FR3080896A1 - TRANSMISSION DEVICE FOR MOTOR VEHICLE - Google Patents

Abstract

The invention relates to a torque transmission device (1) comprising: - a torque input element (2) rotating about an axis (X), - a first torque output element (3), - an inlet web (5) arranged between the torque input member (2) and the torque output member (3); - an input clutch (10) fed by at least one pipe (37); ) of fluid, selectively and frictionally coupling the torque input member (2) and the input web (5), - a first output clutch (20), selectively and frictionally coupling the input web (5) and the first torque output member (3), and - a protective housing (46) arranged to at least partially enclose the torque input member (2), the torque output member ( 3), the inlet clutch (10), the outlet clutch (20) and the inlet web (5), in which the fluid duct (37) is integral with the protective casing ( 46).

Description

Transmission device for motor vehicle

The present invention relates to the field of transmissions for motor vehicles. It relates in particular to a torque transmission device intended to be placed in the traction chain of a motor vehicle, between a heat engine and a gearbox.

The invention relates more specifically to a torque transmission device for a hybrid type motor vehicle in which a rotating electric machine is arranged in the traction chain.

In the prior art, hybrid type motor vehicles are known comprising a torque transmission device disposed between an internal combustion engine and a gearbox, a rotary electrical machine as well as a clutch and a drive member. actuation of this clutch for coupling or uncoupling in rotation a crankshaft of the internal combustion engine to a rotor of the rotary electric machine. Thus, it is possible to shut down the internal combustion engine at each stop of the vehicle and to restart it thanks to the rotating electric machine. The rotating electric machine can also constitute an electric brake or provide additional energy to the internal combustion engine to assist it or prevent it from stalling. When the internal combustion engine is running, the electric machine can act as an alternator. The rotating electric machine can also drive the vehicle independently of the internal combustion engine.

Such a rotary electrical machine can be in line with the torque transmission device, that is to say that the axis of rotation of the rotor of the rotary eclectic machine is coincident with the axis of rotation of the torque transmission device. couple. As a variant, the rotary electric machine can be offset relative to the torque transmission device, that is to say that the axis of rotation of the rotor of the rotary eclectic machine is offset from the axis of rotation of the rotation device. torque transmission.

An internal combustion engine exhibits acyclisms due to the successive explosions in the cylinders of the internal combustion engine, the frequency of acyclisms varying in particular as a function of the number of cylinders and the speed of rotation of the internal combustion engine. In order to filter the vibrations generated by the acyclisms of the internal combustion engine, it is known to integrate torsional vibration dampers with elastic members into the torque transmission devices. In the absence of such shock absorbers, vibrations entering the gearbox would cause particularly undesirable shocks, noises or noise pollution during operation. Such shock absorbers are conventionally arranged between the internal combustion engine and the rotary electric machine and they form with the clutch the torque transmission device. Such a device is for example disclosed in the document FR3015380. The architecture of torque transmitting devices is becoming more and more compact and it is sometimes difficult to house all the components. Thus, due to the presence of the rotary electrical machine, it is necessary to position the input clutch and the associated actuating member on the side of the heat engine, which poses a certain number of problems and in particular the supply of fluid to the clutch and its actuating member.

In current developments in hybrid vehicles, it is necessary to install the rotary electrical machine on the torque transmission device without, however, this having an impact on the axial and radial compactness. Due to the presence of a wet-type clutch, it was necessary to design a torque transmission device allowing the clutch to be supplied with fluid without modifying the size of the torque transmission device. This search for axial and radial compactness is the basis of the invention.

In the state of the art, devices are known in which the supply of fluid intended for cooling the clutches, in particular of the input clutch, is done on the gearbox side, in particular through one of the gearbox input shafts, which complicates the manufacture of the gearbox.

The invention aims to improve the existing design by benefiting from a torque transmission device making it possible to reconcile the requirements of axial and radial compactness while guaranteeing a good supply of the clutch with fluid, in particular with cooling fluid.

