• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a transmission system (1), in particular for a motor vehicle, comprising around an axis (O) at least: - an input hub (2; 102) which is arranged to be rotatably connected to a driving shaft, and - a mechanism (10; 110) with a double wet clutch comprising: ○ an input member (3; 103) formed in particular by a disk carrier and rotatably connected to the input hub (2; ); ○ at least a first clutch (E1) and a second clutch (E2), this mechanism being rotatably connected to the input member for transmitting torque from the driving shaft. Each of the first and second clutches comprises a multi-plate assembly (50; 150; 70; 170) and a reaction member (30a; 30b; 130a; 130b), the multi-disk assembly bearing against a contact zone (32a; 32b; 132a; 132b) of the reaction member when the associated clutch is closed.
    公开号:FR3043435A1
    申请号:FR1560662
    申请日:2015-11-06
    公开日:2017-05-12
    发明作者:Arnaud Dole；Francois Thibaut；Rabah Arhab
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    "Transmission system incorporating a wet dual-clutch mechanism"
    The present invention relates to a transmission system comprising a wet double clutch mechanism.
    Such a transmission system is intended to form part of a transmission, especially for a motor vehicle or for a so-called industrial vehicle, the latter being for example a truck, a public transport vehicle, or an agricultural vehicle.
    The present invention more particularly relates to a transmission system comprising a wet double clutch movable in rotation about a main axis of rotation, which is controlled to selectively couple a drive shaft of a combustion engine to a first driven shaft and to a second driven shaft of a gearbox, said wet double clutch mechanism comprising at least a first clutch and a second clutch respectively multi-disk type, each of said first and second clutches comprising at least one axially movable piston which is driven in displacement at the by means of a control chamber to which is associated a balancing chamber defined at least by a balancing piston, said piston axially clamping in a clutched position a multi-disk assembly against reaction means, said multi-disk assembly comprising flanges and also friction discs linked in rotation via a disk carrier to one of said first and second driven trees.
    Known from the prior art such transmission systems comprising a dual wet clutch mechanism (or "Dual Wet Clutch" in English) generally multidisc type, said mechanism being located in the clutch housing of the motor vehicle.
    In certain applications, in particular but not exclusively for so-called industrial vehicles, the reliable transmission of large torques is sought while having an axial compactness of the transmission system, for example to enable it to be installed between the engine and the engine. gearbox of the vehicle.
    The engine torque to be transmitted by the transmission systems has been constantly increasing for several years, reaching values of over 4000 Nm for industrial vehicles and values of more than 500 Nm for motor vehicles. Known architectures of transmission systems comprising a wet double clutch mechanism, as described in document DE 10 2012 008 779, do not make it possible to transmit these torque values with satisfactory reliability in a satisfactory axial space.
    In DE 10 2012 008 779, the double-clutch mechanism comprises two multi-disk assemblies arranged axially on either side of separate reaction means. Each multi-disk assembly comprises respectively friction disks rotatably connected to the drive shaft via an external disk carrier and flanges rotatably connected to inner disk carriers so as to transmit the torque to the driven shafts. . A large axial space is arranged between the reaction means in order to avoid, when closing one of the two clutches, contacting the reaction means under the effect of flexing under load generated by the movable piston. Such an axial arrangement of the clutches is not favorable for the compactness of the wet double clutch mechanism and the transmission assembly.
    The object of the present invention is in particular to provide a transmission system comprising a wet double clutch mechanism for solving at least some of the problems of the prior art, in particular the axial compactness.
    For this purpose, the invention proposes a transmission system, in particular for a motor vehicle, comprising around an axis of rotation at least: an input hub which is arranged to be connected in rotation to a driving shaft, and a mechanism with a double wet clutch comprising: an input member formed in particular by a disk carrier and rotatably connected to the input hub to transmit the torque coming from the drive shaft; at least one first clutch and a second clutch each comprising a multi-disk assembly and a reaction member, the multi-disk assembly bearing against a contact zone of the reaction member when the associated clutch is closed, characterized in that each reaction member comprises a connecting portion on the input member, and in an axial direction along the axis of rotation, the contact zone associated with one of the clutches is closer to the connecting portion of the the reaction member associated with the other clutch than the junction portion associated with the reaction member of this clutch.
    This transmission system, according to the invention, has the advantage, thanks to the axial proximity of the contact zone of one of the reaction members with respect to the joining portion of the other reaction member, to form a axially compact reaction assembly. In other words, the axial space arranged between the reaction members is reduced while avoiding, during closure of one of the two clutches, contacting these reaction members under the effect of flexing under load generated by the movable piston.
    Preferably, the reaction member of one of the clutches comprises at least one slot defining a space in which is partially received the reaction member of the other clutch. In other words, the reaction members of the first and second clutches overlap axially so as to reduce the axial size. The invention may have one or the other of the characteristics described below combined with each other or taken independently of each other: Preferably, the reaction members of the first and second clutches are identical parts. - The input hub is directly connected to the input member. - The input member is formed by at least one disk carrier. - Alternatively, the input hub is connected to the input member via an intermediate piece. - The reaction member is a separate part of the input member. - The respective contact areas of the reaction members are oriented in two opposite axial directions and angularly offset. - The contact zone and the joining portion of one of the reaction members, in an axial direction along the axis of rotation, are arranged on axially offset planes. The joining portion of one of the reaction members, in an axial direction along the axis of rotation, is disposed axially between the contact zone associated with this reaction member and the contact zone associated with the other member; of reaction. The reaction member of one of the clutches has a distance d between the middle of the thickness of the junction portion and the contact zone, this distance d being greater than or equal to the sum of the half-thickness of the junction portion associated with this reaction member and the thickness of the junction portion associated with the other reaction member. - Each reaction member comprises contact zones angularly distributed about the axis of rotation. The respective contact zones of the reaction members are alternated with respect to one another. - The contact areas of the first and second clutches are formed respectively on separate parts. The contact zones of one of the clutches are formed on the same part and the contact zones of the other clutch are formed on another separate part. - The reaction member comprises a ring connected to the input member. - The joining portion is formed on the ring of the reaction member. Advantageously, the joining portions of the first and second input members are pressed against one another by means of a fixing means, for example a series of rivets. - Alternatively, the connecting portion is formed by a groove which bears on a groove formed on the disk carrier of the input member. For example, the joining portions of the input members are separated by an axial space. Each contact zone is formed by a tab of the reaction member. Two consecutive legs of one of the reaction members form between them a slot in which at least partially extends a tab of the other reaction member. - The leg has a bend on which is formed the contact zone. - The legs are distributed evenly around the axis of rotation. - The tab extends over an angular sector between 10 ° and 110 °, preferably between 15 ° and 30 °. - The wet double clutch mechanism is controlled to selectively couple said drive shaft to a first driven shaft A1 and a second driven shaft A2. - The rim of the first reaction member and the rim of the second reaction member are axially separated from each other by a space corresponding to a game "j".
