WO2021239693A1

WO2021239693A1 - Multidisc-type wet double clutch

Info

Publication number: WO2021239693A1
Application number: PCT/EP2021/063822
Authority: WO
Inventors: Guillaume VUAROQUEAUX; Olivier Doremus; Fabien LEBEAU; Rabah Arhab; Arnaud DOLE; Jean-François BOUGARD; Laurent Caumartin
Original assignee: Valeo Embrayages
Priority date: 2020-05-28
Filing date: 2021-05-25
Publication date: 2021-12-02
Also published as: CN219413322U; DE112021003005T5; FR3110879A1; FR3110879B1

Abstract

Wet double clutch (1) for a torque transmission system, comprising: a torque input web (2) arranged to be kinematically linked with a heat engine around an axis of rotation (X); a first clutch (E1) and a second clutch (E2), both of the multi-disc type, arranged radially one above the other and aligned in a plane (P) perpendicular to the axis of rotation (X); a torque input disc carrier (10, 20) common to the first clutch (E1) and the second clutch (E2) and connected for conjoint rotation with the torque input web (2), said carrier supporting a drive ring (80) arranged to engage with the rotor of the rotating electric machine, the wet double clutch being guided in rotation relative to the torque transmission system by means of axial and radial bearings (41, 42, 43, 44) arranged on either side of the plane (P).

Description

MULTI-DISC TYPE WET DOUBLE CLUTCH

[1] [The present invention relates to a wet double clutch for a hybrid type motor vehicle torque transmission system in which a rotating electric machine is arranged in the torque transmission chain.

[2] The present invention relates in particular to the field of torque transmission chains for motor vehicles, in particular arranged between a thermal motor and a gearbox in which a rotating electrical machine is arranged parallel to the main axis of the transmission.

[3] In the prior art, hybrid type motor vehicles are known comprising a wet double clutch type mechanism disposed between an internal combustion engine and a gearbox, coupled to a rotating electrical machine. According to this type of torque transmission chain, it is possible to shut off the internal combustion engine each time the vehicle stops and to restart it thanks to the rotating electrical machine. The rotating electric machine can also act as an electric brake or add extra energy to the internal combustion engine to assist it or prevent it from stalling. When the internal combustion engine is in operation, the electrical machine can act as an alternator.

[4] Such a rotary electric machine can be arranged in line with the wet double clutch, that is to say that the rate of rotation of the rotor of the rotary electric machine is coincident with the axis of rotation of the clutches as described in the document DE102012006730 A1. In this so-called "on-line" architecture, the rotor of the rotating electrical machine is attached directly to the torque input disc carrier of the wet double clutch, which greatly increases the radial size.

[5] A technical solution making it possible to reduce the radial size consists in shifting the rotating electrical machine relative to the main axis of the transmission, that is to say that the rate of rotation of the rotor of the rotating electrical machine is parallel to the axis of rotation of the clutches as described in document FR3060682 A1. In this architecture, the rotorde rotating electrical machine is kinematically connected with the torque input disk carrier of the double clutch via a toothed drive ring. The torque input disc carrier is supported in rotation by a ball bearing arranged in the center of the double clutch, the ball bearing resting on the actuating device of the clutches.

[6] In this so-called "off-line" architecture, the toothed drive ring is axially offset from the ball bearing whose function is to support the axial and radial loads within the wet double clutch. The central positioning of this ball bearing allows nutation movements of the wet double clutch which, combined with the cantilevered positioning of the toothed drive ring, increases the backlash at the level of the kinematic connection with the machine rotor. rotating electric. This has the effect of generating significant noise within the transmission. The guiding of the wet double clutch is therefore not satisfactory.

[7] The invention aims to improve the existing design by benefiting from a wet double clutch making it possible to reconcile the requirements of axial and radial compactness of the hybrid transmission while ensuring good stability of the ring gear of the wet double clutch. .

[8] For this purpose, the invention provides, according to one of its aspects, a wet double clutch for a torque transmission system comprising:

- a torque input web arranged to be kinematically linked with a heat engine around an axis of rotation X;

a first clutch and a second clutch, respectively of the multi-disc type, controlled to selectively couple the heat engine and a rotating electric machine to a first driven shaft and to a second driven shaft, the first and second clutches being arranged radially to each other above the other and aligned along a plane P perpendicular to the axis of rotation X;

a torque input disc carrier common to the first clutch and to the second clutch, integral in rotation with the torque input web, and supporting a drive ring arranged to mesh with the rotorde the rotating electrical machine; the wet double clutch being remarkable in that it is arranged to be guided in rotation with respect to the torque transmission system by means of a first pair of axial and radial bearings resting on the torque input web, arranged on one side of the plane P and a second pair of axial and radial bearings resting on the common torque input disc holder, arranged on the other side of the plane P. [9] Such a wet double clutch has the advantage, thanks to the arrangement of the first pair of radial and axial bearings and of the second pair of radial and axial bearings on either side of the plane P, of being stable in rotation. while facilitating the integration of the wet double clutch within the torque transmission system. The nutation movements of the wet double clutch are reduced in particular thanks to a substantially symmetrical guide of the bearings. The noise at the level of the engagement of the drive ring gear with the rotorde of the rotating electrical machine is thus reduced.