The invention achieves this, according to one of its aspects, thanks to a torque transmission device, in particular for a motor vehicle, comprising:

- a torque input element in rotation about an axis X, capable of being coupled in rotation to a crankshaft of a heat engine,

- a first torque output element, capable of being coupled in rotation to a first input shaft of a gearbox,

- an entry veil arranged between the torque input element and the torque output element, in the sense of the torque transmission,

- an input clutch supplied by at least one fluid line, selectively and frictionally coupling the torque input element and the input web,

- a first output clutch, selectively and frictionally coupling the input web and the first torque output element, and

a protective casing arranged to at least partially envelop the torque input element, the torque output element, the input clutch, the output clutch and the input web, in which the fluid line comes from material with the protective casing.

Thanks to this architecture, the cooling circuit of the input clutch is integrated into the protective casing, which makes it possible to reduce the number of components of the torque transmission device, to reduce its axial and radial dimensions and contributes to increasing the standardization of its components. For the purpose of the present invention, by “material issue with the casing” is meant “formed integrally with the casing”.

In the following description and the claims, the terms “front” or “rear” depending on the direction relative to an axial orientation determined by the main X axis will be used without limitation and in order to facilitate understanding thereof. of rotation of the transmission of the motor vehicle and the terms "interior / internal" or "exterior / external" with respect to the axis X and in a radial orientation, orthogonal to said axial orientation.

According to one aspect of the invention, the fluid line specifically supplies the input clutch. Within the meaning of the present invention, this indicates that the primary objective of the fluid line is to supply fluid, such as a cooling fluid, to the input clutch. This does not prevent the fluid line from feeding other clutches located radially outside. Indeed, in the context of the present invention, it is entirely possible that after supplying the input clutch, the fluid supplies output clutches located radially outside.

According to another aspect of the invention, the fluid is a cooling fluid.

According to another aspect of the invention, the device comprises a plurality of fluid lines distributed circumferentially around the axis X. These fluid lines are intended to provide cooling and lubrication of the multi-disc assemblies of the clutches of the present invention, and in particular the input clutch.

According to another aspect of the invention, the protective casing can be composed of a front cover located opposite the internal combustion engine, a rear cover located opposite the gearbox and a central element connecting the front cover and the back cover. The front cover, the central element and the rear cover can be fixed together by fixing means, for example of the screw or rivet type. As a variant, the central element can be integrated at least partially into one of the two front or rear covers.

The protective casing can be fixed to the internal combustion engine by means of fixing means, for example of the screw or rivet type. Advantageously, the front cover can be fixed to the internal combustion engine by means of fixing means, for example of the screw or rivet type.

According to another aspect of the invention, the fluid line is made in one piece with the front cover of the protective casing.

According to another aspect of the invention, the front cover of the protective casing is composed of a radial wall and an axial portion and has a general shape substantially in "L" shape, the base of the "L" being situated on the side of the axis of rotation X.

According to another aspect of the invention, the fluid line extends between an inlet orifice and an outlet orifice, the inlet orifice being located in the radial wall and the outlet orifice in the axial portion .

According to another aspect of the invention, the outlet orifice is oriented axially.

According to another aspect of the invention, the inlet port, the first outlet clutch, the first inlet clutch and the outlet port, succeed one another radially in proximity to the axis X.

According to another aspect of the invention, the entire front cover of the protective casing is crossed by the fluid line. Consequently, the fluid pipe follows the shape of the front cover and has a general shape substantially in an "L" shape, the base of the "L" being situated on the side of the axis of rotation X.

According to another aspect of the invention, the device further comprises a rolling member supporting the input element disposed between the radial end of the protective casing, advantageously the inner end of the protective casing and an axial portion of the input element. Even more advantageously, the rolling member supporting the input element is disposed between the front cover, advantageously the axial portion of the front cover and the axial portion of the input element.

According to another aspect of the present invention, the bearing member supporting the input element may be composed of an internal ring in contact with the torque input element and an external ring in contact with the protective casing, in particular the front cover of the protective casing.

According to another aspect of the invention, the device further comprises a second output element, capable of being coupled in rotation to a second input shaft of a gearbox, a second output clutch, coupling selectively and by friction the inlet web and the second torque outlet element.

Within the meaning of the present application, the first output clutch is that located radially on the outside, that is to say furthest from the axis of rotation X of the device. The second output clutch being the one located radially inside, that is to say the one closest to the axis of rotation of the device.

According to one aspect of the invention, the first output clutch, the second output clutch and the input clutch, succeed one another radially in proximity to the axis X. This sequence makes it possible to stack the elements radially so that a device is axially compact. This sequence therefore makes it possible to limit the impact of the device on the axial size of the transmission chain.

