FR3078377A1 - TRANSMISSION DEVICE FOR A HYBRID VEHICLE - Google Patents

Abstract

The invention relates to a device (1) for transmitting torque, in particular for a motor vehicle, comprising: - a torque input element (2) rotating about an axis (X), able to be coupled in rotation to a crankshaft of a heat engine, - a first torque output element (3), adapted to be rotatably coupled to a first input shaft of a gearbox, - an intermediate element (5) arranged between torque input member (2) and the torque output member (3), in the torque transmission sense, the intermediate member (5) comprising an electrically connectable connection area (65) in rotation with a rotating electrical machine about an axis parallel to the axis of rotation (X), - an input clutch (10), selectively and frictionally coupling the torque input element (2) and the intermediate element (5), - a first output clutch (20), selectively and frictionally coupling the elem intermediate member (5) and the first torque output member (3), - an actuating member (40) associated with the input clutch (10), - an actuating member (50) associated with the first clutch output (20) and being adapted to be disposed in a housing of the gearbox, a rolling member (48) supports the electrical connection area (65) and is arranged radially between the electrical connection area (65) and the actuating member (50) associated with the first output clutch (20).

Description

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.

It relates more precisely 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 state of the art, hybrid type motor vehicles are known comprising a torque transmission device disposed between a heat engine and a gearbox, a rotary electrical machine as well as a clutch enabling coupling or uncoupling. in rotation a crankshaft of the heat engine to a rotor of the rotating electric machine. Thus, it is possible to shut down the heat 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 excess energy to the heat engine to assist it or prevent it from stalling. When the engine is running, the electric machine can act as an alternator. The rotating electric machine can also drive the vehicle independently of the heat 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 electric machine is offset from the axis of rotation of the rotation device. torque transmission.

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 of the torque transmission device.

Another problem with this type of architecture is found in the connection area of the rotating electrical machine and the torque transmission device. Indeed, it is necessary to create a durable and reliable mechanical connection between the rotating electric machine and the torque transmission device. This mechanical connection is often poor in terms of accuracy due to the stacking of many parts such as, for example, the supports of different clutches (generally three clutches) constituting the torque transmission device.

The invention aims to remedy the aforementioned problems by benefiting from a torque transmission device making it possible to reconcile the requirements of axial and radial compactness while guaranteeing an optimal mechanical connection between the rotary electrical machine and the torque transmission device.

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, 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 intermediate element arranged between the torque input element and the torque output element, in the sense of the torque transmission, the intermediate element comprising an electrical connection zone capable of being linked in rotation with a machine electric rotating around an axis parallel to the axis of rotation,

- 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,

- an actuating member associated with the input clutch,

- an actuating member associated with the first output clutch and being able to be disposed in a gearbox housing, a rolling member supports the electrical connection area and is arranged radially between the electrical connection area and the actuator associated with the first output clutch.

Thanks to this architecture, the forces generated by the rotary electrical machine are directly taken up by the gearbox housing, which simplifies the chain of ribs of the torque transmission device.

According to one aspect of the invention, the rolling member comprises an inner ring and an outer ring, said inner ring is in contact with the actuating member associated with the first output clutch and said outer ring is in contact with the electrical connection area.

According to an alternative embodiment of the invention, the rolling member comprises an inner ring and an outer ring, said inner ring is in contact with the gearbox housing and said outer ring is in contact with the connection zone electric.

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

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 another characteristic of the invention, the electrical connection zone of the intermediate element comprises a crown capable of being meshed directly by a pinion of the rotary electric machine.

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

According to one aspect of the invention, the electrical connection zone can be radially in line with the actuating member associated with the first output clutch.

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

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

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

- an output disc carrier integral in rotation with the intermediate element 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 another characteristic of the invention, the device comprises a second torque 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 intermediate element and the second torque output element and an actuating member associated with the second output clutch.

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

According to one aspect of the invention, the first and second output elements may comprise a web whose internal periphery is grooved and capable of cooperating, respectively with a first and a second gearbox shaft.

The invention will be better understood, and other objects, details, characteristics and advantages thereof will appear more clearly during the following description of several particular embodiments of the invention, given solely by way of illustration and without limitation. , with reference to the appended figures.