    This transmission system, according to the invention, has the advantage, thanks to the axial clearance between the rims of the first and second reaction members of each of the clutches, to avoid any risk of interaction between the two reaction members. Each of the rims can move axially without coming into contact with the other under the effect of the bending under load generated by the movable piston of the associated clutch.
    According to an advantageous embodiment of the invention, the torque is transmitted to the reaction member from the outer periphery of the input member. Such a transmission system may have one or more of the following other characteristics: the disk carrier of the input member is disposed radially outside the contact zone of the reaction member. - The reaction member comprises a rim on which are connected the tabs, said rim is disposed radially within the contact zone of the reaction member.
    According to another advantageous embodiment of the invention, the torque is transmitted to the reaction member from the central part of the input member. Such a transmission system may have one or more of the following other characteristics: the disk carrier of the input member is disposed radially inside the contact zone of the reaction member. - The reaction member comprises a rim on which are connected the legs, said rim is disposed radially outside the contact zone of the reaction member. Other features and advantages of the invention will appear during the reading of the detailed description which follows for the understanding of which reference will be made to the appended drawings in which: FIG. 1 is a half-view in axial section which represents a transmission system comprising a wet double clutch mechanism according to a first embodiment of the invention; FIG. 2 is a perspective view which partly represents the wet double clutch mechanism and which illustrates the first embodiment of the reaction members according to the invention; - Figure 3 is a half-view in axial section which shows a transmission system comprising a wet double clutch mechanism according to a second embodiment of the invention; - Figures 4 and 5 are axial sectional views which partially show the wet double clutch mechanism and which illustrates the second embodiment of the reaction members according to the invention.
    In the remainder of the description and the claims, the terms "before" or "backward" will be used in a nonlimiting manner and in order to facilitate comprehension, according to the direction considered with respect to an axial orientation determined by the O axis. of rotation and the terms "inner / inner" or "outer / outer" with respect to the distance with the axis O in a radial orientation, orthogonal to said axial orientation.
    FIGS. 1 and 2 show an exemplary embodiment of a transmission system 1, in particular for a motor vehicle, having an axis O of rotation.
    The transmission system 1 comprises an inlet hub 2 arranged to be rotatably connected to a driving shaft of a combustion engine (not shown) and a wet double clutch mechanism 10, rotatable about the axis O which is controlled to selectively couple the drive shaft to a first driven shaft A1 and a second driven shaft A2 of a gearbox.
    Preferably, the first driven shaft A1 and the second driven shaft A2 are coaxial.
    The double wet clutch mechanism 10 comprises in particular an input member 3 rotatably connected to the input hub 2, a first clutch E1 and a second clutch E2 which are respectively multi-disk type. The input member 3 transmits torque from the drive shaft from the input hub 2 to the first and second clutches E1, E2.
    As illustrated in FIG. 1, the inlet hub 2 is connected to the input member 3 via a shell 6.
    The shell 6, generally having an "L" shape, comprises a radially oriented portion connected by a bend to a portion of axial orientation. The shell 6 is an intermediate piece between the inlet hub 2 and the input member 3.
    The inlet hub 2 comprises a radially oriented part and an axially oriented part 4, the inlet hub 2 being arranged radially inwardly with respect to the shell 6.
    The axially oriented portion 4 of the inlet hub 2 located inside the radial portion, extends axially rearward in a direction corresponding to that of the engine.
    The inlet hub 2 comprises splines 5, formed in the outer cylindrical surface of the axial portion, for connection in rotation with the drive shaft.
    The inlet hub 2 can be rotatably connected via the splines 5 at the outlet of a damping or damping device (such as a double damping flywheel, etc.) whose input is connected by the intermediate including a flywheel, the driving shaft formed by a crankshaft that rotates a motor equipping the motor vehicle. The inner end of the radial portion of the shell 6 and the outer end of the radial portion of the inlet hub 2 are integral, preferably fixed together by welding.
    Alternatively, the inner end of the radial portion of the inlet shell 6 and the outer end of the radial portion of the inlet hub 2 are fixed together by riveting.
    In the example shown in Figures 1 and 2, the input member 3 is formed in particular by a disk carrier 40 arranged to cooperate with the first clutch E1, by a disk carrier 60 arranged to cooperate with the second clutch E2 and by a veil 11 drive.
    The driving veil 11 is rotated by the motor via the shell 6. The shell 6 and the driving veil 11 are connected in rotation via a riveted connection 7.
    The wet double clutch mechanism 10 has the following operation:
    The first driven shaft A1 is rotated when said first clutch E1 is closed and the second driven shaft A2 is rotated when said second clutch E2 is closed, said first and second shafts A1, A2 being respectively connected to a box of speeds fitted to the motor vehicle.
    In the wet dual-clutch mechanism 10, the first clutch E1 serves, for example, both to start and engage the odd reports and the second clutch E2 then supports the even and reverse gear ratios, alternatively the ratios supported by said first clutch E1 and second clutch E2 are reversed.
    The first clutch E1 is for example arranged axially in front of the side of the gearbox and the second clutch E2 is for example arranged axially at the rear of the motor side.
    Preferably, the first clutch E1 and the second clutch E2 are in the open state, also called "normally open", and are selectively actuated in operation by a control device (not shown) to go from the open state to the closed state.
    The wet double clutch mechanism 10 is hydraulically controlled through a pressurized fluid, usually oil.
    According to the exemplary embodiment illustrated in FIG. 1, the wet double clutch mechanism 10 comprises a central hub 25 arranged to distribute the oil under pressure from the control device.
    Preferably, said central hub is made in two parts, a first hub 25a and a second hub 25b respectively associated with the first clutch E1 and the second clutch E2.
    The first hub 25a has two bores 26 and 27 which are associated with the control of the first clutch E1 located axially at the front and the second hub 25b also comprises two bores 28 and 29 which are associated with the control of the second clutch E2 situated axially. in back.