Within the meaning of the invention, the radial succession is understood in terms of radial distance. Advantageously, the various aforementioned elements do not overlap radially, that is to say that they are successively one under the other.

According to another aspect of the invention, there is a plane perpendicular to the axis of rotation which intersects both the input clutch and the output clutches.

According to an additional characteristic of the invention, the input clutch and / or the first output clutch comprise:

- an input disc holder integral in rotation with the torque input element for the input clutch, and integral in rotation with the input web for the first output clutch,

- an output disc holder integral in rotation with the input web for the input clutch, and in rotation with the first output element for the first output clutch, and

- A multi-disc assembly comprising at least one friction disc integral in rotation with one of the input and output disc carriers, at least two plates respectively disposed on either side of each friction disc, integral in rotation on the other, input and output disc holders and friction linings arranged between the plates and a friction disc, the input clutch and / or the first output clutch describing a disengaged position and a position clutch in which said plates and the friction disc pinch the friction linings so as to transmit a torque between the input disc holder and the output disc holder.

According to an additional aspect of the invention, the input disc holder and the output disc holder of each of the input and output clutches have radial orifices distributed circumferentially around the axis X and intended to allow a circulation of the cooling fluid radially outward through the multidisk assembly of each of the clutches from the outlet orifice of the fluid line located in the protective casing.

According to another aspect of the invention, the device further comprises:

- an actuating member associated with the input clutch,

- an actuator associated with the first output clutch and

- an actuator associated with the second output clutch, said actuators associated with the first and second output clutches being able to be arranged in a box of the gearbox. The actuators associated with the first and second output clutches belonging to the hydraulic control system.

According to a particular embodiment, the actuating members associated with the first and second output clutches can be stacked radially.

According to one aspect of the invention, each actuator of the present invention may comprise an annular piston mounted to slide axially outside an internal tube, the piston and the tube forming an actuation chamber. The actuating member may also include a rotary stop carried by the piston and cooperating with the force transmitting member. This actuator is also called a "CSG" type actuator ("Concentric Slave Cylinder"). The operating chamber can be sealed and filled with oil. The piston and tube are fixed in rotation so that the actuation chamber and the oil do not rotate.

According to one aspect of the invention, the rotary stop can be a bearing, in particular a rolling bearing. The rolling bearing may include an inner ring fixed to the piston, an outer ring bearing against the force transmission member and rolling bodies interposed between the inner ring and the outer ring. Preferably, the rolling bodies can be balls.

Each piston can be of revolution around the axis of rotation.

The shapes of the piston and / or of the actuator being thus chosen so that the clutch and its actuator can stack radially which contributes to the axial compactness of the device.

According to another aspect of the invention, the device further comprises a force transmission member for each of the input clutch, the first output clutch and the second output clutch, each force transmission member being movable axially to transmit the actuating force from the actuating member to the associated clutch.

Each force transmission member may have a curved outer radial end defining a support surface for exerting the axial force on the multidisk assembly. Each force transmission member may have an inner radial end with which it cooperates with the associated actuating member.

This support surface can come to bear on the end plate of the multidisk assembly. The support surface can be continuous. The outer radial end can be a continuous crown so that the support surface is continuous. The outer radial end may comprise a plurality of fingers of axial extension and distributed around the axis so that the bearing surface is discontinuous.

Each force transmission member, in particular the force transmission member of the input clutch, may have three elbows between which are interposed planar portions. This allows axially compact actuation.

According to another aspect of the invention, the device further comprises an intermediate element arranged between the torque input element on the one hand and the first torque output element or the torque output elements on the other hand , in the sense of torque transmission, the intermediate element comprising an electrical connection area capable of being linked in rotation with an electrical machine rotating about an axis parallel to the axis of rotation X.

According to one aspect of the invention, the electrical connection area is axially offset from the input clutch and / or the output clutches. The electric machine is then called "off-line".

The electrical connection area can be welded, riveted or come in one piece with the rest of the intermediate element.

This arrangement makes it possible to position the electric machine according to the space available in the vehicle's traction chain. This arrangement makes it possible in particular not to have to place the electric machine axially following the clutches, which would be negative for the axial compactness. This arrangement makes it possible in particular not to have to place the electric machine radially beyond the clutches, which would be negative for the radial compactness.

