FR3086711A1 - ASSEMBLED FORCE TRANSMISSION DEVICE AND WET DOUBLE CLUTCH MECHANISM COMPRISING SAID MEMBER - Google Patents

Abstract

The invention relates to an assembled force transmission member (90) for a wet double clutch mechanism, comprising: - an actuation part (91) of revolution form around an axis of rotation (O) comprising a first face support (95) perpendicular to the axis, intended to press on a wet clutch multi-disc assembly, a second support face (96) intended to press on an elastic return device (60), - a part of reinforcement (92) in the form of a revolution about the axis (O) comprising a third bearing face (97) intended to press on a control system of the wet clutch, the third bearing face being offset radially by relative to the second bearing face, the actuating part (91) and the reinforcing part (92) are fixed together at an interface zone offset radially with respect to the third bearing face (97 ).

Description

Assembled force transmission member and wet double clutch mechanism comprising said member

The present invention relates to an assembled force transmission member and a wet double clutch mechanism comprising this assembled force transmission member.

Such a wet double clutch mechanism is intended to constitute part of a torque transmission system, in particular for a motor vehicle or for a so-called industrial vehicle, the latter being for example a heavy goods vehicle, a public transport vehicle, or an agricultural vehicle.

There are known wet double clutch mechanisms comprising first and second clutches arranged radially one above the other and also comprising first and second pistons for actuating a control system making it possible to generate a force for configuring respectively the first and second clutches in a clutched or disengaged configuration. The force generated at each actuating piston is transmitted to the corresponding clutch via a force transmission member.

Thus, the displacement of the actuating piston is transmitted to the corresponding force transmission member which, in turn, displaces first friction elements, for example friction discs, relative to second friction elements of the 'corresponding clutch, for example flanges, to configure it in one or other of the configurations mentioned.

In known manner, if the actuating piston is used to push the force-transmitting member, the retrograde movement of said piston is generated by an elastic return device interposed axially between the clutch and the transmission member force to generate sufficient effort to restore the actuator and the corresponding clutch in their initial configurations. It is known to use helical compression springs as an elastic return device.

Document DE 10 2016 222 739 A1 is known, in which the wet double clutch mechanism implements helical compression springs disposed between the torque input disc holder and each of the force transmission members of the first and second clutches. Each force transmission member comprises in particular a first bearing face intended to press on the multi-disc assembly of the clutch, a second bearing face intended to press on the elastic return device and a third bearing face intended to press the control system. The second support face is arranged radially opposite the third support face.

In this architecture known from the prior art, the elastic return device associated with the first force transmission member passes through orifices made in the second force transmission member. However, due to their structures, the coil compression springs are sensitive to the effects generated by the rotation of the clutch mechanism. Under the effect of centrifugation, the springs deform radially. It is therefore necessary to provide an additional radial space between the springs and the through orifices provided in the second force transmission member to avoid any mechanical interference during operation.

The disadvantage of this architecture of the clutch mechanism lies in the risk of contact between the elastic return device and the force transmission member, which can prevent re-establishing the actuating piston and the corresponding clutch in their initial configurations. .

Another drawback of this architecture of the clutch mechanism also lies in the fact that the general shape of the force transmission members is not favorable in terms of axial stiffness. The stiffness of the second force transmission member is notably affected by the presence of the passage orifices.

The object of the invention is in particular to provide a simple, effective and economical solution to this problem.

The object of the present invention is in particular to propose an assembled force transmission member for a wet double clutch mechanism, comprising:

- An actuating part in the form of a revolution about an axis of rotation O comprising a first bearing face perpendicular to the axis, intended to press on a multidisc wet clutch assembly, a second bearing face intended to press on an elastic return device,

- a reinforcing part in the form of a revolution about the axis O comprising a third bearing face intended to press on a control system of the wet clutch, the third bearing face being offset radially with respect to the second bearing face, in which the actuating part and the reinforcing part are fixed together at an interface zone offset radially with respect to the third bearing face.

This assembled force transmission member according to the invention has the advantage, thanks to the fixing and nesting of the reinforcing part in the actuating part, of increasing the axial stiffness along the axis of rotation O .

The radial offset of the second bearing face with respect to the third bearing face within the wet double clutch mechanism makes it possible to install the elastic return device independently of the position of the control system and of the actuating pistons associated. The design of the wet double clutch mechanism comprising this force transmission member is thus simplified.

