• 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 mechanism (20) with a double wet clutch for a transmission system (10), at least a first clutch (E1) and a second clutch (E2) respectively of multi-disc type, the first clutch (E1) comprising a first piston (30) and the second clutch (E2) having a second piston (90), said first and second pistons (30, 90) being moved to come, in the engaged position, to clamp a multi-disc assembly against means (60) of reaction which are interposed axially between the multi-disk assembly of each of said first and second clutches (E1, E2), said assembly respectively comprising friction discs (64, 114) rotatably connected respectively to the first shaft A1 and the second shaft A2 respectively driven by an outer disk carrier (66,116), each of said outer disk carriers having a radial extension (135,156) and an axial extension (131,151), the axial extension of one of said disk carriers; external surfaces having a radial offset (137).
    公开号:FR3026152A1
    申请号:FR1458830
    申请日:2014-09-18
    公开日:2016-03-25
    发明作者:Rabah Arhab；Herve Ribot；Laurent Caumartin
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a dual wet clutch mechanism for a transmission system.
    [0002] The present invention relates more particularly to a wet dual-clutch mechanism for a transmission system, in particular a motor vehicle, comprising around an axis of rotation at least a first clutch and a second clutch respectively multi-disk type, the first clutch having the at least one first piston and the second clutch comprising at least one second piston, said first and second pistons being displaced axially in opposite directions to come, in the engaged position, clamping a multi-disk assembly against reaction means.
    [0003] Prior art is known such a double wet clutch mechanism for a transmission system, including motor vehicle. There are in particular two designs of double clutch mechanism, on the one hand the so-called "dry" dual clutch mechanisms and, on the other hand, so-called "wet" double clutch mechanisms. The present invention relates more particularly to a double wet clutch (or "double wet clutch" in English). In the case of a wet double clutch mechanism, the clutches are generally multi-disc type and the friction linings of the discs of the multi-disc assembly are kept permanently wet with oil. The transmission system comprising said wet dual-clutch mechanism generally comprises at least one input shell which is rotatably connected to a drive shaft and a drive web to rotatably couple said input shell to said mechanism, which mechanism is controlled to selectively couple said drive shaft to a first driven shaft and a second driven shaft. To do this, the double-clutch mechanism comprises a first clutch which, arranged for example on the gearbox side, serves both for starting and engaging odd gears and a second clutch which, arranged for example on the engine side, takes support even reports and reverse. The first clutch and the second clutch alternately transmit the input power (torque and speed) of the drive shaft, which is rotatably connected to the motor, to one of the two driven shafts that are connected to the gearbox. speeds and generally coaxial. For improved safety, the first clutch and the second clutch of the mechanism are respectively disengaged at rest, ie "normally open", and are actively closed by means of hydraulic actuation of a control device which is associated to the double clutch mechanism.
    [0004] The growing interest in dual-clutch mechanisms is particularly related to the comfort and performance obtained, as well as the continuity of the acceleration during shifts, without breaking torque. Transmission systems comprising such a dual clutch mechanism also provide, in comparison with a conventional automatic gearbox, a gain in consumption and CO2 emissions. For some applications, the first clutch and the second clutch of the wet double clutch mechanism 30 are axially juxtaposed, arranged next to each other, and the pistons of each of said first and second clutches are moved axially in opposite directions for come in the engaged position.
    [0005] The reaction means of the first clutch and the second clutch are then interposed axially between the multi-disk assembly of the first clutch and the multi-disk assembly of the second clutch.
    [0006] The multi-disk assembly of the first clutch and the multi-disk assembly of the second clutch are axially remote from the axis of rotation. The multi-disk assembly of the first clutch El and the second clutch E2 respectively comprising friction discs which are rotatably connected respectively to the first shaft A1 and the second shaft A2 respectively driven by an outer disk carrier forming the output element of the 'clutch. Each outer disk carrier has a radial extension and an axial extension. The axial extension of each of the outer disk carriers extends along an axis parallel to the axis of rotation. Such an arrangement of multi-disk assemblies of the first clutch and the second clutch generates a high inertia. Such inertia can lead to premature wear of the double clutch, see a malfunction of such a double clutch. In addition, such an arrangement is bulky. Therefore, such a dual wet clutch mechanism for a transmission system is not entirely satisfactory, especially in terms of reliability of operation.