According to an additional aspect of the invention, the electrical connection zone of the intermediate element comprises a ring capable of being meshed directly by a pinion of the rotary electric machine.

According to another characteristic of the invention, the crown has a helical toothing of shape complementary to the pinion of the rotary electric machine.

Alternatively, a chain or belt can be used to connect the rotating electrical machine to the electrical connection area.

According to one aspect of the invention, the electrical connection area can be axially offset from the hydraulic control system. Alternatively, the electrical connection zone can be radially in line with the hydraulic control system.

As a variant, provision may be made for the intermediate element to define a rotor support for an electric machine rotating around the axis of rotation. The electric machine is then "in-line".

According to the invention, the clutches, namely the input clutch and the first and second output clutch, can be of the multi-disc type.

According to a characteristic of the invention, the input and output clutches are wet. The clutches being contained in at least one sealed chamber filled with a fluid, in particular oil. For the purposes of the present application, a wet clutch is a clutch which is suitable for operating in an oil bath.

The invention will be better understood, and other objects, details, characteristics and advantages thereof will appear more clearly during the following description of a particular embodiment of the invention, given solely by way of illustration and not limiting, with reference to the appended figure.

Figure 1 is a sectional view of the torque transmission device according to an embodiment of the invention.

In connection with FIG. 1, there is a torque transmission device 1 comprising:

a torque input element 2, in rotation about an axis of rotation X, capable of being coupled in rotation to a crankshaft of a heat engine (not shown),

- a first torque output element 3, capable of being coupled in rotation to a first input shaft of a gearbox (not shown),

- a second torque output element 4, capable of being coupled in rotation to a second input shaft of a gearbox (not shown) and

- An input web 5 arranged between the torque input element 2 and the first and second output elements 3, 4 of torque within the meaning of the present invention.

In the example considered, the second output element 4 is arranged in parallel with the first output element 3 in the direction of the torque transmission. Each of these elements rotates around an axis of rotation X of the device.

The first and second output elements 3, 4 respectively comprise a first and second output interface 3a, 4a whose internal periphery is grooved and able to cooperate, respectively with a first and a second gearbox shaft.

A torsion damper device (not shown) can be positioned between the crankshaft of the engine and the torque input element 2.

In the example considered, the device further comprises an input clutch 10 arranged between the torque input element 2 and the input web 5 in the direction of the torque transmission.

The input clutch 10 selectively and frictionally couples the torque input element 2 and the input web 5 and includes:

- an input disc holder 11 integral in rotation with the torque input element 2,

- an output disc holder 12 integral in rotation with the entry veil 5 and

- A multi-disc assembly 13 comprising several friction discs, here four, integral in rotation with the outlet disc holder 12, several plates respectively arranged on either side of each friction disc, integral in rotation with the disc holder inlet 11 and friction linings arranged between the plates and a friction disc, fixed on each side of the friction discs, the clutch 10 describing a disengaged position and a engaged position in which said plates and the friction disc pinch the linings friction so as to transmit a torque between the input disc holder and the output disc holder.

Each disc holder 11, 12 synchronizes in rotation the set of plates and the set of friction discs. Each disc holder 11, 12 has a cylindrical skirt on which the plates and the friction discs are mounted.

The friction discs of the multidisc assembly 13 cooperate with the cylindrical skirt of the input disc holder 11 along their radially inner periphery by splines. The friction discs are therefore radially outside the cylindrical skirt.

The plates of the multidisc assembly 13 cooperate with the cylindrical skirt of the outlet disc holder 12 along their radially outer periphery by splines. The plates are therefore radially inside the cylindrical skirt.

In the example considered, the device also comprises a first output clutch 20 which selectively and frictionally couples the input web 5 and the first output element 3.

Thus, the first output clutch 20 comprises:

- an entry disc holder 21, integral in rotation with the entry veil,

an output disc holder 22 integral in rotation with the first output element 3 and,

- A multi-disc assembly 23 comprising several friction discs, here three, integral in rotation with the outlet disc holder 22, several plates respectively arranged on either side of each friction disc, integral in rotation with the disc holder inlet 21 and friction linings arranged between the plates and a friction disc, fixed on each side of the friction discs, the clutch 20 describing a disengaged position and a engaged position in which said plates and the friction disc pinch the linings friction so as to transmit a torque between the input disc holder and the output disc holder.

