WO2001007800A1 - Appareil d'accouplement hydrocinetique - Google Patents
Appareil d'accouplement hydrocinetique Download PDFInfo
- Publication number
- WO2001007800A1 WO2001007800A1 PCT/FR2000/002156 FR0002156W WO0107800A1 WO 2001007800 A1 WO2001007800 A1 WO 2001007800A1 FR 0002156 W FR0002156 W FR 0002156W WO 0107800 A1 WO0107800 A1 WO 0107800A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- axial
- transverse plate
- support piece
- transverse
- 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
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- 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
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
- F16H2045/0231—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers arranged in series
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- 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
Definitions
- a hydrokinetic coupling device in particular for a motor vehicle, of the type which comprises a casing provided with an annular axial wall and a front transverse wall, of the type in which the casing is designed to be linked in rotation to a driving shaft, of the type which comprises a turbine wheel housed inside the casing and secured to a hub suitable for being linked in rotation to a driven shaft, of the type in which the rear face of the front transverse wall of the casing has a first bearing surface, of the type in which a locking clutch intervenes between the turbine wheel and the front transverse wall to link them disengageably, and of the type in which the locking clutch comprises a rear piston axially movable relative to at the front transverse wall of the casing and which carries on its front face a second bearing extending opposite the first bearing, is characterized in that the pist one is linked in rotation to the annular axial wall of the casing by an axially elastic
- the outer diameter of the bearing surfaces can be increased since one is no longer limited by the presence, at the outer periphery of the transverse wall of the casing, of a damping device or of a device connecting the piston to the housing.
- the second bearing is located in the vicinity of the outer periphery of the piston;
- the axially elastic device comprises at least one support piece integral in rotation and axially with the annular axial wall of the casing and comprising a transverse plate element, and comprises at least one elastic member which intervenes axially between the piston and the transverse plate of the support piece, and the piston includes means for connecting in rotation with the support piece;
- the mean radius of intervention of the elastic member is less than the outside radius of the second bearing;
- the axially elastic device comprises several support parts distributed circumferentially, in particular regularly;
- the connection in rotation between the piston and the support part or parts has a circumferential clearance;
- the axially elastic device comprises axially elastic tabs, the opposite ends of which are fixed respectively to the piston and to the transverse plate of the support part or parts; - the tongues exert a preload on the piston in the direction of locking the clutch;
- the intensity of the preload is adjusted as a function of the axial positioning of the transverse plate
- the tongues tend to keep the piston in the unlocked position of the clutch; the tabs are distributed circumferentially evenly;
- Each wave type spring sector is fixed by its circumferential ends on the transverse plate or plates, respectively of the support part or parts;
- the annular axial wall of the casing comprises transverse lugs which extend towards the axis and which are each provided with a notch
- the support piece comprises, on its external periphery, transverse lugs which are each provided on their face rear, a lug projecting vis-à-vis a notch, so that the support part is integral in rotation with the axial wall of the housing by interlocking of the bayonet type
- the piston comprises, opposite its rear face, at least one intermediate transverse plate which is fixed by its external periphery to a peripheral axial skirt of the piston, so that the elastic member intervenes between each intermediate transverse plate and each support piece
- the casing comprises a front shell and a rear shell each comprising an axial skirt, the two axial skirts forming the annular axial wall of the casing
- the transverse plate of each support piece is fixed directly to the rear free end of the axial skirt of the front shell, or to the free front end of the axial skirt of the rear shell; each support piece comprises an axial
- each support piece is fixed between the axial skirt of the front shell and the axial skirt of the rear shell;
- FIG. 1 is a half-view in partial axial section which represents a hydrokinetic coupling device produced in accordance with the invention according to a first embodiment in which the axially elastic device comprises axially elastic tongues and in which the support part is fixed by welding to the internal wall of the front axial skirt;
- FIG. 2 is an axial sectional view, on a larger scale, of the axially elastic device of the hydrokinetic coupling device of Figure 1;
- FIG. 3 is a front view, in section along line 3-3 of Figure 2, of the axially elastic device of the hydrokinetic coupling device of Figure 1;
- Figures 14 and 15 are views similar to those of Figures 2 and 3 which illustrate a seventh embodiment of the invention in which the piston has intermediate transverse plates for fixing the elastic tongues;
- Figures 18 and 19 are views similar to those of Figures 2 and 3 which illustrate a ninth embodiment of the invention in which the spring sectors are of the wave type;
- Figure 20 is a partial top view, according to arrow F20 of Figure 19 and with partial cutaway, which illustrates the ninth embodiment of one invention;
- FIG. 21 and 22 are views similar to those of Figures 2 and 3 which illustrate a tenth embodiment of the invention in which the spring sectors are replaced by compression springs of the helical type;
- FIG. 23 and 24 are views similar to those of Figures 2 and 3 which illustrate an eleventh embodiment of the invention in which the elastic member is constituted by a single compression spring of the helical type of large diameter;
- Figures 25 and 26 are views similar to those of Figures 2 and 3 which illustrate a twelfth embodiment of the invention in which the axially elastic device is mounted in the housing by bayonet type fitting;
- FIG. 27 is an exploded perspective view which illustrates the main components of the twelfth embodiment of the invention.