    In variant not shown, said central hub 25 is common to the first clutch E1 and the second clutch E2 which is made in one piece, monobloc.
    The first clutch E1 comprises a piston 41 which is axially movable, here from front to rear, between a disengaged position and an engaged position which respectively correspond to the open and closed states of the first clutch E1.
    As represented in FIGS. 1 and 2, the piston 41 is controlled in displacement by means of a control chamber 42 delimited axially by a front face of an internal radial portion of the piston 41 and by the rear radial face of a piston. 43 closing piece.
    The closing piece 43 is locked axially relative to the first hub 25a.
    The piston 41 has at its radially inner end sealing means 44 which cooperate with the external axial surface 45 of the first hub 25a, when the piston 41 is displaced axially between the disengaged and engaged positions by the pressurization of the chamber 42. control.
    The control chamber 42 is supplied with oil through the bore 27 which passes radially through the first hub 25a, the bore 27 placing said control chamber 42 in communication with the control device.
    The control chamber 42 of the piston 41 of the first clutch E1 is associated with a balancing chamber 46 delimited at least by a balancing piston 47.
    Advantageously, the drive web 11 constitutes the balancing piston 47 of the first clutch E1.
    The drive veil 11 thus provides a dual function, transmission of the input power on the one hand, and balancing piston in the operation of the first clutch E1, on the other hand.
    More specifically, the function of the balance piston 47 of the first clutch E1 is provided mainly by the inner radial portion of said veil 11 drive.
    The equilibrium chamber 46 of the first clutch E1 is delimited axially by the radial front face of the balancing piston 47 formed by the radially inner portion of the drive web 11 and by the rear radial face of the piston 41.
    The balancing chamber 46 is supplied with oil through the bore 26 that the first hub 25a comprises.
    The inner radial portion of the piston 41 of the first clutch E1 extends radially and is arranged axially between the control chamber 42, situated axially at the front, and the equilibrium chamber 46 located axially at the rear.
    The piston 41 of the first clutch E1 comprises, at its outer radial end, an actuating portion formed by fingers 48 which extend axially rearwardly to act on a multi-disk assembly 50 of the first clutch E1.
    Advantageously, the drive web 11 has openings 49 for the axial passage of said fingers 48 forming the actuating portion of the piston 41 of the clutch E1.
    The piston 41 is controlled to axially clamp, in the engaged position, said multi-disk assembly 50 of the first clutch E1 against a reaction assembly 30. The multi-disk assembly 50 of the first clutch E1 comprises at least friction discs 51 which are rotatably connected to said first shaft A1 driven by an outer disk carrier 52. The outer disk carrier 52 forms the output element of the first clutch E1.
    The outer disk carrier 52 comprises at the outer radial periphery an axial portion which is provided with a toothing designed to cooperate with a complementary toothing that each friction disk 51 has at its outer radial periphery.
    The outer disk carrier 52 is rotatably linked by meshing with the friction discs 51 and by a splined connection with said first driven shaft A1.
    The outer disk carrier 52 has an axially extending outlet hub 53 which is radially inwardly of the axial grooves which mesh with complementary grooves of the first driven shaft A1.
    Preferably, the outer disk carrier 52 and the outlet hub 53 are fastened together by welding, alternatively by riveting.
    The friction discs 51 each comprise on their axially opposite radial faces, respectively front and rear, a friction lining. The multi-disk assembly 50 of the first clutch E1 comprises flanges 54 which are provided at their inner radial periphery with a toothing 55 to rotate them with an inner disk carrier 40.
    The inner disc carrier 40 has at its outer radial end an axial portion having an external toothing 56 which, complementary, meshes with the internal toothing 55 of each of the flanges 54 to bind them in rotation without play.
    In the example shown, the flanges 54 are formed from a flat sheet. The thickness of the internal toothing 55 is similar to the rest of the thickness of the flange 54.
    The friction discs 51 are, unitarily, axially interposed between two successive flanges 54. Each of the friction linings of one of the friction discs 51 cooperates in the engaged position with one of the radial faces of the flanges 54 arranged axially on either side, forwardly and rearwardly, of said friction disc 51. The multi-disk assembly 50 of the first clutch E1 axially comprises a flange 54 at each of its ends, respectively a front flange 54 whose front radial face is intended to cooperate in the engaged position with the fingers 48 forming the actuating portion of the piston 41 and a rear flange 54 whose rear radial face is intended to cooperate with a reaction member 30a of the reaction assembly.
    Alternatively, the rear flange 54 may have an axial recess at the rear radial face so that the thickness of the internal toothing 55 is different from the rest of the thickness of the flange 54.
    The first clutch E1 comprises elastic return means to automatically return the piston 41 in the disengaged position, corresponding to an open state of the clutch.
    Preferably, the elastic return means of the piston 41 are formed by elastic washers interposed axially between the flanges 54 and arranged radially inside the friction discs 51, below the friction linings.
    The second clutch E2 of the wet double clutch mechanism 10 of the transmission system 1 is of similar design to that of the first clutch E1, the second clutch E2 being of multidisc type.
    Advantageously, reference is made to the need for the description of the second clutch E2 to the detailed description of the first clutch E1 given previously.
    The second clutch E2 comprises a piston 61 which is axially movable, here from the rear towards the front, between a disengaged position and an engaged position respectively corresponding to the open and closed states of the second clutch E2 of the mechanism 10.
    The piston 41 of the first clutch E1 and the piston 61 of the second clutch E2 of said wet double clutch mechanism 10 move axially in the opposite direction to pass for example from the disengaged position to the engaged position.
    The piston 61 of the second clutch E2 is controlled in displacement by means of a control chamber 62 defined axially by a rear face of an inner radial portion of the piston 61 and by the radial front face of a closure piece 63.
    The control chamber 62 is selectively supplied with oil by the bore 29 passing radially through the second hub 25b. The bore 29 places the control chamber 62 in communication with the control device (not shown).
    The control chamber 62 is associated with a balancing chamber 64 delimited by at least one balancing piston 65. The balancing chamber 64 is supplied with oil via the bore 28 made in the second hub 25b.
    Compared with the balance piston 47 of the first clutch E1 formed by the sail 11 drive, the piston 65 balancing the second clutch E2 is a separate part.