[10] Preferably, the plane P can pass through a friction disc of the multi-disc assembly of the first clutch and a friction disc of the second clutch multi-disc assembly.

[11] Also, the wet double clutch can be remarkable in that it is arranged to be stopped axially in the two directions with respect to the torque transmission system by means of the axial bearings arranged on either side of the plane P The axial loads are generated by the force for actuating the clutches in one direction and in the other direction by the resultant of force applied to the drive ring which generally comprises helical teeth.

[12] Advantageously, the wet double clutch can include housings for the support of the axial bearings oriented axially outwards, in a direction opposite to the plane P. This improves the stability of the wet double clutch.

[13] Preferably, the torque input web may include a first housing for the first radial bearing, the first housing having an outer cylindrical bearing surface along the X axis for the support of the first radial bearing.

[14] Preferably, the torque input web can comprise a second housing for the first axial bearing, the second housing comprising a wall oriented perpendicular to the X axis for the axial support and a cylindrical bearing surface for the centering of the first axial bearing.

[15] Preferably, the common torque input disk carrier may comprise a third housing for the second axial bearing, the third housing comprising a wall oriented perpendicular to the X axis for the axial support and a surface of cylindrical support for centering the second axial bearing.

[16] Preferably, the common torque input disc carrier may comprise a fourth housing for the second radial bearing, the fourth housing comprising an external cylindrical bearing surface along the X axis for the bearing of the second radial bearing.

[17] Such a wet double clutch has the advantage, thanks to the distribution of the four housings on the torque input web and the common torque input disc carrier of being stable in rotation while facilitating the integration of the wet double clutch into the torque transmission system.

[18] Advantageously, the first housing and the second housing of the torque input veil can be contiguous. In this way, the installation of the first pair of axial and radial bearings reduces the axial and radial bulk of the guiding function of the wet double clutch within the torque transmission chain.

[19] Advantageously, the third housing and the fourth housing of the common torque input disc holder can be contiguous. In this way, the placement of the second pair of axial and radial bearings reduces the axial and radial bulk of the guiding function of the wet double clutch within the torque transmission chain.

[20] Preferably, the first housing of the torque input web can be disposed radially on a diameter D1 and the fourth housing of the common torque input disc holder can be disposed radially on a diameter D4, the diameters D1 and D4 being such that D1 x 0.8 <D4 <D1 x 1, 2.

[21] Preferably, the first housing of the torque input web and the fourth housing of the common torque input disc holder may be radially disposed on the same diameter.

[22] Advantageously, the second housing of the torque input veil and the third housing of the common torque input disc holder can be arranged opposite each other with respect to the plane P.

[23] Advantageously, the second housing of the torque input web and the third housing of the common torque input disc holder can be arranged axially at an equal distance from the plane P.

[24] Preferably, the drive ring can be attached to the common torque input disc holder and include external teeth kinematically linked with the rotating electrical machine. The rotating electric machine can thus be eccentric by means of the axis of rotation of the torque transmission chain.

[25] The external teeth may have a helical profile of a shape complementary to the pinion of the rotating electrical machine. [26] Alternatively, the teeth may have a straight profile of complementary shape to a chain or a belt used to connect the rotating electrical machine.

[27] According to a variant, the drive ring can be disposed radially beyond the first clutch and axially in the plane P.

[28] According to another variant, the drive ring can be offset axially with respect to the first clutch and disposed radially between the first clutch and the second clutch.

[29] Preferably, the common torque input disc carrier may comprise a central oil supply hub comprising a first annular cavity disposed on the side of the flange and arranged to receive an actuating piston of the first clutch and a second annular cavity arranged to receive an actuating piston for the second clutch, and at least one oil supply channel opening into one of the annular cavities of the clutches. Thanks to this wet double clutch architecture, the annular cavities form the control chambers of the clutches. The control chambers are concentric and radially arranged in the same plane, which facilitates the installation of wet clutches within the torque transmission chain.

[30] Preferably, the drive ring may include an internal cylindrical seat for the support of an actuating piston seal, the cylindrical seat partly forming the first annular cavity. This wet double clutch, according to the invention, has the advantage, by virtue of the use of an attached ring-shaped drive ring, of reducing manufacturing costs. This added annular part makes it possible to partially form the annular cavity at a lower cost.

