CN110273940B

CN110273940B - Dual wet clutch mechanism with inner disc carrier configured for actuating disc pack

Info

Publication number: CN110273940B
Application number: CN201810215849.9A
Authority: CN
Inventors: 牛耕; 甘涛; 应学军; 石磊; A.多尔; B.雷古尔斯基
Original assignee: Valeo Embrayages SAS
Current assignee: Valeo Embrayages SAS
Priority date: 2018-03-15
Filing date: 2018-03-15
Publication date: 2022-09-13
Anticipated expiration: 2038-03-15
Also published as: CN110273940A

Abstract

The object of the invention is a dual wet clutch mechanism (1) for a transmission system, said dual wet clutch mechanism (1) comprising a first inner disc carrier (4) and a second inner disc carrier (5), wherein each inner disc carrier (4, 5) is movable about the same axis of rotation (O) and comprises a first axial portion (41, 51) and a second axial portion (42, 52), the first axial portion (41, 51) having a toothed engagement portion (44, 54) arranged outwardly and configured to receive a disc pack (101, 201), the second axial portion (42, 52) having an outer contour portion (45, 55) extending radially outwardly and configured as an actuator disc pack (101, 201).

Description

Dual wet clutch mechanism with inner disc carrier configured for actuating disc pack

Technical Field

The present invention relates to a transmission system for a motor vehicle having a dual clutch mechanism.

There is a difference between a so-called double dry clutch mechanism and a so-called double wet clutch mechanism.

The invention finds particular application in dual wet clutch mechanisms.

Background

Such a clutch mechanism is known, for example, from DE 102014209618 a 1. This document describes a dual wet clutch mechanism. The first clutch and the second clutch are arranged one above the other in the radial direction, so that the second clutch is mounted inwardly with respect to the first clutch. Each clutch includes a disc pack disposed between an inner disc carrier and an outer disc carrier. The disc pack includes a flange connected to the outer disc carrier and a friction disc connected to the inner disc carrier. The outer disc carrier of the first clutch is connected to the input hub, and the coupling means hold the outer disc carrier together. The inner disc carrier of the first clutch is connected to the first output hub and the inner disc carrier of the second clutch is connected to the second output hub.

For each clutch, the piston is intended to be pressed against its respective disc pack by the actuator. Each piston extends radially outward from the actuator and then axially up to its disc pack. When the actuator is activated, the piston moves axially to rotationally couple the friction disk of its pack and the flange.

However, such clutch mechanisms are not entirely satisfactory, particularly in terms of their design.

A first disadvantage of such clutch mechanisms is that they occupy a large space in the transmission system, so that the disc carriers extend radially and axially to connect with their respective hubs and the pistons extend radially and axially to transfer axial loads from their actuators to the respective disc packs.

A second disadvantage of this clutch mechanism is that there is an excessive number of components that are necessary to assemble the mechanism.

Disclosure of Invention

The object of the present invention is therefore to eliminate at least one of these disadvantages and in particular to provide a dual wet clutch mechanism which can be manufactured with a relatively small design.

It is an object of the present invention to provide a clutch mechanism for a motor vehicle which overcomes at least one of the drawbacks of the prior art and which is easy to assemble, while being more compact.

This object is achieved by a dual wet clutch mechanism for a transmission system, comprising a first inner disc carrier and a second inner disc carrier, wherein each inner disc carrier is movable about the same axis of rotation and comprises a first axial portion having a toothed engagement portion arranged outwardly and configured to receive a disc pack, and a second axial portion having an outer contour portion extending radially outwardly and configured to actuate the disc pack.

Advantageously, the first and second axial portions extend axially relative to each other in opposite directions.

The first and second axial portions are understood to mean that the first and second axial portions are mechanically dependent on each other. The first and second axial portions are preferably designed as a single piece.

Preferably, the first inner disc carrier is arranged radially outwardly with respect to the second inner disc carrier. The first inner disc carrier and the second inner disc carrier are then arranged one above the other in the radial direction, so that the second clutch is mounted inwardly with respect to the first clutch. Such a design is known as a radial dual wet clutch mechanism.

According to an embodiment, the first inner disc carrier is rotationally connected to the second inner disc carrier, and/or the second inner disc carrier is configured to be rotationally connected to an input hub of the dual wet clutch mechanism.

Such a design is particularly advantageous, since each inner disc carrier of the dual wet clutch mechanism implements (carry out) a piston. This design allows for a reduction in the axial and radial volumes of the dual wet clutch mechanism in the transmission system.

The inner disc carriers advantageously retain the additional function that they are designed, on the one hand, such that the first axial portion realizes a disc pack and, on the other hand, the second axial portion has an outer contour which acts on the respective disc pack to move it axially in the direction of the disc pack to engage one of the output hubs with the input hub of the clutch mechanism.

Due to this design, the number of parts (including the springs) required to assemble the dual wet clutch mechanism is significantly reduced. The dual wet clutch mechanism can then be installed more quickly.

The rotational connection of at least one of the inner disc carriers is realized by the teeth of the outer contour of the respective inner disc carrier. The teeth are disposed on the outer profile to allow one of the inner disc carriers to couple with the dual wet clutch mechanism.

Preferably, the outer contour of each inner disc carrier has teeth. The teeth can be designed by deformation of the ends of the outer contour. For coupling the outer disc carrier to the clutch mechanism, the teeth may advantageously be axially oriented in the direction of the second axial portion.

For acting on the respective disc pack, the outer contour may comprise a finger, which is axially oriented in the direction of the respective disc pack. The fingers act on the disc pack to move it axially in the direction of the disc pack. The fingers are arranged circumferentially about the axis of rotation to distribute axial load from the actuator to the outer profile.

