WO2002021021A1 - Appareil d'accouplement hydrocinetique, notamment pour vehicule automobile - Google Patents
Appareil d'accouplement hydrocinetique, notamment pour vehicule automobile Download PDFInfo
- Publication number
- WO2002021021A1 WO2002021021A1 PCT/FR2001/002745 FR0102745W WO0221021A1 WO 2002021021 A1 WO2002021021 A1 WO 2002021021A1 FR 0102745 W FR0102745 W FR 0102745W WO 0221021 A1 WO0221021 A1 WO 0221021A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- friction
- stop
- hydrokinetic coupling
- friction stop
- 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
- 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
- Hydrokinetic coupling device in particular for a motor vehicle
- the present invention relates to a hydrokinetic coupling device for a motor vehicle.
- a hydrokinetic coupling device in particular for a motor vehicle, of the type comprising: - a casing, intended to link in rotation, around of an X axis, a driving shaft and an impeller, a turbine wheel intended to be linked in rotation to a driven shaft, a clutch for locking the coupling of the driving and driven shafts comprising a piston for releasably connecting the turbine wheel to a substantially radial wall of the casing against which the piston is biased for locking the coupling, and a friction stop interposed axially between the turbine wheel and the piston.
- the casing provided with a substantially radial wall constitutes the input element and the output element is itself constituted by a turbine wheel - hub assembly. housed inside the housing.
- the piston is located between the assembly and the wall and it is mounted to move axially relative to the wall, while being linked in rotation to the latter.
- the turbine wheel is driven by the impeller wheel through the circulation of a fluid, such as oil, contained in the casing.
- the driving shaft is the output shaft of the vehicle engine and the driven shaft is connected to gear change means.
- the locking clutch also called “lock-up”
- This drive control of the shafts is carried out by tightening an annular friction disc arranged between the piston and the locking wall of the casing.
- the hub connecting wall illustrated in this document comprises a substantially radial flange, integrally formed with the hub, and a web connecting this hub to coupling means, with circumferential damping, of the hub and the friction disc.
- the turbine is also connected to the hub flange.
- a spacer member, in the form of a flat ring, is interposed axially between the flange of the hub and the piston and forms a friction stop in order to avoid direct contact between this flange and this piston.
- the object of the invention is in particular to simplify the manufacture of a locking clutch and to minimize the cost thereof, in particular by reducing the number of elements constituting this clutch.
- the invention relates to a hydrokinetic coupling device, of the type mentioned above, characterized in that the friction stop is arranged radially beyond the outer periphery of the flange.
- the realization of the friction stop function of the piston is simplified and makes it possible to avoid any direct contact between the piston, and according to the embodiments, any of the elements of the turbine wheel - hub assembly or an element such as the web of a damping device.
- the friction stop being disposed radially beyond the outer periphery of the flange, the force transmission zone of the turbine on the piston is thus brought closer to the piston support zone. In this way, the deformation of the piston and the relative displacement between the turbine and the casing are reduced so that the piston undergoes less stress.
- the friction stop is carried by one of the elements of the turbine wheel-hub assembly; - the friction stop is carried by the piston;
- the friction stop comprises an active friction part and a passive part comprising assembly means with the element which carries the stop by cooperation of complementary shapes; - the friction stop is in one piece;
- the friction stop is in at least two parts respectively comprising the active part and the passive part;
- the piston includes at least one projecting element which cooperates with complementary assembly means of the friction stop;
- the piston has at least one hole which receives complementary assembly means of the friction stop; - the hole is blind;
- the hole opens out and forms a passage orifice for a tool for fixing the means for rotationally connecting the piston and the casing; sealing means intervene between the piston hole and the passive part of the friction stop, and at least one lubrication groove (R) is formed in the active friction part and / or in the part against which said stop takes support.
- the lessons of the present invention can be implemented in any type of hydrokinetic coupling device, in particular in devices equipped with a clutch of the two-sided type, that is to say comprising two friction surfaces, or even in multi-disc clutches.