[31] Advantageously, the drive crown can be fitted onto the flange of the central hub.

[32] Preferably, the drive ring and the torque input disc holder of the first clutch can be integrally connected in rotation, for example by means of a welded connection.

[33] Also, the wet double clutch can be remarkable in that it comprises a first balancing chamber of the first clutch associated with the first cavity and a second balancing chamber of the second clutch associated with the second cavity, the first balancing chamber being supplied with cooling fluid by at least one oil supply channel passing through the cylindrical portion and the flange.

[34] Advantageously, the central oil supply hub may comprise a cylindrical portion of axis X and a flange extending radially from the cylindrical portion, the oil supply channels of the first cavity and / or of the second cavity being distributed angularly around the axis of rotation X and pass radially through the flange. In this way, their integration into the wet double clutch and their achievements are facilitated. The axial size of such a wet double clutch is thus reduced.

[35] Advantageously, the oil supply channels of the first balancing chamber can be distributedangularly around the axis of rotation X and pass radially through the flange.

[36] Preferably, the oil supply channels for the first cavity, the second cavity and the first balancing chamber can be arranged in the same Q plane perpendicular to the X axis passing through the flange.

[37] Advantageously, a multi-disc clutch assembly can comprise at least one friction disc equipped with friction linings and integral in rotation with one of the input and output disc carriers, at least two plates respectively arranged in on either side of the at least one friction disc, integral in rotation with the other of the input and output disc carriers, the clutch operating between a disengaged position and an engaged position in which said plates and the friction disc clamp the friction linings so as to transmit torque between an input disc carrier and an output disc carrier.

[38] Advantageously, the drive ring can surround the outer periphery of the flange. It is thus possible to arrange the annular cavities associated with the two clutches radially in the same plane.

[39] Preferably, the oil supply channels can open onto the outer periphery of the flange and can be closed by the inner cylindrical bearing surface of the drive ring. In this way, it is possible to seal part of the oil supply channels without using other expensive components

[40] Preferably, the first clutch can be actuated by means of a first actuating piston, movable axially by means of the first annular cavity of the central hub between an engaged position and a disengaged position of the first clutch, the first piston actuation being controlled in motion by means of a control chamber partially delimited by the drive crown. In this way, the control chamber of the first clutch is placed as close as possible to the central oil supply hub, thus reducing leaks within the wet double clutch.

[41] Preferably, the second clutch can be actuated by means of a second actuating piston, movable axially relative to the second annular cavity of the central hub between an engaged position and a disengaged position of the second clutch, the second actuating piston being controlled in movement by means of a control chamber delimited in part by the cylindrical portion of the central hub. In this way, the control chamber of the second clutch is positioned as close as possible to the central oil supply hub thereby reducing leaks within the wet double clutch.

[42] Preferably, the oil supply channel can be produced by drilling successive conduits within the central hub, said conduits being open into one another and arranged to supply pressurized fluid to the control chamber of the clutches. . The fluid can be oil, for example transmission oil.

[43] The invention may have any of the characteristics described below in combination or taken independently of each other:

- the drive ring can be force-fitted on the flange of the central hub.

- the drive ring can be welded to the flange of the central hub.

- the drive ring and the torque input disc holder of the first clutch can be integrally linked in rotation, for example by means of a welded connection.

- the first cavity and the second cavity can be nested radially one above the other.

- The multi-disc assembly of the second clutch can be disposed radially between the first cavity and the second cavity. In this way, it is possible to exploit the internal space available within the wet double clutch and thus reduce the axial size.

- The torque input disc carrier of the second clutch and the central hub may be integrally connected in rotation, for example by means of a welded connection. - The oil supply channel of the balancing chamber can be produced by drilling successive pipes within the central hub, said pipes being open into one another and arranged to supply the cooling fluid chamber of balancing of the first clutch.

- the drive crown can block the oil supply channels passing radially through the flange of the central hub.

[44] Another subject of the invention, according to a second aspect, is a clutch kit comprising a wet double clutch incorporating all or part of the characteristics mentioned above, a first pair of radial and axial bearings and / or a second torque of radial and axial bearings.

[45] This torque cut-off clutch kit, according to the invention, has the advantage of being stable in rotation while facilitating the integration of the wet double clutch into the torque transmission system. The nutation movements of the wet double clutch are reduced in particular thanks to a substantially symmetrical guide of the bearings. This reduces the noise at the meshing of the drive ring with the rotorde of the rotating electrical machine.

[46] The supply of the first pair of radial and axial bearings and / or the second pair of radial and axial bearings can be carried out by the supplier of the wet double clutch or by the manufacturer of the motor vehicle itself.