    The equilibration chamber 64 is delimited axially by the rear radial face of the balancing piston 65 and by the front radial face of the piston 61.
    The inner radial portion of the piston 61 extends radially and is arranged axially between the control chamber 62 located axially rearwardly and the equilibrium chamber 64 located axially forwardly.
    The piston 61 of the second clutch E2 has, at its outer radial end, an actuating portion 66 formed by a boss which extends axially forwardly towards a multi-disk assembly 70 of the second clutch E2. The multi-disk assembly 70 of the second clutch E2 comprises friction disks 71 which are rotatably connected to the second shaft A2 driven by an outer disk carrier 72 forming the output element of the clutch E2.
    The outer disk carrier 72 comprises at the outer radial periphery an axial portion which is provided with an internal toothing intended to cooperate with an external toothing that includes each of the friction disks 71.
    The outer disk carrier 72 is rotatably linked by meshing with the friction disks 71 and by a splined connection with said second driven shaft A2.
    The outer disk carrier 72 has an outlet hub 73 which extends axially and has radially inside the grooves which mesh with complementary grooves of the second driven shaft A2.
    The friction discs 71 each comprise on their axially opposite radial faces, respectively front and rear, a friction lining. The multi-disk assembly 70 of the second clutch E2 comprises flanges 74 which are provided at their inner radial periphery with a toothing 75 to rotate them with an inner disk carrier 60.
    The inner disc carrier 60 has at its outer radial end an axial portion having an external toothing 76 which meshes with the internal teeth 75 of each of the flanges 74 to rotate them without play.
    The friction disks 71 are, unitarily, axially interposed between two flanges 74 consecutive.
    Each of the friction linings of one of the friction disks 71 cooperates in the engaged position with a radial face of one of the two flanges 74 located axially on either side. The multi-disk assembly 70 of the second clutch E2 axially comprises a flange 74 at each of its ends, respectively a rear flange 74 whose rear radial face is intended to cooperate, in the engaged position, with the actuating portion 66 of the piston 61 and a front flange 74 whose front radial face is intended to cooperate with the reaction member 30b of the assembly 30 of reaction.
    The second clutch E2 also comprises elastic return means to automatically return the piston 61 in the disengaged position, corresponding to an open state of the clutch. The elastic return means of the clutch E2 are similar to those used for the clutch E1.
    To directly transmit the input power, the wet double clutch mechanism 10 comprises attachment means 85 common to the first clutch E1 and the second clutch E2 which axially link without play at least the veil 11 drive, the record carrier 40 inside the first clutch E1, the inner disk carrier 60 of the second clutch E2, the balancing piston 65 and the reaction members 30a, 30b of the reaction assembly 30.
    Preferably, the fastening means are made by riveting by means of rivets 85.
    As shown in FIG. 1, the attachment means 85 of the wet double-clutch mechanism 10 are arranged axially between the piston 41 of the first clutch E1 and the piston 61 of the second clutch E2.
    In the transmission system 1 shown in FIGS. 1 and 2, the first clutch E1 and the second clutch E2 of said wet double clutch mechanism 10 are axially juxtaposed, the first clutch E1 and the second clutch E2 being arranged axially on both sides. other of the reaction set. The reaction assembly 30 comprises at least a first reaction member 30a and a second reaction member 30b which, respectively associated with the first clutch E1 and the second clutch E2, are axially separated from one another by a corresponding space to a game "j".
    The first reaction member 30a and the second reaction member 30b are for example made of sheet metal.
    The first reaction member 30a and the second reaction member 30b are circumferentially continuous, so as to form respectively a ring 37a and a ring 37b.
    The ring 37a is connected to the input member 3 via a connecting portion 31a. The joining portion 31a is formed on the ring 37a of the reaction member 30a.
    The ring 37b is connected to the input member 3 via a joining portion 31b. The joining portion 31b is formed on the ring 37b of the reaction member 30b.
    Advantageously, the reaction member 30a comprises at least one contact zone 32a arranged to bear against the multi-disk assembly 50 of the first clutch E1 when the latter is closed.
    Preferably, the rear flange 54 of the multi-disk assembly 50 bears against the contact zone 32a when the clutch E1 is closed.
    The contact zone 32a of the reaction member 30a is oriented forward towards the first clutch E1.
    The contact zone 32a and the joining portion 31a of the reaction member 30a, in an axial direction along the axis of rotation O, are arranged on axially offset planes.
    As illustrated in FIG. 2, the contact zone 32a has a curved reaction surface.
    Alternatively, the contact area 32a may have a planar reaction surface.
    Preferably, the reaction member 30a comprises contact zones 32a distributed angularly around the axis of rotation O. Each contact zone 32a is formed by a tab 34a of the reaction member 30a.
    In the example shown, the tabs 34a extend radially outwardly from the ring 37a and each tab 34a is separated from the adjacent tab 34a by a slot 35a. The reaction member 30a comprises, by way of example, six tabs 34a distributed regularly around the axis of rotation O and each tab extends over an angular sector of the order of 30 °.
    Alternatively, depending on the number of contact zones chosen, the tab 34a may extend over an angular sector between 10 ° and 110 °.
    Each tab 34a has a bend on which is formed the contact zone 32a. The elbow is for example obtained by stamping the reaction member. The elbow has the advantage of stiffening the lug 34a and axially limiting the displacement of the reaction member 30a during closing of the clutch E1.
    Advantageously, the reaction member 30a comprises a rim 36a on which the tabs 34a are connected, said rim 36a is disposed radially outside the contact zone 32a of the reaction member 30a.
    The rim 36a forms a circumferentially continuous outer radial portion so as to connect all the tabs 34a to each other. The rim 36a has the advantage of stiffening the tabs 34a and axially limiting the displacement of the reaction member 30a during closing of the clutch E1.
    Preferably, the reaction members 30a, 30b of the first and second clutches E1, E2 are identical parts so as to reduce the manufacturing costs of the clutches E1 and E2. The reaction members 30a, 30b may also be of different shapes.
    Advantageously, the reaction member 30b comprises at least one contact zone 32b arranged to bear against the multi-disk assembly 70 of the second clutch E2 when the latter is closed.
    Preferably, the flange 74 before the multi-disc assembly 70 bears against the contact zone 32b when the clutch E2 is closed.
    The contact zone 32b of the reaction member 30b is directed rearward towards the second clutch E2.
