WO1998058191A1 - Amortisseur de torsion pour embrayage de verrouillage appartenant a un appareil d'accouplement hydrocinetique, notamment pour vehicule automobile - Google Patents
Amortisseur de torsion pour embrayage de verrouillage appartenant a un appareil d'accouplement hydrocinetique, notamment pour vehicule automobile Download PDFInfo
- Publication number
- WO1998058191A1 WO1998058191A1 PCT/FR1998/001276 FR9801276W WO9858191A1 WO 1998058191 A1 WO1998058191 A1 WO 1998058191A1 FR 9801276 W FR9801276 W FR 9801276W WO 9858191 A1 WO9858191 A1 WO 9858191A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- torsional damper
- spring
- housings
- damper according
- springs
- Prior art date
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
- F16F15/121—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 using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
- F16F15/12313—Wound springs characterised by the dimension or shape of spring-containing windows
-
- 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
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0278—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch comprising only two co-acting friction surfaces
-
- 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
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
Definitions
- the present invention relates to a torsion damper.
- the invention relates in particular to a torsional damper for a locking clutch capable of intervening between the driving element and the driven element of a hydrokinetic coupling device, in particular for a motor vehicle.
- the torsion damper comprises an input element and a coaxial output element movable in rotation relative to each other against at least one compression spring.
- the spring (s) are generally of the circumferential action type, for example being arranged substantially on the same diameter.
- the shock absorber comprises two transverse parts, of radial orientation, adjacent associated with the two input and output elements respectively, which each comprise a housing which receives the spring, the opposite ends of which are capable of cooperating with the extreme surfaces d 'support which delimit the two housings to act between the two elements.
- one of the two housings generally shaped in the form of windows with a contour substantially complementary to that of the spring which is for example a compression coil spring, has one length substantially equal to that of the spring while the other has a window length LF which is significantly greater than the length LR of the spring so as to have, with respect to a rest position in which the spring is centered in the largest of the windows, a dead travel CM in each of the two directions of rotation which is equal to half the difference in length LF - LR.
- the second slope springs are in certain embodiments arranged radially inwards and the space available for arranging the springs, and more particularly for making the windows forming housings which receive them, is reduced.
- the invention provides a torsion damper of the type mentioned above, characterized in that the length of each of the two associated housings, separating the opposite end surfaces of the housing, is greater than the length of the spring at rest .
- each housing is preferably a window formed in the corresponding flat part of the element and the end bearing surfaces are formed by the opposite lateral end edges of the window.
- Each spring is preferably a coil compression spring.
- the two adjacent parts may belong respectively to the input and output elements, the housings being housings of circumferential orientation which receive a spring with circumferential action.
- the damper comprises a series of circumferential action springs arranged substantially on the same diameter and each of which is received in two associated housings according to the invention.
- the input element comprises at least one guide washer which radially maintains the circumferential action spring which is linked to the driven element of the locking clutch
- the output element comprises a flange or web which is linked in rotation with the driving element of the locking clutch
- the input element may comprise two complementary guide washers which each have a transverse part of radial orientation, these two parts being arranged symmetrically on either side of a transverse part. corresponding radial orientation of the flange, these two parts of guide washer comprising facing windows which, associated in pairs, constitute a housing for the input element which receives a circumferential spring, itself received in a housing the part of the flange which extends between the two washers.
- the two complementary washers comprise means for their mutual connection in rotation and the springs, said to be of second slope, with circumferential action are arranged according to a diameter substantially less than the installation diameter of the means for rotating connection of the two washers.
- - Figure 1 is an exploded perspective view, with partial cutaway, of the main components of a hydrokinetic coupling device comprising a torsional damper according to the teachings of the invention
- - Figure 2 is an axial elevational view, along the arrow F2 of Figure 1, with partial cutaway of one of the guide washers;
- FIG. 3 is a sectional view along line 3-3 of Figure 2;
- - Figure 4 is a detail view on a larger scale which illustrates the outline and the shape of one of the windows for a second slope spring of one or the other of the two associated washers;
- FIG. 6B is a detail view in section along line 5-5 of Figure 4; and FIGS. 6A and 6B are two diagrams making it possible to illustrate, in FIG. 6B, the advantages resulting from the design according to the invention compared with the state of the art which is illustrated in FIG. 6A.
- a hydrokinetic coupling device comprises, arranged in the same sealed housing filled with oil and forming a sump, a torque converter and a locking clutch 1, usually called "lock-up".
