 provide access to the steering wheel fixing screws.

 The friction disc 13 is furnished in the usual manner on the two faces of its external peripheral zone with friction linings 18, 19 which are intended to be tightened under the action of the diaphragm 12 by the pressure plate 10 against the reaction plate 2 in the normally engaged position of the clutch. To disengage, the clutch illustrated here being of the pushed type, we will intervene by pushing according to the arrows F, on the fingers 12A of the diaphragm 12 using a clutch release bearing (not detailed) which is mounted movably according to the axis XX of the gearbox.

 It is in this context that the present invention comes into play concerning the mounting of the friction disc 13 so as to obtain flawless operation of the clutch despite a misalignment liable to occur between the axis XX of the gearbox and the 'axis of the engine, here the axis of the shaft (crankshaft) carrying the plate 1 of the damping flywheel. The result of such a misalignment will be a lack of centering of the friction disc 13, or more precisely of its friction linings 18, 19 between the facing faces of the reaction 2 and pressure 10 plates.

 In the normally engaged position of the clutch, such off-centering leads to a disturbance generating wear and noise, since in the regular drive movement in rotation of the input shaft of the gearbox via the hub 16 will be superimposed on periodic stresses in a radial orientation determined by the misalignment.

 In the disengaged position, the linings 18, 19 can lick the pressure plates 10 and reaction plates 2 and therefore wear out.

 According to the present invention, therefore, the conditions for automatic correction of such a misalignment will be achieved in the context of rigid friction of the type considered by introducing into the structure thereof, between the hub and friction linings, a elastically deformable connection within limits corresponding to a predetermined clearance, against damping forces and in the axial direction and in the radial direction with a hysteresis effect.

 Various embodiments of such an arrangement will be described below.

 According to the embodiment of FIG. 2, the connection between disc 13 and veil 15 is produced by means of rivets 14 on a diameter as close as possible to the inside diameter of the linings 18, 19.

 Riveting is carried out with a radial clearance R and an axial clearance A, these clearances being controlled by a rod 21 of rubber or other elastically deformable elastomer material housed in a space 22 cleared for this purpose in the thickness of the web in the form d 'a chamfer surrounding the passage of the rivet.

 This housing 22 in the form of a chamfer makes it possible to exert on its elastomeric lining 21 a radial force accompanied by a radial damping with hysteresis effect, as well as an axial force, source of axial damping.

 The transmission of the torque between sail 15 and lining support 13 is ensured when the clearance between rivet and sail is caught.

 In the embodiment illustrated in FIG. 3, there is a connection by rivets 14 similar to those of FIG. 2. But the web 15A has here, opposite the rivet head, a clearance with a flat bottom forming a support shoulder for a pre-stressed corrugated elastic washer 24 exerting an axial force between the rivet head and said shoulder of the web. This axial force on the washer creates a radial braking force due to the friction of the washer on the web.

 The axial force provides axial damping. The radial force ensures the radial damping. The friction ensures the hysteresis effect.

 Figure 4 shows an embodiment resulting from a combination of the principles of the two previous arrangements. There is a corrugated elastic washer 24A prestressed between the rivet head 14A and a bearing face of the web 15B; and there is also an elastomeric rod 21A but housed here in a groove 14B formed for this purpose in the barrel of the rivet.

 The axial play remains controlled by the pre-stressed wavy washers exerting an axial force between the rivet heads and the web. The radial clearance is controlled both by the wavy washers and by the elastomeric rods exerting a radial force between the rivets and the web.

 The axial force due to the washers ensures axial damping. The radial force due to the deformation of the rods, the more the friction of the washers on the web ensures the radial damping. The friction ensures hysteresis.

In the embodiment illustrated by the figures
SA and 5B, for example, alternately uses riveting organized according to these two figures. The riveting according to FIG. 5A includes the arrangement around the barrel of the rivet 14C of a block of elastic material composed of an annular body 25 filling with a slight prestress the associated drilling of the veil 15C and a compressed shoulder zone 26 between the rivet head and the veil. The rivets thus filled alternate on the periphery of the wall with those 14D of the type of FIG. 5B where the radial R and axial clearances A have been provided.

 The game is controlled by slightly pre-stressed blocks. The cylindrical zone 25 provides radial damping; the shoulder 26 provides axial damping.

The hysteresis is ensured by the internal damping of the rubber.

 The transmission of the torque is ensured by the rivets 14B according to FIG. 5B, therefore separately from the elasticity function and this after taking up the clearances at the rivets 14C.

 This arrangement increases the volume of rubber and therefore ensures better resistance over time.

