阅读说明：本技术 包括改进的密封的湿式离合机构 (Wet clutch mechanism including improved sealing ) 是由 D.费尼欧克斯 A.切龙 A.多尔 G.瓦罗夸奥克斯 J.鲍莱特 F.蒂鲍特 C.费里 于 2019-05-27 设计创作，主要内容包括：本发明涉及一种湿式离合器机构(10),用于扭矩传递系统,所述湿式离合器机构围绕轴线O至少包括：-多盘组件(E1,E2),其由摩擦盘(12,22)组成,-扭矩输入盘支架(6),其被设置为接收所述多盘组件,-活塞(40,50),其相对于所述输入盘支架能够在接合位置与分离位置之间轴向移动,所述活塞通过控制室(32,36)被控制移位,平衡室(34,38)与所述控制室相关联,所述平衡室部分地由所述活塞(40,50)和所述输入盘支架(6)界定,-弹性返回装置(60),其设置成使活塞返回到离合器机构的分离位置,和其中,所述平衡室通过密封支撑件(70)密封。(The invention relates to a wet clutch mechanism (10) for a torque transmission system, comprising at least, about an axis O: -a multi-disc assembly (E1, E2) consisting of friction discs (12, 22), -a torque input disc carrier (6) arranged to receive the multi-disc assembly, -a piston (40, 50) axially movable relative to the input disc carrier between an engaged position and a disengaged position, the piston being controlled for displacement by a control chamber (32, 36), a balance chamber (34, 38) being associated with the control chamber, the balance chamber being defined in part by the piston (40, 50) and the input disc carrier (6), -an elastic return device (60) arranged to return the piston to the disengaged position of the clutch mechanism, and wherein the balance chamber is sealed by a sealing support (70).)

1. Wet clutch mechanism (10) for a torque transmission system, in particular for a motor vehicle, comprising at least about an axis O:

a multiple disc assembly (E1, E2) consisting of a flange (11, 21) and a friction disc (12, 22),

a torque input disc carrier (6) for inputting torque arranged to receive the multi-disc assembly,

a piston (40, 50) axially movable relative to the input disc carrier between an engaged position and a disengaged position of the clutch mechanism, the piston being controlled for displacement by a control chamber (32, 36) with which a balance chamber (34, 38) is associated, the balance chamber being defined in part by the piston (40, 50) and the input disc carrier (6),

an elastic return device arranged to return the piston to a disengaged position of the clutch mechanism, and

the balancing chamber (34, 38) being partially sealed by a seal support (70, 70a, 70b, 70c, 70d), a first seal (71) and a second seal (72), the seal support supporting the first seal and holding the second seal in position axially with respect to the balancing chamber,

-the axial force exerted by said elastic return means (60) effects the compression of said first seal (71).

2. Wet clutch mechanism (10) according to claim 1, wherein the elastic return means (60) exert an axial force between the input disc carrier (6) and the piston (40, 50), the elastic return means bringing the sealing support (70, 70a, 70b, 70c, 70d) against the input disc carrier or the piston.

3. Wet clutch mechanism (10) according to claim 1 or 2, wherein the elastic return means (60) bear a seal support (70, 70b, 70d) against the input disc carrier, the first seal (71) being compressed between the seal support and the input disc carrier.

4. Wet clutch mechanism (10) according to claim 3, wherein the elastic return means (60) are axially interposed between a seal support (70, 70b, 70d) and the piston (40).

5. Wet clutch mechanism (10) according to claim 3 or 4, characterized in that a sealing support (70, 70b, 70d) is axially supported on the input disc carrier and is free to displace radially with respect to the input disc carrier.

6. Wet clutch mechanism (10) according to one of the claims 3 to 5, wherein the second seal (72) slides on a cylindrical bearing (42) provided on the piston (40).

7. Wet clutch mechanism (10) according to claim 1 or 2, wherein the elastic return means (60) bear a seal support (70a, 70c) against the piston (50), the first seal (71) being compressed between the seal support and the piston.

8. Wet clutch mechanism (10) according to claim 7, wherein the elastic return means (60) are axially interposed between a seal support (70a, 70c) and the input disc carrier (6).