- the casing here metallic, constitutes a driving element and it is capable of being linked in rotation to a driving shaft, namely for example a crankshaft of an internal combustion engine (not shown) in the case of an application to a motor vehicle.
- the casing of generally annular shape, consists of two half-shells facing each other and which are tightly fixed at their outer periphery, usually by a welding operation.
- the first shell 2, 3 is capable of being linked in rotation to the driving shaft and it is essentially constituted by an annular wall 2 which is generally of transverse orientation, that is to say which extends in a plane radial perpendicular to the axis XX of the device, and which is extended at its external periphery by an annular cylindrical wall 3 generally of axial orientation.
- the second shell (not shown in the figures for the sake of simplicity, as well as the reaction wheel of the converter) is shaped to define an impeller impeller with blades coming from the internal face of this half-shell. These blades face the blades of a turbine wheel 4 fixed by riveting or welding to a hub web 102 which is linked in rotation with a hub 5 internally grooved for its connection in rotation to a driven shaft (not shown), to know for example the input shaft of the gearbox in the case of an application to a motor vehicle.
- the driven shaft is hollowed out internally to form a channel allowing oil to access a guide ring 6, here massive, which is located axially between the hub 5 and the transverse wall 2.
- the guide ring is constituted by a front section 106 forming a centralizer and by a rear section 108.
- the front section 106 of smaller diameter of the guide ring 6 has the function of ensuring the fixing of the guide ring 6 to the transverse wall 2, here by welding, while the rear section 108 of larger diameter is delimited radially outwards by a machined cylindrical surface 110 for the guide in axial sliding of a piston 9 which has, for this purpose, a ferrule 112 of axial orientation which is here axially turned rearwards, that is to say in the direction of the web 102 of the splined hub 5.
- the bearing surface 110 has a groove which receives an annular sealing gasket (not referenced) for sliding tight mounting of the ferrule 12 along the bearing surface 110.
- the hub 5 has a front section penetrating the interior of the ring 6.
- the piston 9 defines, with the guide ring 6, the transverse wall 2 and an annular disc 10 (bearing fixing, for example by gluing on each of these opposite transverse faces, friction linings 11) a chamber 30 with variable volume supplied through the guide ring 6 provided with holes (not referenced) for this purpose.
- the disc 10 is located at the outer periphery of the piston 9 and it has at its outer periphery, radially beyond the piston 9, lugs with a radial orientation part 200 provided with notches 202 in each of which a lug 14 d 'axial orientation drive which has an outer guide washer 12 at its outer part.
- the disc 10 is carried by the washer 12 and is thus linked in rotation, with the possibility of axial mobility, to the guide washer 12 by a connection 13 of the tenon-mortise type with lugs 14 and notches 202.
- the tabs 14 are of axial orientation being obtained, by cutting and folding, from a portion 206 overall transverse orientation that has the outer guide washer 12 which is here a metal washer.
- the tabs 14 extend axially in the direction of the internal face 124 of the transverse wall 2.
- the transverse portion 206 is extended at its external periphery by an annular portion of axial orientation 15, in the form of an annular cylindrical skirt, serving to maintain , radially externally, coil springs 16 which are also retained, radially internally, by an annular holding portion 17 of an inner guide washer 18.
- the inner guide washer 18 has internally a transverse portion 208, in the form of a flat ring, connecting to the annular portion 17, - generally of frustoconical shape, for holding the springs 16 and which is itself extended externally by a second transverse portion 201 in the form of a flat ring which is parallel to the first transverse portion 208 and which is offset axially relative to the latter, in the direction of the turbine wheel 4.
- the second transverse portion 201 of the washer 18 has, at its outer periphery, notches 212 which, in the embodiment illustrated in detail in FIGS. 2 and 5, are constituted by slots in which penetrated studs 211, of axial orientation, belonging to the free end of the annular portion 15 of the outer guide washer 12 adjacent to the piston 9.
- the pins 211 are formed in favor of the free end edge of the annular portion 15 and extend axially in the opposite direction relative to the offset drive lugs 14 internally inwardly relative to said portion 15 arranged as close as possible to the wall 3 of the half-shell in order to arrange the springs 16 further outward in order to increase performance.
- the pins 211 have a central clearance for, in known manner, to facilitate the creep of the material in contact with the face of the second portion 201 during the crimping operation.