- the front shell 14 has a front transverse wall 18 and a front annular axial skirt
- the rear shell 16 forms a semi-toric rear annular envelope 22 and comprises a rear annular axial skirt 24 which extends forward, and which is received axially inside the front axial skirt 20.
- a first annular bearing 26 of transverse orientation is formed at the external periphery of the internal face of the front transverse wall 18.
- a second annular bearing 28 of transverse orientation is formed at the external periphery of the front face of a rear piston 30.
- the bearing surfaces 26 and 28 are here in one piece with the front transverse wall 18 and the piston 30 respectively.
- at least one of the bearing surfaces 26 and 28 may belong to an additional part added, for example by welding to the element concerned.
- the vanes 34 of an impeller 36 are internally fixed on the semi-toric casing 22.
- the vanes 34 face the vanes 38 of a turbine wheel 40, and the piston 30 is disposed axially between the impeller.
- This turbine wheel 40 internally comprises a ring 42, optionally split, by means of which it is fixed, here by rivets 44 or alternatively by welding, on the periphery outer of a hub 46 directed axially forward and generally L-shaped in axial section.
- transverse orientation part 48 in the form of a radial flange, of the hub 46, that the ring 42 is fixed, while the tubular axial orientation part 50 of the hub 46 is internally grooved for rotation connection of the hub 46, and therefore of the turbine wheel 40, with a driven shaft (not shown).
- This driven shaft is, in known manner, provided centrally with a channel for supplying a hydraulic control chamber 52 delimited axially by the piston 30 and the front transverse wall 18 and radially, internally, by the axial part 50 of the hub 46 .
- At least one passage 54 exists between the free end of the axial part 50 and the front transverse wall 18 for passage of the control fluid, here oil, coming from the channel of the driven shaft.
- the axial part 50 is generally of tubular shape and it has externally, at its front free end, external grooves 56.
- the axial part 50 has externally, between the flange 48 and the grooves 56, a smooth surface 58 of diameter slightly greater than that of grooves 56, so that the axial part 50 is stepped in diameter.
- a seal 60 is mounted in a groove made in the bearing 58. This seal 60 cooperates with a ferrule 62 of axial orientation that the piston 30 has at its internal periphery. A seal is therefore produced at this level.
- the hydrokinetic coupling apparatus 10 comprises an axially elastic device 64 which links in rotation the piston 30 at the annular axial wall 13 of the casing 12.
- the axially elastic device 64 comprises a support piece 66 which consists of an annular transverse plate 68 at the external periphery of which extends an axial annular ring 70 oriented towards the back.
- the support piece 66 is fixed to the annular axial wall 13 of the casing 12, here by welding the axial annular ring 70 on the internal face 21 of the front axial skirt 20 in the form of a bead 19.
- the support piece 66 is force-fitted into the casing 12, or else it is crimped into the casing 12.
- the transverse plate 68 has at its internal radial periphery cutouts 72, one of which is visible from the front in FIG. 3.
