EP3759369A1 - Transmission device for a vehicle - Google Patents
Transmission device for a vehicleInfo
- Publication number
- EP3759369A1 EP3759369A1 EP19708471.8A EP19708471A EP3759369A1 EP 3759369 A1 EP3759369 A1 EP 3759369A1 EP 19708471 A EP19708471 A EP 19708471A EP 3759369 A1 EP3759369 A1 EP 3759369A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- clutch
- input
- output
- torque
- rotation
- 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.)
- Pending
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0661—Hydraulically actuated multiple lamellae clutches
Definitions
- the present invention relates to the field of transmissions for motor vehicles. It relates in particular to a torque transmission device intended to be arranged in the drive train of a motor vehicle, between a heat engine and a gearbox.
- It relates more specifically to a torque transmission device for a hybrid type of motor vehicle in which a rotating electrical machine is disposed in the drive chain.
- hybrid motor vehicles comprising a torque transmission device disposed between a heat engine and a gearbox, a rotating electrical machine and a clutch for coupling or uncoupling rotating a crankshaft of the heat engine to a rotor of the rotating electrical machine.
- the rotating electrical machine can also constitute an electric brake or bring a surplus of energy to the engine to assist or prevent it from stalling.
- the electric machine can act as an alternator.
- the rotating electrical machine can also drive the vehicle independently of the engine.
- Such a rotating electrical machine may be in line with the torque transmission device, that is to say that the axis of rotation of the rotor of the rotating eclectic machine coincides with the axis of rotation of the transmission device. couple.
- the rotating electrical machine can be offset relative to the torque transmission device, that is to say that the axis of rotation of the rotor of the rotating electrical machine is offset from the axis of rotation of the device. torque transmission.
- it is necessary to implement the rotating electrical machine torque transmission device without this does not impact the axial compactness and radial torque transmission device.
- Another problem of this type of architecture is at the fastening of the constituent elements of the torque transmission device, such as for example the supports of different clutches.
- it is necessary to add at least one support point to the support of the clutches in order to center it and guide it correctly in rotation while allowing the clutch actuation forces to be withstood.
- the invention also aims to remedy the aforementioned problems by benefiting from a torque transmission device to reconcile the requirements of axial and radial compactness while ensuring an optimum mechanical connection between the rotating electrical machine and the torque transmission device.
- a torque transmission device in particular for a motor vehicle, comprising:
- a torque input member rotated about an axis, adapted to be rotatably coupled to a crankshaft of a heat engine
- a first torque output element able to be coupled in rotation to a first input shaft of a gearbox
- an input clutch selectively and frictionally coupling the torque input element and the intermediate element
- a first output clutch selectively and frictionally coupling the intermediate element and the first torque output element
- a rolling member is arranged radially between the intermediate element and the torque input element.
- the intermediate element which is a clutch support is centered and guided in rotation and the rolling member ensures the recovery of clutch actuation forces.
- the intermediate element comprises an electrical connection zone capable of being rotatably connected to a rotating electrical machine about an axis parallel to the axis of rotation.
- the electrical machine is called "off-line” because the axis of rotation of the rotating electrical machine is offset from the axis of rotation of the torque transmission device.
- the electrical connection zone is axially offset from the input clutch and / or the first output clutch.
- This arrangement makes it possible to position the electric machine according to the space available in the vehicle's drivetrain.
- This arrangement makes it possible in particular not to have to arrange the electrical machine axially after the clutches, which would be negative for the axial compactness.
- This arrangement makes it possible in particular not to have to dispose of the electrical machine radially beyond the clutches, which would be negative for the radial compactness.
- the intermediate element defines a rotor support of an electric machine in rotation about the axis of rotation.
- the electric machine is then "in-line".
- the electrical connection zone may be radially to the right of the actuating member associated with the first output clutch.
- the rolling member comprises an inner ring and an outer ring, said inner ring upper is in contact with the torque input member and said outer ring is in contact with the intermediate member.
- the rolling member is disposed axially between the actuating member associated with the input clutch and the actuating member associated with the first output clutch.
- the rolling member is placed between a radial end of the intermediate element and a fixed portion of the torque input element.