Advantageously, the reinforcing part comprises a cantilevered portion, extending radially in the direction of the axis O from the interface zone and on which the third bearing face is located. This cantilevered portion according to the invention has the advantage of freeing up space at the center of the assembled force transmission member.

Preferably, the mean support diameter of the first support face Dial, the mean support diameter of the second support face Dia2 and the mean support diameter of the third support face Dia3 can be offset radially, so that:

Dial> Dia2> Dia3.

Advantageously, the average support diameter of the second support face Dia2 and the average support diameter of the third support face Dia3 are offset proportionally according to a ratio

R = Dia3 / Dia2 for which R is less than 90%, preferably less than 80%.

This assembled force transmission member according to the invention has the advantage of being able to install a control system having a small radial size and offset with respect to the elastic return device.

The invention may have one or other of the characteristics described below, combined together or taken independently of one another:

- the actuating part and the reinforcing part can be force-fitted one into the other;

- the actuating part and the reinforcing part can be assembled by crimping, or by welding, or by bonding;

- the actuating part and the reinforcing part can use separate materials, for example of metallic or plastic or composite type;

- The interface zone can be located radially beyond the second bearing face of the actuating part;

- the interface zone can be annular;

- the interface area can be continuous;

- The interface zone can be circular of diameter D, the diameter D of the interface zone being greater than the average support diameter of the third support face Dia3.

- The interface zone can be formed by a series of discontinuous supports, angularly distributed around the axis O;

- the third bearing face of the reinforcement part can be curved;

- The reinforcing part may have in section in a plane passing through the axis of rotation O an L shape and a cylindrical reinforcing wall;

- The reinforcing part can comprise stiffening elements, for example ribs produced by stamping.

- The external surface of the cylindrical reinforcement wall can be supported on the actuating part;

the actuating part can be produced by stamping and have a complementary cylindrical wall arranged opposite the reinforcing part, said complementary cylindrical wall being adapted to the cylindrical reinforcing wall.

- The internal surface of the complementary cylindrical wall can be supported on the external surface of the reinforcing cylindrical wall.

According to one of its aspects, the invention also relates to a wet double clutch mechanism intended to be installed between an engine and a motor vehicle transmission, comprising:

- A first clutch and a second clutch respectively of the multidisc type in rotation about an axis of rotation O, controlled to selectively couple a shaft leading to a first driven shaft and to a second driven shaft via a carrier common torque input discs, the first clutch being disposed radially beyond the second clutch;

- a clutch control system comprising first and second actuating pistons arranged to control the first and second clutches;

a first elastic return device associated with the first actuating piston, the first elastic return device being supported on the input disc holder, and

- A first assembled force transmission member incorporating all or part of the characteristics mentioned above and inserted axially between the first clutch and the first actuation piston.

The wet double clutch mechanism, according to this other aspect of the invention, has the advantage of being space-saving radially at the level of the control system. In particular, the first force transmission member of the first clutch can come to bear on the first actuating piston on a reduced diameter.

Preferably, the wet double clutch mechanism according to this other aspect of the invention, can comprise:

a second elastic return device associated with the second actuating piston, the second elastic return device being in abutment on the input disc holder and disposed radially outside the first elastic return device,

- a second force transmission member axially interposed between the second clutch and the second actuating piston,

- the first assembled force transmission member passing through orifices arranged in the second force transmission member to press on the first elastic return device.

The dual wet clutch mechanism, according to this other aspect of the invention, has the advantage of avoiding any risk of contact between the first elastic return device and the second force transmission member. The establishment of elastic return devices within the input disc holder also has the advantage of reducing the axial and radial size of the first and second clutches.

This other aspect of the invention may have one or other of the characteristics described below, combined together or taken independently of one another:

- The first and the second elastic return device respectively comprise a first series of helical springs distributed angularly around the axis O pressing on the first force transmission member assembled via a first annular plate, a second series helical springs angularly distributed around the axis O pressing on the second force transmission member by a second annular plate, and a common support plate joining together the first and second series of helical springs;

- A guide bearing can be arranged radially inside the input disc holder to support the first and second clutches relative to the control system;

- The guide bearing can be of the ball bearing type;

- The guide bearing can be of the needle bearing type;

- The control system may include an axial extension span extending towards the input disc holder, the guide bearing being arranged radially outside the axial extension span;

- the first and second elastic return devices can be housed in a recess formed in the entry disc holder;

- support legs formed on the actuating member of the first assembled force transmission member can pass through the second force transmission member to press on the first elastic return device;

- The ends of the support legs can form the second support face of the actuator;

- the support legs can be angularly distributed around the axis O.