- the axially elastic device 64 also comprises axially elastic tongues 74, the opposite tangential ends of which are fixed, by a first fixing point 76, on the rear transverse face 78 of the piston 30 and, by a second fixing point 80, on the face transverse front 82 of the transverse plate 68.
- the first attachment point 76 is located opposite a cutout 72 of the transverse plate 68 and the second attachment point 80 is located in the vicinity of an edge 73 of the circumferential end of the cutout 72.
- the fixing of the tabs 74 is done here by rivets, but it can be achieved by other known means.
- the rear face 78 of the piston 30 comprises, at the first fixing point 76, a convex boss 84 which extends in relief axially towards the rear and, opposite the second fixing point
- the number of tongues 74 depends on the applications, these being regularly distributed circumferentially along several of them with tongues 74, each set comprising here at least one tab 74.
- the device 64 may for example comprise three sets of tabs 74.
- the hydrokinetic coupling apparatus 10 has an axis of axial symmetry and rotation XX ′.
- the apparatus 10 also includes a reaction wheel 88 for forming a torque converter in a known manner.
- the casing 12 is sealed and filled with oil.
- the locking clutch comprising the bearing surfaces 26, 28 and the torsional damper 90, is engaged, or bridged, so that the rotational drive movement is transmitted directly from the driving shaft (not shown), for example the crankshaft of a motor vehicle in the case of an application for a motor vehicle, to the shaft driven by the clutch of locking, without relative sliding between the impeller 40 and impeller 36 wheels. This makes it possible in particular to reduce the consumption of the vehicle.
- the tongues 74 are mounted so that they tend to keep the piston 30 in the unhooked position.
- the tongues 74 can be fixed by any known means on the piston 30 and the support piece 66.
- they can be fixed by means of rivets whose bodies are extruded on the piston 30 or the support piece 66, or by welding, or by screwing.
- the friction disc 92 carries, for fixing on each of its opposite transverse faces, front and rear friction linings 96.
- the linings 96 are integral with the bearing surfaces 26, 28 which are then fixing bearing surfaces.
- the friction disc 92 is at its outer periphery embedded in a friction lining. As a variant, the friction disc 92 rubs directly against the bearing surfaces 26, 28.
- the lining or linings 96 are provided with grooves extending from their internal periphery to their external periphery for good cooling, the grooves being in contact with the bearing surfaces 26, 28 or with the friction disc 92.
- the hydrokinetic coupling device 10 produced in accordance with the invention makes it possible to increase the capacity in driving torque of the driven shaft thanks to the increase in the radius means of the bearings 26, 28, which are no longer radially limited in size by the presence of a device on the external periphery of the front transverse wall 18 of the front shell 14.
- the invention makes it possible to reduce the number of parts required compared to the prior art, this reduces the cost of the device 10.
- a friction means 41 acts between a front transverse bearing surface 43 formed on the flange 48 of the hub 46 and the piston 30 which is disengageably linked to the front transverse wall 18 thanks to the second bearing 28 extending vis-à-vis screw of the first bearing 26 as mentioned above.
- the friction means 41 avoids any direct contact between the piston 30 and the transverse bearing surface 43 of the hub
- This friction means 41 comprises at least one friction element, preferably with a low coefficient of friction.
- This friction element is preferably made of synthetic material such as plastic, advantageously reinforced by fibers and / or beads such as fibers and / or glass beads.
- the piston 30 is adjacent to the turbine wheel 40 - hub 46 and is shaped to carry the friction means 41, and the hub 46 has an annular portion of axial orientation directed towards the front transverse wall 18 and surrounded by the piston 30 mounted axially movable relative to said portion. Thanks to this arrangement, the flange 48 of the hub 46 does not need to undergo an additional machining operation since the friction means 41 is carried by the piston 30.
- piston 30 is linked in rotation to the axial wall of the casing 12 which allows the creation of a radial clearance between the ferrule 62 and the bearing surface 58, so that the risks of jamming of the piston 30 are eliminated.