    The contact zone 32b and the joining portion 31b of the reaction member 30b, in an axial direction along the axis of rotation O, are arranged on axially offset planes.
    As illustrated in FIG. 2, the contact zone 32b has a curved reaction surface.
    Alternatively, the contact area 32b may have a planar reaction surface.
    Preferably, the reaction member 30b comprises contact zones 32a distributed angularly around the axis of rotation O. Each contact zone 32b is formed by a tab 34b of the reaction member 30b.
    In the example shown, the tabs 34b extend radially outwardly from the ring 37b and each tab 34b is separated from the tab 34b adjacent by a slot 35b.
    Each leg 34b has a bend on which is formed the contact zone 32b. The elbow is for example obtained by stamping the reaction member. The bend has the advantage of stiffening the lug 34b and axially limiting the displacement of the reaction member 30b during the closure of the clutch E2.
    Advantageously, the reaction member 30b comprises a rim 36b on which are connected the tabs 34b, said rim 36b is disposed radially outside the contact zone 32b of the reaction member 30b.
    The rim 36b forms a circumferentially continuous outer radial portion so as to connect all the tabs 34b to each other. The rim 36b has the advantage of stiffening the tabs 34b and axially limiting the displacement of the reaction member 30b during closing of the clutch E2.
    Alternatively not shown, the first reaction member and the second reaction member may comprise at least a circumferentially discontinuous outer radial portion which is formed of a plurality of tabs. This variant is distinguished by the absence of external rim.
    According to the invention, the reaction member 30a comprises a joining portion 31a on the input member 3 and a contact zone 32a, and in an axial direction along the axis of rotation O, the contact zone 32a associated with the first clutch E1 is closer to the junction portion 31b of the reaction member 30b associated with the second clutch E2 than the junction portion 31a associated with the reaction member 30a of the clutch E1.
    Conversely, the reaction member 30b comprises a joining portion 31b on the input member 3 and a contact zone 32b, and in an axial direction along the axis of rotation O, the contact zone 32b associated with the second clutch E2 is closer to the junction portion 31a of the reaction member 30a associated with the first clutch E1 than the junction portion 31b associated with the reaction member 30b of the clutch E2.
    The contact areas 32a, 32b of the first and second clutches E1 and E2 are respectively formed on separate parts. The reaction member 30a of the first clutch E1 comprises a plurality of slots 35a defining a space in which is partially received the reaction member 30b of the second clutch E2. The reaction members 30a, 30b of the first and second clutches E1, E2 axially overlap so as to reduce the axial size of the wet dual-clutch mechanism 10 and the transmission system 1. Advantageously, the two consecutive legs of one of the reaction members form between them a slot in which at least partially extends a tab of the other reaction member. The assembly of the reaction members 30a, 30b according to the invention makes it possible to reduce the axial size of the transmission system 1. The respective contact areas 32a, 32b of the reaction members 30a, 30b are alternated with respect to one another.
    In the embodiment shown in FIGS. 1 and 2, the disc carrier 40 of the inlet member 3 is disposed radially inside the contact zone 32a of the reaction member 30a and carries it disc 60 of the input member 3 is disposed radially inside the contact zone 32b of the reaction member 30b.
    The actuating portion formed by the fingers 48 of the piston 41 of the first clutch E1 and the actuating portion 66 of the piston 61 of the second clutch E2 of said wet double clutch mechanism 10 are located radially on the same radius centered on the axis. O of the transmission system 1.
    Advantageously, the actuating portions of the pistons 41 and 61 are located on the same radius centered on the axis O as the summit portion of the tabs 34a and 34b forming the contact zones 32a and 32b.
    The piston 41 of the first clutch E1 and the piston 61 of the second clutch E2 each apply a clamping force to the multi-disc assembly 50, 70 which is associated with them in the axial direction but in an opposite direction, as opposed to the reaction s'. performing on the reaction members 30a and 30b.
    The respective contact areas 32a, 32b of the reaction members 30a, 30b are oriented in two opposite axial directions and angularly offset.
    When assembling the wet dual-clutch mechanism 10, the reaction members 30a, 30b are mounted inverted relative to each other so as to place the lugs of one of the reaction members in the slots of FIG. the other and vice versa. In this way, the joining portion 31a of the reaction member 30a, in an axial direction along the axis of rotation O, is arranged axially between the contact zone 32a associated with this reaction member and the contact zone 32b associated with the other reaction member 30b. Similarly, the joining portion 31b of the reaction member 30b, in an axial direction along the axis of rotation O, is disposed axially between the contact zone 32b associated with this reaction member and the associated contact zone 32a to the other reaction member 30a.
    As illustrated in Figures 1 and 2, the joining portions 31a, 31b are formed in the thickness of the sheet in which are formed the reaction members 30a and 30b.
    Advantageously, the reaction member 30a of the clutch E1 has a distance d between the middle of the thickness of the joining portion 31a and the contact zone32a, this distance d being greater than or equal to the sum of the half thickness of the joining portion 31a associated with this reaction member and the thickness of the joining portion 31b associated with the other reaction member 30b. Similarly, the reaction member 30b of the clutch E2 has a distance d between the middle of the thickness of the joining portion 31b and the contact zone32b, this distance d being greater than or equal to the sum of the half thickness of the joining portion 31b associated with this reaction member and the thickness of the joining portion 31a associated with the other reaction member 30a. The reaction member, made for example of sheet metal, has a neutral fiber defining the medium of the thickness of said reaction member.
    The rim of the first reaction member 30a and the rim of the second reaction member 30b are axially separated from each other by a space corresponding to the game "j". Due to the axial clearance "j", the first reaction member 30a and the second reaction member 30b are free to move axially independently of one another. The axial displacement corresponds to the bending either of the first reaction member 30a or of the second reaction member 30b under the axial load transmitted by the pistons 41, 61 of the first and second clutches E1, E2.
    Advantageously, the reaction members 30a and 30b may comprise additional rib-type stiffening means.
    It eliminates any risk of interaction between the first reaction member 30a of the first clutch E1 and the second reaction member 30b of the second clutch E2 during operation of the double clutch mechanism wet.
    The reaction members 30a and 30b are separate parts of the input member 3.
    By separate parts, it is meant that the first reaction member 30a and the second reaction member 30b are parts independent of one another and at least until their assembly within the double clutch mechanism wet. As illustrated in FIG. 1, the reaction members 30a, 30b are assembled on the input member 3 and the junction portions 31a, 31b are pressed against one another by means of the fixing means 85. represented in the form of a series of rivets.
