CN110273936B - Clutch mechanism with plastic spacer arranged between the plate package and the reaction element - Google Patents

Abstract

A clutch mechanism (1) for a transmission system, the clutch mechanism (1) having at least one clutch (100, 200), the clutch (100, 200) having a reaction means (65, 75) and a disc pack (101, 201) configured to act on the reaction means (65, 75), wherein a plastic washer (81, 82) is arranged axially between the reaction means (65, 75) and the disc pack (101, 201).

Description

Clutch mechanism with plastic washer arranged between the plate package and the reaction device

Technical Field

The invention relates to a transmission system for a motor vehicle with a clutch mechanism.

The invention finds particular application in wet clutch mechanisms.

Background

Such a wet clutch mechanism is known, for example, from DE 10 2014 209 A1. This document describes a 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 outwardly from the actuator and then axially up to its disc pack by means of fingers acting on the plastic disc pack. When the actuator is activated, the piston moves axially to rotationally couple the friction disks of its pack and the metal. The axial load is then transferred from the piston to the disc pack. The discs of the disc pack then push against the reaction means of the respective outer disc carrier, so that the axial load is transferred from the input hub to the output hub.

However, such clutch mechanisms are not satisfactorily curved, particularly in terms of their design.

A first drawback of such a clutch mechanism is that the frictional contact between the fingers and the disc carrier when the fingers of the respective piston act on the disc package results in a high friction coefficient, increasing the temperature of the first disc of the disc package facing the reaction means and the reaction means. Such rubbing may prematurely degrade the disc pack and/or the reaction device.

Another disadvantage of such clutch mechanisms is that when the disc pack of one clutch of the mechanism is disengaged, it can still be actuated when the disc pack of the other clutch of the mechanism is engaged so that engine torque can be transferred to both clutches.

Disclosure of Invention

The object of the present invention is therefore to obviate at least one of these drawbacks, and in particular to provide a clutch mechanism which can transmit axial loads with low friction between the disc pack and the reaction means.

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

This object is achieved by a clutch mechanism for a transmission system having at least one clutch with a reaction means and a plate package configured to act on the reaction means, wherein a plastic shim plate is arranged axially between the reaction means and the plate package.

The plastic shim allows axial loads to be transferred from the disc pack to the reaction means, so that there is no longer friction between the disc pack and the reaction means. Axial loads are transferred from the disc pack to the reaction means through the plastic shim. As a result, premature failure of the disc pack and reaction device is significantly reduced.

According to the invention, the plastic shim allows an axial clearance between the reaction means and the disc pack, so that it separates the reaction means and the disc pack axially from each other. The plastic shim is designed such that the axial clearance still has a non-zero value when the clutch mechanism is in the closed position.

According to the invention, the axial thickness of the plastic shim forms the axial gap.

Advantageously, the axial thickness of the plastic shim can be used to adjust the axial clearance of the clutch. For this purpose, the plastic shim is selected among panels comprising plastic shims of different thicknesses.

According to an embodiment, the reaction means comprise a circumferential groove in which said plastic gasket is arranged. The circumferential groove radially retains the plastic shim during assembly of the clutch mechanism.

According to one embodiment, the plastic shim is intended to act on a radially intermediate position of the disc pack. Advantageously, the plastic shim has a smaller radial surface than the disc pack. Such a design is advantageously used to transmit axial loads through the smallest radial surface of the plastic shim.

According to the invention, the disc pack has at least one flange, the disc pack being delimited axially by two flanges, and wherein the radial face of one flange interacts with the plastic shim. Thus, in such a design, the plastic shim avoids contact between the radial face of the flange and the reaction means. Such contact generates high friction because the flange and the reaction means are designed in the same metallic material. Preferably, the flange and the reaction means are designed in a steel material.

According to one embodiment, a circumferential groove is formed on the flange radial face.

According to the invention, the reaction means have a reaction face oriented towards the disc pack, an axial clearance being defined between the reaction face and the radial face. A circumferential groove is formed on the reaction face of the reaction means.

According to one embodiment, the pack has at least one friction disc, the pack being radially delimited by two friction discs, and wherein a friction face of one friction disc interacts with the plastic shim. In such a design, the plastic shim avoids contact between the friction faces of the friction disc and the reaction device.