Each disc holder 21, 22 comprises a cylindrical skirt on which the plates and the friction discs are mounted.

The friction discs of the multidisc assembly 23 cooperate with the cylindrical skirt of the outlet disc holder 22 along their radially outer periphery by splines. The friction discs are therefore radially inside the cylindrical skirt.

The plates of the multidisc assembly 23 cooperate with the cylindrical skirt of the input disc holder 21 along their radially outer periphery by splines. The plates are therefore radially inside the cylindrical skirt.

In the example considered, the device 1 comprises a second output clutch 30, which selectively and frictionally couples the input web 5 and the first output element 4.

The second output clutch 30 includes:

- an entry disc holder 31 integral in rotation with the entry veil 5,

an output disc holder 32 integral in rotation with the second output element 4 and,

- A multi-disc assembly 33 comprising several friction discs, here four.

The multi-disc assembly 33 has the same technical characteristics as the multi-disc assembly of the clutch 20.

Commonly to the two clutches 10, 20 and 30, the linings can be fixed to the friction discs, in particular by gluing, in particular by riveting, in particular by overmolding. As a variant, the linings are fixed to the plates.

Each disc holder 11, 12, 21, 22, 31, 32 can synchronize in rotation all of the plates or all of the friction discs.

According to one aspect of the invention, the plates can be secured in rotation to the input disc holder 11, 21, 31 and the friction discs can be secured to the outlet disc holder 12, 22, 32. As a variant, the plates can be integral in rotation with the output disc holder 12, 22, 32. The discs can be secured in rotation with the input disc holder 11, 21, 31.

The clutches are of the wet type and comprise between two and seven friction discs, preferably four friction discs. Such multi-disc clutches make it possible to limit the radial height and limit the axial extent.

The output clutches 20, 30 can be arranged so as not to be simultaneously in the same engaged configuration. However, they can simultaneously be configured in their disengaged position.

In the example considered, the second output clutch 30, the first output clutch 20 and the input clutch 10 succeed one another radially in proximity to the axis X. There is a plane perpendicular to the axis of rotation which cuts both the output clutches 20, 30 and the input clutch 10.

Advantageously, the entry veil 5 is fixed in rotation to the entry disc holder 21 of the first exit clutch 20, by means of a splined connection and a circlip.

In the example considered, the device 1 also comprises a protective casing 46 arranged to at least partially envelop the torque input element 2, the torque output element 3, the input clutch 10, the output clutch 20 and the input web 5.

The protective casing 46 is composed of a front cover 25 situated opposite the internal combustion engine, a rear cover 26 situated opposite the gearbox BV and a central element 27 connecting the front cover 25 and the rear cover 26. The front cover 25, the central element 27 and the rear cover 26 are fixed to each other by fixing means, for example of the screw or rivet type visible in FIGS. 13 and 14. As a variant, the central element 27 can be integrated at least partially into one of the two covers. The protective casing 22 is fixed to the internal combustion engine by means of fixing means, for example of the screw or rivet type. Advantageously, the front cover 25 can be fixed to the internal combustion engine by means of fixing means, for example of the visible screw or rivet type.

In the example considered, the fluid line 37 comes from material, that is to say in one piece with the protective casing 46. Advantageously, the fluid line 37 comes from material with the front cover 25 of the protective housing 46.

In the example considered, the front cover 25 of the protective casing 46 consists of a radial wall 46a and an axial portion 46b and has a general shape substantially in "L" shape, the base of the "L" being located in the side of the axis of rotation X.

In the example considered, the entire front cover 25 of the protective casing 46 is crossed by the fluid line. Consequently, the fluid pipe follows the shape of the front cover and, like the front cover 25, has a generally substantially "L" shape, the base of the "L" being situated on the side of the axis of rotation X.

In the example considered, the fluid line 37 extends between an inlet port 38 and an outlet port 39, the inlet port 38 being located in the radial wall 46a and the outlet port 39 in the axial portion 46b.

The inlet port 38, the first outlet clutch 20, the first inlet clutch 10 and the outlet port 39, succeed one another radially in proximity to the axis X. Thus the outlet port of the pipe 37 is located near the input clutch.