- the piston 30 cooperates with its ferrule 62 only with the seal 60 which is mounted on the hub 46, so that the friction means 41 have a good contact surface with the flange 48, because thanks to the tongues 74 and to the seal 60 , the piston 30 has a possibility of movement, in particular angular, so that the contact surface between the friction means 41 and the flange 48 is always maximum.
- one of the friction means 41 with the piston 30 has at least one projection engaged in a complementary manner in a hole 45 in the rear face 78 of the piston.
- This mode of connection by cooperation of shapes is simple and economical to produce, and makes it possible to center the friction means 41 well, while ensuring a connection in rotation.
- the hole 45 is blind, so that the tightness of the chamber 52 is preserved.
- the blind hole 45 is advantageously produced by stamping or extrusion.
- the friction means 41 consists of a washer intended to come into contact with a transverse bearing surface 43 of the hub 46 formed in favor of the flange 48, radially below the fixing rivets 44.
- This transverse bearing 43 is turned towards the front.
- the washer 41 has a plurality of pins 47 each engaged, here with axial and radial clearance, in a blind hole 45 produced locally by extruding the metal from the piston 30 in the direction of the front.
- the pins 47 and the holes 45 are of cylindrical shape, here with a circular section, alternatively with a square section or any other shape.
- the contact surface 43 between the flange 48 and the washer 41 is maximum due to the mounting of the pins 47 in the axial and radial play in the holes 45.
- FIG. 4 represents a second embodiment of the axially elastic device similar to the previous one, in which the axial annular ring 70 is inserted axially and radially between the internal face 21 of the front axial skirt 20 and the external face 25 of the rear axial skirt 24, so that these three elements are fixed together, here by welding in the form of a single bead 23.
- Figures 5 and 6 show a third embodiment of the axially elastic device which comprises several support parts 66 forming tabs.
- These support tabs 66 are preferably regularly distributed circumferentially and are for example three in number.
- the support tabs 66 do not comprise an element of annular axial crown 70 as previously.
- Each support leg 66 has a sector 100 of annular transverse plate 68.
- the sector 100 of annular transverse plate 68 has at its external periphery slots 102 which fit in a complementary manner between legs 104 extending axially forward from the free front end of the rear axial skirt 24 of the rear shell 16.
- the fixing of the slots 102 on the lugs 104 can be carried out for example by crimping or by welding.
- Each sector 100 of transverse plate has on its front transverse face 82 a second attachment point 80 of an axially elastic tongue 74.
- the assembly of the tongue 74 at the second point of fixing 80 is of the same type as that of the first embodiment.
- a first difference is that the rear axial skirt 24 is centered, at its free end, around the rear free end of the front axial skirt 20, and is fixed, here by welding, to the front axial skirt 20.
- a second difference is that the legs 104 belong to the rear free end of the front axial skirt 20.
- the support legs 66 which are identical to those of the second embodiment, fit together by their slots 102 between the legs 104 of the front axial skirt 20.
- FIGS. 9 and 10 show a fifth embodiment similar to the fourth embodiment, but in which each axially elastic tongue 74 is in one piece with a sector 100 of transverse plate of a support tab 66.
- the sector 100 of transverse plate no longer has a second fixing point 80.
- the radially internal periphery of the sector 100 of transverse plate extends substantially circumferentially by a tongue 74 which extends to the first fixing point 76 which is always located on a convex boss 84 of the rear face 78 of the piston 30.
- the sector 100 of transverse plate is in the same transverse plane as the tongue 74.
- each support tab 66 has a sector 106 of annular crown, similar to the crown 70, which is fixed, here by welding 19, on the internal face 21 of the axial skirt before 20.
- this embodiment differs in that the piston 30 has at its outer periphery an axial skirt 108 which extends towards the rear.
- the rear free end edge 109 of the axial skirt 108 of the piston comprises, facing each support tab 66, notches 110.
- each notch 110 is capable of abutting against the radial edges 114 of each sector 100 of the transverse plate.
- the mounting of the support legs 66 in the notches 110 has a circumferential clearance, in particular to prevent the piston 30 from being hampered in its axial movement.