- FIG. 1 is a half-view in axial section of an apparatus for hydrokinetic coupling according to a first embodiment of the invention
- Figure 2 is a partial view of an axial section similar to that of Figure 1, along a section plane angularly offset from that of Figure 1
- Figure 3 is a partial view of a section similar to Figure 1 showing a hydrokinetic coupling apparatus according to a second embodiment of the invention
- Figure 4 is a partial sectional view of a detail of the third embodiment
- Figure 5 is a partial sectional view of a detail of the fourth embodiment
- Figure 6 is a partial sectional view of a detail of the fifth embodiment.
- FIG. 1 shows a hydrokinetic coupling device according to a first embodiment of the invention, designated by the general reference 10.
- This device 10 is intended to couple two driving and driven shafts, for example in an automatic transmission of a motor vehicle.
- the driving shaft is the output shaft of the vehicle engine and the driven shaft is connected to gear change means.
- the hydrokinetic coupling apparatus 10 comprises a casing 12, intended to link in rotation the driving shaft and an impeller.
- the drive shaft and the impeller known per se, are not shown in the figures.
- the apparatus 10 further comprises a hub 14 intended to link in rotation the driven shaft 16 and a turbine wheel 18 of which only a part of the profile is shown in dashed lines in FIG. 1.
- a hub 14 intended to link in rotation the driven shaft 16 and a turbine wheel 18 of which only a part of the profile is shown in dashed lines in FIG. 1.
- the axial orientations and radial are considered in relation to the X axis of the device.
- the casing 12 comprises a substantially radial wall 20 provided with a surface 20E, external to the casing, carrying conventional means of coupling with the driving shaft.
- These coupling means notably comprise a centering member 22 and screwing means 23.
- the hub 14 here comprises a substantially radial flange 24 provided with conventional means 26 for securing with the turbine wheel 18.
- the hub 14 is coupled to the driven shaft 16 by cooperation of grooves and axial grooves formed on the latter.
- the hydrokinetic coupling apparatus 10 further comprises a clutch 28 for locking the coupling of the driving and driven shafts.
- This clutch 28 is activated after starting the vehicle and hydraulic coupling of the driving and driven shafts.
- the clutch 28 comprises a movable locking piston 30 intended to be pressed against the casing 12 to lock the coupling of the shafts or check the slip between the impeller and impeller.
- the clutch is here of the two-sided type in which a friction disc 32 is intended to be clamped between the piston 30 and a surface 201 of the wall 20, internal to the casing 12.
- the friction disc 32 inserted axially between the piston 30 and the wall 20, called the locking wall, has friction linings G arranged here and in a manner known per se on its two opposite faces.
- the friction could be carried out directly between the parts 30, 32, 20 having preferably been treated with a view to such an application.
- the friction linings G can be arranged directly or indirectly on the friction disc 32 or on the piston 30 and / or the surface 201.
- at least one of the linings can belong to an additional part added by any means , for example by welding.
- the different embodiments above can of course be combined.
- the outer periphery of the disc 32 is embedded in a friction lining.
- the linings G are provided with grooves which allow, in addition to better cooling, to work in controlled sliding.
- the friction disc 32 is here connected to the hub 14 by means of a damping device further comprising means 34, 38.
- the means 34 comprise a web 36 connected to the flange 24 of the hub using for example securing means 26, such as rivets or a weld, common to the turbine wheel 18 and to the web 36.
- Elastic members 38 with circumferential action are inserted, in a manner known per se, between the friction disc 32 and the web 36, in order to ensure the desired depreciation effect.
- flange 24 and the web 36 form a substantially radial connecting wall and integral with the hub 14.
- the hydrokinetic coupling apparatus 10 further comprises at least one sealing means 41, such as a segment or a seal, acting between one end of the shaft 16 and the piston 30 and intended to separate two chambers 58, 59 which will be described later.
- sealing means 41 can be carried by the shaft 16 or by the piston 30.
- end of the driven shaft 16 is provided with a terminal chamfer to facilitate here the fitting by fitting of the sealing segment 41.
- the piston 30 comprises a radially inner substantially axial annular part which internally delimits a cylindrical bearing surface 30P cooperating by sliding with the sealing segment 41 of the driven shaft 16.
- the sealing segment 41 interposed between the end of the driven shaft 16 and the bearing surface 30P of the piston, is housed for example in an annular groove 54 produced in the driven shaft 16.