In the example considered, the fluid line 37 specifically feeds the input clutch 10. Indeed, unlike many devices of the prior art in which the input clutch is supplied with fluid after the clutches of output, the device of the present invention has the advantage of providing a specific cooling system to the input clutch, the latter being the first clutch supplied with fluid from the fluid line 37.

In the example considered, the device 1 comprises an actuating member 40 and a force transmitting member 41 associated with the input clutch 10. A member for holding the disengaged position can be provided to push the member force transmission 41 of the input clutch 10. The input clutch is of the “normally open” type.

The force transmitting member 41 is axially movable to transmit the actuating force from the actuating member 40 to the input clutch 10. The force transmitting member exerts an axial force on the multidisk assembly 13 for moving the platters towards the discs. 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 axial force on the multidisc assembly, continuous or discontinuous in the example considered.

The force transmission member 41 of the input clutch 10 has three elbows between which are interposed planar portions. This allows axially compact actuation. This shape also makes it possible to orient and guide the fluid from the outlet orifice 39 of the pipe 37 to the inlet clutch 10, and more particularly to the multidisk assembly 13 of the clutch d 'entry 10.

The actuator 40 comprises an annular piston 42 slidably mounted. The piston 42 and the front cover 25 of the casing 46 together form an actuation chamber 43. The actuation member 40 comprises a rotary stop, which here is a rolling bearing 44, carried by the piston 42 and cooperating with a inner radial end of the force transmission member 41.

The fluid pressures associated with the “engaged” and “disengaged” positions are the pressures of the actuation chamber 43.

The rolling bearing 44 includes an outer ring fixed 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 around the axis of rotation X.

In the example considered, the clutches 10, 20, 30 are arranged in a sealed chamber filled with oil, the protective casing 46 partially defines this sealed chamber.

In the example considered, the device 1 comprises a rolling member supporting the input element 47, here a ball bearing. The rolling element supporting the input element 47 is disposed between the radial end of the protective casing 46, in particular the axial portion 46b and an axial portion of the input element 2. A circlip is provided on the fixed portion of the input element 2 in order to axially block the rolling member 47.

In the example considered, the fluid line 37 has an axially oriented outlet port 39. Advantageously, the outlet orifice 39 is located axially between the rolling member supporting the input element 47 and the input disc port 11 of the input clutch.

In the example considered, the orifice 38 is located to the right of the multidisk assembly 13 of the input clutch. This makes it possible to obtain a more direct and simplified supply from the fluid line 37.

There is a plane perpendicular to the axis of rotation which intersects both the input clutch 10, the actuating member 40 of the input clutch 10 and the rolling member 47 supporting the input element 2.

In the example considered, a rolling member 49 supports the entry veil 5. The rolling member 49 is here a ball bearing, and is arranged radially between the entry veil 5 and the entry element of torque 2.

In the example considered, the device 1 also comprises a hydraulic control system 80 comprising:

an actuating member 50 and a force transmitting member 51 associated with the first output clutch 20. The force transmitting member 51 is axially movable to transmit the actuating force from the actuating member 50 to the input clutch 20.

- An actuating member 60 and a force transmitting member 61 associated with the second output clutch 30. The force transmitting member 61 is axially movable to transmit the actuating force from the actuating member 60 to the second output clutch 30.

A member for holding in the disengaged position can be provided to push the force transmission members 51, 61 from the output clutches 20, 30. The output clutches 20, 30 are of the “normally open” type.

These actuating members 50, 60 use the same elements as those detailed in connection with the actuating member 40 of the input clutch, except that they are housed in the same casing and form only one single and same component conventionally called hydraulic control system or double concentric actuator. The shapes of the pistons and / or of 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 actuators 50, 60 of the output clutches 20, 30, in particular their actuation 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 elements 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 multidisk assemblies, 23, 33. The actuation is thus "pushed" type.

In the example considered, 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 axis X so that their bearing surface is discontinuous. In the example considered, the fingers 53 pass here through openings formed 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 85.

In the example considered, the intermediate element 85 comprises an electrical connection area 65 capable of being linked in rotation with a rotary electrical machine (not shown) around an axis parallel to the axis of rotation.