- the circumferential end edges 112 of the notches 110 serve as a circumferential stop for the support legs 66 which makes it possible to avoid buckling of the axially elastic tongues 74, when there is transmission of a significant torque by the housing assembly 12 - piston 30 which induces a longitudinal compression force on the tongues 74.
- FIGS. 14 and 15 show a seventh embodiment in which the piston 30 comprises, facing its rear transverse face 78, intermediate transverse plates 116, the piston 30 also comprising an axial skirt 108 similar to that of the previous embodiment.
- Each intermediate transverse plate 116 has an ear 117 which carries the first attachment point 76 of an axially elastic tongue 74.
- Each intermediate transverse plate 116 has at its outer periphery transverse fixing lugs 120 which are each engaged in a complementary manner in a notch 122 formed in the rear free end edge of the axial skirt 108 of the piston 30.
- a support piece 66 in the shape of a tab is fixed on the front axial skirt 20, opposite each intermediate transverse plate 116, the rear axial skirt 24 being centered around the front axial skirt 20 as in the fourth embodiment .
- This support tab 66 comprises a transverse plate 126 at the outer periphery of which extends an annular crown sector 128 which is centered internally in the front axial skirt 20.
- the transverse plate 126 comprises an ear 130 which carries the second point of fixing 80 of the axially elastic tongue 74.
- the rear free end of the annular crown sector 128 comprises transverse fixing lugs 132 which are each engaged, radially outward, in a complementary manner in a notch 134 formed in the free end of the front axial skirt 20.
- Two transverse fixing lugs 120 and 132 are provided for each intermediate transverse plate and for each support lug 66. Of course, this number depends on the applications.
- the metal is made to flow, respectively from the axial skirt 108 of the piston 30 and the front axial skirt 20 of the front shell 14, this which allows to immobilize axially respectively the transverse fixing lugs 120, 132, between the bottom of the notches 122, 134, and the material to flow back during creep of the lateral edges of the notches 122, 134.
- the intermediate transverse plate 116 and the support tab 66 are fixed by crimping here respectively on the axial skirt 108 of the piston 30 and the front axial skirt 20 of the front shell 14.
- the front axial skirt 20 of the front shell 14 can partially surround the rear axial skirt 24 of the rear shell 16, so that the notches 134 can be produced in the rear axial skirt 24.
- the transverse fixing lugs 120, 132 are fixed by welding or gluing, respectively to the axial skirt 108 of the piston 30 and to one of the front axial skirts 20 or rear 24 of the casing 12.
- annular crown sector 128 of the support tab 66 is fixed by welding, for example by laser type transparency welding, on the front axial skirt 20 of the front shell 14.
- the intermediate transverse plate 116 can be welded directly to the rear face 78 of the piston 30.
- the intermediate transverse plate 116 then comprises a first portion for fixing the end concerned with a set of tabs 74 and a second offset portion axially for fixing by welding the intermediate transverse plate 116.
- the piston 30 can also have at its external periphery a transverse return, possibly fragmented in legs, directed towards the axis XX 'and which then replaces the intermediate transverse plate 116 to carry the first attachment point 76 of the tongue 74.
- Figures 16 and 17 show an eighth embodiment of the axially elastic device 64 in which the axially elastic tongues have been eliminated.