- the inner guide washer 12 is thus robust. It will be noted that the tabs of the disc 10 are offset axially in the direction of the turbine wheel 4 relative to the main part of the disc 10 carrying the friction linings 11 to reduce the length of the tabs 14, reduce the axial size and avoid interference.
- the guide washers 12 and 18 are fixed together at their internal periphery by posts 24.
- the washers 12 and 18 are arranged axially on either side of a flange 19 provided with circumferential openings 25 traversed at circumferential clearance by the balusters 24.
- the outer guide washer 12 comprises an annular portion of transverse orientation 222 which is adjacent to the transverse face opposite 224 of the flange 19, while the first transverse portion 208 of the inner guide washer 18, of radial orientation, is adjacent to the face 226 of the flange 18 , adjacent to the turbine 4.
- the flange 19 has, at its outer periphery, radial lugs 20 forming bearing portions for the circumferential ends of the springs 16 with circumferential action.
- the legs 20 carry circumferential fingers for retaining the springs 16 of the coil type, said fingers penetrating inside the springs 16 extending between two legs 20.
- the inner 12 and outer 18 guide washers are provided facing stampings 230 and 232 respectively for support of the circumferential ends of the springs 16, the lugs 20 being allowed to penetrate between the stampings, which stiffen the washers 12,18.
- the disc 10 is coupled elastically to the flange 19 for good filtration of vibrations.
- the flange 19 is fixed by riveting, alternatively by welding, to the web 102 of the splined hub 5 at the same time as the turbine wheel 4 provided for this purpose with lugs (not shown) at its external periphery.
- the flange 19 is fixed by its internal radial part in the form of a flat ring 80 which extends substantially in the same plane as the lugs 20 and which is offset axially, towards the turbine wheel 4, relative to its external radial part in the form of a flat ring 82 crossed by the balusters 24.
- the parts of the hydrokinetic coupling device are metallic, usually stamped sheet metal except the springs 16.
- the locking clutch 1 comprises a shock absorber of torsion 23 which is located axially for the most part between the turbine wheel 4 and the wall 2 at the outer periphery of the first shell 2,3, with an inlet part constituted by the washer 12 disposed radially above the piston 9 and linings 11 being constituted by the guide washer 12 in the form of a half-shell, the coil springs 16 and an outlet part constituted by the flange 19.
- the outlet part 19 is linked in rotation to the turbine wheel 4, more precisely to the grooved hub 5 of the latter, while the inlet part 12 is linked in rotation to the disc 10 projecting radially with respect to the piston 9.
- the inlet part 12 is therefore disengageably linked, via the disc 10 and the linings 11, to the driving shaft.
- the disc 10 with its friction linings 11 is suitable for being axially tightened so disengageable on the piston 9 and the portion opposite the internal face 124 of the transverse wall 2 forming a counter-piston.
- the disc 10 is therefore coupled elastically to the splined hub 5 and to the turbine wheel 4.
- the piston 9 is linked in rotation to the transverse wall 2 of the first shell by elastic tongues 40 of tangential orientation distributed regularly circumferentially, these tongues 40 allowing an axial movement of the piston 9.
- two-part fixing means are used, requiring only intervention on one side of the piston 9 as described in document FR-A-2 726 620 to which reference may be made.
- the torsion damper 23 comprises a second series of circumferential action springs 300, said second slope springs.
- the springs 300 are coil compression springs which are all arranged circumferentially on the same diameter, this diameter being less than the installation diameter of the balusters 24, that is to say that the springs of second slope 300 are generally installed radially inwards with respect to the first slope springs 16.
- each spring 300 is received in a window-shaped housing 302 which is formed in a central portion 304 in the form of a flat ring of the flange 19 which extends in a plane which is offset axially, in the direction of the internal face 124 of the transverse wall 2, relative to the plane of the tabs 20 and of the internal radial part 80 of the flange 19.
- each window 302 is delimited by these opposite lateral end edges 304 of radial orientation.
- the circumferential length of the window 302 is significantly greater than the circumferential length of the corresponding spring 300.
- the two associated outer 12 and inner 18 guide washers have pairs of associated windows 306 and 308.
- the outer 12 and inner 18 guide washers each have a transverse inner part in the form of a flat ring of radial orientation 310, 312 respectively.
- These flat parts 310 and 312 are parallel and adjacent to the flange and extend opposite the part 303 of the flange 19 comprising the windows.