The electrical connection area 65 is here axially offset from the clutches 10, 20, 30. The electrical machine is said to be "off-line" because it is not concentric with the transmission shaft but on a parallel shaft. The electrical connection area 65 is able to cooperate directly with a pinion of the rotary electrical machine.

The electrical connection zone 65 can be produced in the form of a crown capable of being meshed directly by a pinion or indirectly (belt, chain, etc.) of the rotary electric machine (not visible). The crown can have a helical toothing of complementary shape to the pinion of the rotary electric machine.

In the example considered, a support bearing member 48 of the input disc carrier 21, here a ball bearing, is disposed axially between the actuating members 50, 60 of the output clutches on the one hand and the elements of exit 3, 4 on the other hand.

In the example considered, the device also comprises a first, a second and a third axial rolling member 70, 71, 72. The first axial rolling member 70 is positioned axially between the first and second outlet disc ports 22, 32 The second axial rolling member 71 is positioned axially between the second outlet disc carrier 32 and the support 81 of the hydraulic control system 80. The third axial rolling member 72 is positioned axially between the inlet web 5 and the first output disc holder 22.

Although the invention has been described in connection with several particular embodiments, it is obvious that it is in no way limited thereto and that it includes all the technical equivalents of the means described as well as their combinations if these are within the scope of the invention.

In the claims, any reference sign in parentheses cannot be interpreted as a limitation of the claim.

Claims (10)

1. Torque transmission device (1), in particular for a motor vehicle, comprising: - a torque input element (2) rotating around an axis (X), capable of being coupled in rotation to a crankshaft of a heat engine, - a first torque output element (3), capable of being coupled in rotation to a first input shaft of a gearbox, - an input web (5) arranged between the torque input element (2) and the torque output element (3), in the sense of the torque transmission, - an input clutch (10) supplied by at least one fluid line (37), selectively and frictionally coupling the torque input element (2) and the input web (5), - a first output clutch (20), selectively and frictionally coupling the input web (5) and the first torque output element (3), and - a protective casing (46) arranged to at least partially envelop the torque input element (2), the torque output element (3), the input clutch (10), the clutch outlet (20) and the inlet web (5), characterized in that the fluid line (37) is made in one piece with the protective casing (46). 2. Device (1) for transmitting torque according to claim 1, characterized in that the protective casing (46) is composed of a front cover (25) located opposite the internal combustion engine, of a rear cover (26) located opposite the gearbox (BV) and a central element (27) connecting the front cover (25) and the rear cover (26). 3. Device (1) for transmitting torque according to the preceding claim, characterized in that the fluid line (37) is made in one piece with the front cover (25) of the protective casing (46). 4. Device (1) for transmitting torque according to any one of claims 2 to 3, characterized in that the front cover (25) of the protective casing (46) is composed of a radial wall (46a) and d 'an axial portion (46b) and has a general shape substantially in "L", the base of the "L" being located on the side of the axis of rotation (X). 5. Device (1) for torque transmission according to torque according to the preceding claim, characterized in that the fluid line (37) extends between an inlet orifice (38) and an outlet orifice (39), l 'inlet port (38) being located in the radial wall (46a) and the outlet port (39) in the axial portion (46b). 6. Device (1) for transmitting torque according to the preceding claim, characterized in that the inlet port (38), the first outlet clutch (20), the first inlet clutch (10) and the outlet orifice (39), follow one another radially in proximity to the axis (X). 7. Device (1) for transmitting torque according to any one of the preceding claims, characterized in that it further comprises a rolling member supporting the input element (47) disposed between the radial end of the protective casing (46) and an axial portion of the input element (2). 8. Device (1) for transmitting torque according to any one of the preceding claims, characterized in that it also comprises a second output element (4), capable of being coupled in rotation to a second input shaft of a gearbox, a second output clutch (30), selectively and frictionally coupling the input web (5) and the second torque output element (4). 9. A device (1) for transmitting torque according to claim 8, characterized in that the first output clutch (20), the second output clutch (30) and the input clutch (10) succeed one another radially. approaching the axis (X). 10. Device (1) for transmitting torque according to any one of the preceding claims, characterized in that it further comprises an intermediate element (85) arranged between the torque input element (2) and the first torque output element (3), in the direction of torque transmission, the intermediate element (85) comprising an electrical connection zone (65) capable of being linked in rotation with an electrical machine rotating about a parallel axis to the axis of rotation (X).