9. Wet clutch mechanism (10) according to claim 7 or 8, characterized in that a sealing support (70a, 70c) bears axially on the piston (50) and is free to displace radially with respect to the piston.

10. Wet clutch mechanism (10) according to one of the claims 7 to 9, wherein the second seal (74) slides on a cylindrical bearing provided on the input disc carrier (6) or on a balancing cover (39) of a balancing chamber attached to the input disc carrier (6).

11. Wet clutch mechanism (10) according to any of the preceding claims, wherein the seal support (70, 70a, 70b, 70c, 70d) comprises a radially extending bearing portion (74) and an axially extending bearing portion (75) supporting the first seal (71) and the second seal (72).

12. Wet clutch mechanism (10) according to one of the preceding claims, wherein the seal support (70, 70a, 70b, 70c, 70d) comprises a radially extending bearing portion (74) comprising an annular recess (76) in which the first seal (71) is inserted.

13. Wet clutch mechanism (10) according to any of the preceding claims, wherein the first seal (74) and the second seal (72) are made in the form of a single identical seal directly overmoulded on the seal support (70, 70a, 70b, 70c, 70 d).

14. Wet clutch mechanism (10) according to any one of claims 1 to 12, wherein the first seal (71) and the second seal (72) are separate, the elastic return means (60) comprising two bearing plates (61,62) of annular shape, one of which (61,62) carries the second seal (72), and a series of helical springs (63) circumferentially distributed between them.

15. Wet clutch mechanism (10) according to one of the preceding claims, wherein the elastic return means (60) are arranged outside the balancing chamber (34, 38).

Technical Field

The present invention relates to a wet clutch mechanism including an improved seal at the balance chamber.

Background

Such wet clutch mechanisms are intended to form part of a torque transmission system, in particular for motor vehicles or for so-called industrial vehicles, the latter being, for example, trucks, public transport vehicles or agricultural vehicles.

Patent application EP 2909052 a1 discloses a wet dual clutch mechanism for a motor vehicle comprising a torque input device for coupling to a crankshaft, a first torque output shaft, a second torque output shaft, a first clutch and a second clutch, the first clutch being able to couple or decouple the torque input device and the first torque output shaft, the second clutch being able to couple or decouple the torque input device and the second torque output shaft. The first and second clutches, each of the multiple-disc type, are arranged radially one above the other. Each multi-plate clutch includes a flange rotationally connected to an input plate carrier forming a torque input device and a friction plate rotationally connected to an output plate carrier. Each clutch further comprises an axially movable piston which is controlled in displacement by means of a control chamber which is associated with a balancing chamber which is delimited at least by a balancing cover.

The control chamber is supplied with pressurized hydraulic fluid to allow the movable piston to be displaced between a first position corresponding to an engaged configuration of the clutch and a second position corresponding to a disengaged configuration of the clutch.

Instead, the balance chamber is supplied with a so-called cooling hydraulic fluid, which allows to lubricate the components of the clutch mechanism and to compensate the axial force generated by the movable piston.

The movable piston of the clutch mechanism is located in an intermediate position between the balance chamber and the control chamber, so that it delimits the two chambers of the clutch mechanism. The balance chamber of the first clutch is formed by the input disc carrier and the movable piston and includes an opening that allows a leakage flow of cooling fluid, typically located in a lower portion of the balance chamber, to pass therethrough. The leakage flow is directed in the direction of the multi-plate clutch.

It is also necessary to ensure that the balance chamber is sealed at the junction of the movable piston and the input disc carrier. The tightness of the balancing chamber is achieved in particular by dynamic seals attached and vulcanized on the axially movable piston. The dynamic seal slides along a cylindrical bore formed directly in the input disc carrier. Such an arrangement is known from document EP 2909052 a 1.

The drawbacks associated with this arrangement relate to the complex manufacture of the movable piston, obtained for example by stamping and multiple machining, to adapt said piston to different clutch mechanisms. In practice, the piston is a regulating member machined according to the other constituent parts of the clutch mechanism and the torque capacity to be transmitted by said clutch mechanism. The piston is a stamped plate member that includes an axial extension, typically in the form of an actuating finger, that exerts an axial force on the stack of flanges and friction discs to transmit drive torque within the clutch.