- transverse legs 154 are distributed circumferentially in a regular manner and in pairs, here three in number, so that two transverse legs 154 delimit between them a notch
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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 (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/806,029 US6688441B1 (en) | 1999-07-27 | 2000-07-27 | Hydrokinetic coupling appliance |
JP2001512200A JP4933710B2 (ja) | 1999-07-27 | 2000-07-27 | 自動車用流体動力結合装置 |
DE10082530T DE10082530B3 (de) | 1999-07-27 | 2000-07-27 | Hydrodynamischer Momentwandler |
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR9909740A FR2797013B1 (fr) | 1999-07-27 | 1999-07-27 | Appareil d'accouplement hydrocinetique, notamment pour vehicule automobile |
FR9909739A FR2797012B1 (fr) | 1999-07-27 | 1999-07-27 | Appareil d'accouplement hydrocinetique, notamment pour vehicule automobile |
FR99/09739 | 1999-07-27 | ||
FR99/09740 | 1999-07-27 | ||
FR99/12402 | 1999-10-05 | ||
FR9912402A FR2797014B1 (fr) | 1999-07-27 | 1999-10-05 | Appareil d'accouplement hydrocinetique |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2001007800A1 true WO2001007800A1 (fr) | 2001-02-01 |
Family
ID=27253546
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2000/002156 WO2001007800A1 (fr) | 1999-07-27 | 2000-07-27 | Appareil d'accouplement hydrocinetique |
Country Status (6)
Country | Link |
---|---|
US (1) | US6688441B1 (fr) |
JP (1) | JP4933710B2 (fr) |
KR (1) | KR100661990B1 (fr) |
DE (1) | DE10082530B3 (fr) |
FR (1) | FR2797014B1 (fr) |
WO (1) | WO2001007800A1 (fr) |
Families Citing this family (22)
Publication number | Priority date | Publication date | Assignee | Title |
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FR2797012B1 (fr) * | 1999-07-27 | 2001-11-02 | Valeo | Appareil d'accouplement hydrocinetique, notamment pour vehicule automobile |
DE10102718A1 (de) * | 2001-01-22 | 2002-07-25 | Zf Sachs Ag | Hydrodynamische Kopplungseinrichtung |
DE10162530B4 (de) * | 2001-12-19 | 2015-11-26 | Zf Friedrichshafen Ag | Hydrodynamische Kopplungseinrichtung |
DE102006028557B4 (de) * | 2005-07-14 | 2018-11-15 | Schaeffler Technologies AG & Co. KG | Hydrodynamischer Drehmomentwandler |
US20070012537A1 (en) * | 2005-07-14 | 2007-01-18 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydrodynamic torque converter |
KR20080075884A (ko) * | 2005-12-20 | 2008-08-19 | 루크 라멜렌 운트 쿠프룽스바우 베타일리궁스 카게 | 토크 컨버터의 외부 에지에 설치된 클러치 및, 토크 컨버터내에 클러치를 조립하기 위한 방법 |
WO2007128259A1 (fr) * | 2006-05-04 | 2007-11-15 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Convertisseur de couple hydrodynamique avec dispositif élastique d'accouplement pour le piston |
DE102008020674A1 (de) * | 2007-05-09 | 2008-11-13 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Drehmomentwandler mit Strömungsanordnung für ein Kühlfluid und mit Anordnung zur Drehmomentübertragung auf einen Dämpfer |
DE102008028903A1 (de) * | 2007-07-12 | 2009-01-15 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Drehmomentwandler mit zentrierter Turbine |
DE102008057104B4 (de) * | 2007-11-22 | 2018-10-31 | Schaeffler Technologies AG & Co. KG | Kraftübertragungsvorrichtung und Verfahren zur Montage einer Dämpferanordnung in einer Kraftübertragungsvorrichtung |
DE102008060577A1 (de) * | 2007-12-12 | 2009-06-18 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Stützplattenbefestigung mit doppelter Überlappung |
US8677598B2 (en) * | 2009-10-20 | 2014-03-25 | Schaeffler Technologies AG & Co. KG | Piston plate connection with blind riveting |
US8720658B2 (en) | 2010-09-30 | 2014-05-13 | Aisin Aw Co., Ltd. | Starting device and damper device for use therein |