- Figure 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,

- Figure 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 torque transmission device,

- Figure 5 is a perspective view of the electrical connection area.

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 intermediate element 5 arranged between the torque input element 2 and the first 3 and second 4 torque output element, in the sense of the torque transmission.

A torsional damping device can be positioned between the crankshaft of the heat engine and the torque input element 2.

In the example considered, the first 3 and second 4 output elements comprise a web whose internal periphery is grooved and able to cooperate, respectively with a first and a second gearbox shaft. In the example considered, the first and second box shafts are coaxial.

In the example considered, the device 1 also comprises an input clutch 10 which selectively and frictionally couples the input element 2 and the intermediate element 5.

The input clutch 10 includes:

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

- an output disc holder 12 integral in rotation with the intermediate element 5 and,

- A multi-disc assembly 13 comprising several friction discs, here four, integral in rotation with the input disc holder 11, several plates respectively arranged on either side of each friction disc, integral in rotation with the output disc holder 12 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 friction 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 each 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 selectively and frictionally coupling the intermediate element 5 and the first output element 3.

The first output clutch 20 includes:

- an input disc holder 21 integral in rotation with the intermediate element 5,

an output disc holder 22 integral in rotation with the first output element 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 each has 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, selectively and frictionally coupling the intermediate element 5 and the second output element 4.

The second output clutch 30 includes:

- an input disc holder 31 integral in rotation with the intermediate element 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, integral in rotation with the output disc holder 32, several plates respectively arranged on either side of each friction disc, which are rotatable with the disc holder d entry 31 and friction linings arranged between the plates and a friction disc, fixed on each side of the friction discs, the clutch 30 describing a disengaged position and a engaged position 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.

Each disc holder 31, 32 each has a cylindrical skirt on which the plates 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 along their radially outer periphery by splines. The friction discs are therefore radially inside the cylindrical skirt.

The plates of the multidisc assembly 33 cooperate with the cylindrical skirt of the input disc holder 31 along their radially outer periphery by splines. The plates are therefore radially inside the cylindrical skirt.

Commonly to the three clutches 10, 20, 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.

In the example considered, 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 output 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.

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.

The actuator 40 comprises an annular piston 42 mounted to slide axially outside an internal tube, the piston 42 and the tube forming an actuation chamber 43. The actuator 40 comprises a rotary stop , which here is a rolling bearing 44, carried by the piston 42 and cooperating with an 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 tube of the actuating member 40 of the input clutch is formed in a transverse partition 46 which defines a network for supplying fluid to the actuating member 40 as well as the clutch cooling circuit 10, 20, 30.

In the example considered, the clutches 10, 20, 30 are arranged in a sealed chamber filled with oil, the transverse partition 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 transverse partition 46 and an axial portion of the input element 2. A circlip is formed on the fixed portion of the input element 2 in order to axially block the rolling member 47.

In the example considered, a rolling 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 element 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 element 2 and said outer ring 49b is in contact with the intermediate element 5. L the 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 disposed axially between the actuating member 40 associated with the input clutch 10 and the first torque output element 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 produced in the form a hook enabling the rolling member 49 to be axially blocked. A circlip is formed on the fixed portion of the input element 2 in order to axially block the rolling member 49.

The rolling member 49 thus makes it possible to center the intermediate element 5 and to ensure the resumption 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 actuating member of the input clutch 40 and the bearing member supporting the input element 47 succeed one another radially. More precisely, in this example considered, the aforementioned elements are stacked radially in proximity to the axis X.

In the example considered, the device 1 also comprises 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 force d actuation of the actuating member 50 towards the input clutch 20.

The device 1 also includes 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 of the member actuation 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 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 are housed in a box 80 of the gearbox.

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. These fingers 53, 63 pass here through openings made 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.

In the example considered, the intermediate element 5 also 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 X. The connection area electric 65 is here axially offset from the clutches 10, 20, 30. The electric machine is then called "off-line". The electrical connection area 65 is able to cooperate directly with a pinion of the rotary electrical machine.

The force transmission members 51, 61 of the output clutches 20, 30 are crossed by the intermediate element 5 to provide the connection area 65.