- the driven shaft 16 is provided with an axial bore 56 opening at the free end of this shaft 16.
- the bore 56 communicates with a chamber 58, called the control of the locking clutch 28, which is delimited in particular by the radial wall 20 of the casing, the piston 30 and the friction disc 32.
- the chamber 58 is supplied with oil under pressure by a hydraulic circuit conventional to which the bore 56 of the driven shaft 16 is connected.
- the control chamber 58 is isolated from a chamber 59 in which the turbine wheel 18 extends, called the turbine chamber, in particular by the piston 30 and the sealing means 41.
- the piston 30 is linked in rotation to the locking wall 20 of the casing by conventional means described for example in document WO 99/45294.
- These connecting means here comprise flexible tongues 60 of tangential orientation distributed circumferentially. These tongues 60, interposed between the piston 30 and the locking wall 20 of the casing, allow - by elastic deformation - an axial displacement, that is to say the guiding in translation of the piston 30.
- the number of tabs 60 depends on the applications, these preferably being distributed regularly circumferentially according to several sets of tabs, each set comprising at least one tab.
- the tongues 60 may be of transverse orientation, being for example of triangular or rectangular shape or else of tangential orientation.
- a first end of the tongues 60 is connected to the locking wall 20 here by means of a crown 62 fixed to this wall 20 by rivets 64 made integrally with the casing 12 (see FIGS. 1 and 2).
- the second end of the tongues 60 is connected to the piston 30 by rivets 66 (see FIG. 2).
- the tongues 60 guide the piston 30 axially between the flange 24 and the locking wall 20.
- the mounting of the piston 30 in the housing 12 is known per se. First of all, the tongues 60 are hooked to the crown 62 and to the piston 30, then, this crown 62 is fixed on the locking wall 20. To achieve this last fixing operation, through holes 30T formed in the piston 30 substantially in line with the rivets 64 and form passage orifices for access to the rivets 64 of a fixing or mounting tool and. In order to ensure the tightness of the control chamber 58, the orifices 30T, distributed circumferentially on the piston 30, are each closed by means such as plugs 68 after the piston 30 has been mounted in the casing 12.
- the locking (also called bridging) of the clutch 28 and the unlocking (also called removal) of this clutch 28 are carried out in a manner known per se by varying the pressure between the control chamber 58 and the turbine chamber 59.
- a friction stop 68 is interposed axially between the turbine wheel 18 and the piston 30, so that any direct contact between the piston 30 and an element opposite, here the veil 36 is avoided.
- the friction stop 68 is arranged radially beyond the outer periphery 100 of the flange 24.
- the flange can not be interpreted restrictively to the embodiments shown in which said flange 24 came integrally with the hub 14 thus alternatively the flange 24, which here designates a substantially radial wall, is constituted by the turbine wheel or by a element linked in rotation to it or to the hub, the veil of the shock absorber could for example constitute this element.
- the force transmission zone of the turbine on the piston is brought closer to the support zone of the piston, that is to say the zone in which the friction linings G are arranged and, in this way, the deformation of the piston 30 and the relative displacement between the turbine 18 and the casing 12, so that the piston is subjected to less significant stresses than in the case where the friction stop is arranged for example radially at the internal periphery of the flange 24 .
- the friction stop 68 comprises an active friction part 68A and a passive part 68P comprising assembly means 68J with the element which carries the stop, here the piston 30.
- the stop is here in one piece.
- the assembly of the stop 68 and the piston 30 is here achieved by cooperation of complementary shapes, but it could of course be achieved by any other means, for example by welding or gluing.
- at least a portion of the plugs forming means for closing the orifices 30T also advantageously constitutes friction stops 68 interposed between the turbine wheel - hub and piston 30 assembly. understand by crew within the meaning of the present invention one of the turbine wheel-hub elements or any element linked in rotation to the latter.
- the friction stop 68 that is to say here one of the plugs, is preferably made of a material chosen from thermoplastic or thermosetting synthetic materials, mixtures of materials synthetic, these materials being reinforced or not by fibers such as glass fibers, aramids (especially sold under the name KEVLAR) or carbon or glass beads.