The fingers and teeth can be designed together by deformation of the outer contour. As a result, the first portion of the outer contour may extend radially outward up to a middle position of the respective disc pack. Then, after the first portion, the second portion of the outer contour may extend axially and radially along the respective disc pack to act on the respective disc pack. Finally, a third portion succeeding the second portion may extend axially in the direction of the second axial portion. The end of the second portion and the front of the third portion linked to each other form a finger, while the end of the third portion forms a tooth.

According to the invention, the outer contour comprises a circular border, which is axially oriented in the direction of the respective disc pack. This means that there are no fingers circumferentially spaced around the axis of rotation. The circular boundaries act axially on the respective disc packs around the rotation axis.

The circular boundary can be designed by deformation of the outer contour. The rounded border and the teeth can be designed together by deformation of the outer contour. In this embodiment, the end of the second portion and the front of the third portion linked to each other form a rounded border, while the end of the third portion forms a tooth.

The outer contour may be integrally formed with the inner disc carrier. In particular, the outer contour may be integrally formed with the second axial portion of the inner disc carrier. Such a design means that the outer contour and the inner disc carrier are formed as a one-piece body. Such a one-piece body is realized by a pressing process or by a molding process.

According to the invention, the outer contour may be attached to the inner disc carrier, for example by welding. In this design, the outer contour is fastened to the inner disc carrier by a peripheral weld. More particularly, the outer contour is attached to the second axial portion of the inner disc carrier, for example by welding.

According to the invention, the second axial portion of the first inner disc carrier extends radially inwardly to form an inner profile of the first inner disc carrier, the inner and outer profiles of the first inner disc carrier together forming an actuation piston of a disc pack cooperating with the first inner disc carrier.

Due to such a design, the first inner disc carrier can axially press its disc pack. When the actuator acts on the first inner disc carrier, it exerts a circumferential axial load on the inner contour of the first inner disc carrier. The inner contour of the first inner disc carrier is then moved axially from the open position. The outer profile of the first inner disc carrier, which is formed with (or secured to) the first inner disc carrier, moves in the direction of the disc packs and, in a closed position, engages the friction discs and the flange of the respective disc packs with one another, in which closed position the input hub drives the first output hub.

According to the invention, the inner contour comprises a connecting means configured to rotationally connect the second inner disc carrier. The connection means are advantageously formed by notches. In this design, the teeth of the outer contour of the second inner disc carrier are received in the notches of the inner contour of the first inner disc carrier, so that the first inner disc carrier centers the second inner disc carrier. According to this design, the inner disc carriers are coupled together about the rotational axis, so that the second inner disc carrier is centered by the first inner disc carrier about the rotational axis. In a preferred configuration, the second inner disc carrier may be driven by the first inner disc carrier which is capable of transmitting a high torque. Advantageously, the notches open inwardly.

The inner and outer profiles of the first inner disc carrier are offset with respect to each other. The biasing is realized such that, when fastened to each other, each inner disc carrier is axially movable by its actuator.

According to the invention, the second axial section of the second inner disc carrier forms an outer contour, the outer contour of the second inner disc carrier forming an actuating piston of a disc pack cooperating with the second inner disc carrier. Such a second inner disc carrier is advantageously simpler to implement. This outer contour of the second inner disc carrier is formed, for example, by deformation of a metal plate.

When the actuator acts in the second inner disc carrier, it exerts a circumferential axial load on the outer contour of the second inner disc carrier. The outer profile portion of the second inner disc carrier is then moved axially in the direction of the disc pack from an open position and in a closed position the friction discs and the flanges of the respective disc packs are engaged with each other, in said closed position the input hub drives the second output hub.

Opposite the first inner disc carrier, an axial load transferred to the second inner disc carrier is applied against the outer contour of the second inner disc carrier. Such a design is particularly advantageous by significantly reducing the radial distance between the disc package cooperating with the second inner disc carrier and the actuator. Thus, the distance between the disc package cooperating with the first inner disc carrier and the actuator is reduced considerably. The disc packs of the second inner disc carrier then face at least the actuator thereof.

According to the invention, the dual wet clutch mechanism comprises a rotationally connected transmission plate and a blocking plate, the transmission plate being rotationally connected to the input hub, the blocking plate having a radially inner portion comprising notches arranged to receive teeth of the outer profile of the first inner disc carrier, whereby the first inner disc carrier and the second inner disc carrier are driven by the transmission plate. Due to this design, the first inner disc carrier is coupled with the transmission plate about the rotational axis, so that the first inner disc is centered about the rotational axis by the transmission plate. The first inner disc carrier is centered with respect to the rotation axis, the first inner disc carrier for centering the second inner disc carrier with respect to the rotation axis. The drive plates are then able to transmit high torques to each inner disc carrier. Advantageously, the slot of the radially inner portion of the blocking plate opens inwardly.

When the input hub rotates, the first inner disc carrier and the second inner disc carrier rotate at the same speed. Depending on the desired dual wet clutch mechanism, either the first inner disc carrier or the second inner disc carrier is engaged by its actuator.

According to the present invention, the driving plate includes an opening formed at a periphery. When the clutch mechanism rotates, oil for lubricating the disc pack is thrown radially outward and is released from the clutch mechanism through the opening of the drive plate. The openings are formed circumferentially around the axis of rotation.

Advantageously, the drive plate comprises a radially oriented inner portion and an axially oriented outer portion. The radially inner portion and the axially outer portion are contiguous to each other. The opening extends at least partially over the radially inner portion and at least partially over the axially outer portion so that oil is easily released from the clutch mechanism. Embodiments are equally possible in which the opening is formed exclusively on an axially outer portion of the drive plate.