    As previously described, said central hub 25 is preferably made in two parts, respectively the first hub 25a and the second 25b hub.
    In the exemplary embodiment shown in FIGS. 1 and 2, the first reaction member 30a and the second reaction member 30b are respectively connected in rotation to the hubs 25b and 25a by welding.
    Advantageously, the hubs 25b, 25a are independent of said reaction members 30a, 30b so as to be able in particular to be made of a material different from that used for the reaction members 30a, 30b, according to a chosen manufacturing method.
    In variant not shown, the reaction member is formed in one piece with the hub.
    FIGS. 3, 4 and 5 show a second embodiment of the invention with a transmission system 1 substantially similar to that just described in FIGS. 1 and 2, with the exception of the fact that that the inlet hub 102 is directly connected to the input member 103.
    In this example, the transmission system 1 comprises an inlet hub 102 arranged to be rotatably connected to a drive shaft and a double wet clutch mechanism 110, comprising an input member 103, a first clutch E1 and a second clutch E2 which are respectively multidisc type. The wet double clutch mechanism 110 is controlled to selectively couple the drive shaft to a first driven shaft A1 and a second driven shaft A2 of a gearbox.
    The inlet hub 102 has splines 105, formed in the outer cylindrical surface of the axial portion 104, for connection in rotation with the drive shaft. The input member 103 is formed in particular by a disk carrier 140 arranged to cooperate with the first and second clutches E1 and E2.
    The disk carrier 140 and the inlet hub 102 are integral, preferably secured together by welding.
    The first clutch E1 and the second clutch E2 of said double clutch mechanism 110 are axially juxtaposed, the first clutch E1 and the second clutch E2 being arranged axially on either side of a reaction assembly 130.
    As illustrated in Figure 3, the first clutch E1 is arranged axially at the rear of the engine side and the second clutch E2 is arranged axially at the front of the gearbox side. The reaction assembly 130 comprises at least a first reaction member 130a and a second reaction member 130b. The first reaction member 130a and the second reaction member 130b are circumferentially continuous, so as to form respectively a ring 137a and a ring 137b.
    The ring 137a is connected to the input member 103 via a joining portion 131a. The joining portion 131a is formed on the ring 137a of the reaction member 130a. The joining portion 131a is formed by a groove 138a which bears on a groove 156 formed on the radial outer end of the disk carrier 140 of the input member 103.
    The ring 137b is connected to the input member 103 via a joining portion 131b. The joining portion 131b is formed on the ring 137b of the reaction member 130b. The joining portion 131b is formed by a groove 138b which bears on the groove 156 formed on the radially outer end of the disk carrier 140 of the input member 103.
    Advantageously, the reaction member 130a comprises at least one contact zone 132a arranged to bear against a multi-disk assembly 150 of the first clutch E1 when the latter is closed.
    Advantageously, the reaction member 130b comprises at least one contact zone 132b arranged to bear against a multi-disk assembly 170 of the second clutch E2 when the latter is closed. Unlike the first embodiment of the invention, the disk holder 140 of the input member 103 is disposed radially outside the contact zones 132a, 132b of the reaction members 130a, 130b.
    The first clutch E1 comprises a piston 141 which is axially movable, here from the rear to the front, between a disengaged position and an engaged position. The piston 141 is controlled to clamp axially, in the engaged position, the multi-disk assembly 150 of the first clutch E1 against the reaction member 130a. The multi-disk assembly 150 of the first clutch E1 comprises at least flanges 154 which are rotatably connected to said first shaft A1 driven by an inner disk carrier 152.
    In the example shown, the flanges 154 are formed from a flat sheet and the connection in rotation with the disk carrier 140 is via splines.
    The inner disk carrier 152 forms the output element of the first clutch E1. The multi-disk assembly 150 of the first clutch E1 comprises at least friction disks 151 which are rotatably connected to the drive shaft by the disk carrier 140 outside.
    The outer disk carrier 140 has at its outer radial end an axial portion having an internal toothing 156 which, in a complementary manner, meshes with the external toothing 153 of each of the friction discs 151 to rotate them without play.
    The friction disks 151 are, unitarily, axially interposed between two successive flanges 154. The multi-disk assembly 150 of the first clutch E1 comprises axially a front flange 154 whose front radial face is intended to cooperate in the engaged position with the reaction member 130a of the reaction assembly 130.
    The second clutch E2 comprises a piston 161 which is axially movable, here from front to rear, between a disengaged position and an engaged position. The piston 161 is controlled to clamp axially, in the engaged position, the multi-disk assembly 170 of the second clutch E2 against the reaction member 130b. The multi-disk assembly 170 of the second clutch E2 comprises at least flanges 174 which are rotatably connected to said first shaft A2 led by an internal disk carrier 172.
    In the example shown, the flanges 174 are formed from a flat sheet and the connection in rotation with the disk carrier 140 is via splines.
    The inner disk carrier 172 forms the output element of the first clutch E2. The multi-disc assembly 170 of the second clutch E2 comprises at least friction disks 171 which are rotatably connected to the drive shaft by the outer disk carrier 140.
    The outer disk carrier 140 has at its outer radial end an axial portion having an internal toothing 156 which, in a complementary manner, meshes with the external teeth 173 of each of the friction disks 171 to rotate them without play.
    The disks 171 of friction are, unitarily, axially interposed between two successive flanges 174. The multi-disk assembly 170 of the second clutch E2 axially comprises a rear flange 174 whose rear radial face is intended to cooperate in the engaged position with the reaction member 130b of the reaction assembly 130.
    According to the invention, the reaction member 130a comprises a connecting portion 131a on the input member 103 and a contact zone 132a, and in an axial direction along the axis of rotation O, the contact zone 132a associated with the first clutch E1 is closer to the junction portion 131b of the reaction member 130b associated with the second clutch E2 than the junction portion 131a associated with the reaction member 130a of the clutch E1.
    Conversely, the reaction member 130b includes a connecting portion 131b on the input member 103 and a contact zone 132b, and in an axial direction along the axis of rotation O, the contact zone 132b associated with the second clutch E2 is closer to the junction portion 131a of the reaction member 130a associated with the first clutch E1 than the junction portion 131b associated with the reaction member 130b of the clutch E2.