- the plugs 68 forming stops preferably each comprise a support head 68T constituting the active part 68A of the friction stop, here against the web 36.
- the head 68T is extended by a skirt 68J which is, fitted into the orifice of passage 30T and which constitutes the passive part 68P of the stop.
- the skirt 68J constitutes the assembly means by cooperation of shapes of the stop 68 on the piston 30.
- skirt 68J can be discontinuous, the assembly means can then be produced in the form of axial lugs, preferably at least two diametrically opposite with respect to the through hole 30T.
- the assembly by cooperation of shapes of the skirt 68J, or of the legs, can for example consist of a snap-fastening or an elastic interlocking.
- at least one lubrication groove R is formed in the active part 68A of the friction stop 68, here in its support head 68T in contact with the web 36, in order to facilitate sliding between the parts by establishing a passage of the fluid or at least the formation of a film.
- the groove or grooves could be inversely made on the part against which the friction stop 68 comes to bear, that is to say here the web 36, but also in other possible embodiments one of the elements of the turbine wheel - hub 18, 36, 24.
- the grooves R are produced on the two parts, that is to say on the plug 68 and on the part against which it bears 18, 36, 24.
- Such grooves make it possible to renew the film of oil (of fluid) between the support head 68T of the plug 68 and the web 36 so that the wear resulting from friction is reduced and the risks of sticking between the parts avoided.
- sealing means 70 such as a seal, intervene between the passive part 68P comprising the means for assembling the plug forming a stop and the contour of the passage orifice 30T.
- the production of grooves is favorable to the increase in the life of the friction stop 68, as well as to the reliability of the assembly.
- 68 is carried by the piston 30, it is arranged radially beyond the outer periphery 100 of the flange 24, and is made in one piece.
- the friction stop 68 is also constituted by the sealing means, here metal plugs preferably made of stamped sheet metal, and which are for example fitted by force into the corresponding passage openings 30T.
- Each stopper 68 has a general shape of a bowl and includes a rolled in edge 68R here constituting the active part 68A of the friction stop 68, the edge 68R being in abutment against the web 36.
- the metal plugs in particular the active part 68A, can be subjected to treatment in order to improve the properties thereof, for example their coefficients of friction.
- the passive part 68P comprising the assembly means by cooperation of complementary shapes with the piston 30, is here constituted by the edges of the plug 68 which cooperate with those of the orifice 30T.
- the friction stop 68 is carried by the piston 30, radially beyond the outer periphery 100 of the flange 24, and it is produced in two pieces comprising respectively an active part 68A and a passive part 68P.
- the friction stops 68 also constitute sealing means or plugs for the passage orifices 30T produced in the piston 30, the passive part 68P of which comprises assembly means with the said piston by cooperation of complementary shapes.
- the passive part 68P consists of a first metal part 168, for example of sheet metal, having substantially the shape of a bowl, this part being force fitted into the holes or orifices 30T. No sealing means is then necessary between the hole 30T of the piston and the passive part 68P.
- the active part 68A of the friction stop is constituted by a second part 268, preferably made of synthetic material, which is attached to the first part 168.
- the part 268 forming the active part 68A has a head d 68T support.
- At least one lubrication groove (R) can be made in the active part 68A of the stop 68, here more particularly in the head 68T, and / or in the part against which said stop bears.
- the second part 268 forming the active part 68A of the stop consists of a plug force-fitted into the first part 168.
- the second part 268 has an axial clearance relative to the first part 168 without, however, being able to come completely out of the bowl 168.
- the first part 168 in the form of a bowl comprises, on the side where it is open, at least two legs 168P while the second part 268 consists of a plug fitted in said opening and which has a head 68T in which a groove 110 is formed.
- the connection between the first and second parts forming the friction stop 68 is produced by crimping, the tabs 100 being folded down in the groove 110.
- the second part 268 forming the active part 68A comprises at its external periphery a skirt or legs 268P for its clipping or elastic interlocking on the first part 168.
- the plug 68 forming a friction stop can cooperate with any wall integral with the turbine wheel 18, namely in particular a connecting wall integral with the hub 14, as described above or a wall delimiting the turbine wheel 18 itself. - even .
- many variants are possible.