- the rolling member is disposed axially between the actuating member associated with the input clutch and the first torque output member.
- the input clutch and / or the first output clutch comprise:
- a multi-disk assembly comprising at least one friction disk rotating in solidarity with one of the input and output disk carriers, at least two plates respectively disposed on either side of each friction disk, integral with each other; rotation of the other input and output disk carriers and friction linings disposed between the platens and a friction disk, the input clutch and / or the first output clutch decribing a disengaged position and an engaged position in which said platens and the friction disk pinch the friction liners so as to transmit a torque between the input disk carrier and the output disk carrier.
- the device comprises a second torque output element, able to be coupled in rotation to a second input shaft of a gearbox, a second output clutch, coupling selectively and by friction the intermediate element and the second torque output member and an actuating member associated with the second output clutch.
- the device comprises a force transmission shaft for each of the input clutch, the first output clutch and the second output clutch, each force transmission member being axially movable. for transmitting the actuating force from the actuating member to the associated clutch.
- the first and second output elements may comprise a web whose inner periphery is grooved and adapted to cooperate with a first and a second gearbox shaft, respectively.
- the intermediate element comprises an electrical connection zone capable of being connected in rotation with a rotating electrical machine about an axis parallel to the axis of rotation of the torque transmission device.
- the invention also relates to a hybrid transmission module for a motor vehicle, the hybrid transmission module comprises a torque transmission device according to the preceding characteristics and a rotating electrical machine, the intermediate element comprising the electrical connection zone being connected to the rotating electrical machine so that the axis of rotation of the rotating electrical machine is offset from the axis of rotation of the torque transmission device.
- FIG. 1 is a sectional view of the torque transmission device according to a first embodiment of the invention
- FIG. 2 is a sectional view of the torque transmission device according to a second embodiment of the invention. invention
- FIG. 3 is a sectional view of the torque transmission device according to a third embodiment of the invention.
- FIG. 4 is a perspective view of the coupled transmission device
- FIG. 5 is a perspective view of the electrical connection area.
- a torque transmission device 1 comprising:
- a torque input element 2 rotating about an axis of rotation X, able to be coupled in rotation to a crankshaft of a heat engine (not shown),
- a first torque output element 3 able to be coupled in rotation to a first input shaft of a gearbox (not represented),
- a second torque output element 4 able to be coupled in rotation to a second input shaft of a gearbox (not shown) and
- a torsion damping device can be positioned between the crankshaft of the heat engine and the torque input member 2.
- the first 3 and second 4 output members comprise a web whose inner periphery is grooved and able to cooperate with a first and a second gear box shaft respectively. speeds.
- the first and second gear shafts are coaxial.
- the device 1 also comprises an input clutch 10 selectively and frictionally coupling the input element 2 and the intermediate element 5.
- the input clutch 10 comprises:
- a multi-disk assembly 13 comprising a plurality of friction disks, here four, integral in rotation with the input disk carrier January 1, a plurality of trays respectively disposed on either side of each friction disk, rotating solids of the carrier; disc outlet 12 and friction linings disposed between the plates and a friction disk, fixed on each side of the friction discs, the clutch 10 describing a disengaged position and an engaged position in which said plates and friction disk pin the friction linings to transmit torque between the input disk carrier and the output disk carrier.
- Each disk carrier 11, 12 synchronizes in rotation all the trays and the set of friction discs.
- Each disk holder 11, 12 each comprises a cylindrical skirt on which the plates and the friction discs are mounted.
- the friction discs of the multi-disc assembly 13 cooperate with the cylindrical skirt of the input disc carrier 11 along their radially inner periphery by fluting.
- the friction discs are radially outwardly of the cylindrical skirt.
- the device also comprises a first output clutch 20 selectively and frictionally coupling the intermediate element 5 and the first output element 3.
- the first output clutch 20 comprises:
- a multi-disk assembly 23 comprising a plurality of friction disks, here three, integral in rotation with the output disk carrier 22, a plurality of trays respectively disposed on either side of each friction disk, rotating in rotation with the disk carrier, inlet 21 and friction linings disposed between the platens and a friction disc, fixed on each side of the friction discs, the clutch 20 describing a disengaged position and an engaged position in which said platens and the friction disk pinch the friction linings to transmit torque between the input disk carrier and the output disk carrier.