According to the invention, the radially inner portion of the blocking plate extends through the axially outer portion. The axially outer portion and the radially inner portion of the blocking plate are continuous with respect to each other.

The axially outer portion of the drive plate is in circumferential contact with the axially outer portion of the blocking plate. The transmission plate and the blocking plate are then fastened by their axially outer parts so that they are rotationally connected to each other. Preferably, the driving plate and the blocking plate are fastened together by welding. Such welding may be effected around the circumferential contact of the plates.

According to the invention, the first inner disc carrier and the second inner disc carrier are axially movable relative to the axis of rotation.

For this purpose, the first inner disc carrier can then be moved axially, guided in a circular manner by its teeth, which engage in the notches of the blocking plate. Similarly, the second inner disc carrier can then be moved axially, guided in a circular manner by its teeth, which engage in the notches of the first inner disc carrier.

As previously introduced, such a design allows centering the first inner disc carrier and the second inner disc carrier with respect to the rotation axis. When one of the actuators is actuated, the axial load moves the respective inner disc carrier, such that this centering allows the inner disc carrier to move axially and press the discs of the respective disc pack against each other.

According to the invention, the dual wet clutch mechanism comprises a first outer disc carrier and a second outer disc carrier, the first inner disc carrier and the first outer disc carrier receiving a first disc pack, the second inner disc carrier and the second outer disc carrier receiving a second disc pack, wherein the first outer disc carrier is fastened to the first output hub and the second outer disc is fastened to the second output hub.

Advantageously, each disc pack is axially retained between the outer contour of its respective outer disc carrier and its respective inner disc carrier. More particularly, the respective outer disc carrier is arranged such that it extends radially from an output hub having a wave shape to form a reaction means for allowing the disc pack to be pressed against it.

For supporting the axial load, a first axial needle bearing is arranged between the first outer disc carrier and the second outer disc carrier. Similarly, a second axial needle bearing is arranged between the second outer disc carrier and the drive plate.

According to the invention, the dual wet clutch mechanism comprises an actuation system with a housing, wherein at least one of the inner disc carriers is radially smaller than the actuation system housing. Preferably, the second inner disc carrier is radially smaller than the actuation system housing. More preferably, the disc pack of the second inner disc carrier is radially smaller than the actuation system housing.

According to the invention, the actuation system housing comprises a first actuator intended for actuating the first inner disc carrier and a second actuator intended for actuating the second inner disc carrier, the first actuator acting on the first inner disc carrier via its inner contour and the second actuator acting on the second inner disc carrier via its outer contour.

In the open position, when the first and second actuators are disconnected, the outer profile of the second inner disc carrier and the inner profile of the first inner disc carrier may be in the same plane perpendicular to the axis of rotation.

Advantageously, a first shim is arranged between the inner contour of the first inner disc carrier and the first actuator, and a second shim is arranged between the outer contour of the second inner disc carrier and the second actuator. These adjustment shims may be selected during assembly of the dual clutch mechanism so that in the open position there is no axial clearance between the respective actuator and its inner disc carrier.

The dual wet clutch mechanism may include a support shaft, the support bearing being axially disposed between the support shaft and the second outer disc carrier. More precisely, the support shaft has an internal shoulder at least partially receiving the support bearing, so that the support bearing is axially retained between the support shaft and the second outer disc carrier and radially between the support shaft and the second output hub.

The various features which are characteristic of the invention are set forth with particularity in the claims which form a part of this specification. For a better understanding of the invention, its operating advantages and specific objects attained by its uses, reference should be made to the accompanying drawings and descriptive matter in which there is illustrated and described a preferred embodiment of the invention.

Drawings

The invention will now be discussed in more detail using preferred embodiments and with reference to the accompanying drawings, in which:

figure 1 shows a perspective view of a clutch mechanism according to the invention,

figure 2 shows an axial half-section of the clutch mechanism shown in figure 1,

fig. 3 shows an exploded view of the first and second inner disc carriers, the transmission plate and the blocking plate.

Detailed Description

In the following description and claims, the terms "front" or "rear" will be used in a non-limiting manner to aid understanding according to a direction determined with respect to an axial orientation determined with respect to the rotation axis O of the dual wet clutch mechanism 1, and the terms "inward" or "outward" will aid understanding with respect to the rotation axis O and according to a radial orientation orthogonal to said axial orientation.

Referring to fig. 2 and 3, a radial dual wet clutch mechanism 1 for a transmission system (not shown), the clutch mechanism 1, is shown about an axis of rotation O. The transmission system is designed to be installed in a motor vehicle. The dual wet clutch mechanism 1 has a drive plate 2 connected to an input hub 20 (shown in fig. 2) and a blocker plate 3 fastened to the drive plate 2. The first inner disc carrier 4 and the second inner disc carrier 5 of the clutch mechanism 1 are partially shown. The blocking plate 3 is arranged such that it rotationally connects the

inner disc carriers

4, 5 to the transmission plate 2.

As shown in fig. 2 and 3, the clutch mechanism 1 shows at least one input hub 20 about the axis of rotation O, which is rotationally connected to a transmission shaft (not shown). The clutch mechanism 1 is controlled to selectively couple the transmission shaft to first and second driven shafts (not shown). Preferably, the first driven shaft and the second driven shaft are coaxial. The clutch mechanism 1 has at least a first clutch 100 and a second clutch 200, each of which is of a multi-plate type. When the first clutch 100 is closed, a first driven shaft is caused to rotate, and when the second clutch 200 is closed, a second driven shaft is caused to rotate, the first and second driven shafts being respectively connected to a gearbox (not shown), which is part of a motor vehicle. The first clutch 100 is arranged radially outward with respect to the second clutch 200, for example. The first and

second clutches

100, 200 are then arranged radially one relative to the other. Such a design is a so-called radial dual clutch mechanism 1.