- only part of the plugs forming the closure means 68 also constitute friction stop means 68 for the piston 30.
- only one in two plugs combine, for example, the two shutter and friction stop functions.
- closure means 68 and friction stop may be constituted by a single piece such as a plug, according to the embodiments detailed above, but they can also without departing from the scope of the present invention, be distinct.
- a part forming the friction stop is attached to one or more of the closure means 68.
- a plug preferably metallic, carries a part ensuring the function of friction stop, which is by example made of synthetic material or any other material.
- the stopper then has a part such as a head on which the friction stop would be attached.
- clipping may be made, without limitation, of clipping, overmolding, snap-fastening, interlocking, buttoning, screwing, riveting or even bayonet mounting.
- a flat head may be provided thereon extended by a flange for better mechanical strength, that is to say substantially the shape of a rivet head.
- stops comprising lugs to attach them to the closure means by clipping or snap-fastening, and thus form a friction stop assembly - closure plug 68.
- the maintains can also be ensured by an additional part such as clips.
- the friction stop is of the synthetic material type, it is possible to make as many stops as there are plugs which form pads, these pads having different geometries according to the desired application for example circular, rectangular or oblong.
- the friction stop 68 consists of a single piece having substantially the shape of a crown or of a ring. It will be noted that in some of the embodiments, several functions are advantageously cumulated by the same member, in particular here the cumulation of the sealing and friction stop functions by at least one plug 68. This thus succeeds in reducing the number of elements constituting the locking clutch and reducing the manufacturing cost of the hydrokinetic coupling device.
- the hole receiving the complementary assembly means of the friction stop 68 is a blind hole.
- the invention is in no way limited to the embodiments described above in which the friction stop 68 is carried by the piston. In fact, as a variant, the friction stop is carried by the turbine wheel or a veil such as the veil of the damping device.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10196585.0T DE10196585B3 (de) | 2000-09-05 | 2001-09-05 | Hydrodynamische Kupplungsvorrichtung, insbesondere für ein Kraftfahrzeug |
US10/344,679 US6948602B2 (en) | 2000-09-05 | 2001-09-05 | Hydrokinetic coupling apparatus, in particular for motor vehicle |
KR1020037003204A KR100818646B1 (ko) | 2000-09-05 | 2001-09-05 | 차량용 유체 동역학적 연결 장치 |
JP2002525399A JP4888874B2 (ja) | 2000-09-05 | 2001-09-05 | 自動車用の流体結合装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR00/11318 | 2000-09-05 | ||
FR0011318A FR2813651B1 (fr) | 2000-09-05 | 2000-09-05 | Appareil d'accouplement hydrocinetique, notamment pour vehicule automobile |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2002021021A1 true WO2002021021A1 (fr) | 2002-03-14 |
Family
ID=8853996
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2001/002745 WO2002021021A1 (fr) | 2000-09-05 | 2001-09-05 | Appareil d'accouplement hydrocinetique, notamment pour vehicule automobile |
Country Status (6)
Country | Link |
---|---|
US (1) | US6948602B2 (fr) |
JP (1) | JP4888874B2 (fr) |
KR (1) | KR100818646B1 (fr) |
DE (1) | DE10196585B3 (fr) |
FR (1) | FR2813651B1 (fr) |
WO (1) | WO2002021021A1 (fr) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE112005003047A5 (de) * | 2004-12-24 | 2007-09-13 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Dichtung für Wandlerüberbrückungskupplung |
US8328647B2 (en) * | 2009-01-30 | 2012-12-11 | Schaeffler Technologies AG & Co. KG | Torque converter leaf spring connections |