According to this embodiment, the reaction means has a reaction face oriented towards the disc pack, an axial gap being defined between the reaction face and the friction face. Advantageously, the circumferential groove is formed on a reaction face of the reaction means. In another embodiment, the circumferential groove is formed on a friction surface of the friction disc facing the reaction surface.

According to the invention, the plastic shim allows axial loads to be transmitted from the disc pack to the reaction means through said plastic shim. The plastic insert is advantageously designed with a plastic material which can absorb high axial pressures with minimal axial deformation.

Advantageously, the plastic gasket is made of PET plastic. PET plastics are advantageous because their object properties in particular have high dimensional stability and high abrasion resistance. Furthermore, with such PET plastics, the plastic shim thickness can be designed with great accuracy.

Advantageously, the plastic gasket is made of POM plastic. POM plastics are advantageous because their physical properties are, in particular, high mechanical strength and shock resistance and high dimensional stability.

In another embodiment, advantageously, the plastic shim is made of Torren (Torlon) plastic. Advantageously, a radially inner portion of the outer disc carrier of the clutch mechanism at least partially forms the reaction means.

Advantageously, the outer disc carrier is rotationally connected to the output hub.

Advantageously, the clutch mechanism is a dual clutch mechanism.

Advantageously, each clutch has a reaction means and a disc pack configured to act on the reaction means, wherein the plastic spacer is axially arranged between the reaction means and the disc pack.

Advantageously, the clutch mechanism is a dual wet clutch mechanism. Advantageously, the clutch mechanism is a radial dual clutch mechanism. Obviously, the clutch mechanism may be a radial double wet clutch mechanism.

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

fig. 2A and 2B show partial sections AA and BB of the clutch mechanism of fig. 1.

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 axis of rotation O of the dual wet clutch mechanism 1, and the terms "inner/inner" or "outer/outer" will aid understanding with respect to the axis of rotation O and according to a radial orientation orthogonal to said axial orientation.

Fig. 1 shows a radial dual wet clutch mechanism 1 for a transmission system (not shown), the clutch mechanism 1 having an axis of rotation O. Such transmission systems are designed to be installed in motor vehicles. The dual wet clutch mechanism 1 has a transmission plate 2 connected to an input hub 20 and a blocking plate 3 fastened to the transmission 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 also shown in fig. 1, 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, which are each 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 a driving spline, via an engine flywheel, to a drive shaft constituted by a crankshaft caused to rotate by an engine that is part of the motor vehicle. Then, the engine causes the drive plate 2 to rotate via 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 driving 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 transmission plate 2 is rotationally connected to a blocking plate 3, which blocking plate 3 rotationally connects said transmission 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 driving 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 driving plate 2 has, at the free front end of its forward axially external portion, a rim 22A forming said circumferentially discontinuous 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 circumferentially discontinuous 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.

As a further variant, at least the driving plate 2 and/or the blocking plate 3 has, at the free end of its axially outer portion, a rim forming said circumferentially discontinuous and radially oriented connecting portion of the blocking plate 3 or of the driving 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 connecting means, preferably with zero axial clearance c1. The zero axial clearance d rotary connection allows 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, 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, in the engaged position, interacts with one of radial faces 101B' of flanges 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 interacts, in the engaged position, with one of the radial faces 201B' of flanges 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 interact 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 provided with a toothed engagement 74 intended to interact 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, the second axial needle bearing 304 is arranged between the radially inner part 71 of the second outer disc carrier 7 and the radially inner part 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 outer portion 62, 72 of each of the first and second outer disc carriers 6, 7 equipped with the toothed meshes 64, 74 and are intended for the passage of oil introduced into the pack 201 of the second clutch 200 or released from the pack 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 portions 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 rearward against the disc pack 101 by the outer contour 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 which extends 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 a finger 48, which is axially oriented in the direction of the first axial portion 41. The finger 48 acts on the first axial portion 101 to extend it axially in the direction of the first axial portion 41. The fingers 48 are arranged circumferentially around the rotation axis O to distribute axial load from the first actuator 401 through the inner profile portion 46 of the first inner disc carrier 4 to the outer profile portion 45. The first piston 47 is controlled to cause, in the engaged position, an axial clamping of said first packet 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 circumferentially arranged 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 for axial control thereof. The second actuator 402 extends axially and is axially disposed between the axially forward positioned actuation system 400 and the axially rearward 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 57 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 45, 55 of the second inner disc carrier 5 comprises a finger 58, which is axially oriented in the direction of the first axial portion 51. The fingers 58 act on the disc pack 201 of the second clutch 200 to extend it axially in the direction of the first axial portion 51. The fingers 58 are arranged circumferentially around the rotation axis O to distribute 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.