The torque to be transmitted at the clutch is defined by the number of friction discs forming the multi-plate assembly. Accordingly, the torque to be transmitted constrains the geometry of the axial extension of the piston. Thus, the greater the torque to be transmitted, the greater the number of friction discs, and the need to reduce the axial extension of the piston to maintain a constant axial dimension. Accordingly, the piston is a component whose geometry is rarely standardized to several applications of wet clutch mechanisms that use the same input disc carrier.

The application of seals on pistons is therefore part of the background of a complex industrialization and it seems necessary to simplify the manufacturing process in order to better control the sealing at the balancing chamber on the one hand and to reduce the manufacturing costs on the other hand. This is even more critical when the seal is obtained by overmoulding directly on the piston: such vulcanization operations are often carried out by external subcontractors, which adds to the complexity of the industrialization.

Disclosure of Invention

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

It is an object of the present invention, inter alia, to provide a wet clutch mechanism for a torque transmission system which allows at least part of certain disadvantages of the prior art to be solved.

To this end, the invention proposes a wet clutch mechanism for a torque transmission system, in particular for a motor vehicle, comprising at least, about an axis O:

a multi-disc assembly consisting of a flange and friction discs,

a torque input disc carrier arranged to receive the multi-disc assembly,

a piston axially movable relative to the input disc carrier between an engaged position and a disengaged position of the clutch mechanism, the piston being controlled in displacement by a control chamber, the control chamber being associated with a balance chamber, the balance chamber being delimited in part by the piston and the input disc carrier,

-elastic return means arranged to return the piston to the disengaged position of the clutch mechanism, and

the balancing chamber is partially sealed by a seal support, which supports the first seal and maintains the second seal in a proper axial position with respect to the balancing chamber,

the compression of the first seal is achieved by the axial force exerted by the elastic return means.

Such a wet clutch mechanism according to the invention has the advantage of simplifying the manufacturing process of the piston, since the first seal and the second seal are arranged on the seal support. The retention of the first seal in place within the wet clutch mechanism eliminates the need for complex assembly operations such as riveting or welding operations. The axial force of the elastic return means now ensures the positioning of the first seal and the sealing of the balancing chamber.

Preferably, the resilient return means applies an axial force between the input disc carrier and the piston, the resilient return means urging the seal support against the input disc carrier or the piston. In this way, the axial force of the elastic return means prevents any rotation of the seal support during its operation on the vehicle and ensures the sealing of the balancing chamber.

Advantageously, the seal support is a separate component from the input disc carrier and the piston. In this way, the material of the support can be chosen indistinguishable from the material of the input disc carrier or the piston, and the geometry of the support can be more easily adapted to the type of seal used.

The invention may have one or other of the features described below, in combination with each other or independently of each other:

the sealing support may be made of a plate, in particular a steel or aluminium plate;

the seal support may be made by stamping a plate;

the sealing support can be made by machining;

the seal support may comprise a radially extending bearing portion supporting the first seal and/or the second seal;

the seal support may comprise an axially extending bearing portion supporting the first seal and/or the second seal;

the radially extending bearing portion of the seal support may comprise an annular recess in which the first seal is inserted;

the elastic return means may comprise two supporting plate members of annular shape and a series of helical springs circumferentially distributed between them;

one of the two supporting plates of the elastic return means may carry a second seal;

the elastic return means may comprise an annular elastic gasket;

the elastic return means may comprise a wave washer;

the elastic return means may be supported on a radially extending support portion of the seal support;

the elastic return means may be arranged outside the balancing chamber;

the elastic return means may be arranged radially outside the axially extending support;

the elastic return means may be arranged radially inside the axially extending support;

the first and second seals may be separate;

the first seal and/or the second seal may be lip seals;

the first seal and/or the second seal may be O-ring seals;

the first seal and/or the second seal may be overmoulded directly on the seal support, for example according to a vulcanisation method;

the first and second seals may be made in the form of a single identical seal, overmoulded directly on the seal support;

the sealing support can be shared with one of the annular bearing plates of the elastic return means;

the multi-plate clutch may comprise a flange rotationally connected to the input plate carrier and friction plates rotationally connected to the output plate carrier.