- Each disc holder 21, 22 each comprises a cylindrical skirt on which the trays and the friction discs are mounted.
- the friction discs of the multi-disc assembly 23 cooperate with the cylindrical skirt of the output disc holder 22 along their radially outer periphery by fluting. The friction discs are therefore radially inside the cylindrical skirt.
- the trays of the multidisk assembly 23 cooperate with the cylindrical skirt of the inlet disk carrier 21 according to their radially outer periphery by splines. The trays are therefore radially inside the cylindrical skirt.
- the device 1 comprises a second output clutch 30, selectively and frictionally coupling the intermediate element 5 and the second output element 4.
- the second output clutch 30 comprises:
- a multi-disk assembly 33 comprising a plurality of friction disks, here four, integral in rotation with the outlet disk carrier 32, a plurality of trays respectively disposed on either side of each friction disk, rotating in rotation with the disk carrier, inlet 31 and friction linings disposed between the platens and a friction disk, fixed on each side of the friction discs, the clutch 30 describing a disengaged position and an engaged position in which said platens and the friction disk pinches the friction liners to transmit torque between the input disk carrier and the output disk carrier.
- Each disc carrier 31, 32 each has a cylindrical skirt on which the trays and the friction discs are mounted.
- the friction discs of the multi-disc assembly 33 cooperate with the cylindrical skirt of the outlet disc holder 32 according to their radially outer periphery by fluting. The friction discs are therefore radially inside the cylindrical skirt.
- the trays of the multidisk assembly 33 cooperate with the cylindrical skirt of the inlet disk carrier 31 according to their radially outer periphery by splines. The trays are therefore radially inside the cylindrical skirt.
- the gaskets may be fixed to the friction discs, in particular by bonding, in particular by riveting, in particular by overmolding.
- the fittings are fixed on the trays.
- Each disk carrier 11, 12, 21, 22, 31, 32 can synchronize in rotation all the trays or all of the friction discs.
- the trays can be integral in rotation with the input disk carrier 11, 21, 31 and the friction disks can be integral with the output disk carrier 12, 22, 32.
- the plates can be integral in rotation with the output disk carrier 12, 22, 32.
- the disks can be integral in rotation with the input disk carrier 11, 21, 31.
- the clutches are wet type and have between two and seven friction discs, preferably four friction discs. Such multi-disk clutches can limit the radial height to limit the axial extent.
- the first output clutch 20, the second output clutch 30 and the input clutch 10 are stacked radially. There is a plane perpendicular to the axis of rotation which intersects both the outlet clutches 20, 30 and the input clutch 10. There is also a plane perpendicular to the axis of rotation which intersects both the actuating member 40 of the input clutch 10, the rolling member 47 supporting the input element 2.
- the device 1 comprises an actuating member 40 and a force transmission member 41 associated with the input clutch 10.
- a holding member in the disengaged position can be provided to push the force transmission 41 of the input clutch 10.
- the input clutch is of the "normally open" type.
- the force transmission member 41 is axially movable to transmit the actuating force of the actuating member 40 to the input clutch 10.
- the force transmission member exerts an axial force on the multi-disk assembly 13 for moving the trays to the disks.
- the actuation is thus of the "pushed" type.
- the force transmission member 41 has a curved outer radial end defining a bearing surface for exerting the force axial on the multidisk assembly, continuous or discontinuous in the example.
- the force transmission member 41 of the input clutch 10 has three bends between which are interposed flat portions. This allows axially compact operation.
- the actuating member 40 comprises an annular piston 42 mounted to slide axially on the outside of an inner tube, the piston 42 and the tube forming an actuating chamber 43.
- the actuating member 40 comprises a rotary stop , which is here a rolling bearing 44, carried by the piston 42 and cooperating with an inner radial end of the force transmission member 41.
- the fluidic pressures associated with the "engaged" and "disengaged” positions are the pressures of the operating chamber 43.