The input hub 20 preferably has at least a drive plate 2, which is fastened to the input hub 20. The drive plate 2, here having a general L-shape, has a radially oriented inner portion 21 and an axially oriented outer portion 22. The input hub 20 has a radially oriented portion 20A and an axially oriented portion 20B. The input hub 20 is arranged radially inwardly with respect to the drive plate 2. The axially oriented portion 20B of the input hub 20 extends axially rearward in the direction of the engine. The input hub 20 and the drive plate 2 are designed as one piece. Advantageously, the input hub 20 may have drive splines configured in the inner cylindrical surface of its axial portion 20B for rotationally connecting the drive plate 2 and the input hub 20 to the drive shaft. The inner end of the radially inner portion 21 of the drive plate 2 and the outer end of the radial portion of the input hub 20 are preferably fastened to each other by welding.

The input hub 20 is rotationally connected, for example by means of drive splines, via an engine flywheel to a driveshaft constituted by a crankshaft which is caused to rotate by an engine which is part of the motor vehicle. Then, the engine causes the drive plate 2 to rotate through the input shaft 20, so that the drive plate 2 has the same rotational speed as the engine. The axially outer portion 22 of the drive plate 2 has a circular border at its free front axial end. Said circular border of the drive plate 2 is oriented axially forward. Said circular boundary of the driving plate 2 is constituted by a circumferentially continuous rim 22A. As a variant, said circular boundary of the transmission plate 2 is circumferentially discontinuous.

The driving plate 2 is rotationally connected to a blocking plate 3, which blocking plate 3 rotationally connects said driving plate 2 to the clutch mechanism 1. The blocking plate 3 has a radially oriented inner portion 31 connected to the clutch mechanism and an axially oriented outer portion 32 connected to the transmission plate 2. The axially outer portion of the blocking plate 3 has a circular border at its free front axial end. Said circular border of the blocking plate 3 is oriented axially rearwards. Said circular border of the blocking plate 3 is constituted by a circumferentially continuous rim 32A.

The driving plate 2 has, at the free front end of its axially forward outer portion, a rim 22A forming a circular continuous and radially oriented connecting portion end of the driving plate 2; the blocking plate 3 has at the free rear end of its rearward axially outer portion a rim 32A forming said circular continuous and radially oriented connecting portion end of the blocking plate 3. Thereby, at least one of said radially oriented connection portion ends is constituted by a circumferentially

continuous rim

22A, 32A.

As a variant, the transmission plate 2 has, at the free front end of its forward axially outer portion, a rim 22A forming said circumferentially continuous and radially oriented connecting portion end of the transmission plate 2; the blocking plate 3 has at the free rear end of its rearward axially outer portion a rim 32A forming said circumferentially continuous and radially oriented connecting portion end of the blocking plate 3.

As a further variant, at least the transmission plate 2 and/or the blocking plate 3 has, at the free end of its axially outer portion, a

rim

22A, 32A forming said circumferentially discontinuous and radially oriented connecting portion of the blocking plate 3 or of the transmission plate 2.

The transmission plate 2 and the blocking plate 3 are rotationally connected by means of their axially

outer portions

22, 32 by means of a connecting means, preferably with a zero axial clearance c 1. A rotational connection with zero axial play allows a high torque to be transmitted from the transmission plate 2 to the blocking plate 3. Said zero axial clearance connection means of the driving plate 2 and the blocking plate 3 are attached by welding.

Said connection means are constituted, for example, by a bead which may be circumferentially continuous or discontinuous, in particular depending on the connection portions of the transmission plate 2 and the blocking plate 3, one and/or the other of which may also be circumferentially continuous or discontinuous between the axially outer portion 22 of the transmission plate 2 and the axially outer portion 32 of the blocking plate 3. When the coupling device is attached in a bead, the bead is thus obtained, for example, by additive material welding.

The transmission plate 2 and the blocking plate 3 are rotationally connected together by their axially

outer portions

22, 32 and delimit a space in which said first clutch 100 and second clutch 200 of the clutch mechanism 1 are received in particular.

First clutch 100 has a first pack 101 having at least a friction disc 101A rotationally connected to the first driven shaft through a first outer disc carrier 6. The first outer disc carrier 6 forms the output element of the first clutch 100. Friction discs 101A of first pack 101 are individually axially interposed between two successive flanges 101B. Each friction face 101A 'of one of friction discs 101A cooperates, in the engaged position, with one of radial faces 101B' of a flange 101B arranged axially on either side of said friction disc 101A. Such flange 101B is preferably a metal disc.

The second clutch 200 has a second pack 201 with at least friction discs 201A rotationally connected to the second driven shaft by a second outer disc carrier 7. The second outer disc carrier 7 constitutes an output element of the second clutch 200. Like the first clutch 100, the friction discs 201A of the second pack 201 are individually axially interposed between two consecutive flanges 201B. Each friction face 101A 'of one of friction discs 201A cooperates, in the engaged position, with one of the radial faces 201B' of a flange 201B arranged axially on either side of said friction disc 201A.

The driving plate 2 includes an opening 23 formed at the periphery. When the clutch mechanism 1 rotates, the oil for lubricating the disc packs 101, 201 is thrown radially outward and is released from the clutch mechanism 1 through the openings 23 of the drive plate 2. These openings 23 are formed circumferentially around the rotation axis O. The opening 23 extends at least partly over the radially inner portion 21 and at least partly over the axially outer portion 22 of the drive plate 2, so that oil is released from the clutch mechanism 1 more quickly.