According to yet another aspect of the invention, the wet double clutch mechanism can comprise:

a second elastic return device associated with the second actuating piston, the second elastic return device being in abutment on the input disc holder and disposed radially inside the first elastic return device,

- a second force transmission member axially interposed between the second clutch and the second actuating piston,

- the first assembled force transmission member passing through orifices arranged in the second force transmission member to press on the first elastic return device.

The invention will be better understood on reading the description which follows, given solely by way of example and made with reference to the appended drawings in which:

Figure 1 is an axial sectional view of a wet double clutch mechanism comprising a force transmission member assembled according to a first embodiment of the invention;

Figure 2 is an isometric view of the wet double clutch mechanism according to the first embodiment of the invention of Figure 1;

Figure 3 is a sectional view of the force transmission member assembled according to the first embodiment of the invention of Figure 1;

Figure 4 is an isometric view of the force transmission member assembled according to the first embodiment of the invention of Figure 1;

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

There is shown in Figure 1 a first embodiment of the invention in which a wet double clutch mechanism 1 for the torque transmission system comprises an assembled force transmission member.

The wet double clutch mechanism is of the multi-disc type and has a main axis of rotation O.

The wet double clutch mechanism 1 comprises around the axis O at least one input element 2 which is linked in rotation to a driving shaft (not shown). The input element 2 is located at the rear of the wet double clutch mechanism 1.

In the first embodiment, the input element 2 having an overall “L” shape, comprises an annular portion of radial orientation formed by an entry web 3 and a portion of axial orientation formed by a hub 4. The inlet web 3 and the inlet hub 4 are integral and welded together by laser welding by transparency.

The hub 4 is arranged radially inside with respect to the entry web 3.

The input hub 4 is for example linked in rotation via the grooves 5 to the output of a damping device (such as a double damping flywheel, etc.) whose input is linked, by l 'Intermediate including a flywheel, the drive shaft formed by a crankshaft which rotates an engine fitted to the motor vehicle.

The entry web 3 has, at its outer radial end of axial orientation, teeth 9 which extend radially outwards and which are supported on an input disc holder 10 of torque.

The wet double clutch mechanism 1 is controlled to selectively couple said shaft leading to a first driven shaft A1 and to a second driven shaft A2 connected to a gearbox fitted to the motor vehicle.

Preferably, the first driven shaft A1 and the second driven shaft A2 are coaxial. The first driven shaft A1 is driven in rotation when said first clutch E1 is closed and the second driven shaft A2 is driven in rotation when said second clutch E2 is closed.

The wet double clutch mechanism 1 comprises a first clutch E1 and a second clutch E2, which are respectively of the multi-disc type, as well as a control system 100 arranged to engage or disengage said first π

and second clutches E1, E2. The control system 100 is fixed to a transmission casing 150.

As illustrated in FIG. 1, the first clutch E1 is arranged radially above the second clutch E2.

The wet double clutch mechanism 1 is hydraulically controlled by means of a pressurized fluid, generally oil. The control system 100 comprises: a first actuating piston 110 arranged to configure the first clutch E1 in a configuration comprised between the engaged configuration and the disengaged configuration;

a second actuating piston 120 arranged to configure the second clutch E2 in a configuration between the engaged configuration and the disengaged configuration;

a housing 130 in which are housed at least (in part) the first or the second actuating piston 110, 120.

The first and second clutches E1, E2 are supported on the control system 100 by means of force transmission members 90, 75.

For example, the actuation system may include an axial extension range 140 integrated in the casing 130 and extending axially in the direction of the input element 2. The axial extension range 140 is arranged to support the first and second clutches.

A guide bearing 80 is disposed between the axial extension bearing 140 and the input disc holder 10. The guide bearing 80 is of the ball bearing type and guides the first and second clutches E1, E2 in rotation relative to to the control system 100. The guide bearing 80 is in axial support on the input disc holder 10. On its internal periphery, the input disc holder 10 comprises a cylindrical bearing portion 13 in which the ring is inserted outside of the guide bearing 80. The integration of the guide bearing within the input disc holder 10 allows a resumption of the axial forces without altering the axial size of the wet double clutch mechanism.

The guide bearing 80 is common to the first and second clutchesEl and E2.

For example, the guide bearing 80 is an angular contact ball bearing. In a variant not shown, the guide bearing can be a needle bearing.