- the rolling bearing 44 has an outer ring attached to the piston, an inner ring bearing against the force transmission member and rolling bodies interposed between the inner ring and the outer ring.
- the piston 42 is of revolution about the axis of rotation X.
- the tube of the actuating member 40 of the input clutch is formed in a transverse partition 46 which defines a fluid supply network of the actuating member 40 as well as the clutch cooling circuit 10, 20, 30.
- the clutches 10, 20, 30 are arranged in a sealed chamber filled with oil, the transverse partition 46 defines in part this sealed chamber.
- the device 1 comprises a bearing member supporting the input element 47, here a ball bearing.
- the support bearing member of the input element 47 is disposed between the radial end of the transverse partition 46 and an axial portion of the input element 2.
- a circlip is formed on the fixed portion of the input member 2 to axially lock the rolling member 47.
- a bearing member 49 supports the intermediate element 5.
- the rolling member 49 is here a ball bearing, and is arranged radially between the intermediate element 5 and the torque input member 2.
- the rolling member 49 comprises an inner ring 49a and an outer ring 49b, said inner ring 49a is in contact with the torque input member 2 and said outer ring 49b is in contact with the intermediate element 5.
- L rolling member 49 is disposed axially between the actuating member 40 associated with the input clutch 10 and the actuating member 50 associated with the first output clutch 20.
- the rolling member 49 is arranged axially between the actuating member 40 associated with the input clutch 10 and the first torque output member 3.
- the rolling member 49 is disposed between a radial end of the intermediate element 5 and a fixed portion of axial extension of the torque input element 2.
- the radial end of the intermediate element 5 is formed in the form of a stall for axially locking the bearing member 49.
- a circlip is formed on the fixed portion of the input member 2 to axially lock the rolling member 49.
- the rolling member 49 thus makes it possible to center the intermediate element 5 and to ensure the recovery of the control forces of the output clutches 20, 30.
- the first output clutch 20, the second output clutch 30, the input clutch 10, the input clutch actuator 40 and the support member of the input element 47 follow each other radially. More precisely, in this example, the aforementioned elements are stacked radially towards the X axis.
- the device 1 also comprises an actuating member 50 and a force transmission member 51 associated with the first output clutch 20.
- the force transmission member 51 is axially movable to transmit the actuating force of the actuating member 50 to the input clutch 20.
- the device 1 also comprises an actuating member 60 and a force transmission member 61 associated with the second output clutch 30.
- the force transmission member 61 is axially movable to transmit the actuating force of the organ actuating device 60 to the second output clutch 30.
- a holding member in the disengaged position may be provided to push back the force transmission members 51, 61 of the output clutches 20, 30.
- the output clutches 20, 30 are of the "normally open" type.
- actuating members 50, 60 have the same elements as those detailed in connection with the actuating member 40 of the input clutch, with the difference that they are housed in one and the same envelope and form only one single and same component conventionally called double concentric actuator.
- the shapes of the pistons and / or the actuating members 40, 50, 60 are chosen so that they can be stacked radially, which contributes to the axial compactness of the device 1.
- the actuating members 50, 60 of the output clutches 20, 30 are housed in a housing 80 of the gearbox.
- the actuating members 50, 60 of the outlet clutches 20, 30, in particular their actuating chamber are stacked radially.
- the actuating members 50, 60 of the output clutches 20, 30 are on one side, axially speaking, first and second output members 3, 4 and the actuating member 40 of the input clutch 10. is on the other side of the first and second output elements 3, 4.
- the force transmission members 51, 61 of the output clutches 20, 30 each have a curved outer radial end defining a bearing surface for exerting the axial force on the multi-disk assemblies, 23, 33.
- the actuation is thus of type "pushed".
- the outer radial end of these two force transmission members 51, 61 comprises a plurality of axial extension fingers, respectively numbered 53, 63, and distributed around the X axis so that their bearing surface is discontinuous. These fingers 53, 63 pass here through openings in the intermediate element 5.
- These fingers 53, 63 allow the force transmission members 51, 61 to be able to actuate the multidisk assembly through the intermediate element.
- the intermediate element 5 also comprises an electrical connection zone 65 adapted to be rotatably connected to a rotating electrical machine (not shown) around an axis parallel to the axis X.