    [0007] The object of the present invention is in particular to provide a wet double clutch mechanism for a transmission system for solving at least part of the problems of the prior art, in particular the reliability. For this purpose, the invention provides a wet double clutch mechanism of the type previously described, wherein the axial extension of at least one of said outer disk carriers has a radial offset.
    [0008] Advantageously, the radial offset can significantly reduce the inertia of the multi-disk assembly and reduce the radial size of the clutch. According to other features of the invention: the outer disk carrier of the second clutch is housed inside the outer disk carrier of the first clutch, the outer disk carrier of the first clutch comprising said axial extension with the radial offset. . the axial extension of the axially offset outer disk carrier comprises a first portion and a second portion each of which is respectively located in a first cylinder and in a second cylinder, the radius R 1 of the first portion being greater than the radius R 2 of the second part. - the first part and the second part form one piece. Thus, advantageously, along the axial extension is formed locally a section of frustoconical shape, the section of this frustoconical shape narrowing away from the radial extension. - The first part and the second part each form a separate part, said parts being connected in rotation, for example by welding or riveting. The second part is connected to the first part while being offset radially in the direction of the axis of rotation relative to the first part. Such an axial extension in two parts makes it possible to have parts of different thickness with respect to each other. Thus, the inertia and the stress on the furthest part of the radial extension can be more easily controlled. one end of the first part and one end of the second part each form a radial flange, the flange of the first part and the flange of the second part being connected in rotation with each other. one end of the first part and one end of the second part each form an axially extending peripheral edge, the peripheral edge of the first part and the peripheral edge of the second part being connected in rotation with each other; by superimposing their respective peripheral edge. The connection between these two edges being such that the second part is radially offset relative to the first part. the radius R2 of the second part is reduced to a value corresponding to a clearance J measured between the two outer disk carriers, at the location of the second part of the axial extension, the clearance J being sufficient to allow the sliding from one of the outer disk carriers to the other of the outer disk carriers during assembly. More specifically, teeth of the outer disk carrier which is farthest from the axis of rotation are inserted through a toothing complementary to the other of the outer disk carrier with a slight clearance J at the time of assembly. - The axial extension of the outer disk carrier comprises at least one stiffening means for stiffening said extension.
    [0009] Due to the extension made in two parts, the near part of the radial extension can be reduced to a minimum thickness. Its rigidity can be reinforced by the presence of stiffening means on this same part. Thus, it is possible to reduce the thickness and the inertia of the clutch. the axial extension forms at least one local deformation extending in the direction opposite to the axis of rotation. the local deformation is at least partially annular. the axial extension comprises a fluted peripheral external surface. the axial extension comprises at least one opening. Thus, the inertia of the mechanism can be further reduced.
    [0010] The invention also relates to a wet double clutch mechanism of the type described above, wherein the axial extension of at least one of the two outer disk carriers of at least one of the two clutches comprises a first part and a second part each forming a separate part, the second part serving as support for the disks, the parts being rotatably connected to each other. The second part may be offset radially with respect to the first part or may be arranged along the same axis as that of the first part. Thus, such an axial extension in two parts makes it possible to have parts of different thickness relative to each other. Inertia and effort on the furthest part of the radial extension can then be more easily controlled.