- the windows 306 are produced by cutting and stamping in the portion 310 and they are shaped with convex longitudinal edges 314 so as to conform to the cylindrical external profile of the coil spring 300 which it receives.
- Windows 306 and 308 thus have a robust contour allowing the springs 300 to be properly retained.
- each window 306, 308 is defined by the opposite end lateral edges 316, 318 respectively of the window.
- the washers 12 and 18 are associated with each other by the balusters 24, each passing through an oblong passage 25 of the flange 19, so that the associated windows 306 and 308 are facing each other, the windows 306 and 308 being of circumferential lengths LF equal to each other and also, in accordance with the embodiment of the invention illustrated in the figures, of length equal to the circumferential length of the corresponding window 302 of the flange 19.
- the advantage provided by the design will now be explained the invention with reference to Figures 6A and 6B.
- the circumferential length of the windows 302 of the flange 19 is substantially equal to the length LR at rest of the spring 300, while the windows 306 and 308 of the washers 12 and 18 have a window length LF significantly greater than the length LR thus providing, in both directions, a dead stroke CM when, from the rest position illustrated in FIG. 6A, the input element constituted by the washers 12 and 18 can move angularly, in one or the other direction relative to the outlet element constituted by the flange 19, of an angular travel corresponding to the circumferential dead travel CM, and this before that the second slope springs do not intervene.
- the lengths of the windows 302 of the flange 19 and of the windows 306 and 308 of the washers 12 and 18 are substantially equal to each other and have a common length LF greater than the length LR of the spring 300. It can be seen that there is obtained, in each direction, a circumferential dead travel CM equal to that according to the solution of the state of the art of FIG. 6A by making windows 306, 308 whose length LF is reduced by a dead stroke CM compared to the state of the art.
- the torsional damper may consist of clutch friction, the flange 19 being integral with an internally grooved hub for its rotational connection with the input shaft of the gearbox in the case of a application for motor vehicle.
- the linings are intended to be clamped between the pressure and reaction plates of the clutch integral in rotation in this case with the crankshaft of the vehicle engine.
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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
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/242,319 US6176362B1 (en) | 1997-06-17 | 1998-06-17 | Torsional damper for locking clutch pertaining to a hydrokinetic coupling apparatus, in particular for motor vehicle |
DE19881099T DE19881099B3 (de) | 1997-06-17 | 1998-06-17 | Drehschwingungsdämpfer für eine verriegelbare Kupplung, die zu einem hydrodynamischen Momentwandler gehört, insbesondere für Kraftfahrzeuge |
JP50388699A JP4380804B2 (ja) | 1997-06-17 | 1998-06-17 | トーションダンパー |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR9707479A FR2764661B1 (fr) | 1997-06-17 | 1997-06-17 | Amortisseur de torsion pour embrayage de verrouillage appartenant a un appareil d'accouplement hydrocinetique, notamment pour vehicule automobile |
FR97/07479 | 1997-06-17 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1998058191A1 true WO1998058191A1 (fr) | 1998-12-23 |
Family
ID=9508050
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR1998/001276 WO1998058191A1 (fr) | 1997-06-17 | 1998-06-17 | Amortisseur de torsion pour embrayage de verrouillage appartenant a un appareil d'accouplement hydrocinetique, notamment pour vehicule automobile |
Country Status (5)
Country | Link |
---|---|
US (1) | US6176362B1 (fr) |
JP (1) | JP4380804B2 (fr) |
DE (1) | DE19881099B3 (fr) |
FR (1) | FR2764661B1 (fr) |
WO (1) | WO1998058191A1 (fr) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2782362B1 (fr) * | 1998-07-08 | 2001-04-27 | Valeo | Appareil d'accouplement hydrocinetique, notamment pour vehicule automobile |