The intermediate element 5 comprises a plurality of protrusions 67 passing through openings of each force transmission member 51,61. The protuberances 67 are angularly offset with respect to the axis of rotation X and are eight in number

In the example considered, the electrical connection area 65 is located radially in line with the actuating members 50, 60 associated with the first 20 and second 30 output clutches.

A rolling member 48 supports the electrical connection area 65 and is arranged radially between the electrical connection area 65 and the actuating member 50 associated with the first output clutch 20. The rolling member 48 is here a bearing with 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 area 65.

In the example considered in FIG. 1, the rolling member 48 comprises an inner ring 48a and an outer ring 49b, said inner ring 48a is in contact with the gearbox 80 and said outer ring 48b is in 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 blocked by a shoulder made in the gearbox 80 of the gearbox and at least one circlip formed in a groove in the crown 90.

The electrical connection area 65 is produced in the form of a ring 90 capable of being meshed directly by a pinion of the rotary electrical machine (not visible). The crown 90 has a helical toothing of complementary shape to the pinion of the rotary electric machine. The crown 90 has two sides which are on each side of the helical toothing.

The crown 90 has at least one cavity 91 on the sidewall which is located opposite the intermediate element 5. The crown 90 in this case has eight cavities 91, that is to say a number complementary to the protuberances 67 of the intermediate element 5. The electrical connection area 65 and the intermediate element 5 therefore mesh with each other by cooperation of shapes. The cavities 91 thus 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 crown 90 and the intermediate element 5.

In the embodiment of Figure 1, the rolling member 48 is disposed between the inner diameter of the crown 90 and the housing 80 of the gearbox. This arrangement makes it possible to simply fix the rolling member 48 directly on the gearbox 80 while limiting the positioning tolerances.

Rolling members 70, preferably needle bearings, are provided between the intermediate element 5, the first output element 3, the second output element 4 to axially wedge these said elements together.

The device of FIG. 2 differs from that of FIG. 1 in terms of the positioning of the rolling member 48. In fact, in FIG. 2, the rolling member 48 comprises an inner ring 48a and an outer ring 48b, said inner ring 48a is in 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 precisely said inner ring 48a is in contact with the casing actuating members 50, 60 of the output clutches 20, 30.

In this second embodiment of the invention, the rolling member 48 is axially blocked by a shoulder formed in the envelope of the actuating members 50, 60 of the output clutches 20, 30 and at least one circlip formed in a groove in the crown 90.

The particularity of this second embodiment is that the rolling member 48 is installed directly on the envelope of the actuating members 50, 60 of the output clutches 20, 30, which are housed in the housing 80 of the gearbox. speeds. This makes it possible 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 device of FIG. 3 differs from FIG. 2 at the level of the axial locking of the rolling member 48. In fact, the rolling member 48 comprises an inner ring 48a and an outer ring 48b, said inner ring 48a is in 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 precisely, said inner ring 48a is in contact with the envelope of the actuating members 50, 60 of the output clutches 20, 30.

In this third embodiment of the invention, the rolling member 48 is axially blocked by a stop 81 of the gearbox 80 of the gearbox and at least one circlip formed in a groove in the crown 90.

The particularity of this third embodiment is that the rolling member 48 is installed on an element carried by the box 80 of the gearbox, that is to say the envelope of the actuating members 50, 60 output clutches 20, 30, which makes it possible to simply fix the rolling member 48 and potentially supply 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 gearbox 80 of the gearbox makes it possible to limit the tolerance of axial positioning of the gear of the pinion of the rotary electric machine and the crown 90 of the electrical connection area.

Figures 4 and 5 show the mechanical connection between the intermediate element 5 and the electrical connection area 65, in particular the ring 90. In Figure 4 are visible the plurality of protrusions 67. The protrusions 67 are angularly offset relative to the axis of rotation and are eight in number, which means that each protuberance 67 is angularly offset by 45 °. The protrusions 67 have a shape substantially in "Ω" projecting therefrom from the intermediate element 5. The protrusions 67 are capable of being inserted in a removable manner in the cavities 91 associated with the crown 90 visible in FIG. 5.