The first and second

outer disc carriers

6, 7 are arranged side by side. The first outer disc carrier 6 has a radially inner portion 61 extending outwardly from the first output hub 60 and at an outer radial end through an axially outer portion 62 extending in a forward orientation. The axially outer portion 62 of the first outer disc carrier 6 is provided with a toothed engagement 64 intended to cooperate with a complementary set of teeth each of the friction discs 101A has at its outer radial periphery. The second outer disc carrier 7 has a radially inner portion 71 extending outwardly from the second output hub 70 and at an outer radial end through an axially outer portion 72 extending in a forward orientation. The axially outer portion 72 of the second outer disc carrier 7 is equipped with a toothed engagement 74 intended to cooperate with complementary sets of teeth each of the friction discs 201A has at its outer radial periphery. Preferably, the first and

second output hubs

60, 70 are coaxial. A snap ring 305 axially retains the first output hub 60.

Then, the first and second

outer disc carriers

6, 7 are each rotationally connected to the

friction discs

101A, 201A by meshing and connected to the respective first and second driven shafts by spline connection. The first and second

outer disc carriers

6, 7 have a general L-shape, which is formed by their radially

inner portions

61, 71 and axially

inner portions

62, 72. Preferably, they are fastened to the first and

second output hubs

60, 70, respectively, or made as a single piece. Preferably, the first outer disc carrier 6 and the first output hub 60 are fastened together by welding. Similarly, the second outer disc carrier 7 and the second output hub 70 are fastened together by welding.

For supporting the axial load, a first axial needle bearing 303 is arranged between the first outer disc carrier 6 and the second outer disc carrier 7. Similarly, a second axial needle bearing 304 is arranged between the second outer disc carrier 7 and the drive plate 2. More precisely, the first axial needle bearing 303 is arranged between the radially inner portion 61 of the first outer disc carrier 6 and the radially inner portion 71 of the second outer disc carrier 7. Similarly, a second axial needle bearing 304 is arranged between the radially inner portion 71 of the second outer disc carrier 7 and the radially inner portion 21 of the drive plate 2.

The support bearing 301 is axially arranged between the support shaft 300 and the second outer disc carrier 7. More particularly, the support shaft 300 has an inner shoulder 302 that at least partially receives the support bearing 301, such that the support bearing 301 is axially retained between the support shaft 300 and the second outer disc carrier 7 and radially between the support shaft 300 and the second output hub 70.

The first and second

outer disc carriers

6, 7 have

radial holes

63, 73, which are circumferentially distributed in said first axially

external portion

62, 72 of each of the first and second

outer disc carriers

6, 7 equipped with the

toothed engagements

64, 74 and are intended for the passage of oil introduced into the disc package 201 of the second clutch 200 or released from the disc package 101 of the first clutch 100.

Each flange 101B of the disc pack 101 of the first clutch 100 is equipped at their inner radial periphery with a set of teeth to rotationally connect them to the first inner disc carrier 4. Also, each flange 201B of the pack 201 of the second clutch 200 is equipped at their inner radial periphery with sets of teeth to rotationally connect them to the second inner disc carrier 5.

Preferably, the first clutch 100 and the second clutch 200 are in an open state and are selectively actuated during operation by the actuation system 400 to shift the axial load from the open state to the closed state. The clutch mechanism 1 is normally hydraulically controlled by means of a hydraulic fluid, such as oil.

The first and second

inner disc carriers

4, 5 are each movable around the same axis of rotation O and comprise a first

axial portion

41, 51 and a second

axial portion

42, 52. The first

axial portion

41, 51 has a toothed engagement portion 44 disposed outwardly and configured to receive the

disc pack

101, 201. For each of the first and second

inner disc carriers

4, 5, the second

axial portion

42, 52 has an

outer profile

45, 55 extending radially outwardly and configured for actuating the

respective disc pack

101, 201. The first

axial portion

41, 51 and the second

axial portion

42, 52 extend axially relative to each other in opposite directions. The first

axial section

41, 51 and the second

axial section

42, 52 are preferably designed as one piece. Such a single piece may be obtained from a tooling plate by a press process. The first inner disc carrier 4 is arranged radially outwardly with respect to the second inner disc carrier 5. The first inner disc carrier 4 and the second inner disc carrier 5 are then one above the other in the radial direction. For each

inner disc carrier

4, 5, the

toothed engagement portion

44, 54 of the first

axial portion

41, 51 engages the set of teeth of each

flange

101B, 201B in a complementary manner so as to rotationally connect them. The

outer contour parts

45, 55 of the first and second

inner disc carriers

4, 5 are formed integrally with the respective

inner disc carrier

4, 5.

In order to selectively control the state changes of the first clutch 100 and the second clutch 200 of the clutch mechanism 1, the actuation system 400 has a first actuator 401 and a second actuator 402 mounted in a housing 403 of the actuation system 400. The first clutch 100 and the second clutch 200 of the clutch mechanism 1 are actuated axially in the same direction. More specifically, the first clutch 100 is actuated axially rearwardly against the disc pack 101 by the outer profile 45 of the first inner disc carrier 4. In a similar manner, the second clutch 200 is actuated axially rearward against the disc pack 201 by the outer contour 55 of the second inner disc carrier 5.

The second axial portion 42 of the first inner disc carrier 4 extends radially inwardly to form an inner profile 46 of the first inner disc carrier 4, the inner profile 46 and the outer profile 45 together forming an actuating piston 47 (said first piston 47) of the disc pack 101 cooperating with the first inner disc carrier 4.