    [0011] At least one opening in at least one of the parts may be provided. Advantageously, the opening is made in the first part which is related to the radial extension. Other characteristics and advantages of the invention will emerge during the reading of the detailed description which will follow 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 and which illustrates an embodiment of the reaction means according to the invention; - Figure 2 is a half-view in axial section which, angularly offset from that of Figure 1; FIGS. 3A and 3B are respectively a sectional view and a three-dimensional view of a disk carrier of the first clutch, according to the invention; FIGS. 4A and 4B are respectively a sectional view and a three-dimensional view of the disk carrier of the first clutch, according to a variant of the invention, FIG. 5 is a three-dimensional view of the disk carrier of the first clutch, according to a variant 6A and 6B are respectively a sectional view and a three-dimensional view of the disk carrier of the first clutch, according to another variant of the invention; FIGS. 7A and 7B are respectively views in axial and transverse section of the disk carriers of the transmission system, 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 axis 0. of rotation and the terms "inner / inner" or "outer / outer" with respect to the distance with the axis 0 in a radial orientation, orthogonal to said axial orientation. FIGS. 1 and 2 show an exemplary embodiment of a transmission system 10, in particular for a motor vehicle, having an axis of rotation. The transmission system 10 comprises around the axis 0 at least one input element which is rotatably connected to a driving shaft (not shown). Preferably, the input element of the system 10 comprises at least one input shell 12 which is rotatably connected to an input hub 14.
    [0012] The inlet shell 12, generally having an "L" shape, has a radially oriented portion connected by a bend to a portion of axial orientation. The hub 14 has a radially oriented portion and an axially oriented portion, the hub 14 being arranged radially inwardly relative to the shell 12. The axially oriented portion of the hub 14 located within the the radial portion extends axially rearward in a direction corresponding to that of the engine.
    [0013] The hub 14 has splines 16, formed in the outer cylindrical surface of the axial portion, for connection in rotation with the drive shaft of the input element formed by at least the shell 12 and the hub 14.
    [0014] The inner end of the radial portion of the shell 12 and the outer end of the radial portion of the hub 14 input are integral, preferably secured together by welding. Alternatively, the inner end of the radial portion of the inlet shell 12 and the outer end of the radial portion of the inlet hub 14 are secured together by riveting. The hub 14 of input is for example linked in rotation through the splines 16 at the output of a damping or damping device (such as a double damping flywheel, etc.) whose input is linked, particularly via a flywheel, the driving shaft formed by a crankshaft that rotates a motor equipping the motor vehicle. The input shell 12 is rotated by the motor via the hub 14 input.
    [0015] The inlet shell 12 is rotatably connected to a drive veil 18, which drive vane 18 rotates said inlet shell 12 to a wet double clutch mechanism 20. The inlet shell 12 and the driving veil 18 are rotatably connected by cooperation of shapes. The inlet shell 12 has, at its radially external external end, lugs 17 which extend radially outwards and which interpenetrate with lugs 19 which comprise, at its radially outward end of orientation axial, the veil 18 drive. The lugs 19 of the drive web 18 extend radially inward and are angularly offset relative to the tabs 17 to circumferentially axially insert between two lugs 17 consecutive shell 12 input. An annular ring 21 is housed axially between the lugs 17 of the input shell 12 and the lugs 19 of the drive veil 18. The wet double clutch mechanism 20 is controlled to selectively couple said drive shaft to a first driven shaft A1 and a second driven shaft A2. Preferably, the first driven shaft A1 and the second driven shaft A2 are coaxial. The wet double clutch mechanism 20 comprises at least a first clutch E1 and a second clutch E2, which are respectively multidisc type. 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 driven shafts A1, A2 being respectively connected to a box. of gear equipping the motor vehicle. In the wet dual-clutch mechanism 20, the first clutch E1 serves, for example, both to start and engage the odd gears, and the second clutch E2 then supports the even and reverse gears, alternatively the The ratios supported by said first clutch E1 and second clutch E2 are reversed. The first clutch El 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 of the hub 14 input. The first clutch E1 and the second clutch E2 alternately transmit the input power (torque and speed) of the drive shaft, which receives the input shell 12 of the system 10, to one of the two shafts Al , A2 conducted, depending on the open or closed state of each clutch El and E2. Preferably, the first clutch El 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 dual-clutch mechanism 20 is hydraulically controlled via a pressurized fluid, usually oil. To selectively control the change of state of the first clutch E1 and the second clutch E2 of the mechanism 20 of the transmission system 10, the control device comprises at least one control shaft 22 having oil supply channels 24, for example four in number as shown in Figure 1. The mechanism 20 comprises at least one hub having radial bores which are each connected to one of the channels 24 for supplying oil.