- the connection zone electrical 65 is here shifted axially clutches 10, 20, 30.
- the electric machine is then called "off-line”.
- the electrical connection zone 65 is able to cooperate directly with a pinion of the rotating electrical machine.
- the force transmission members 51, 61 of the outlet clutches 20, 30 are traversed by the intermediate element 5 to provide the connection zone 65.
- the intermediate element 5 comprises a plurality of protuberances 67 passing through openings of each force transmission member 51, 61.
- the protrusions 67 are angularly offset with respect to the axis of rotation X and are eight in number.
- the electrical connection zone 65 is located radially to the right of the actuating members 50, 60 associated with the first 20 and second 30 output clutches.
- a rolling member 48 supports the electrical connection zone 65 and is arranged radially between the electrical connection zone 65 and the actuating member 50 associated with the first output clutch 20.
- the rolling member 48 is here a bearing. balls, and is arranged radially between the electrical connection zone 65 and the actuating members 50, 60 of the output clutches.
- the rolling member 48 thus makes it possible to take up the axial, radial and tangent forces due to the passage of torque in the gear of the electrical connection zone 65.
- the rolling member 48 comprises an inner ring 48a and an outer ring 49b, the inner ring 48a is in contact with the gearbox casing 80 and the outer ring 48b is in position. contact with the electrical connection area 65.
- the particularity of this first embodiment is that the rolling member 48 is installed directly on the housing 80 of the gearbox.
- the rolling member 48 is axially locked by a shoulder formed in the gearbox housing 80 and at least one circlip formed in a groove of the crown 90.
- the electrical connection zone 65 is made in the form of a ring gear 90 adapted to be geared directly by a pinion of the rotating electrical machine (not visible).
- the ring 90 has a helical toothing complementary shape to the pinion of the rotating electrical machine.
- a chain or belt can be used to connect the pinion of the rotating electrical machine to the ring 90.
- the ring 90 has two flanks which are on each side of the helical cut.
- the ring 90 has at least one cavity 91 on the sidewall facing the intermediate element 5.
- the ring 90 has in this case eight cavities 91, a number complementary to the protrusions 67 of the intermediate element 5.
- the electrical connection zone 65 and the intermediate element 5 thus mesh by cooperation of shapes.
- the cavities 91 thus cooperate with the protrusions 67 of the intermediate element 5 and are designed to be assembled with a radial clearance of 0.5 mm in order to compensate for any radial and / or angular misalignment between the ring 90 and the intermediate element 5.
- the rolling member 48 is disposed between the inner diameter of the ring 90 and the housing 80 of the gearbox. This arrangement makes it possible to fix in a simple manner the rolling member 48 directly on the housing 80 of the gearbox while limiting the positioning tolerances.
- Bearing members 70 are provided between the intermediate element 5, the first output element 3, the second output element 4 to axially wedge these elements together.
- the device of FIG. 2 differs from that of FIG. 1 in the positioning of the rolling member 48.
- the rolling member 48 comprises an inner ring 48a and an outer ring 48b, the said inner ring 48a is in contact with the actuating member 50 associated with the first outlet clutch 20 and said outer ring 49b is in contact with the electrical connection zone 65. More specifically said inner ring 48a is in contact with the envelope actuating members 50, 60 of the outlet clutches 20, 30.
- the rolling member 48 is axially locked by a shoulder formed in the casing of the actuating members 50, 60 of the outlet clutches 20, 30 and at least one circlip arranged in a groove of the crown 90.
- this second embodiment is that the rolling member 48 is installed directly on the casing of the actuating members 50, 60 of the outlet clutches 20, 30, which are housed in the housing 80 of the box of speeds. This makes it possible to simply fix the rolling member 48 and to potentially provide the crown 90, the bearing 48 and the actuating members 50, 60 of the output clutches 20, independently of the transmission device 1.
- the device of FIG. 3 differs from FIG. 2 in the axial locking of the rolling member 48.