As illustrated in FIGS. 1 and 2, the wet double clutch mechanism 1 comprises a first elastic return device 60 of the first actuating piston 110 and a second elastic return device 70 of the second actuating piston 120. The first and second elastic return device 60, 70 bears on the input disc holder 10 and are in particular housed in a recess 15.

The recess 15 formed in the input disc holder 10 is arranged on a diameter located beyond the bearing portion of the cylindrical support portion 1 3.

Each of the elastic return devices 60, 70 makes it possible to generate an axial force sufficient to restore the actuating piston and the corresponding clutch in the initial configuration known as disengaged.

The first elastic return device 60 comprises a first series of helical springs 61 distributed angularly around the axis O arranged to come to bear on a first force transmission member 65. The first force transmission member 90 is axially interposed between the first clutch E1 and the first actuating piston 110.

The second elastic return device 70 comprises a second series of helical springs 71 angularly distributed around the axis O arranged to come to bear on a second force transmission member 75. The second force transmission member 75 is axially interposed between the first clutch E1 and the first actuating piston 120.

In the first embodiment of the invention, the second elastic return device 70 is arranged radially beyond the first elastic return device 60. The first series of helical springs 61 rests on the first force transmission member 90 by means of a first annular plate 62. The second series of helical springs 71 presses on the second force transmission member 75 by means of a second annular plate 72.

A common support plate 17 fastens together the first and second series of helical springs 61, 71. The common support plate 17 is supported on the input disc holder 10.

In order to reduce the axial size of the wet double clutch mechanism 1, the first and second clutches E1, E2, the first and second elastic return devices 60, 70 and the guide bearing 80 are concentric and are nested radially within the input disc holder 10.

In particular, a plane orthogonal to the axis O, geometrically crosses the guide bearing 80, the first and second clutches E1, E2 as well as the first and second elastic return devices 60,70. Said plane passes through the center of the balls of the guide bearing 80.

In order to reduce the axial compactness, the first force transmission member 90 passes through orifices 76 formed in the second force transmission member 75 to press on the first elastic return device.

The first force transmission member 90 is assembled by means of an actuation part 91 and a reinforcement part 92. This assembly makes it possible to obtain a first assembled force transmission member 90 having an improved axial stiffness.

As illustrated in FIGS. 3 and 4, the first assembled force transmission member 90 comprises in particular:

- An actuating part 91 of form of revolution about an axis of rotation O comprising a first bearing face 95 perpendicular to the axis, intended to press on the multidisk assembly of the first clutch E1, a second face d 'support 96 intended to press the first elastic return device 60, and

a reinforcing part 92 in the form of a revolution around the axis O comprising a third support face 97 intended to press on the control system 100.

The third support face 97 is offset radially with respect to the second support face 96. The third support face 97 has a convex type profile suitable for pressing on the first actuating piston 110.

The actuating part 91 and the reinforcing part 92 are fixed together at the level of a circular interface zone of diameter D. The interface zone is offset radially with respect to the third bearing face 97. The diameter D of the interface zone is greater than the average support diameter of the third support face Dia3.

The reinforcing part 92 has in section in a plane passing through the axis of rotation O a shape of L and a cylindrical reinforcing wall 99. The reinforcing part 92 comprises a cantilevered portion 94, extending radially in direction of axis O from the interface zone and on which the third bearing face is located. The internal periphery of the second force transmission member 75 is housed inside the cantilever portion 94.

As illustrated in FIG. 3, the average support diameter of the first support face Dial, the average support diameter of the second support face Dia2 and the average support diameter of the third face d 'support Dia3 are offset radially, so that Dial> Dia2> Dia3.

In the first embodiment, the actuating part 91 and the reinforcing part 92 are force-fitted one into the other. Alternatively, the actuating part and the reinforcing part can be assembled by crimping, or by welding, or by gluing.

The average support diameter of the second support face Dia2 and the average support diameter of the third support face Dia3 are offset proportionally according to a ratio R = Dia3 / Dia2 for which the ratio R is less than 90% , preferably less than 80%.

The axial stiffness measured along the axis O between the first bearing face 95 and the third bearing face 97 is between 8000 and 11000 N / mm for a clutch mechanism suitable for a motor vehicle. To further increase the stiffness, the reinforcing part 92 may include ribs produced by stamping.