[47] The invention also relates, according to a third aspect, to a torque transmission system for a motor vehicle comprising:

- a wet double clutch incorporating all or part of the characteristics mentioned above;

- a closing cover rotatingly supporting the wet double clutch;

- a first pair of axial and radial bearings interposed between the closing cover and the wet double clutch;

a transmission casing rotatingly supporting the wet double clutch, the transmission casing being integral with the closing cover; and

- a second pair of axial and radial bearings, interposed between the transmission housing and the wet double clutch.

[48] This torque transmission system, according to this other aspect of the invention, has the advantage of reducing the axial size and improving the energy performance of the motor vehicle. [49] The invention will be better understood, and other aims, details, characteristics and advantages thereof will emerge more clearly from the following description of a particular embodiment of the invention, given solely by way of illustration. and not limiting, with reference to the attached figures.

[50] - [Figure 1] shows an axial sectional view of a wet double clutch according to a first embodiment of the invention.

[51] - [Figure 2] shows an axial sectional view of the wet double clutch according to a second embodiment of the invention.

[52] In the remainder of the description and of the claims, the terms "front" or "rear" will be used without limitation and in order to facilitate understanding thereof in the direction relative to an axial orientation determined by the main axis X of rotation of the transmission of the motor vehicle and the terms “inside / inside” or “outside / outside” with respect to the X axis and in a radial orientation, orthogonal to said axial orientation.

[53] There is shown in Figure 1 a first embodiment of a double wet clutch 1 according to the invention, shown in a torque transmission system 100 for a motor vehicle. The wet double clutch 1 is guided in rotation by means of a transmission housing 102 equipped with two shafts A1, A2 driven for torque output. The wet double clutch 1 is kinematically linked with a heat engine around an axis of rotation X via a torque input web 2.

[54] The torque input web 2 rotatably linked to a drive shaft (not shown) is located in front of the wet double clutch 1.

[55] In the first embodiment, the torque input web 2 generally having an "L" shape, comprises a radially oriented portion formed by a web 3 and an axially oriented portion formed by a hub 4 torque input. The web 3 and the hub 4 are integral, preferably fixed together by welding. The torque input hub 4 is rotatably guided within a closing cover 101 fixed relative to the torque transmission chain.

[56] The torque input hub 4 is for example linked in rotation by means of splines formed at the output of a damping device (such as a double damping flywheel, etc.) whose input is linked, in particular by means of an engine flywheel, to the driving shaft formed by a crankshaft which is driven in rotation by a heat engine fitted to the motor vehicle. [57] The wet double clutch 1 comprises a first clutch E1 and a second clutch E2 respectively of the multidisc type, controlled to selectively couple a heat engine and a rotating electric machine to a first driven shaft and to a second driven shaft. The first and second clutches E1, E2 are arranged radially one above the other around the axis of rotation X

[58] The wet double clutch 1 comprises an input disc carrier 10, 20 of torque common to the first clutch E1 and to the second clutch E2. This common disc carrier comprises in particular a torque input disk carrier 10 of the first clutch E1, a torque input disk carrier 20 of the second clutch E2 and a central oil supply hub 50 for the first clutch. E1 and the second clutch E2.

[59] The common torque input disc holder 10, 20 is rotatably integral with the torque input web 2 and supports a drive ring 80 arranged to mesh with the rotor of the rotating electrical machine.

[60] The central oil supply hub 50 comprises:

- a cylindrical portion 55 of axis X,

- a flange 53 extending radially from the cylindrical portion 55,

- a first annular cavity 51 arranged on the side of the flange and arranged to receive an actuating piston 15 of the first clutch E1,

- a second annular cavity 52 disposed on the same side of the flange as the first annular cavity 51 and arranged to receive an actuating piston 25 of the second clutch E2,

- oil supply channels 54a, 54b and 54c passing through the cylindrical portion 55 and the flange 53, and opening into the annular cavities.

[61] The annular cavities 51, 52 of the first clutch E1 and of the second clutch E2 are oriented in the same direction, in this example in the direction of the driving shaft, that is to say in the direction of the heat engine of the torque transmission chain.

[62] The central oil supply hub 50 is able to transmit the torque coming from two separate sources, thermal and electrical. The torque from the heat engine and the electric motor can then be transmitted to the coaxial shafts A1, A2 of the gearbox as a function of the closing of one or the other of the first clutch E1 or of the second clutch E2. [63] The first driven shaft A1 is rotated when said first clutch E1 is closed and the second driven shaft A2 is rotated when said second clutch E2 is closed.