DE102010024926A1 (de) * | 2009-07-09 | 2011-01-13 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Verschlussstopfen für Drehmomentwandler |
DE102011111965B4 (de) * | 2010-09-23 | 2023-12-21 | Schaeffler Technologies AG & Co. KG | Drehmomentwandler mit einer Kolbendichtung mit Zentrierscheibe |
US9010507B2 (en) * | 2012-03-06 | 2015-04-21 | Schaeffler Technologies AG & Co. KG | Torque converter with a clutch centering feature |
US10323698B2 (en) * | 2016-11-01 | 2019-06-18 | GM Global Technology Operations LLC | Torque transferring clutch separation |
US11326678B2 (en) | 2020-06-17 | 2022-05-10 | Valeo Kapec Co., Ltd. | Friction disc apparatus and related torque converter assemblies for use with vehicles |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4437551A (en) * | 1980-08-07 | 1984-03-20 | Fichtel & Sachs Ag | Hydrodynamic torque converter |
US4982821A (en) * | 1987-12-07 | 1991-01-08 | Kabushiki Kaisha Daikin Seisakusho | Friction device of lockup clutch |
US5482151A (en) * | 1993-10-07 | 1996-01-09 | Kabushiki Kaisha Daikin Seisakusho | Lockup unit for torque converter having a friction element |
WO1999045294A1 (fr) | 1998-03-03 | 1999-09-10 | Valeo | Appareil d'accouplement hydrocinetique, notamment pour vehicule automobile |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2943194A1 (de) * | 1979-10-25 | 1981-04-30 | Toyota Jidosha Kogyo K.K., Toyota, Aichi | Hydraulische kupplung mit sperrkupplung |
US4413711A (en) * | 1981-03-30 | 1983-11-08 | Borg-Warner Corporation | Extended travel damper in a lock-up clutch for a torque converter |
JPH0643863B2 (ja) * | 1987-12-07 | 1994-06-08 | 株式会社大金製作所 | ロックアップクラッチの摩擦装置 |
JPH0643864B2 (ja) * | 1987-12-07 | 1994-06-08 | 株式会社大金製作所 | ロックアップクラッチの摩擦装置 |
US5070974A (en) * | 1990-09-19 | 1991-12-10 | Borg-Warner Automotive Transmission & Engine Components Corporation | Hydraulic torsional vibration damper |
JP3219834B2 (ja) * | 1991-05-02 | 2001-10-15 | ルーク ラメレン ウント クツプルングスバウ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | トルク伝達装置 |
US6451343B1 (en) | 1998-03-11 | 2002-09-17 | Smithkline Beecham Corporation | Composition for treating dementia and Alzheimer's disease |
DE19906888B4 (de) * | 1999-02-19 | 2007-11-15 | Zf Sachs Ag | Drehmomentwandler mit einer Reibvorrichtung im Torsionsschwingungsdämpfer |
-
2000
- 2000-09-05 FR FR0011318A patent/FR2813651B1/fr not_active Expired - Fee Related
-
2001
- 2001-09-05 WO PCT/FR2001/002745 patent/WO2002021021A1/fr active Application Filing
- 2001-09-05 DE DE10196585.0T patent/DE10196585B3/de not_active Expired - Fee Related
- 2001-09-05 US US10/344,679 patent/US6948602B2/en not_active Expired - Lifetime
- 2001-09-05 KR KR1020037003204A patent/KR100818646B1/ko not_active IP Right Cessation
- 2001-09-05 JP JP2002525399A patent/JP4888874B2/ja not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4437551A (en) * | 1980-08-07 | 1984-03-20 | Fichtel & Sachs Ag | Hydrodynamic torque converter |
US4982821A (en) * | 1987-12-07 | 1991-01-08 | Kabushiki Kaisha Daikin Seisakusho | Friction device of lockup clutch |
US5482151A (en) * | 1993-10-07 | 1996-01-09 | Kabushiki Kaisha Daikin Seisakusho | Lockup unit for torque converter having a friction element |
WO1999045294A1 (fr) | 1998-03-03 | 1999-09-10 | Valeo | Appareil d'accouplement hydrocinetique, notamment pour vehicule automobile |
Also Published As
Publication number | Publication date |
---|---|
KR20030033046A (ko) | 2003-04-26 |
FR2813651A1 (fr) | 2002-03-08 |
DE10196585T1 (de) | 2003-07-10 |
US20050029067A1 (en) | 2005-02-10 |
JP2004508516A (ja) | 2004-03-18 |
DE10196585B3 (de) | 2016-02-11 |
JP4888874B2 (ja) | 2012-02-29 |
FR2813651B1 (fr) | 2004-06-11 |
KR100818646B1 (ko) | 2008-04-01 |
US6948602B2 (en) | 2005-09-27 |
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