- the rolling member 48 comprises an inner ring 48a and an outer ring 48b, the inner ring 48a is made of contact with the actuating member 50 associated with the first output clutch 20 and said outer ring 49b is in contact with the electrical connection zone 65. More specifically said inner ring 48a is in contact with the envelope of the actuating members 50, 60 of the output clutches 20, 30.
- the rolling member 48 is axially locked by a stop 81 of the gearbox housing 80 and at least one circlip formed in a groove of the crown 90.
- the rolling member 48 is installed on an element carried by the housing 80 of the gearbox, that is to say the envelope of the actuating members 50, 60 output clutches 20, 30, which allows to simply fix the rolling member 48 and potentially provide the crown 90, the rolling member 48 and the actuating members 50, 60 of the output clutches 20, 30 independently of the transmission device 1.
- the axial locking of the rolling member 48 by the housing 80 of the gearbox limits the axial positioning tolerance of the pinion gear of the rotating electrical machine and the crown 90 of the electrical connection area.
- FIGS. 4 and 5 show the mechanical connection between the intermediate element 5 and the electrical connection zone 65, in particular the ring 90.
- the plurality of protuberances 67 are visible.
- the protuberances 67 are offset angularly relative to each other. to the axis of rotation and are eight in number, which means that each outgrowth 67 is angularly offset by 45 °.
- the protuberances 67 have a substantially "W" shape protrude from the intermediate element 5.
- the protrusions 67 are adapted to be inserted removably into the associated cavities 91 of the crown 90 visible in Figure 5.
- the cavities 91 are located on the side of the ring 90 which is facing the intermediate element 5.
- the ring 90 also has eight cavities 91 angularly offset relative to the axis of rotation and are eight in number, which means that each cavity 91 is angularly offset by 45 °.
- the cavities 91 have a "W" shape adapted to receive the protuberances 67 of the intermediate element 5 visible in FIG. 4.
- the cavities 91 cooperate with the protuberances 67 of the intermediate element 5 and are designed to be assembled with a radial clearance of 0.5 mm in order to compensate for any radial and / or angular misalignment between the ring 90 and the intermediate element 5.
- the ring 90 is supported by the rolling member 48 which is itself supported by the casing of the actuating members 50, 60 or by the housing 80 of the gearbox.
- the protuberances 67 can be on the ring 90 and the cavities 91 can be on the intermediate element 5.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1851729A FR3078378B1 (en) | 2018-02-27 | 2018-02-27 | TRANSMISSION DEVICE FOR VEHICLE |
PCT/EP2019/054900 WO2019166511A1 (en) | 2018-02-27 | 2019-02-27 | Transmission device for a vehicle |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3759369A1 true EP3759369A1 (en) | 2021-01-06 |
Family
ID=62143376
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19708471.8A Pending EP3759369A1 (en) | 2018-02-27 | 2019-02-27 | Transmission device for a vehicle |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3759369A1 (en) |
FR (1) | FR3078378B1 (en) |
WO (1) | WO2019166511A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3117954B1 (en) * | 2020-12-17 | 2022-11-25 | Valeo Embrayages | TORQUE CUT CLUTCH |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2830590B1 (en) * | 2001-10-08 | 2004-07-09 | Valeo | TRANSMISSION ASSEMBLY COMPRISING TWO CLUTCHES AND AN ELECTRIC MACHINE, IN PARTICULAR FOR A MOTOR VEHICLE |
WO2015048960A2 (en) * | 2013-10-04 | 2015-04-09 | Schaeffler Technologies AG & Co. KG | Pulse-separation clutch arrangement |
DE102017206215A1 (en) * | 2017-04-11 | 2018-10-11 | Zf Friedrichshafen Ag | Multiple clutch assembly, dual clutch transmission assembly and motor vehicle |
-
2018
- 2018-02-27 FR FR1851729A patent/FR3078378B1/en active Active
-
2019
- 2019-02-27 WO PCT/EP2019/054900 patent/WO2019166511A1/en unknown
- 2019-02-27 EP EP19708471.8A patent/EP3759369A1/en active Pending
Also Published As
Publication number | Publication date |
---|---|
FR3078378B1 (en) | 2020-02-28 |
WO2019166511A1 (en) | 2019-09-06 |
FR3078378A1 (en) | 2019-08-30 |
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