    As illustrated in Figures 4 and 5, the junction portions 131a, 131b are formed in the thickness of the sheet in which are formed the reaction members 130a and 130b. Unlike the first embodiment of the invention, the joining portions 131a, 131b of the input members 130a, 130b are separated by an axial space.
    The joining portions 131a, 131b are respectively in contact with elastic rings 139a, 139b inserted into grooves formed on the axial portion of the disk carrier 140. The reaction members 130a, 130b are retained axially by means of these rings. elastics 139a and 139b.
    Advantageously, the reaction member 130a of the clutch E1 has a distance d between the middle of the thickness of the joining portion 131a and the contact zone 132a, this distance d being greater than or equal to the sum of the half thickness of the joining portion 131a associated with this reaction member and the thickness of the joining portion 131b associated with the other reaction member 130b. Similarly, the reaction member 130b of the clutch E2 has a distance d between the middle of the thickness of the joining portion 131b and the contact zone 132b, this distance d being greater than or equal to the sum of the half-thickness of the joining portion 131b associated with this reaction member and the thickness of the joining portion 131a associated with the other reaction member 130a.
    As illustrated in FIGS. 4 and 5, each contact zone 132a is formed by a tab 134a of the reaction member 130a. The tabs 134a extend radially inwardly from the crown 137a and each tab 134a is separated from the adjacent tab 134a by a slot 135a.
    Advantageously, the reaction member 130a comprises a rim 136a on which are connected the tabs 134a, said rim 136a is disposed radially inside the contact zone 132a of the reaction member 130a.
    Similarly, each contact zone 132b is formed by a tab 134b of the reaction member 130b. The tabs 134b extend radially inwardly from the ring 137b and each tab 134b is separated from the adjacent tab 134b by a slot 135b.
    Advantageously, the reaction member 130b includes a rim 136b on which are connected the tabs 134b, said rim 136b is disposed radially inside the contact zone 132b of the reaction member 130b.
    According to the invention, the rim of the first reaction member 130a and the rim of the second reaction member 130b are axially separated from one another by a space corresponding to a set "j".
    权利要求:
    Claims (15)
    [1" id="c-fr-0001]
    Transmission system (1), in particular for a motor vehicle, comprising around an axis of rotation (O) at least: - an input hub (2; 102) which is arranged to be rotatably connected to a driving shaft, and - a mechanism (10; 110) with a double wet clutch comprising: an input member (3; 103) rotatably connected to the input hub (2; 102) and formed in particular by a disk carrier (40; 60; 140) for transmitting torque from the driving shaft; at least one first clutch (E1) and one second clutch (E2) each comprising a plurality of multidiscs (50; 150; 70; 170) and a reaction member (30a; 30b; 130a; 130b); in abutment against a contact zone (32a; 32b; 132a; 132b) of the reaction member when the associated clutch is closed, characterized in that each reaction member (30a; 30b; 130a; 130b) comprises a portion joining means (31a; 31b; 131a; 131b) on the input member and in an axial direction along the axis of rotation (O) the contact zone (32a; 32b; 132a; one of the clutches is closer to the junction portion of the reaction member associated with the other clutch than the junction portion associated with the reaction member of this clutch.
    [2" id="c-fr-0002]
    2. Transmission system (1) according to claim 1, characterized in that the reaction member (30a; 30b; 130a; 130b) of one of the clutches (E1; E2) comprises at least one slot (35a; 35b; 135a; 135b) defining a space in which the reaction member of the other clutch is partially received.
    [3" id="c-fr-0003]
    3. Transmission system (1) according to one of claims 1 to 2, characterized in that the respective contact areas (32a, 32b, 132a, 132b) of the reaction members are oriented in two opposite axial directions and angularly offset. .
    [4" id="c-fr-0004]
    4. Transmission system (1) according to one of claims 1 to 3, characterized in that the contact zone (32a; 32b; 132a; 132b) and the connecting portion (31a; 31b; 131a; 131b) of one of the reaction members, in an axial direction along the axis of rotation (O), are arranged on axially offset planes.
    [5" id="c-fr-0005]
    5. Transmission system (1) according to one of the preceding claims, characterized in that the joining portion (31a; 31b; 131a; 131b) of one of the reaction members, in an axial direction along the axis rotation (O) is disposed axially between the contact zone associated with this reaction member and the contact zone associated with the other reaction member.
    [6" id="c-fr-0006]
    Transmission system (1) according to one of the preceding claims, characterized in that the reaction member (30a; 30b; 130a; 130b) of one of the clutches (E1; E2) has a distance d between the middle of the thickness of the junction portion and the contact zone, this distance d being greater than or equal to the sum of the half-thickness of the junction portion associated with this reaction member and the thickness of the junction portion associated with the other reaction member.
    [7" id="c-fr-0007]
    7. System (1) for transmission according to one of the preceding claims, characterized in that each reaction member (30a, 30b; 130a; 130b) comprises contact zones (32a; 32b; 132a; 132b) angularly distributed around of the axis of rotation (O).
    [8" id="c-fr-0008]
    8. Transmission system (1) according to one of the preceding claims, characterized in that each contact zone (32a; 32b; 132a; 132b) is formed by a tab (34a; 34b; 134a; 134b) of the reaction organ.
    [9" id="c-fr-0009]
    9. Transmission system (1) according to claim 8, characterized in that two consecutive lugs (34a; 34b; 134a; 134b) of one of the reaction members form between them a slot (35a; 35b; 135a; 135b) in which at least partially extends a tab of the other reaction member.
    [10" id="c-fr-0010]
    10. System (1) for transmission according to claim 8, characterized in that the tab (34a; 34b; 134a; 134b) comprises a bend on which is formed the contact zone (32a; 32b; 132a; 132b).
    [11" id="c-fr-0011]
    Transmission system (1) according to one of the preceding claims, characterized in that the disk carrier (140) of the input member (103) is arranged radially outside the contact zone ( 132a; 132b) of the reaction member (130a; 130b).
    [12" id="c-fr-0012]
    12. System (1) for transmission according to the preceding claim, characterized in that the reaction member (130a; 130b) comprises a rim (136a; 136b) on which are connected the tabs (134a; 134b), the said rim is disposed radially within the contact zone (132a; 132b) of the reaction member.
    [13" id="c-fr-0013]
    Transmission system (1) according to one of claims 1 to 10, characterized in that the disk carrier (40; 60) of the input member (3) is arranged radially inside the contact zone (32a; 32b) of the reaction member (30a; 30b).