The cavities 91 are located on the side of the crown 90 which is located opposite the intermediate element 5. The crown 90 also has eight cavities 91 angularly offset with respect to the axis of rotation and are eight in number, this which means that each cavity 91 is angularly offset by 45 °. The cavities 91 have a “Ω” shape capable of receiving 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 5 0.5mm in order to compensate for any radial and / or angular misalignment between the crown 90 and the intermediate element 5.

The crown 90 is supported by the rolling member 48 which is itself supported by the envelope of the actuating members 50, 60 or by the housing 80 of the gearbox.

Alternatively and not shown, the protuberances 67 can be located on the crown 90 and the cavities 91 can be located on the intermediate element 5.

Although the invention has been described in conjunction 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 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 (9)

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 intermediate element (5) arranged between the torque input element (2) and the torque output element (3), in the sense of torque transmission, the intermediate element (5) comprising a zone electrical connection (65) capable of being linked in rotation with an electric machine rotating about an axis parallel to the axis of rotation (X), - an input clutch (10), selectively and frictionally coupling the torque input element (2) and the intermediate element (5), - a first output clutch (20), selectively and frictionally coupling the intermediate element (5) and the first torque output element (3), - an actuating member (40) associated with the input clutch (10), - an actuating member (50) associated with the first output clutch (20) and being able to be arranged in a gearbox housing, characterized in that a rolling member (48) supports the connection area electrical (65) and is arranged radially between the electrical connection area (65) and the actuating member (50) associated with the first output clutch (20). 2. Device (1) according to claim 1, characterized in that the rolling member (48) comprises an inner ring (48a) and an outer ring (49b), said inner ring (48a) is in contact with a housing (80) of the gearbox and said outer ring (48b) is in contact with the electrical connection area (65). 3. Device (1) according to claim 1, characterized in that the rolling member (48) comprises an inner ring (48a) and an outer ring (48b), said inner ring (48a) is in contact with the actuator (50) associated with the first output clutch (20) and said outer ring (49b) is in contact with the electrical connection area (65). 4. Device (1) according to one of the preceding claims, characterized in that the electrical connection zone (65) is axially offset from the input clutch (10) and / or from the first output clutch (20) . 5. Device (1) according to any one of the preceding claims, characterized in that the electrical connection zone (65) of the intermediate element (5) comprises a ring (90) capable of being meshed directly by a pinion of the rotating electric machine. 6. Device (1) according to the preceding claim, characterized in that the crown (90) has a helical toothing of complementary shape to the pinion of the rotary electric machine. 7. Device (1) according to any one of the preceding claims, characterized in that the input clutch (10) and / or the first output clutch (20) comprise: - An input disc holder (11, 21) integral in rotation with the input element (2) for the input clutch (10), and integral in rotation with the intermediate element (5) for the first output clutch (20), - an output disc holder (12, 22) integral in rotation with the intermediate element (5) for the input clutch (10), and integral in rotation with the first output element (3) for the first clutch outlet (20), and - a multi-disc assembly (13, 23) comprising at least one friction disc integral in rotation with one of the inlet (11, 21) and outlet (12, 22) disc holders, at least two plates respectively arranged on each side of each friction disc, integral in rotation with the other of the inlet (11, 21) and outlet (12, 22) disc holders and friction linings arranged between the plates and a friction disc, the input clutch (10) and / or the first output clutch (20) describing a disengaged position and a engaged position in which said plates and the friction disc pinch the friction linings so as to transmit a torque between the input disc holder (11, 21) and the output disc holder (12, 22). 8. Device (1) according to any one of the preceding claims, characterized in that the device comprises a second torque output element (4), capable of being coupled in rotation to a second input shaft of a box gear, a second output clutch (30), selectively and frictionally coupling the intermediate element (5) and the second torque output element (4) and an actuating member (60) associated with the second output clutch (30). 9. Device (1) according to any one of the preceding claims, characterized in that the device comprises a force transmission member (41,51, 61) for each of the input clutch (10), from the first output clutch (20) and the second output clutch (30), each force transmission member (41, 51, 61) being axially movable to transmit the actuating force from the actuator (40, 50, 60) towards the associated clutch.