[64] The multi-disc assembly of the first clutch E1 comprises plates 11 connected in rotation to the input disc holder 10 attached to the central oil supply hub 50 and friction discs 12 connected in rotation to a door -output discs 13. The friction discs 12 are individually axially interposed between two successive plates 11.

[65] In the present case, the input disc holder 10 comprises an internal spline 10a which meshes with the multi-disc assembly of the first clutch E1, the input disc holder 10 being firmly fixed to the central hub 50 by the intermediate of a weld bead.

[66] The output disc holder 13 of the first clutch E1 is connected in rotation by meshing with the friction discs 12 and by a splined connection with said first driven shaft A1. The output disc holder 13 has an overall "L" shape, the inner radial end of which is secured to a splined output hub.

[67] The multi-disc assembly of the second clutch E2 comprises desplateaux21 connected in rotation to an input disc carrier 20 attached to the central oil supply hub 50 and friction discs 22 connected in rotation to a carrier. output discs 23.

[68] In the present case, the input disc holder 20 comprises an internal spline 20a which meshes with the multi-disc assembly of the second clutch E2, the input disc holder 20 being firmly fixed to the central hub 50 by the intermediate of a weld bead.

[69] The output disc carrier 23 of the second clutch E2 is rotatably linked by meshing with the friction discs 22 and by a splined connection with said second driven shaft A2. The output disc holder 23 has an overall "L" shape, the inner radial end of which is secured to a splined output hub.

[70] It will be noted that the first and second clutches E1 and E2 are arranged radially one above the other and aligned along a plane P perpendicular to the axis of rotation X This geometric plane P passes in particular through a disc 12 of the friction disc assembly of the first clutch assembly and a friction disc 22 of the second clutch multi-disc assembly. [71] The drive ring 80 is attached to the outer periphery of the flange 53 of the central hub 50. The function of the central hub 50 is to transmit the torque within the wet double clutch 1. For this, the drive ring 80 is integral in rotation with the central hub 50, in this case by means of a press fit. The drive ring 80 is in the first embodiment of the invention offset axially with respect to the first clutch E1 and disposed radially between the first clutch E1 and the second clutch E2. The drive ring 80 is also offset with respect to the plane P.

[72] The drive ring 80 comprises external teeth kinematically linked with the rotating electrical machine, said teeth being made from material with the drive ring or attached to the drive ring. The external teeth have a helical profile of complementary shape to the pinion of the rotating electrical machine. Alternatively, the teeth could have a straight profile of complementary shape to a chain or a belt used to connect the rotating electrical machine.

[73] The wet double clutch 1 is hydraulically operated by means of a pressurized fluid, usually oil.

[74] To selectively control the change of state of the first clutch E1 and the second clutch E2, a wet double clutch controller manages the supply of pressurized oil within separate control chambers. The control device is generally integrated into the transmission casing 102 of the gearbox. The controller is connected to the central oil supply hub 50 which has channels 54a and 54c for supplying pressurized oil as shown in Figure 1.

[75] As is known in the operation of a wet clutch, a balancing chamber is associated with each control chamber. Usually, the balancing chamber is arranged axially next to the annular cavity acting as a control chamber. The balancing chambers are supplied with cooling fluid. The coolant forms an oil supply channel 54b separate from the other oil supply channels 54a and 54c. This oil supply channel 54b is also formed in the central oil supply hub 50.

[76] The oil supply channels 54a, 54b and 54c are angularly distributed around the cylindrical portion 55. Each of the oil supply channels 54a, 54b and 54c consist of substantially radial and axial bores directed in the direction from control chambers of the first and second clutches E1, E2, but also in the direction of the balancing chambers 31, 32 of the first and second clutches E1, E2.

[77] For example, the oil supply channel 54b of the balancing chamber 31 is produced by drilling successive axial and radial pipes within the central hub 50. Partially, the channel 54b extends radially through the flange 53 and opens into the balancing chamber 31 of the first clutch.

[78] From Figure 1, we understand that all the oil supply channels 54a, 54b, and 54c are arranged in the same Q plane perpendicular to the X axis passing through the flange 53. The channels oil supply 54a and 54b open radially on the outer periphery of the flange 53 and are closed by an internal bore of the drive ring 80. The drive ring 80 surrounds the outer periphery of the flange 53.

[79] In particular, the drive ring 80 comprises an internal cylindrical bearing surface 81 for supporting a seal of the actuating piston 15 of the first clutch E1, the cylindrical bearing surface 81 partly forming the first cavity 51 annular.

[80] The actuating piston 15 of the first clutch E1 is axially movable, here from the rear to the front, between a disengaged position and an engaged position which correspond respectively to the open and closed states of the first clutch E1. The actuating piston 15 is controlled in movement by means of a control chamber delimited by the first cavity 51.

[81] The multi-disc assembly of the first clutch E1 is actuated directly by the first actuating piston 15.