The first piston 47 is movable axially rearward between a disengaged position and an engaged position, which correspond to the open and closed states of the first clutch 100, respectively. The first actuator 401 is axially mounted in the actuation system 400 for axial control thereof. The first actuator 401 extends axially and is arranged axially between the axially forward positioned actuation system 400 and the axially rearward positioned first piston 47. More precisely, the first actuator 401 is arranged to act on the inner contour 46 of the first inner disc carrier 4.

The first piston 47 of the first clutch 100 has at its outer radial end an actuating portion constituted by a finger 48 extending axially rearwards so as to act on the first packet 101 of the first clutch 100. More particularly, the outer contour 45 of the first inner disc carrier 4 comprises fingers 48, which are axially oriented in the direction of the first disc pack 101. Fingers 48 act on first disc pack 101 to extend it axially in the direction of first disc pack 101. The fingers 48 are arranged circumferentially around the axis of rotation O to distribute axial loads from the first actuator 401 through the inner profile 46 to the outer profile 45 of the first inner disc carrier 4. The first piston 47 is controlled to cause, in the engaged position, an axial clamping of said first pack 101 of the first clutch 100 against the reaction means 65 of the first clutch 100.

The outer contour 45 of the first inner disc carrier 4 advantageously has teeth 49. The teeth 49 are arranged circumferentially to allow coupling of the first inner disc carrier 4 with the dual clutch mechanism 1.

For coupling the first outer disc carrier 6 to the clutch mechanism 1, the teeth 49 of the first inner disc carrier 4 are advantageously oriented axially in the direction of the second axial portion 42. The radially inner portion 31 of the blocking plate 3 comprises a notch 33 arranged to receive a tooth 49 of the outer profile 45 of the first inner disc carrier 4, so that the transmission plate 2 drives the first inner disc carrier 4.

The first inner disc carrier 4 has radial holes 43 which are distributed circumferentially in said first axial portion 41 of the first inner disc carrier 4 equipped with the toothed meshing 44 and are intended for the passage of oil introduced into the disc package 101 of the first clutch 100.

The second axial portion 52 of the second inner disc carrier 5 extends to form an outer contour 55 of the second inner disc carrier 5. The outer contour 55 of the second inner disc carrier 5 forms an actuation piston 57 (said second piston 57) of the disc package 201 cooperating with the second inner disc carrier 5.

The second piston 57 is movable axially rearward between a disengaged position and an engaged position, which correspond to the open and closed states of the second clutch 200, respectively. The second actuator 402 is axially mounted in the actuation system 400, which is axially controlled thereby. The second actuator 402 extends axially and is axially disposed between the axially forwardly positioned actuation system 400 and the axially rearwardly positioned second piston 57. More precisely, the second actuator 402 is arranged to act on the outer contour 55 of the second inner disc carrier 5.

The second piston of the second clutch 200 has at its outer radial end an actuating portion constituted by a finger 58 extending axially rearwards so as to act on the disc pack of the second clutch 200. More precisely, the outer contour 55 of the second inner disc carrier 5 comprises fingers 58, which are axially oriented in the direction of the second disc pack 102. The fingers 58 act on the disc pack 201 of the second clutch 200 to extend it axially in the direction of the second disc pack 102. The fingers 58 are arranged circumferentially around the rotation axis O to distribute the axial load from the second actuator 402 to the outer contour 55 of the second inner disc carrier 5. The second piston 57 is controlled to, in the engaged position, cause axial clamping of said disc pack 201 of the second clutch 200 against the reaction means 75 of the second clutch 200.

The outer contour 55 of the second inner disc carrier 5 advantageously has teeth 49. These teeth 49 are arranged circumferentially to allow coupling of the second inner disc carrier 5 with the dual clutch mechanism 1.

For coupling the second outer disc carrier 7 to the clutch mechanism 1, the teeth 59 of the second inner disc carrier 5 are advantageously oriented axially in the direction of the second axial section 52. The inner contour 46 of the first inner disc carrier 4 comprises notches 40 which are arranged to receive the teeth 59 of the outer contour 55 of the second inner disc carrier 5, so that the transmission plate 2 drives the second inner disc carrier 5.

The second inner disc carrier 5 has radial bores 53 which are distributed circumferentially in said first axial section 51 of the first inner disc carrier 5 equipped with the toothed toothing 54 and are intended for the passage of oil introduced into the disc package 201 of the second clutch 200.

Due to this design, the tooth 49 of the first inner disc carrier 4 and the notch 33 assembly of the blocking plate 3 allow centering the first inner disc carrier 4 and the second inner disc carrier 5 with respect to the blocking plate 3 around the rotation axis O. Furthermore, the first inner disc carrier 4 and the second inner disc carrier 5 are rotationally connected to the transmission plate 2 and axially movable with respect to the axis of rotation O. When one of the actuators 47, 57 is actuated, the axial load moves the respective inner disc carrier, so that the centering allows the respective

inner disc carrier

4, 5 to move axially and press the discs of the

respective disc pack

101, 201 against each other. The first inner disc carrier 4 can then be moved axially and guided in a circular manner by its teeth 49 engaging in the notches 33 of the blocking plate 3. Alternatively, the second inner disc carrier 5 may then be moved axially and guided in a circular manner by its teeth 59 engaging in the notches 40 of the first inner disc carrier 4.

As mentioned, the second inner disc carrier 5 is radially smaller than the actuation system 400 housing 403. The disc package 202 of the second inner disc carrier 5 is radially smaller than the actuation system 400 housing 403.