As also shown in fig. 2A and 2B, a first plastic shim 81 is arranged axially between said first reaction means 65 and the first disc pack 101. Said first plastic shim 81 allows an axial clearance c1 (said first axial clearance c 1) between first reaction means 65 and first disc pack 101, so that said first plastic shim 81 axially separates first reaction means 65 and first disc pack 101. The axial thickness d1 of the first plastic shim 81 forms a first axial gap c1. The first reaction means 65 of the first outer disc carrier 6 comprise a circumferential groove 66 in which said first plastic gasket 81 is arranged. Said first plastic gasket 81 is intended to act on a radially intermediate position of first pack 101.

When the disc pack 101 of the first clutch 100 is pushed backwards, i.e. in the closed position, said first plastic washer 81 absorbs the axial load transmitted in the closed position of the disc pack 101. This axial load is then transmitted to the first reaction means 65 through said first plastic shim 81. As a result, the axial load of the first clutch 100 can be transmitted from the first inner disc carrier 4, which forms the first piston 47, to the first outer disc carrier 6.

Similarly, a radially inner portion 71 of the second outer disc carrier 7 extending radially from the second output hub 70 has a wave shape. Radially inner portion 71 engages at least partially forward in the direction of second pack 201 to form reaction means 75 (said second reaction means 75) for allowing pack 201 to be pushed forward. The second reaction means 75, which are formed by parts of the radially inner portion 71, are circumferentially continuous around the axis of rotation.

A second plastic shim 82 is arranged axially between said second reaction means 75 and the second disc pack 201. Said second plastic shim 82 allows an axial clearance c2 (said second axial clearance c 2) between the second reaction means 75 and the second disc pack 201, whereby said second plastic shim 82 axially separates the second reaction means 75 and the second disc pack 201. The axial thickness d2 of the second plastic shim 82 forms a second axial gap c2. The second reaction means 75 of the second outer disc carrier 7 comprise a circumferential groove 76 in which said second plastic gasket 82 is arranged. Said second plastic shim 82 is intended to act on the second disc pack 201 in a radially intermediate position.

When the disc pack 201 of the second clutch 200 is pushed backwards, said second plastic washer 82, i.e. in the closed position, said first plastic washer 81 absorbs the axial load transmitted in the closed position of the disc pack 201. This axial load is then transferred to the second reaction means 75 through said second plastic washer 82. As a result, the axial load of the second clutch 200 can be transmitted from the second inner disc carrier 5, which forms the second piston 57, to the second outer disc carrier 7.

Due to the plastic shims 81, 82, the axial load is selectively transferred to the first or second outer disc carrier 6, 7, so that an axial gap c1 is always present between the respective disc pack 101, 201 and the first or second reaction means 65, 75. The first and second plastic shims 81, 82 avoid direct mechanical contact between the first or second reaction means 65, 75 and their respective tray packs 101, 201 to prevent any premature failure due to friction. Advantageously, any risk of interaction between the reaction means 65, 75 of the first or second clutch 100, 200 and the respective disc package 101, 201 during operation of the clutch mechanism 1 is significantly reduced.

According to this embodiment, each of the packs 101, 102 of the first and second clutches 100, 200 is axially delimited by two flanges 101B, 201B, so that the radial faces 101B ', 201B' of one flange 101B interact with the respective plastic shim 81, 82, while the radial faces 101B ', 201B' of the other flange 101B, 201B interact with the outer contour 45, 55 of the respective inner disc carrier 4, 5.