[82] The second clutch E2 comprises an actuating piston 25 which is movable axially, here from the rear to the front, between a disengaged position and an engaged position which correspond respectively to the open and closed states of the second clutch E2. The multidisc assembly of the second clutch E2 is actuated directly by the second actuating piston 25 made from a stamped sheet. The actuating piston 25 is axially movable relative to the second annular cavity 52 of the central hub 50. The actuating piston 25 is controlled in movement by means of a control chamber 32 delimited by the second cavity 52. [83] We will now explain how the wet double clutch 1 is guided in rotation with respect to the torque transmission system 100 in order to reduce the noise at the level of the engagement of the drive ring 80 with the rotorde. rotating electric machine.

[84] In particular, the wet double clutch 1 is guided in rotation relative to the torque transmission system 100 by means of a first pair of axial and radial bearings 41, 42 resting on the torque input web 2, arranged on one side of the plane P and a second pair of axial and radial bearings 43, 44 resting on the input disc carrier 10, 20 of common torque, arranged on the other side of the plane P .

[85] The first pair of bearings thus comprises a first radial bearing 41 and a first axial bearing 42 and the second pair of bearings comprises a second radial bearing 44 and a second axial bearing 43.

[86] The arrangement of the first pair of radial and axial bearings 41, 42 and of the second pair of radial and axial bearings 43, 44 on either side of the plane P ensures rotational stability of the wet double clutch 1 within the torque transmission system. The nutation movements of the wet double clutch are reduced in particular thanks to a substantially symmetrical guide of the bearings. As a result, the noise within the torque transmission system is reduced.

[87] In this first embodiment, the wet double clutch 1 is stopped axially in both directions with respect to the torque transmission system via the axial bearings42, 43 arranged on either side of the plane P. The axial loads generated by the actuating pistons 15, 25 are taken up by the axial bearing 42. In the other direction, the axial bearing 43 takes up the axial load generated by the resultant force applied to the drive ring which has a helical toothing. Depending on the architecture of the wet clutches and the location of the rotating electrical machine, the direction of the forces may vary.

[88] To hold the first radial bearing 41 in position, the torque input web 2 comprises a first housing 91 having an external cylindrical bearing surface along the X axis for the support of said first radial bearing 41.

[89] The torque input web 2 also comprises a second housing 92 pourle first axial bearing 42, the second housing 92 having a wall oriented perpendicular to the X axis for the axial support and a cylindrical bearing surface for the centering of said first axial bearing 42. [90] To maintain the second axial bearing 43 in position, the input disc carrier 10, 20 of common torque comprises a third housing 93 having a wall oriented perpendicular to the X axis for the axial support and a surface d 'cylindrical support for centering said second axial bearing 43.

[91] The input disc holder 10, 20 of common torque comprises a fourth housing 94 for the second radial bearing 44, the fourth housing 94 comprising an external cylindrical bearing surface along the X axis for the support of said second radial bearing 44.

[92] The third housing 93 and the fourth housing 94 of the common torque input disk carrier 10, 20 are contiguous. Thus, the implementation of the second pair of axial and radial bearings 43, 44 reduces the axial and radial bulk of the guiding function of the wet double clutch within the torque transmission system.

[93] Such a wet double clutch has the advantage, thanks to the distribution of the four housings 91, 92, 93 and 94 on the torque input web and the common torque input disc carrier of being stable. rotating while facilitating the integration of the wet double clutch into the torque transmission system.

[94] A description will now be given with reference to FIG. 2, of a wet double clutch 1 according to a second embodiment of the invention in which the position of the axial 42, 43 and radial 41, 44 bearings is optimal with respect to the geometric plane P.

[95] The torque transmission system 100 comprises a closing cover 101 rotatingly supporting the wet double clutch 1 and a first pair of axial and radial bearings 41, 42 interposed between the closing cover 101 and the wet double clutch. The torque transmission system 100 also includes a transmission housing 102 rotatingly supporting the wet double clutch and a second pair of axial and radial bearings 43, 44 interposed between the transmission housing 102 and the wet double clutch. The transmission casing 102 is integral with the closing cover 101.

[96] The layout of the various components of the torque transmission system 100 is substantially symmetrical with respect to the geometric plane P.

[97] In this second embodiment, the drive ring 80 is attached directly to the input disc holder 10, 20 of common torque and comprises an external toothing kinematically linked with the rotating electrical machine. The drive ring 80 is disposed radially beyond the first clutch E1 and axially in the plane P. The rotating electrical machine is thus eccentric with respect to the axis of rotation of the torque transmission chain.