The inner profile 46 and the outer profile 45 of the first inner disc carrier 4 are offset with respect to each other. The biasing is implemented such that, when rotationally connected to each other, each

inner disc carrier

4, 5 is axially movable by means of their actuator 47, 57. Advantageously, the biasing of the inner and

outer profiles

45, 46 of the first inner disc carrier 4 allows the second inner disc carrier 5 to be mounted radially inwardly relative to the first inner disc carrier 4.

The outer contour 55 of the second inner disc carrier 5 is similar to the outer contour 45 of the first inner disc carrier 4. In the common description applied to the first and second

inner disc carriers

4, 5, the

fingers

48, 58 and the

teeth

49, 59 are designed together by deformation of the

outer contour parts

45, 55. As a result, the

first portion

45A, 55A of the

outer contour

45, 55 may extend radially outward up to a mid-position of the

respective disc pack

101, 201. Then, after the

first portion

45A, 55A, the

second portion

45B, 55B of the

outer contour

45, 55 may extend axially and radially along the

respective disc pack

101, 201 to act on the

respective disc pack

101, 201. Finally, a

third portion

45C, 55C, succeeding the

second portion

45B, 55B, may extend axially in the direction of the second

axial portion

42, 52. The ends of the second and

third portions

45B, 55B linked to each

other form fingers

48, 58, while the ends of the

third portions

45C,

55C form teeth

49, 59.

According to another embodiment applied to the first and second

inner disc carriers

4, 5, the outer contour 45 of the respective

inner disc carrier

4, 5 comprises a circular boundary oriented axially in the direction of the

respective disc pack

101, 201. The rounded profile is a variation of the outer profile embodiment that includes

fingers

48, 58. The circular boundaries act axially on the respective disc packs 101, 201 about the rotation axis O to distribute axial loads to the disc packs 101, 201. The circular boundary can be designed by deformation of the

outer contour

45, 55.

The rounded border and the

teeth

49, 59 can be designed together by deformation of the

outer contour

45, 55. In this embodiment, the ends of the

second portions

45B, 55B and the front of the

third portions

45B, 55B linked to each other form rounded borders 48, 58, while the ends of the

third portions

45C,

55C form teeth

49, 59.

The first piston 47 of the first clutch 100 and the second piston of the second clutch 200 are selectively moved axially in the same direction from the disengaged position to the engaged position and vice versa.

The actuating portions formed by the fingers 48 of the first piston 47 of the first clutch 100 and the actuating portions of the second piston 57 of the second clutch 200 of said clutch mechanism 1 are positioned radially on different radii centered on the rotation axis O.

The radially inner portion 61 of the first outer disc carrier 6 extending radially from the first output hub 60 has a wave shape. The radially inner portion 61 engages at least partially forward in the direction of the respective disc package to form a reaction means 65 of the first clutch 100 (said first reaction means 65) for allowing the disc package to be pushed forward. The first reaction means 65, formed by part of the radially inner portion 61, is circumferentially continuous around the axis of rotation.

The first clutch 100 and the second clutch 200 each have a

plastic shim

81, 82 arranged between the

respective reaction device

65, 75 and its

pack

101, 201. Said

plastic shims

81, 82 allow an axial clearance between the reaction means 65, 75 and its

disc pack

101, 201, so that said plastic shims 81, 82 axially separate the reaction means 65, 75 and the

disc pack

101, 201 from each other.

The radially

inner part

61, 71 of each

outer disc carrier

6, 7 is made of, for example, sheet metal.

Advantageously, the first shim 83 is arranged between the inner contour 46 of the first inner disc carrier 4 and the first actuator 401, and the second shim 84 is arranged between the outer contour 55 of the second inner disc carrier 5 and the second actuator 402. The spacer shims 83, 84 may be selected during assembly of the clutch mechanism 1 such that in the open position the

respective actuator

401, 402 is always engaged against the respective

inner disc carrier

4, 5.

Preferably, the

elastic return period

85, 86 for the first or

second clutch

100, 200 is constituted by elastic wave spring washers, each of which is axially interposed between the two

flanges

101B, 201B of the

pack

101, 201. When clutch 100, 200 is disconnected from its closed position to its open position, resilient return means 85, 86

push flange

101B, 201B and

friction disc

101A, 201A forward so that they are no longer coupled.

The above detailed description of the first clutch 100 may be advantageously consulted as needed for the description of the second clutch 200 and vice versa.

The foregoing description of exemplary embodiment(s) of the invention has been presented for purposes of illustration in accordance with the provisions of the patent statutes. It is not intended to be exhaustive or to limit the invention to the precise form disclosed. The embodiments disclosed above were chosen in order to best illustrate the principles of the invention and its practical application to thereby enable others skilled in the art to best utilize the invention in various embodiments and with various modifications as are suited to the particular use contemplated, provided the principles described herein are followed. This application is therefore intended to cover any variations, uses, or adaptations of the invention using its general principles. Further, this application is intended to cover such departures from the present disclosure as come within known or customary practice in the art to which this invention pertains. Thus, changes may be made in the above invention without departing from the intent and scope thereof. It is also intended that the scope of the invention be defined by the claims appended hereto.

Claims

1. A dual wet clutch mechanism (1) for a transmission system, the dual wet clutch mechanism (1) comprising a first inner disc carrier (4) and a second inner disc carrier (5), wherein each inner disc carrier (4, 5) is movable about the same axis of rotation (O) and comprises a first axial portion (41, 51) and a second axial portion (42, 52), the first axial portion (41, 51) having a toothed engagement portion (44, 54) arranged outwardly and configured to receive a first disc pack (101) and a second disc pack (201), the second axial portion (42, 52) having an outer profile portion (45, 55) extending radially outwardly and configured to actuate the first disc pack (101) and the second disc pack (201).