Of course the number of blocks depends on the applications. We can for example mount a block at the rate of two, or even more.

 In the embodiment of FIGS. 6A, 6B, 6C the rivets 14E alternate, for example along the internal peripheral zone of the disc 13 and the external peripheral zone of the web 15 with sections 28 of a rubber band bonded or adhered between disc and veil.

The transmission of the torque takes place, as in the previous case, by the rivets 14E ensuring the limitation of the play and a predetermined preload of the rubber band.

The latter provides radial and axial damping as well as the hysteresis effect. Of course the number of sections 28 depends on the applications. It will be appreciated that the volume of rubber is increased.

 In the variant illustrated in FIGS. 7A and 7B, the radial and axial damping is still ensured by a rubber band 30 but which, instead of being split cons in the previous case, here extends around the entire periphery in a ring continuous bonded or bonded between a peripheral zone provided for this purpose along the radially outer circumference of the web 15C and the radially inner circumference of the disc 13C. In place of the riveting of the preceding arrangements, there are here for the transmission of the torque, the drive fingers 31 formed projecting from the outer circumference of the web and cooperating with lights 32 of corresponding shape formed in the disc with clearances Ri, R2 determined according to the planned operating conditions.

 This arrangement makes it possible to further increase the volume of rubber available. If a prestressing of this volume proves desirable, it can be carried out for example by means of an application washer arranged in contact with the dorsal face of the internal peripheral zone of the disc 13C, as indicated in 33, and secured to this face by means of pins 34 to be provided in the terminal portion projecting from the fingers 31.

 In the embodiments considered hitherto considered the hub cover 15 was secured to the hub 16 of the clutch, by welding for example, as illustrated in FIG. 1.

 In the embodiment shown in Figures 8A and 8B we are dealing with a hub 16D carrying, in itself usual, a peripheral toothing 41 in which a corresponding toothing formed on the radially inner circumference of the web 15D is adapted to mesh. The lining support disc 13D (which is mounted in FIGS. 8A and 9A without the linings 18 - 19) is fixed here by normal riveting 14 to the radially external periphery of the web 15D, but with interposition in contact with the external face (opposite on the steering wheel) of the web 15D of a washer 42 of special shape cut from an appropriate sheet to constitute in this example the elastic damping means according to the invention.

The disc 13D and the washer 42 are therefore mounted on either side of the web 15D while being assembled by the rivets 14.

 This washer 42 comprises, from a peripheral zone 43 reserved for assembly by riveting with the web and the disc, a series of curved spokes 44 bypassing the slots 40 for access to the steering wheel mounting screws. On the radially inner side, these spokes are connected to a central toothing zone 45 adapted to mesh practically without play with the toothing 41 of the hub. The teeth 41 are stepped so that there are interposed shoulders between the web 15D and the washer 42 for axial setting of the web 15D relative to the hub 16D.

 The degree of freedom required by the conditions for setting up the engine and the gearbox is achieved here by fitting a corresponding clearance between the teeth 41 of the hub 16D and the internal teeth of the web 15D, the hub 16D carrying the web 15D.

 The elastic means constituted by the washer 42-45 is adapted to produce the radial and axial forces making it possible to ensure and the radial damping with hysteresis and the axial damping required for the automatic centering of the linings and therefore of the whole of the 'clutch.

 In the eighth embodiment illustrated in FIGS. 9A and 9B, there is a hub cover 15E which comes in one piece with the hub 16E. For its part, there is here a lining support disc 130 come in one piece with a series of tabs 140 obtained by stamping cutting with a profile adapted to that of the web so as to produce elastic supports around the periphery of the hub in extending radially between the ports 40 of access to the steering wheel mounting screws. The riveting 14 is again found at the periphery of the web for the transmission of the torque with the games provided according to the invention under the control of the elastic system formed here by the set of tongues.

 This latter embodiment appears to be advantageous due to the simplicity of the manufacturing and mounting processes.

Claims (11)