    [0016] Preferably, said at least one hub is made in two parts, a first hub 25A and a second hub 25B respectively associated with the first clutch El 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 El 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.
    [0017] In variant not shown, said at least one hub is a hub common to the first clutch El and the second clutch E2 which is made in one piece, monobloc.
    [0018] The first clutch E1 of multi-disk type comprises a piston 30 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 El. in FIGS. 1 and 2, the piston 30 is controlled in displacement by means of a control chamber 32 delimited axially by a front face of an internal radial portion of the piston 30 and by the rear radial face of a piece 34 of closing. The closing piece 34 carries at its radially outer end sealing means 36 which cooperate with an inner face of an axial portion of the piston 30 and at its radially inner end sealing means 38 which cooperate with an axial surface 40. external of the first hub 25A. Preferably, the closing piece 34 is associated with a bearing piece 42 which is axially locked by a locking ring 44 mounted in a groove 45 of the first hub 25A. Advantageously, the axial forces associated with the pressurization of the control chamber 32 are taken up by the support piece 42 and not by the closure piece 34, however, the sealing means 36 and 38. The piston 30 has at its radially inner end sealing means 46 which cooperate with the external axial surface 40 of the first hub 25A, when the piston 30 is moved axially between the disengaged positions and engaged by the pressurization of the chamber. 32 order. The piece 34 closing the chamber 32 for controlling the piston 30 comprises, between its two radial ends carrying the sealing means 36 and 38, a convex portion which cooperates with the front radial face of the piston 30 axially vis-à-vis. -screw.
    [0019] The volume of the control chamber 32 comprises an outer portion and an inner portion, located radially on either side of said convex portion of the closure piece 34.
    [0020] The control chamber 32 is fed with oil through the bore 27 which passes radially through the first hub 25A, the bore 27 placing said control chamber 32 in communication with one of the oil supply channels 24.
    [0021] The control chamber 32 of the piston 30 of the first clutch El is associated with a balancing chamber 48 delimited at least by a balancing piston 50. Advantageously, the driving veil 18 constitutes the balancing piston 50 of the first clutch El.
    [0022] The drive veil 18 thus provides a dual function, transmission of the input power on the one hand, and balancing piston in the operation of the first clutch El, on the other hand. More precisely, the function of the balancing piston 50 of the first clutch El is ensured mainly by the internal radial portion of said web 18. In a variant, the balancing piston 50 and the driving veil 18 are made in the form of two separate pieces.
    [0023] The equilibrium chamber 48 of the first clutch E1 is delimited axially by the front radial face of the balancing piston 50 formed by the radially inner portion of the driving veil 18 and by the rear radial face of the piston 30. The chamber 48 d balancing is supplied with oil through the bore 26 that includes the first hub 25A. The sealing of the equilibration chamber 48 is provided radially outwardly by means 52 for sealing which are carried by the piston 30 and which cooperate with the internal face of an axial portion of the balancing piston 50 formed by the training veil. The piston 30 of the first clutch El extends radially between the control chamber 32 located axially at the front and the equilibrium chamber 48 located axially at the rear. The piston 30 of the first clutch E1 has, at its outer radial end, an actuating portion formed by fingers 54 which extend axially rearwardly to act on a multi-disk assembly of the first clutch El. Advantageously, the veil 18 comprises openings 56 for the axial passage of said fingers 54 forming the actuating portion of the piston 30 of the clutch El. The piston 30 is controlled to clamp axially, in the engaged position, said plurality of multidiscs of the first clutch El against means 60 of reaction. In the transmission system 10 shown in FIGS. 1 and 2, the first clutch E1 and the second clutch E2 of said wet double clutch mechanism 20 are axially juxtaposed, the first clutch E1 and the second clutch E2 being arranged axially on both sides. other of said reaction means 60. Said reaction means 60 comprise at least a first reaction element 58 and a second reaction element 62 which, respectively associated with the first clutch E1 and with the second clutch E2, are axially separated from each other by a clearance " j ". Advantageously, the first reaction element 58 and the second reaction element 62 are axially separated from one another by a void space corresponding to said set "j". Due to the axial clearance "j", the first reaction element 58 and the second reaction element 62 are free to move axially independently of one another.