According to another aspect of the invention, the object of the invention also relates to a wet clutch mechanism which employs all or part of the above features and in which the resilient return means urges the seal support against the input disc carrier, the first seal being compressed between the seal support and the input disc carrier.

Preferably, the seal support is axially supported on the input disc carrier and is free to displace radially relative to the input disc carrier.

This further aspect of the invention has the advantage of simplifying the assembly of the wet clutch mechanism. The seal support and the first seal are simply placed on the input disc carrier and then compressed axially by placing the resilient return means in position. The retention of the first seal in place within the wet clutch mechanism eliminates the need for complex assembly operations such as riveting or welding operations. The risk of misalignment and concentricity defects along the axis O of the seal support with respect to the piston are avoided.

Advantageously, the elastic return means may be axially interposed between the sealing support and the piston.

Preferably, the second seal is slidable on a cylindrical bearing provided on the piston.

The seal support may include a rotation stop tab circumferentially disposed about the radially extending bearing portion, the tab being inserted in a form stamping made in the disk carrier so as to completely prevent rotation of the seal support relative to the input disk carrier.

According to another aspect thereof, the object of the invention also relates to a wet clutch mechanism which employs all or part of the above features and in which the elastic return means bear the seal support against the piston, the first seal being compressed between the seal support and the piston.

Preferably, the seal support is axially supported on the piston and is free to displace radially relative to the piston.

This further aspect of the invention has the advantage of simplifying the assembly of the wet clutch mechanism. The seal support and the first seal are simply placed on the piston and then compressed axially by placing the elastic return means in position. The retention of the first seal in place within the wet clutch mechanism eliminates the need for complex assembly operations such as riveting or welding operations. The risk of misalignment and concentricity defects along the axis O of the seal support with respect to the input disc carrier are avoided.

Advantageously, the elastic return means may be axially interposed between the sealing support and the input disc carrier.

The elastic return means may be supported directly on the input disc holder. Alternatively, the elastic return device can be supported indirectly on the input disc carrier, in particular on a balancing cover attached to the input disc carrier.

Preferably, the second seal member is slidable on a cylindrical support portion provided on the input disc carrier or on a balance cover attached to a balance chamber of the input disc carrier.

The seal support may comprise a rotation stop tab circumferentially arranged inside the radially extending bearing portion, said tab being inserted in a shaped stamping made in the piston so as to completely avoid rotation of the seal support relative to the piston.

According to another aspect thereof, the present invention also relates to a wet double clutch mechanism for a torque transmission system, in particular for a motor vehicle, comprising, about an axis O:

a torque input disc carrier arranged to be rotatably connected to the drive shaft,

-first and second clutches controlled to selectively couple the drive shaft to first and second driven shafts and arranged radially one above the other;

each clutch comprises a multi-plate assembly comprising a flange rotationally connected to the input plate carrier and friction plates rotationally connected to the output plate carrier,

at least one of the clutches comprises:

a piston axially movable relative to the input disc carrier between an engaged position and a disengaged position of the clutch, the piston being controlled in displacement by a control chamber, the control chamber being associated with a balance chamber, the balance chamber being delimited in part by the piston and the input disc carrier,

-elastic return means arranged to return the piston to the disengaged position of the clutch, and

the balancing chamber is partially sealed by a seal support, which supports the first seal and maintains the second seal in a proper axial position with respect to the balancing chamber,

the compression of the first seal is achieved by the axial force exerted by the elastic return means.

In the context of the wet clutch mechanism according to the invention, the first clutch and/or the second clutch adopt all or part of the features described above.

Drawings

The invention will be better understood from reading the following description, which is given by way of example only and with reference to the accompanying drawings, in which:

fig. 1 is an axial sectional view of a wet double clutch mechanism according to a first embodiment of the invention;

FIG. 2 is an enlarged partial view in axial cross-section of the first embodiment of the present invention of FIG. 1;

FIG. 3 is an isometric view of a single seal support according to the first embodiment of the invention of FIG. 1;

fig. 4 is a partially enlarged view of a wet double clutch mechanism according to a second embodiment of the invention;

fig. 5 is a partially enlarged view of a wet double clutch mechanism according to a third embodiment of the invention.