2. Double wet clutch mechanism (1) according to claim 1, wherein the first inner disc carrier (4) is arranged radially outwards with respect to the second inner disc carrier (5).

3. The dual wet clutch mechanism (1) according to claim 1 or 2, wherein the first inner disc carrier (4) is rotationally connected to the second inner disc carrier (5) and/or the second inner disc carrier (5) is configured to be rotationally connected to an input hub (20) of the dual wet clutch mechanism (1).

4. Double wet clutch mechanism (1) according to claim 1 or 2, wherein the rotational connection of at least one of the inner disc carriers (4, 5) is realized by teeth of the outer contour (45, 55) of the respective inner disc carrier (4, 5).

5. Double wet clutch mechanism (1) according to claim 4, wherein the teeth are designed by deformation of the ends of the outer contour (45, 55).

6. The dual wet clutch mechanism (1) according to claim 1 or 2, wherein the outer contour portion (45, 55) comprises fingers (48, 58), the fingers (48, 58) being axially oriented in the direction of a respective one of the first pack (101) and the second pack (201).

7. The dual wet clutch mechanism (1) as claimed in claim 1 or 2, wherein the outer profile (45, 55) is attached to the inner disc carrier (4, 5).

8. Double wet clutch mechanism (1) according to claim 7, wherein the outer contour (45, 55) is attached to the inner disc carrier (4, 5) by welding.

9. The dual wet clutch mechanism (1) according to claim 1 or 2, wherein the first inner disc carrier (4) and the second inner disc carrier (5) are axially movable relative to the axis of rotation (O).

10. The dual wet clutch mechanism (1) according to claim 1 or 2, wherein the second axial portion (42, 52) of the first inner disc carrier (4) extends radially inwardly to form an inner contour (46) of the first inner disc carrier (4), the inner contour (46) and the outer contour (45) of the first inner disc carrier together forming an actuation piston (47) of the first pack (101) cooperating with the first inner disc carrier (4).

11. Double wet clutch mechanism (1) according to claim 10, wherein the inner contour (46) comprises a connecting means configured to rotationally connect the second inner disc carrier (5).

12. Double wet clutch mechanism (1) according to claim 11, wherein the connecting means are formed by a notch (40).

13. The dual wet clutch mechanism (1) of claim 12, wherein the notch (40) opens inwardly.

14. Double wet clutch mechanism (1) according to claim 1 or 2, wherein the second axial portion (52) of the second inner disc carrier (5) extends to form an outer contour portion (55) of the second inner disc carrier (5), the outer contour portion (55) of the second inner disc carrier (5) forming an actuating piston (57) of the second disc pack (201) cooperating with the second inner disc carrier (5).

15. The dual wet clutch mechanism (1) as claimed in claim 12, wherein the rotational connection of at least one of the inner disc carriers (4, 5) is effected by teeth of the outer contour (45, 55) of the respective inner disc carrier (4, 5), and wherein the teeth (59) of the outer contour (55) of the second inner disc carrier (5) are received in the notches (40) of the inner contour (46) of the first inner disc carrier (4) such that the first inner disc carrier (4) centers the second inner disc carrier (5).

16. A dual wet clutch mechanism (1) according to claim 3, wherein the dual wet clutch mechanism (1) comprises a rotationally connected transmission plate (2) and a blocking plate (3), the transmission plate (2) being rotationally connected to the input hub (20), the blocking plate (3) having a radially inner portion (31), the radially inner portion (31) comprising a notch (33), the notch (33) being arranged to receive a tooth (49) of an outer profile (45) of the first inner disc carrier (4) such that the first inner disc carrier (4) and the second inner disc carrier (5) are driven by the transmission plate (2).

17. The dual wet clutch mechanism (1) according to claim 1 or 2, wherein the dual wet clutch mechanism (1) comprises a first outer disc carrier (6) and a second outer disc carrier (7), the first inner disc carrier (4) and the first outer disc carrier (6) receiving the first disc pack (101), the second inner disc carrier (5) and the second outer disc carrier (7) receiving the second disc pack (201), wherein the first outer disc carrier (6) is fastened to the first output hub (60) and the second outer disc (7) is fastened to the second output hub (70).

18. The dual wet clutch mechanism (1) according to claim 1 or 2, wherein the dual wet clutch mechanism (1) comprises an actuation system (400) with a housing (403), wherein at least one of the inner disc carriers (4, 5) is radially smaller than the housing (403) of the actuation system (400).

19. Double wet clutch mechanism (1) according to claim 18, wherein the housing (403) of the actuation system (400) comprises a first actuator (401) intended for actuating the first inner disc carrier (4) and a second actuator (402) intended for actuating the second inner disc carrier (5), the first actuator (401) acting on the first inner disc carrier (4) by means of its inner contour (46) and the second actuator (402) acting on the second inner disc carrier (5) by means of its outer contour (55).

20. The dual wet clutch mechanism (1) according to claim 1 or 2, wherein the outer contour (55) of the second inner disc carrier (5) and the inner contour (46) of the first inner disc carrier (4) lie in the same plane perpendicular to the rotation axis (O) when the clutch mechanism (1) is in the open position.

21. The dual wet clutch mechanism (1) according to claim 1 or 2, wherein the first shim (83) is arranged between the inner contour (46) of the first inner disc carrier (4) and the first actuator (401), and wherein the second shim (84) is arranged between the outer contour (45, 55) of the second inner disc carrier (5) and the second actuator (402).