    [0024] Advantageously, any risk of interaction between the first reaction element 58 of the first clutch E1 and the second element 62 of the second clutch E2 during operation of the mechanism 20 is eliminated.
    [0025] The first reaction element 58 has a reaction face 59 oriented towards the front towards the first clutch E1 and the second reaction element 62 has a reaction face 61 directed rearward towards the second clutch E2.
    [0026] In the embodiment shown in the figures, the first reaction element 58 and the second reaction element 62 are in the form of at least two distinct parts. By at least two separate parts, it is meant that the first reaction element 58 and the second reaction element 62 are parts that are independent of one another and that at least until said elements 58, 62 are assembled to within the mechanism 20 double wet clutch. The first element 58 of reaction and the second element 62 of reaction are for example made of sheet metal. In variant not shown, the first element 58 of reaction and the second element 62 of reaction are made in one piece, so as to form before assembly a one-piece assembly.
    [0027] The first reaction element 58 and the second reaction element 62, made in one or at least two parts, are rotatably connected to the at least one hub of the mechanism 20. As previously described, said at least one hub is preferably made in two parts, respectively the first hub 25A and the second 25B hub. In variant not shown, said at least one hub is made in one piece, monobloc.
    [0028] Preferably, the first reaction element 58 and the second reaction element 62 are rotatably connected to the at least one hub, such as a common hub or two hubs 25A and 25B, by welding.
    [0029] Alternatively, the first reaction element 58 and the second reaction element 62 are rotatably connected to said at least one hub, such as a common hub or two hubs 25A and 25B, by riveting. Advantageously, said at least one hub, in one piece or in two parts 25A, 25B, is independent of said reaction elements 58 and 62 so as to be able in particular to be made of a material different from that used for elements 58 and 62 of reaction, according to a selected manufacturing method.
    [0030] In variant not shown, the first element 58 of reaction is formed in one piece with said first hub 25A of the first clutch El and the second element 62 of reaction is made in one piece with said second hub 25B of the second clutch E2.
    [0031] The first reaction element 58 and the second reaction element 62 comprise at least one bearing boss which convexly extends axially towards the multi-disk assembly of that of said first and second clutches E1, E2 to which the element reaction is associated.
    [0032] The first reaction element 58 comprises at least one bearing boss 63 whose front radial face constitutes said reaction face 59. The second reaction element 62 comprises at least one bearing boss 65 whose rear radial face constitutes said reaction face 61. The bosses 63 and 65 support are for example obtained by stamping said elements 58 and 62 of reaction.
    [0033] Preferably, said at least one bearing boss 63 of the first reaction element 58 and said at least one axial bearing boss 65 of the second reaction element 62 are located radially on the same radius with respect to the axis O.
    [0034] The first reaction element 58 and the second reaction element 62 are circumferentially continuous so as to form a disk. As a variant not shown, the first reaction element 58 and the second reaction element 62 comprise at least one circumferentially discontinuous outer radial portion which is formed of a plurality of reaction arms. According to this variant, the reaction element 58, 62 preferably comprises a circumferentially continuous inner radial portion formed by a ring, in particular for the rotational connection of said reaction element with said at least one hub 25A, 25B supporting it. In such an alternative, the reaction arms extend radially outwardly from the annular inner radial portion and each reaction arm is separated from the adjacent reaction arm by a radial slot. The reaction arms according to this variant advantageously comprise bearing bosses 63 and 65 respectively carrying the faces 59 and 61 of reaction. Advantageously, the first reaction element 58 and the second reaction element 62 separated axially by the clearance "j" comprise stiffening means for stiffening them and axially limiting the deflection of the first reaction element 58 and the second reaction element 62. Such stiffening means are for example formed by stampings made in the first element 58 of reaction and the second element 62 of reaction, radially below the bosses 63 and 65 support.