First reaction means 65 have reaction surfaces 65 'oriented forward toward first disc pack 101 and second reaction means 75 have reaction surfaces 75' oriented forward toward second disc pack 201. The reaction surfaces 65', 75' each do not contact the radial surface 101B ' facing the respective flange 101B.

In fig. 1, 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 portion 52. The inner contour 46 of the first inner disc carrier 4 comprises a notch 40 which is arranged to receive a tooth 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 relative 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 offset is realized such that each inner disc carrier 4, 5 is axially movable by means of its actuator 47, 57 when being rotationally connected to each other. 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 together are designed 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 radially intermediate 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 in the direction of the first axial portion 41, 51 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 and the front of the 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 first axial portion 41, 51. The rounded profile is a variation of the embodiment comprising the 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 and third portions 45B, 55B and the front of the third portions 45B, 55B linked to each other form a rounded border 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 portion formed by the fingers 48 of the first piston 47 of the first clutch 100 and the actuating portion of the second piston 57 of the second clutch 200 of said clutch mechanism 1 are positioned radially on different radii centered on the axis of rotation 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 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 adjusting 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 can advantageously be consulted as required 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 (15)

1. A clutch mechanism (1) for a transmission system, the clutch mechanism (1) having at least one clutch (100, 200), the clutch (100, 200) having a reaction means (65, 75) and a disc pack (101, 201) configured to act on the reaction means (65, 75), wherein a shim (81, 82) is arranged axially between the reaction means (65, 75) and the disc pack (101, 201), the shim (81, 82) being manufactured from plastic.

2. The clutch mechanism (1) according to claim 1, wherein the spacers (81, 82) are made of POM, PET or torron.

3. The clutch mechanism (1) according to claim 1 or 2, wherein the spacer (81, 82) allows an axial gap (c 1, c 2) between the reaction means (65, 75) and the disc pack (101, 201) such that the spacer (81, 82) axially separates the reaction means (65, 75) and the disc pack (101, 201) from each other.

4. The clutch mechanism (1) according to claim 3, wherein the axial thickness (d 1, d 2) of the spacers (81, 82) forms the axial gap (c 1, c 2).

5. Clutch mechanism (1) according to claim 4, wherein the axial thickness (d 1, d 2) of the spacer (81, 82) allows adjusting the axial play of the clutch (100, 200).

6. The clutch mechanism (1) according to claim 1, wherein the reaction means (65, 75) comprises a circumferential groove (66, 76), in which circumferential groove (66, 76) the shim (81, 82) is arranged.

7. The clutch mechanism (1) according to claim 1, wherein the shim (81, 82) is intended to act on a radially intermediate position of the disc pack (101, 201).

8. Clutch mechanism (1) according to claim 3, wherein the disc pack (101, 201) has at least a flange (101B, 201B), the disc pack (101, 201) being axially delimited by two flanges (101B, 201B), and wherein a radial face (101B ', 201B') of one flange (101B, 201B) interacts with the spacer (81, 82).

9. The clutch mechanism (1) of claim 8, wherein the reaction means (65, 75) has a reaction face (65 ', 75') oriented towards the disc pack (101, 201), and an axial gap (c 1, c 2) is defined between the reaction face (65 ', 75') and the radial face (101B ', 201B').

10. The clutch mechanism (1) according to claim 1, wherein the spacer (81, 82) allows axial loads to be transferred from the disc pack (101, 201) to the reaction means (65, 75) through the spacer (81, 82).

11. The clutch mechanism (1) as claimed in claim 1, wherein a radially inner portion (64, 71) of the outer disc carrier (6, 7) of the clutch mechanism (1) at least partially forms the reaction means (65, 75).

12. The clutch mechanism (1) according to claim 1, wherein the outer disc carrier (6, 7) is rotationally connected to the output hub (60, 70).

13. The clutch mechanism (1) according to claim 1, wherein the clutch mechanism (1) is a dual clutch mechanism.

14. The clutch mechanism (1) according to claim 13, wherein the clutch mechanism (1) is a double wet clutch mechanism.

15. A clutch mechanism (1) according to claim 12 or 13, wherein the clutch mechanism (1) is a radial double clutch mechanism.

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