Detailed Description

In the following description and in the claims, the following terms are used in a non-limiting manner and for ease of understanding: the terms "front" or "rear" are along a direction relative to an axial orientation determined by the main axis of rotation O of the transmission of the motor vehicle, the terms "inside/inner" or "outside/outer" are relative to the axial direction O and along a radial orientation orthogonal to said axial orientation.

Fig. 1 to 3 show a first embodiment of a wet clutch mechanism 10 according to the invention. And more particularly to a wet dual clutch mechanism 10 having a primary axis of rotation O. The wet dual clutch mechanism 10 rotates within the transmission housing 100.

The wet dual clutch mechanism 10 for the torque transfer system 1 comprises, about an axis O, at least one input element 2, which input element 2 is rotationally connected to a drive shaft (not shown). The input member 2 is located at the rear of the wet double clutch mechanism 1.

In the first embodiment, the input element 2, which has an L-shape as a whole, comprises a radially oriented portion formed by the input web 3 and an axially oriented portion formed by the hub 4. The input web 3 and the input hub 4 are joined, preferably fixed together by welding.

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

The input hub 4 is rotationally connected, for example by means of splines 5, to the output of a damping device (for example a double flywheel damper or the like), the input of which is connected, in particular by means of a motor flywheel, to a drive shaft formed by a crankshaft driving in rotation a motor equipped with a motor vehicle.

The input web 3 comprises teeth 9 at the outer radial end of its axial orientation, the teeth 9 extending radially outward and bearing on the input disk carrier 6 for the input torque.

The wet double clutch mechanism 10 is controlled to selectively connect the drive shaft to the first driven shaft a1 and the second driven shaft a 2.

Preferably, the first driven shaft a1 and the second driven shaft a2 are coaxial. The first driven shaft a1 is driven in rotation when the first clutch E1 is closed, and the second driven shaft a2 is driven in rotation when the second clutch E2 is closed, the first driven shaft a1 and the second driven shaft a2 being respectively connected to a gearbox equipping a motor vehicle.

The wet dual clutch mechanism 1 includes a first clutch E1 and a second clutch E2, which are each of a multi-plate type.

The multi-plate assembly of the first clutch E1 includes a flange 11 rotationally connected to the input plate carrier 6 and friction plates 12 rotationally connected to the output plate carrier 13. The friction discs 12 are uniformly interposed axially between two consecutive flanges 11.

The output disc carrier 13 of the first clutch E1 is rotationally connected to the friction discs 12 by meshing and rotationally connected to the first driven shaft a1 by a splined connection.

The output disc carrier 13 has an overall "L" shape with its inner radial end coupled to the output splined hub.

The multi-plate assembly of the second clutch E2 includes a flange 21 rotationally connected to the input plate carrier 6 and friction plates 22 rotationally connected to the output plate carrier 23.

The output disc carrier 23 of the second clutch E2 is rotationally connected by meshing engagement with the friction discs 22 and rotationally connected by a splined connection with the second driven shaft a 2.

The output disc support 23 has an overall "L" shape with its inner radial end coupled to the output splined hub.

The input disc carrier 6 further comprises a cylindrical hub 7 with an axis of rotation O, an outer disc carrier 14 for the first clutch E1 and an inner disc carrier 24 for the second clutch E2.

The outer disc carrier 14 for the first clutch E1 includes, inter alia, an axial extension 15 and an annular portion 16, the axial extension 15 being arranged to receive the multi-disc assembly of the first clutch, the annular portion 16 extending radially inwardly from the axial extension 15 along a plane perpendicular to the axis O.

The axial extension 15 forms an internal channel that receives the flange 11 of the multi-plate assembly of the first clutch.

The inner disc carrier 24 for the second clutch E2 includes an axial extension 25, the axial extension 25 being arranged to receive the multi-disc assembly of the second clutch. The inner disc support 24 has an annular shape. The axial extension 25 forms an external groove that receives the flange 21 of the multi-plate assembly of the second clutch.