 1. Rigid friction clutch for association with a flywheel of the so-called shock absorber type, of the type comprising a lining carrier disc (13) secured to a web (15) carried by a hub (16), characterized by the arrangement between disc ( 13) and hub (16) of a predetermined clearance as a function of the engine-gearbox misalignment tolerances and of an elastic system for controlling the compensation for this clearance by the development of damping forces in the axial direction and in the radial direction with hysteresis effect until the misalignment is removed.
 2. Clutch according to claim 1, with fixing by riveting of the lining carrier disc (13) on the web (15), characterized in that the predetermined clearance being provided in the rivet-web connection, the elastic system comprises an elastic means (21, 24) associated with each rivet (14).
 3. Clutch according to claim 2, characterized in that the elastic means is an elastomeric rod (21) disposed in a housing (22) in the form of a chamfer of the web (15).
 4. Clutch according to claim 2, characterized in that the elastic means is a wavy washer (24) inserted with prestress under the rivet head (14, 14A).
 5. Clutch according to claim 2, characterized in that the elastic means comprises a corrugated washer (24A) inserted with prestress under the rivet head (14A) and an elastomeric rod (24A) in a groove (14B) formed in the barrel of the rivet.
 6. Clutch according to claim 1, with fixing by riveting of the lining carrier disc (13) on the hub web (15), characterized in that the riveting comprises rivets (14C) furnished with blocks of elastic material alternating with rivets (14D) performing the predetermined play.
 7. Clutch according to claim 6, characterized in that the blocks comprise a cylindrical zone (25) of radial damping and a shoulder (26) of axial damping.
 8. Clutch according to claim 1, with fixing by riveting of the lining carrier disc (13) on the web (15), characterized in that rivets (14E) alternate with sections of elastomer strip (28) glued or bonded between disc and veil, said rivets ensuring the limitation of the play and a prestressing of said strip sections.
 9. Clutch according to claim 1 with coupling disc-disc by drive fingers 31 formed projecting from the outer periphery of the disc (15C), characterized in that the elastic system comprises a continuous annular strip of elastomeric material (30) interposed between the radially internal peripheral zones of the discs (13C) and external of the web (15C).
 10. Clutch according to claim 1, characterized in that the predetermined clearance being formed between web and hub, the elastic system comprises a sheet metal washer (42) having between an external peripheral zone (43) for securing with disc and web and a inner peripheral zone (45) for securing with the hub, spokes (44) for bypassing lights (40) formed in the web for access to the steering wheel mounting screws (4) (1).
 11. Clutch according to claim 1 with fixing by riveting of the lining carrier disc on the web, characterized in that the predetermined clearance being provided in the rivet-web connection, the elastic system comprises tongues (140) coming from a single part with the lining-carrying disc and adapted to take elastic rest on the web (15E) and the hub (16E).
FR9411500A 1994-09-27 1994-09-27 Rigid friction clutch having the packing disk provided with an elastic system for catching the predetermined game between the disc and the hub Expired - Fee Related FR2724995B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
FR9411500A FR2724995B1 (en) 1994-09-27 1994-09-27 Rigid friction clutch having the packing disk provided with an elastic system for catching the predetermined game between the disc and the hub

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR9411500A FR2724995B1 (en) 1994-09-27 1994-09-27 Rigid friction clutch having the packing disk provided with an elastic system for catching the predetermined game between the disc and the hub

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FR2724995A1 true FR2724995A1 (en) 1996-03-29
FR2724995B1 FR2724995B1 (en) 1997-01-10

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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19716397A1 (en) * 1997-04-18 1998-10-22 Bayerische Motoren Werke Ag Outer rim of vehicle clutch
EP0936057A2 (en) * 1998-02-17 1999-08-18 Yamada Dobby Co., Ltd. Press
FR2781266A1 (en) 1998-07-17 2000-01-21 Mannesmann Sachs Ag Clutch friction disc for friction clutches in vehicles, with zone between hub and friction disc to allow axial movement and bending
WO2001086162A1 (en) * 2000-05-10 2001-11-15 Valeo Disc for rigid friction clutch
FR2821398A1 (en) * 2001-02-23 2002-08-30 Luk Lamellen & Kupplungsbau Clutch disc
WO2003019023A1 (en) * 2001-08-24 2003-03-06 Automotive Products Group Limited Clutch driven plate
US6536575B1 (en) 1998-07-17 2003-03-25 Mannesmann Sachs Ag Clutch disk for a motor vehicle friction clutch
FR2922282A1 (en) 2007-10-10 2009-04-17 Valeo Embrayages Friction disk for motor vehicle's clutch, has web's internal teeth presenting radial and angular clearances with hub's external teeth, and transmission disk including middle part with axial and radial flexibility connecting peripheral parts
CN105202049A (en) * 2014-06-26 2015-12-30 Valeo离合器公司 Clutch disc
WO2018150133A1 (en) * 2017-02-14 2018-08-23 Valeo Embrayages Clutch disc provided with a torsionally flexible flange intended for damping vibration