US6663526B2 (en) | 2002-01-08 | 2003-12-16 | Ford Global Technologies, Llc | Transmission isolation assembly |
DE102008032459A1 (de) * | 2007-08-02 | 2009-02-05 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Vorrichtung zur Dämpfung von Schwingungen, insbesondere einen mehrstufigen Drehschwingungsdämpfer |
DE102010004651A1 (de) * | 2009-01-27 | 2010-10-07 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Bogenfederdämpfer mit geringer Reibung |
FR2947025B1 (fr) * | 2009-06-18 | 2011-07-15 | Valeo Embrayages | Amortisseur, notamment pour un dispositif de couplage en rotation de vehicule automobile |
JP2011106555A (ja) * | 2009-11-17 | 2011-06-02 | Aisin Seiki Co Ltd | トルクコンバータ装置 |
US11333217B2 (en) * | 2018-08-12 | 2022-05-17 | Schaeffler Technologies AG & Co. KG | Drive assembly including hub assembly extension |
DE102021130139A1 (de) | 2021-10-05 | 2023-04-06 | Schaeffler Technologies AG & Co. KG | Torsionsschwingungsdämpfer mit einem durch einen Flansch ausgebildeten axialen Federrausfallschutz |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2549180A1 (fr) * | 1983-06-23 | 1985-01-18 | Daikin Mfg Co Ltd | Disque d'amortisseur mince, notamment pour convertisseur de couple |
EP0286213A1 (fr) | 1987-04-09 | 1988-10-12 | Automotive Products Public Limited Company | Dispositif amortisseur de torsion |
US5105680A (en) * | 1990-06-15 | 1992-04-21 | Valeo | Damped double flywheel for a motor vehicle |
FR2695975A1 (fr) * | 1992-09-24 | 1994-03-25 | Valeo | Embrayage de verrouillage pour appareil d'acouplement hydrocinétique. |
WO1994007058A1 (fr) | 1992-09-24 | 1994-03-31 | Valeo | Amortisseur de torsion pour embrayage de verrouillage et embrayage de verrouillage comportant un tel amortisseur de torsion |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3872038T2 (de) * | 1987-04-22 | 1993-01-14 | Yoshida Kogyo Kk | Maschine zum handhaben eines laenglichen artikels mit einer entladevorrichtung. |
GB2240607A (en) * | 1990-01-10 | 1991-08-07 | Automotive Products Plc | Friction clutch driven plates |
US5782694A (en) * | 1995-07-21 | 1998-07-21 | Exedy Corporation | Damper disc assembly having a plate formed with lubricating members for reducing friction caused by engagement with damper springs |
FR2739425B1 (fr) * | 1995-09-29 | 1997-11-28 | Valeo | Amortisseur de torsion a rondelle entretoise, notamment pour vehicule automobile |
-
1997
- 1997-06-17 FR FR9707479A patent/FR2764661B1/fr not_active Expired - Lifetime
-
1998
- 1998-06-17 DE DE19881099T patent/DE19881099B3/de not_active Expired - Fee Related
- 1998-06-17 WO PCT/FR1998/001276 patent/WO1998058191A1/fr active Application Filing
- 1998-06-17 US US09/242,319 patent/US6176362B1/en not_active Expired - Lifetime
- 1998-06-17 JP JP50388699A patent/JP4380804B2/ja not_active Expired - Fee Related
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2549180A1 (fr) * | 1983-06-23 | 1985-01-18 | Daikin Mfg Co Ltd | Disque d'amortisseur mince, notamment pour convertisseur de couple |
EP0286213A1 (fr) | 1987-04-09 | 1988-10-12 | Automotive Products Public Limited Company | Dispositif amortisseur de torsion |
US5004088A (en) | 1987-04-09 | 1991-04-02 | Automotive Products Plc | Torsional vibration damper |
US5105680A (en) * | 1990-06-15 | 1992-04-21 | Valeo | Damped double flywheel for a motor vehicle |
FR2695975A1 (fr) * | 1992-09-24 | 1994-03-25 | Valeo | Embrayage de verrouillage pour appareil d'acouplement hydrocinétique. |
WO1994007058A1 (fr) | 1992-09-24 | 1994-03-31 | Valeo | Amortisseur de torsion pour embrayage de verrouillage et embrayage de verrouillage comportant un tel amortisseur de torsion |
US5590750A (en) | 1992-09-24 | 1997-01-07 | Valeo | Torsion damper for a lock-up clutch, and a lock-up clutch having such a torsion damper |
Also Published As
Publication number | Publication date |
---|---|
DE19881099T1 (de) | 1999-07-15 |
JP4380804B2 (ja) | 2009-12-09 |
US6176362B1 (en) | 2001-01-23 |
FR2764661B1 (fr) | 1999-09-10 |
JP2000517040A (ja) | 2000-12-19 |
DE19881099B3 (de) | 2012-01-19 |
FR2764661A1 (fr) | 1998-12-18 |
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