JP5556546B2 (ja) * | 2010-09-30 | 2014-07-23 | アイシン・エィ・ダブリュ株式会社 | 流体伝動装置 |
JP5477249B2 (ja) | 2010-09-30 | 2014-04-23 | アイシン・エィ・ダブリュ株式会社 | 発進装置 |
JP5556551B2 (ja) | 2010-09-30 | 2014-07-23 | アイシン・エィ・ダブリュ株式会社 | 流体伝動装置 |
US9206864B2 (en) * | 2012-04-16 | 2015-12-08 | Schaeffler Technologies AG & Co. KG | Torque converter lug |
US9897149B2 (en) | 2015-02-17 | 2018-02-20 | Allison Transmissions, Inc. | Torque converter lockup clutch backing plate |
US10288157B2 (en) * | 2016-08-24 | 2019-05-14 | Schaeffler Technologies AG & Co. KG | Torque converter including integral front cover fluid flow baffles |
US9915332B1 (en) * | 2016-10-26 | 2018-03-13 | Schaeffler Technologies AG & Co. KG | Motor vehicle clutch assembly including shock absorber for smoothing clutch engagement |
DE102018221613A1 (de) * | 2018-12-13 | 2020-06-18 | Zf Friedrichshafen Ag | Kupplungsanordnung mit einem Gehäuse und mit einem Tilgersystem |
US11649883B1 (en) * | 2022-04-05 | 2023-05-16 | Schaeffler Technologies AG & Co. KG | Connection interface for reaction plate in torque converter |
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DE3224403A1 (de) * | 1982-06-30 | 1984-01-05 | LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl | Reibungskupplung sowie verfahren zu deren montage |
DE3410526A1 (de) * | 1984-03-22 | 1985-10-03 | Sachs Systemtechnik Gmbh, 8720 Schweinfurt | Fliehkraftbetaetigbare ueberbrueckung fuer hydrodynamische kupplungen und wandler |
FR2608238B1 (fr) * | 1986-12-15 | 1991-01-25 | Valeo | Embrayage a friction a progressivite d'actionnement |
JPH07501387A (ja) * | 1992-09-24 | 1995-02-09 | ヴァレオ | ロックアップ・クラッチ用ねじり緩衝器及びそのねじり緩衝器を有するロックアップ・クラッチ |
FR2703743B1 (fr) * | 1993-04-08 | 1995-06-02 | Valeo | Mécanisme d'embrayage, notamment pour véhicule automobile. |
FR2726620B1 (fr) * | 1994-11-04 | 1997-01-10 | Valeo | Procede de montage d'un embrayage de verrouillage pour accouplement hydrocinetique, notamment pour vehicule automobile, embrayage de verrouillage et accouplement hydrocinetique le comportant |
JP4341992B2 (ja) * | 1997-06-30 | 2009-10-14 | ヴァレオ | 自動車用ロックアップクラッチを有する流体動力カプリング装置 |
FR2765296B1 (fr) * | 1997-06-30 | 1999-12-03 | Valeo | Appareil d'accouplement hydrocinetique a embrayage de verrouillage, pour vehicule automobile |
FR2768794A1 (fr) * | 1997-09-23 | 1999-03-26 | Valeo | Embrayage de verrouillage pour un appareil d'accouplement hydrocinetique, notamment de vehicule automobile |
-
1999
- 1999-10-05 FR FR9912402A patent/FR2797014B1/fr not_active Expired - Lifetime
-
2000
- 2000-07-27 US US09/806,029 patent/US6688441B1/en not_active Expired - Lifetime
- 2000-07-27 KR KR1020017003831A patent/KR100661990B1/ko not_active IP Right Cessation
- 2000-07-27 WO PCT/FR2000/002156 patent/WO2001007800A1/fr active IP Right Grant
- 2000-07-27 DE DE10082530T patent/DE10082530B3/de not_active Expired - Fee Related
- 2000-07-27 JP JP2001512200A patent/JP4933710B2/ja not_active Expired - Fee Related
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2942043A1 (de) * | 1979-10-17 | 1981-05-07 | Automobiles Peugeot, Paris | Getriebe, insbesondere fuer kraftfahrzeuge |
FR2748539A1 (fr) | 1996-05-07 | 1997-11-14 | Valeo | Appareil d'accouplement hydrocinetique a piece d'entrainement de languettes, notamment pour vehicule automobile |
Also Published As
Publication number | Publication date |
---|---|
FR2797014A1 (fr) | 2001-02-02 |
KR20010075367A (ko) | 2001-08-09 |
JP2003505652A (ja) | 2003-02-12 |
JP4933710B2 (ja) | 2012-05-16 |
FR2797014B1 (fr) | 2001-11-02 |
DE10082530B3 (de) | 2013-01-03 |
DE10082530T1 (de) | 2002-01-10 |
US6688441B1 (en) | 2004-02-10 |
KR100661990B1 (ko) | 2006-12-28 |
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