In the first embodiment, the actuating part 91 and the reinforcing part 92 are produced by stamping sheet steel. Alternatively, the actuating part and the reinforcing part can use separate materials, for example of the metallic or plastic or composite type.

The circular interface zone of diameter D is located radially beyond the second bearing face 96 of the actuating part 91. The interface zone is annular and continuous.

The external surface of the reinforcing cylindrical wall 99 of the reinforcing part is in contact with the actuating part 91 at the level of the interface zone. The actuating part 91 has a complementary cylindrical wall 77 arranged opposite the reinforcing part 92, said complementary cylindrical wall 77 being adapted to the cylindrical reinforcing wall 99.

For example, the internal surface of the complementary cylindrical wall 77 is supported on the external surface of the reinforcing cylindrical wall 99.

According to another variant not shown, the interface zone can be formed by a series of discontinuous supports, angularly distributed around the axis O.

The first assembled force transmission member 90 also includes support legs 93 formed on the actuating part. The support legs 93 are angularly distributed around the axis O and thus pass through through orifices 76 of the second force transmission member 75. The ends of the support legs 93 form the second support face 96 of the actuating member and are supported on the first annular plate 62 of the first elastic return device 60.

The wet double clutch mechanism also includes a lubrication ring 50 is also disposed radially between the axial extension bearing 140 and the input disc carrier 10. The lubrication ring 50 is in axial support on the guide bearing 80. The lubrication ring 50 is retained axially by a split ring fitted in a groove arranged on the axial extension surface 140 of the casing 130.

Advantageously, the lubrication ring 50 comprises lubrication lines 51 passing radially right through the ring and opening onto the outer periphery. The lubrication lines 51 are oriented radially in the direction of the clutches E1 and E2.

The casing 130 of the control system 100 comprises cooling fluid supply lines 131 which communicate directly with the lubrication lines 51. The lubrication ring 50 thus channels the cooling fluid coming from the actuation system towards the first and second clutches E1, E2 and promotes their lubrication.

The multi-disc assembly of the first clutch E1 comprises flanges 11 linked in rotation to the input disc holder 10 and friction discs 12 linked in rotation to a first torque output disc holder 30. The friction discs 12 are, axially, axially interposed between two successive flanges 11.

The torque output disc holder 30 of the first clutch E1 is linked in rotation by engagement with the friction discs 12 and by a splined connection with said first driven shaft A1. The output disc holder 30 includes an output hub 31 connected to the driven shaft A1.

The multi-disc assembly of the second clutch E2 comprises flanges 21 linked in rotation to the input disc holder 10 and friction discs 22 linked in rotation to a second torque output disc holder 40.

The torque output disc holder 40 of the second clutch E2 is linked in rotation by engagement with the friction discs 22 and by a splined connection with said second driven shaft A2. The output disc holder 40 includes an output hub 41 connected to the driven shaft A2.

The input torque carrier 10 is common to the first and second clutch E1 and E2. The input disc holder 10 further comprises an outer disc holder 14 of the first clutch E1 and an inner disc holder 24 of the second clutch E2.

The external disc holder 14 of the first clutch E1 notably comprises an axial extension arranged to receive the multi-disc assembly of the first clutch. The axial extension forms an internal groove receiving the flanges 11 of the multidisk assembly of the first clutch E1.

The inner disc holder 24 of the second clutch E2 comprises an axial extension arranged to receive the multi-disc assembly of the second clutch. The axial extension forms an internal groove receiving the flanges 21 of the multidisk assembly of the second clutch E2.

A second embodiment (not shown) of a double wet clutch mechanism 1 comprising the assembled force transmission member 90 is possible. This second mode of implementation is substantially similar to the first mode of implementation with the exception that the second elastic return device 70 associated with the second actuating piston 75 is arranged radially inside the first device. elastic return 60.

In this second embodiment, the second force transmission member 75 is axially interposed between the second clutch E2 and the second actuating piston 120, and the first assembled force transmission member 90 passes through orifices arranged in the second force transmission member to press the first elastic return device.

The invention is not limited to the examples of implementation which have just been described. The wet double clutch mechanism according to the invention may comprise first and second clutches, first and second elastic return devices and a guide bearing nested radially within an input disc holder and in which each of the devices elastic recalls 60, 70 can be formed by an annular elastic washer arranged in place of the series of helical springs. The annular elastic washer can press directly on the force transmission member assembled at the second bearing face.