[98] The external teeth of the drive ring 80 has a helical profile of complementary shape to the pinion of the rotating electrical machine. The axial load generated by the resultant force applied to the drive ring gear is taken up by one of the axial bearings 42 or 43.

[99] In order to optimize the absorption of forces by the axial and radial bearings, the first housing 91 of the torque input web 2 adapted to receive the radial bearing 41 and the fourth housing 94 of the input disc holder 10 , 20 of common torque suitable for receiving the radial bearing 44 are disposed radially on the same diameter. The radial bearings are thus standardized. The housings 91 and 94 include an outer cylindrical bearing surface along the X axis for the support of the first radial bearing and may include an axial bearing surface.

[100] The first housing 91 of the torque input web 2 is radially disposed on a diameter D1 and the fourth housing 94 of the common torque input 10.20 disc holder is radially disposed on a diameter D4. There is a homogeneous distribution of the forces between the two radial bearings41 and 44 when the diameters D1 and D4 are such that D1 x 0.8 <D4 <D1 x 1, 2. The distribution of the forces is ideal when the diameter D1 is equal to the diameter D4.

[101] The radial bearings can be fitted or pre-assembled on the wet double clutch 1 before assembly on the torque transmission system 100. Likewise, the axial bearings can be fitted or pre-assembled on the wet double clutch 1 before assembly on the system torque transmission 100.

[102] According to a variant, the first radial bearing 41 and / or the first axial bearing 42 can be fitted or pre-assembled on the closing cover 101 before assembly of the torque transmission system 100.

[103] According to another variant, the second radial bearing 44 and / or the second axial bearing 43 can be fitted or pre-assembled on the transmission casing 102 before assembly of the torque transmission system 100.

[104] As illustrated in Figure 2, the second housing 92 of the torque input web 2 adapted to receive the axial bearing 42 and the third housing 93 of the input disc holder 10, 20 of common torque adapted to receive the axial bearing 43 are arranged opposite each other with respect to the plane P. The axial bearings are thus standardized. Housing 92 and 93 have a wall oriented perpendicular to the X axis for the axial support and a cylindrical support surface for the centering of the axial bearings 42 and 43.

[105] The first housing 91 and the second housing 92 of the torque inlet veil 2 are contiguous. In this way, the installation of the first pair of axial and radial bearings reduces the axial and radial bulk of the guiding function of the wet double clutch within the hybrid transmission.

[106] The third housing 93 and the fourth housing 94 of the common torque input disk carrier 10, 20 are contiguous. In this way, the installation of the second pair of axial and radial bearings reduces the axial and radial bulk of the guiding function of the wet double clutch within the hybrid transmission.

[107] Also, the second housing 92 of the torque input web 2 and the third housing 93 of the common torque input disc holder 10, 20 can be arranged axially at an equal distance from the plane P.

[108] This second mode has the advantage of suppressing the nutation movements of the wet double clutch 1 at the geometric plane P. Consequently, the noise within the torque transmission system 100 is reduced.

[109] The invention should not, however, be limited to the means and configurations described and illustrated here, and it also extends to any equivalent means or configuration and to any technical combination operating such means. In particular, the position of the radial and axial bearings can be changed without harming the invention, since these components, in fine, fulfill the same functions as those described in this document.

[110] The invention also relates to the supply of a clutch kit comprising the wet double clutch 1 according to one of the embodiments described above or any other embodiment, a first couple of radial and axial bearings and / or a second pair of radial and axial bearings. As we have seen previously, the radial or axial bearings can be fitted or pre-assembled on the wet double clutch 1 before mounting on the torque transmission system 100. As a variant, the radial or axial bearings can be delivered separately from the supplier of the wet double clutch. . For example, the supply of the clutch kit can be done in a packaging box in which we find separately the wet double clutch and at least one of the radial or axial bearings [111] Within the meaning of the present application, a wet clutch is a clutch which is adapted to operate in an oil bath or in an enclosure comprising oil.

[112] The wet double clutch 1 according to the invention could be associated with a cut-off clutch of the KO type which would in this case be placed upstream of the torque input web 2. The KO cut-off clutch would then make it possible to disconnect the heat engine from the rest of the torque transmission chain.

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

Claims

[Claim 1] [Wet double clutch (1) for torque transmission system comprising:

- a torque input web (2) arranged to be kinematically linked with a heat engine around an axis of rotation (X);

- a first clutch (E1) and a second clutch (E2) respectively of the multi-disc type, controlled to selectively couple the heat engine and a rotating electric machine to a first driven shaft and to a second driven shaft, the first and second clutches (E1 , E2) being arranged radially one above the other and aligned along a plane (P) perpendicular to the axis of rotation (X),

- a torque input disc carrier (10, 20) common to the first clutch (E1) and to the second clutch (E2), integral in rotation with the torque input web (2), and supporting a ring gear 'drive (80) arranged to mesh with the rotor of the rotary electric machine, characterized in that the wet double clutch is arranged to be guided in rotation with respect to the torque transmission system by means of a first torque of axial and radial bearings (41, 42) resting on the torque input web (2), arranged on one side of the plane (P) and a second pair of axial and radial bearings (43, 44) in support on the input disc holder (10, 20) of common torque, arranged on the other side of the plane (P).