    [14" id="c-fr-0014]
    14. System (1) for transmission according to the preceding claim, characterized in that the reaction member (30a; 30b) comprises a rim (36a; 36b) on which are connected the tabs (34a; 34b), the said rim is disposed radially outside the contact area (32a; 32b) of the reaction member.
    [15" id="c-fr-0015]
    15. System (1) for transmission according to one of claims 12 and 14, characterized in that the rim (36a; 136a) of the first reaction member (30a; 130a) and the rim (36b; 136b) of the second member reaction members (30b; 130b) are axially separated from each other by a space corresponding to a set "j".
    类似技术:
    公开号 | 公开日 | 专利标题
    EP3371474B1|2019-09-11|Transmission system comprising a dual wet-clutch mechanism
    EP2998603B1|2016-10-12|Dual wet clutch mechanism for a transmission system
    EP2993367B1|2017-05-31|Dual wet clutch mechanism for a transmission system
    EP3364063A1|2018-08-22|Compact dual clutch mechanism and transmission system comprising such a dual clutch mechanism
    EP3006761B1|2018-09-12|Transmission system comprising a dual wet clutch mechanism
    EP2993368B1|2020-02-26|Transmission system comprising a dual wet clutch mechanism
    FR3059742A1|2018-06-08|ASSEMBLED DISC RACK AND DUAL WET CLUTCH MECHANISM INCLUDING THE ASSEMBLED DISK HOLDER
    WO2018024966A1|2018-02-08|Compact dual-clutch mechanism and transmission system comprising such a dual-lutch mechanism
    EP3580468B1|2021-03-03|Detachable double-clutch mechanism
    EP3219998B1|2019-01-02|Clutch mechanism and method of assembling such a mechanism on a transmission chain
    FR3034480B1|2019-08-16|TRANSMISSION SYSTEM COMPRISING A WET DOUBLE CLUTCH MECHANISM
    WO2018096114A1|2018-05-31|Radial assembly of a clutch mechanism on a transmission
    EP3252333B1|2019-01-09|Axial interlocking system for a clutch mechanism
    WO2018104139A1|2018-06-14|Torsion damping device
    FR3051863B1|2019-07-26|COMPACT CLUTCH MECHANISM COMPRISING SEPARATE RADIAL BEARINGS OF AXIAL BEARINGS
    FR3097920A1|2021-01-01|WET DOUBLE CLUTCH MECHANISM INCLUDING ASSEMBLED DISC HOLDER
    FR3097922A1|2021-01-01|ASSEMBLED DISC CARRIER AND WET DOUBLE CLUTCH MECHANISM INCLUDING SUCH ASSEMBLED DISC CARRIER
    WO2018211099A1|2018-11-22|Dual clutch mechanism
    FR3101926A1|2021-04-16|"COMPACT WET DOUBLE CLUTCH MECHANISM"
    WO2021105266A1|2021-06-03|Clutch module
    WO2018086905A1|2018-05-17|Compact dual-clutch mechanism and transmission system comprising such a dual-clutch mechanism
    FR3085731A1|2020-03-13|DOUBLE CLUTCH MECHANISM
    同族专利:
    公开号 | 公开日
    EP3371474A1|2018-09-12|
    EP3371474B1|2019-09-11|
    FR3043435B1|2018-02-09|
    WO2017076752A1|2017-05-11|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE102007041575A1|2007-09-01|2009-03-05|Borgwarner Inc., Auburn Hills|Method for fitting and aligning clutch has alignment jig fitted into clutch and moved axially and rotationally by an external tool|
    DE102008048801B3|2008-09-24|2010-06-17|Getrag Ford Transmissions Gmbh|Support element i.e. disk-like support plate, for clutch device arranged between engine and transmission of motor vehicle, has segments arranged at periphery of plate, separated by radial gaps and associated to respective support units|
    DE102009047953A1|2009-10-01|2011-04-07|Volkswagen Ag|Clutch i.e. double clutch, for automatic or automated double clutch transmission of motor vehicle, has supporting disk supported at external lamella carrier or internal lamella carrier, where spring arrangements are supported at disk|
    US20130153355A1|2011-12-16|2013-06-20|Eaton Corporation|Hydraulic clutch assembly|FR3081947A1|2018-05-30|2019-12-06|Valeo Embrayages|REACTION ELEMENT FOR A MULTI-DISC CLUTCH|
    DE102016222971A1|2016-11-22|2018-05-24|Schaeffler Technologies AG & Co. KG|coupling device|
    FR3067076B1|2017-05-31|2019-12-06|Valeo Embrayages|CLUTCH MECHANISM COMPRISING TWO SEPARATE ASSEMBLIES BY A DEVICE FOR ADJUSTING AN AXIAL DISTANCE|
    FR3067077B1|2017-05-31|2019-12-06|Valeo Embrayages|CLUTCH MECHANISM COMPRISING TWO ASSEMBLIES CONNECTED BY AN ASSEMBLY DEVICE|
    CN110273936A|2018-03-15|2019-09-24|法雷奥离合器公司|The clutch mechanism of plastic spacer is disposed between Pan Bao and reaction device|
    法律状态:
    2016-11-30| PLFP| Fee payment|Year of fee payment: 2 |
    2017-05-12| PLSC| Publication of the preliminary search report|Effective date: 20170512 |
    2017-11-30| PLFP| Fee payment|Year of fee payment: 3 |
    2019-11-29| PLFP| Fee payment|Year of fee payment: 5 |
    2020-11-30| PLFP| Fee payment|Year of fee payment: 6 |
    2021-11-30| PLFP| Fee payment|Year of fee payment: 7 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1560662|2015-11-06|
    FR1560662A|FR3043435B1|2015-11-06|2015-11-06|TRANSMISSION SYSTEM COMPRISING A WET DOUBLE CLUTCH MECHANISM|FR1560662A| FR3043435B1|2015-11-06|2015-11-06|TRANSMISSION SYSTEM COMPRISING A WET DOUBLE CLUTCH MECHANISM|
    PCT/EP2016/075987| WO2017076752A1|2015-11-06|2016-10-27|Transmission system comprising a dual wet-clutch mechanism|
    EP16787879.2A| EP3371474B1|2015-11-06|2016-10-27|Transmission system comprising a dual wet-clutch mechanism|
    [返回顶部]