Claims (15)

1. Assembled force transmission member (90) for a wet double clutch mechanism, comprising: - An actuating part (91) of revolution form around an axis of rotation (O) comprising a first bearing face (95) perpendicular to the axis, intended to press on a multidisc wet clutch assembly , a second bearing face (96) intended to press on an elastic return device (60), - a reinforcing part (92) of revolution shape around the axis (O) comprising a third bearing face (97) intended to press on a control system (100) of the wet clutch, the third face support being offset radially with respect to the second support face, characterized in that the actuating part (91) and the reinforcement part (92) are fixed together at an interface zone offset radially relative to the third bearing face (97). 2. An assembled force transmission member (90) according to claim 1, in which the reinforcement part (92) comprises a cantilevered portion (94), extending radially in the direction of the axis (O) from the interface zone and on which the third bearing face (97) is formed. 3. Assembled force transmission member (90) according to claim 1 or 2, in which the average support diameter of the first support face (Dial) the average support diameter of the second support face ( Dia2) and the average support diameter of the third support face (Dia3) are offset radially so that Dial> Dia2> Dia3. 4. Assembled force transmission member (90) according to any one of the preceding claims, in which the mean bearing diameter of the second bearing face (Dia2) and the mean bearing diameter of the third face d 'support (Dia3) are offset proportionally according to a ratio R = Dia3 / Dia2 for which R is less than 90%, preferably less than 80%. 5. Assembled force transmission member (90) according to any one of the preceding claims, in which the interface zone is annular. 6. Assembled force transmission member (90) according to the preceding claim, in which the reinforcing part (92) has an L-shaped section and a cylindrical reinforcing wall (99), said external surface of the cylindrical wall. reinforcement (99) is supported on the actuating part (91). 7. Assembled force transmission member (90) according to any one of claims 1 to 4, in which the interface zone is formed by a series of discontinuous supports, angularly distributed around the axis (O). 8. An assembled force transmission member (90) according to any one of the preceding claims, in which the actuating part (91) and the reinforcing part (92) are force-fitted into each other. 9. assembled force transmission member (90) according to any one of claims 1 to 7, in which the actuating part (91) and the reinforcement part (92) are assembled by crimping, or by welding, or by collage. 10. Double wet clutch mechanism (1) intended to be installed between an engine and a motor vehicle transmission, comprising: - a first clutch (E1) and a second clutch (E2) respectively of the multidisc type in rotation about an axis of rotation (O), controlled to selectively couple a shaft leading to a first driven shaft (A1) and to a second driven shaft (A2) via a common torque input disc carrier (10), the first clutch (E1) being arranged radially beyond the second clutch (E2); - a clutch control system (100) comprising first and second actuation pistons (110, 120) arranged to control the first and second clutches (E1, E2); a first elastic return device (60) associated with the first actuating piston (110), the first elastic return device being supported on the input disc holder, and - A first assembled force transmission member (90) according to any one of claims 1 to 9 and interposed axially between the first clutch (E1) and the first actuating piston. 11. A wet double clutch mechanism according to the preceding claim, comprising: - a second elastic return device (70) associated with the second actuating piston (120), the second elastic return device being supported on the input disc holder (10) and disposed radially outside the first elastic return device (60), - a second force transmission member (75) axially interposed between the second clutch (E2) and the second actuating piston (1 20), - The first assembled force transmission member (90) passing through orifices (76) arranged in the second force transmission member (75) to press on the first elastic return device (60). 12. Double wet clutch mechanism (10) according to the preceding claim, in which the first and the second elastic return device (60, 70) respectively comprise: a first series of helical springs (61) angularly distributed around the axis (O) pressing on the first assembled force transmission member (90) via a first annular plate (62), a second series of helical springs (71) angularly distributed around the axis (O) pressing on the second force transmission member (75) by a second annular plate (72), and a common support plate (17) joining together the first and second series of helical springs (61, 71). 13. wet double clutch mechanism (10) according to the preceding claim, wherein the first and second elastic return devices (60, 70) are housed in a recess (15) formed in the input disc holder (10) . 14. A wet double clutch mechanism (10) according to any one of claims 10 to 13, in which a guide bearing (80) is arranged radially inside the input disc holder (10) to support the first and second clutches (E1, E2) relative to the control system (100). 15. Double wet clutch mechanism (10) according to any one of claims 11 to 14, in which support tabs (93) formed on the actuating member (91) of the first assembled force transmission member (90) pass through the second force transmission member (75), the ends of the support legs (93) forming the second support face (96) of the actuating member.