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2104106A (en) * 1936-09-12 1938-01-04 Borg Warner Friction clutch plate
FR1040461A (en) * 1951-08-10 1953-10-15 Consortium Des Pieces Standard Improvements to flexible couplings
DE919335C (en) * 1951-10-25 1954-10-18 Pius Buchegger Friction disc clutch for motor vehicles
US2775105A (en) * 1954-02-10 1956-12-25 New Prod Corp Torsional vibration absorber
FR1419293A (en) * 1964-02-17 1965-11-26 friction clutch driven plate
US3897859A (en) * 1973-09-28 1975-08-05 John A Norcia Clutch friction plate construction
US4068749A (en) * 1976-06-09 1978-01-17 General Motors Corporation Clutch plate and damper assembly
EP0372118A1 (en) * 1988-12-09 1990-06-13 Borg-Warner Automotive GmbH Friction element with a clamping sleeve connection between friction hub and hub
DE4322578A1 (en) * 1992-07-09 1994-01-13 Luk Lamellen & Kupplungsbau Coupling disc esp. for vehicles - has hub inner profile engaging with the gear's prim. shaft, and outer profile engaging with disc's inner profile

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2104106A (en) * 1936-09-12 1938-01-04 Borg Warner Friction clutch plate
FR1040461A (en) * 1951-08-10 1953-10-15 Consortium Des Pieces Standard Improvements to flexible couplings
DE919335C (en) * 1951-10-25 1954-10-18 Pius Buchegger Friction disc clutch for motor vehicles
US2775105A (en) * 1954-02-10 1956-12-25 New Prod Corp Torsional vibration absorber
FR1419293A (en) * 1964-02-17 1965-11-26 friction clutch driven plate
US3897859A (en) * 1973-09-28 1975-08-05 John A Norcia Clutch friction plate construction
US4068749A (en) * 1976-06-09 1978-01-17 General Motors Corporation Clutch plate and damper assembly
EP0372118A1 (en) * 1988-12-09 1990-06-13 Borg-Warner Automotive GmbH Friction element with a clamping sleeve connection between friction hub and hub
DE4322578A1 (en) * 1992-07-09 1994-01-13 Luk Lamellen & Kupplungsbau Coupling disc esp. for vehicles - has hub inner profile engaging with the gear's prim. shaft, and outer profile engaging with disc's inner profile

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19716397A1 (en) * 1997-04-18 1998-10-22 Bayerische Motoren Werke Ag Outer rim of vehicle clutch
DE19716397B4 (en) * 1997-04-18 2006-01-05 Bayerische Motoren Werke Ag Single disc clutch for manual transmission
EP0936057A2 (en) * 1998-02-17 1999-08-18 Yamada Dobby Co., Ltd. Press
US6112871A (en) * 1998-02-17 2000-09-05 Yamada Dobby Co., Ltd. Clutch/brake device in press for little noise
EP0936057A3 (en) * 1998-02-17 1999-10-20 Yamada Dobby Co., Ltd. Press
DE19901043B4 (en) * 1998-07-17 2013-01-17 Zf Friedrichshafen Ag Clutch disc for a motor vehicle friction clutch
FR2781266A1 (en) 1998-07-17 2000-01-21 Mannesmann Sachs Ag Clutch friction disc for friction clutches in vehicles, with zone between hub and friction disc to allow axial movement and bending
US6536575B1 (en) 1998-07-17 2003-03-25 Mannesmann Sachs Ag Clutch disk for a motor vehicle friction clutch
DE19926382B4 (en) * 1998-07-17 2013-01-17 Zf Friedrichshafen Ag Clutch disc for a motor vehicle friction clutch
FR2808850A1 (en) * 2000-05-10 2001-11-16 Valeo Rigid friction clutch, for automobile, comprises friction disc fixed on annular web engaged on hub outer rim
WO2001086162A1 (en) * 2000-05-10 2001-11-15 Valeo Disc for rigid friction clutch
FR2821398A1 (en) * 2001-02-23 2002-08-30 Luk Lamellen & Kupplungsbau Clutch disc
WO2003019023A1 (en) * 2001-08-24 2003-03-06 Automotive Products Group Limited Clutch driven plate
GB2384035A (en) * 2001-08-24 2003-07-16 Automotive Products Group Ltd Clutch driven plate
FR2922282A1 (en) 2007-10-10 2009-04-17 Valeo Embrayages Friction disk for motor vehicle's clutch, has web's internal teeth presenting radial and angular clearances with hub's external teeth, and transmission disk including middle part with axial and radial flexibility connecting peripheral parts
CN105202049A (en) * 2014-06-26 2015-12-30 Valeo离合器公司 Clutch disc
WO2018150133A1 (en) * 2017-02-14 2018-08-23 Valeo Embrayages Clutch disc provided with a torsionally flexible flange intended for damping vibration

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