As shown in fig. 1, the inner disc support 24 is attached and rotationally coupled to the annular portion 16 of the outer disc support 14.

The cylindrical hub 7 is common to the first clutch E1 and the second clutch E2. The cylindrical hub 7 is inserted into a hole provided in the transmission case 100.

As shown in fig. 1, the first clutch E1 is disposed radially above the second clutch E2.

Preferably, the first and second clutches E1, E2 are in an open state, also referred to as "normally open," and are selectively actuated in operation by a control device (not shown) contained within the transmission housing 100 to transition from an open state to a closed state.

The wet double clutch mechanism 1 is hydraulically controlled by a pressurized fluid (usually oil).

To selectively control the state change of the first clutch E1 and the second clutch E2 between the disengaged position and the engaged position, the pressurized oil supply of the device management mechanism 10 is controlled. The control device is connected to the cylindrical hub 7, and the cylindrical hub 7 includes oil supply passages 71a, 71b, and 71c, the number of which is three, for example, as shown in fig. 1.

Passages 71a, 71c axially located at the front and rear ends of the cylindrical hub 7 are associated with the control chamber 32 of the first clutch E1 and the control chamber 36 of the second clutch E2, respectively. The passage 71b, which is axially between the passages 71a, 71c, is associated with the balance cavity 34 of the first clutch E1 and the balance cavity 38 of the second clutch E2, respectively.

The first clutch E1 of the multi-plate type includes a piston 40, where the piston 40 is axially movable from front to rear between a disengaged position and an engaged position, which correspond to the open and closed states of the first clutch E1, respectively.

Advantageously, the piston 40 comprises, at its outer radial end, a support 41 extending axially rearwards. The support 41 is supported on the end flange 12 of the multiple disk assembly of the first clutch E1. In the example shown in fig. 1, the support 41 is discontinuous.

The control chamber 32 for the piston 40 of the first clutch E1 is associated with a balance chamber 34, the balance chamber 34 being bounded by a portion of the cylindrical hub 7, a portion of the input disc carrier 16 and a portion of the piston 40.

The piston 40 of the first clutch E1 extends radially and is arranged axially between the axially forward control chamber 32 and the axially rearward balance chamber 34. The piston 40 is concentric with the input disc holder 6.

As shown in fig. 1, the piston 40 is controlled to be displaced by the control chamber 32, the control chamber 32 being axially delimited by a front face of the inner radial portion of the piston 40 and by a rear radial face of the closing member 45.

The balance chambers 34, 38 are supplied with cooling oil through the passage 71 b.

The piston 40 is controlled to axially clamp the multi-plate assembly of the first clutch E1 in the engaged position against the reaction means 8 formed directly in the input web 3.

The first clutch E1 includes a resilient return means 60, which in the example of fig. 1 is made in the form of a helical spring, to return the piston 40 automatically to the disengaged position. In this position, the piston 40 axially releases the multi-disk assembly, which in turn no longer transmits torque in the direction of the first driven shaft A1. The elastic return means 60 exert an axial force between the input disc carrier 6 and the piston 40. In a variant not shown, the elastic return means may comprise an annular elastic washer or a wave washer.

As shown in fig. 2, the elastic return means 60 comprise, in particular, two supporting plate elements 61,62 in the form of rings and a series of helical springs 63 distributed circumferentially between the two supporting plate elements 61, 62.

The bearing plate 61 is axially supported on the seal support 70 of the balancing chamber 34.

The balance chamber 34 is sealed by a seal support 70, a first seal 71 and a second seal 72. In this example, the seal support 70 supports the first seal 71 and axially retains the second seal 72 in position relative to the balance chamber 34.

The compression of the first seal 71 is achieved by the axial force exerted by the elastic return means 60. Thus, the holding of the first seal 71 in place within the wet clutch mechanism no longer requires a complex assembly operation.

The seal support 7 is a separate component from the input disc carrier and the piston and can therefore be made more easily from stamped steel or aluminium sheet. The shape of the seal support 70 is adapted to a first seal 71 and a second seal 72, the first seal 71 and the second seal 72 being made in the form of a single identical seal directly overmoulded on the seal support. The seal support comprises in particular a radially extending bearing portion 74 supporting the first seal 71 and an axially extending bearing portion 75 supporting the second seal 72. The radially extending bearing portion 74 of the seal support comprises an annular recess 76, the first seal 71 being inserted in this recess 76.