[Claim 2] A wet double clutch (1) according to claim 1, wherein the torque input web (2) comprises a first housing (91) for the first radial bearing (41), the first housing having a bearing surface. external cylindrical along the axis (X) for the support of the first radial bearing.

[Claim 3] Double wet clutch (1) according to one of claims 1 or 2, wherein the torque input web (2) comprises a second housing (92) for the first axial bearing (42), the second housing comprising a wall oriented perpendicular to the axis (X) for the axial support and a cylindrical support surface for the centering of the first axial bearing.

[Claim 4] Wet double clutch (1) according to one of claims 1 to 3, wherein the common torque input disc carrier (10, 20) comprises a third housing (93) for the second axial bearing ( 43), the third housing comprising a wall oriented perpendicular to the axis (X) for the axial support and a cylindrical support surface for the centering of the second axial bearing.

[Claim 5] Wet double clutch (1) according to one of claims 1 to 4, wherein the common torque input disc carrier (10, 20) comprises a fourth housing (94) for the second radial bearing (44). ), the fourth housing comprising an external cylindrical bearing surface along the axis (X) for the bearing of the second radial bearing.

[Claim 6] Wet double clutch (1) according to the combination of claims 2 and 5, wherein the first housing (91) of the torque input web (2) is radially disposed on a diameter D1 and the fourth housing (94). ) of the input disc carrier (10, 20) of common torque is disposed radially on a diameter D4, the diameters D1 and D4 being such that D1 x 0.8 <D4 <D1 x 1, 2, for example the first housing (91) of the torque input web (2) and the fourth housing (94) of the common torque input disc holder (10, 20) are arranged radially on the same diameter.

[Claim 7] Wet double clutch (1) according to the combination of claims 3 and 4, wherein the second housing (92) of the torque input web and the third housing (93) of the disc carrier (10, 20) d 'common torque input are arranged opposite each other with respect to the plane (P).

[Claim 8] Wet double clutch (1) according to any one of the preceding claims, wherein the drive ring (80) is attached to the common torque input disc carrier (10, 20) and comprises toothing externally linked kinematically with the rotating electric machine.

[Claim 9] Wet double clutch (1) according to any one of the preceding claims, in which the drive ring (80) is axially offset with respect to the first clutch (E1) and disposed radially between the first clutch (E1) and the second clutch (E2).

[Claim 10] A wet dual clutch (1) according to any preceding claim, wherein the common torque input disc carrier (10, 20) comprises an oil supply central hub (50) comprising a first annular cavity (51) disposed on the side of the flange and arranged to receive an actuating piston (15) of the first clutch (E1) and a second annular cavity (52) arranged to receive an actuating piston (25) of the second clutch (E2), and at least one oil supply channel (54a, 54c) opening into one of the annular cavities (51, 52) of the clutches.

[Claim 11] Wet double clutch (1) according to the preceding claim, wherein the central oil supply hub (50) comprises a cylindrical portion (55) of axis (X) and a flange (53) s' extending radially from the cylindrical portion (55), the oil supply channels (54a, 54c) of the first cavity (51) and / or of the second cavity (52) are angularly distributed around the axis of rotation (X) and radially pass through the flange (53).

[Claim 12] Wet double clutch (1) according to the preceding claim, in which the drive ring (80) is fitted on the flange (53) of the central hub (50).

[Claim 13] Wet double clutch (1) according to one of claims 1 to 8, wherein the drive ring (80) is disposed radially beyond the first clutch (E1) and axially in the plane (P) .

[Claim 14] A clutch kit comprising a wet double clutch (1) according to any one of the preceding claims, a first pair of radial and axial bearings (41, 42) and / or a second pair of radial and axial bearings ( 43, 44).

[Claim 15] A torque transmission system (100) for a motor vehicle comprising:

- a wet double clutch (1) according to any one of claims 1 to 13;

- a closing cover (101) supporting the wet double clutch (1) in rotation,

- a first pair of axial and radial bearings (41, 42) interposed between the closing cover (101) and the wet double clutch (1),

- a transmission casing (102) supporting the wet double clutch (1) in rotation, the transmission casing being integral with the closing cover (101), and

- a second pair of axial and radial bearings (43, 44), interposed between the transmission housing (102) and the wet double clutch (1). ]