The first seal is axially compressed between two components, i.e. the input disc carrier and the seal support, which do not move relative to each other. The first seal 71 is here shown in the form of a lip seal, but may be replaced by an O-ring seal or a flat seal.

The second seal 72 is interposed between two components having relative movement between each other, namely the piston and the seal support. The second seal 72 is a lip seal that slides on a cylindrical bearing 42 provided on the piston 40.

As shown in fig. 3, the seal support includes a rotation stop tab 77 disposed circumferentially about the radially extending bearing portion 74, which is inserted in a form stamp 68 made in the input disc carrier 6 in order to prevent rotation of the seal support 70 relative to the input disc carrier 6.

The design of the second clutch E2 of the wet dual clutch mechanism 1 is similar to that of the first clutch E1, the second clutch E2 preferably being of the multi-plate type.

Advantageously, for the description of the second clutch E2, reference will be made to the detailed description of the first clutch E1 given above, as required.

The second clutch E2 includes a piston 50, where the piston 50 is axially movable from rear to front between a disengaged position and an engaged position, which correspond to the open and closed states of the second clutch E2, respectively.

The piston 40 of the first clutch E1 and the piston 50 of the second clutch E2 of the wet dual clutch mechanism 1 are axially displaced in opposite directions to shift from the disengaged position to the engaged position, for example.

Advantageously, the piston 50 comprises, at its outer radial end, a support 51 extending axially forward. The support 51 is supported on the end flange 21 of the multiple disk assembly of the second clutch E2.

The piston 50 is controlled to axially clamp the multi-plate assembly of the second clutch E2 against the reaction member 28 at the engaged position. The reaction device 28 is formed directly on the annular portion 16 of the outer disc carrier 14 for the first clutch E1.

The second clutch E2 also includes a resilient return device 60 for automatically returning the piston 50 to the disengaged position. The elastic return means 60 comprise two supporting plates 61,62 of annular shape and a series of helical springs 63 circumferentially distributed between these two supporting plates 61, 62.

The bearing plate 61 is axially supported on the seal support 70a of the balancing chamber 38.

The balance chamber 38 is sealed by a seal support 70a, a first seal 71 and a second seal 72. In this example, the seal support 70a supports the second seal 72 and the first seal 71 relative to the balance chamber 38. The seal support 70a includes only radially extending bearing portions that support the first seal 71 and the second seal 72.

The compression of the first seal 71 is achieved by the axial force exerted by the elastic return means 60. The elastic return means 60 abut the sealing support 70a against the piston 50.

The elastic return means 60 are supported on the balancing cover 39 of the balancing chamber 38, the balancing cover 38 being attached to the input disc support 6. The second seal 72 is interposed between the two components with relative movement between them, i.e. the piston and the balance cap 39. The second seal 72 is a lip seal that slides on a cylindrical bearing provided on the balance cover 39.

Referring now to fig. 4, the wet double mechanism 10 according to the second embodiment of the invention is substantially similar to the first embodiment except that the seal support 70b of the balance chamber 34 of the first clutch E1 is common to one of the annular bearing plates of the elastic return device.

The sealing support 70c of the balancing chamber 38 of the second clutch E2 comprises a centering pin 78 for the elastic return means 60.

Referring now to fig. 5, a wet double mechanism 10 according to a third embodiment of the invention is substantially similar to the first embodiment except that a seal support 70d supports the first seal 71 and holds the second seal 72 axially in position relative to the balance chamber 34. The elastic return means 60 comprise an annular bearing plate 61, which annular bearing plate 61 brings the sealing support 70d against the input disc support 6. The bearing plate 61 includes a cylindrical bearing portion that extends axially around the axially extending bearing portion 75 of the seal support 70 d. The axial ends of the support plate 61 and the axially extending support 75 form a cavity capable of receiving the second seal 72. The second seal 72 is a lip seal that slides on a cylindrical bearing 42 provided on the piston 40.

The present invention is not limited to the above-described embodiments.