    [0035] The first clutch E1 and the second clutch E2 of said wet double clutch mechanism 20 are axially actuated in opposite directions, axially from front to rear against the face 59 for the piston 30 of the first clutch E1 and axially of the clutch. rearward forward against the face 61 for that of the second clutch E2. The multi-disk assembly of the first clutch El comprises at least friction disks 64 which are rotatably connected to said first shaft A1 led by an outer disk carrier 66. The outer disk carrier 66 forms the output element of the first clutch E1. The outer disk carrier 66 comprises at the outer radial periphery an axial extension 131 which is provided with a toothing 67 intended to cooperate with a complementary toothing 68 which comprises each friction disk 64 at its outer radial periphery. The outer disk carrier 66 forms the output element of the first clutch El and has a radial extension 135 and the axial extension 131. According to the invention, the axial extension 131 of the outer disk carrier 66 has a radial offset 137. The axial extension 131 includes a first portion 141 located near the radial extension 135 and a second portion 142 located remote from the radial extension 135. The first portion 141 and the second portion 142 are respectively in a first cylinder and in a second cylinder. According to the invention, the radius RI of the first part is greater than the radius R2 of the second part. According to a first embodiment of the invention FIGS. 3A and 3B, the first portion 141 and the second portion 142 are formed in one piece. The first part 141 and the second part 142 are arranged in such a way that the axial extension 131 locally comprises a substantially frustoconical section 137. On either side of this frustoconical section extends the remainder of the axial extension. 131 along an axis substantially parallel to the axis of rotation O. The frustoconical section 137 is arranged such that it narrows away from the radial extension 135.
    [0036] According to a second embodiment of FIGS. 4A and 4B, the axial extension 131 comprises a first portion 143 and a second portion 144 that are distinct from one another. The first portion 143 is formed continuously with the radial extension 135. The first portion 143 and the second portion 144 are rotatably connected by riveting. In this example, one end of each of the parts 143 and 144 forms a radial flange respectively 145 and 146 at least partially peripheral. The two parts 143 and 144 are connected in rotation by connecting the two collars 144 and 146 with each other. They are joined to each other with a radial offset of the second portion 144 relative to the first portion 142 before being riveted. The first portion 142 and the second portion 144 could be welded to each other.
    [0037] According to a third embodiment of the invention, FIGS. 6A and 6B, the axial extension 131 comprises a first portion 147 and a second portion 148. One end of each of the portions 147 and 148 forms an axial peripheral edge 149 and 150 respectively. The portions 147 and 148 are rotatably connected to each other by radial offset of the second portion 148 relative to the first portion 147 and by superposition of the axial peripheral edge 149 and the axial peripheral edge 150, one on the other. Preferably, the two peripheral edges 149 and 150 are welded to each other.
    [0038] 4A, 4B, the axial extension 131 may have at least one stiffening means 152,153 to stiffen the outer disk carrier 66. In the example illustrated in FIGS. 4A and 4B, two local deflections, such as 152, 153, extend at least partially over the peripheral periphery of said axial extension 131. Each deformation may have a localized shape extending in the direction opposite to the axis 0 or well towards the O axis.
    [0039] FIG. 5 illustrates another variant of disk carrier 66 of the first clutch with a first part having fluted shapes 157. Although not shown in FIGS. 1, 2, 3A, 3B, 6A, 6B, 7A and 7B, the deformations localized as illustrated in 152,153 in Figures 4A, 4B or 157 in Figure 5 this pressed 152,153 can also be formed by each of the axial extensions as illustrated in these other embodiments of the invention. The outer disk carrier 66 has radial holes distributed circumferentially in said axial portion provided with the toothing 67 and intended to be traversed by the oil introduced into the multi-disk assembly of the first clutch El. The outer disk carrier 66 is connected in rotation by meshing with friction discs 64 and a splined connection with said first driven shaft A1. The outer disk carrier 66 has an axially extending outlet hub 70 which has radially inside the axial grooves 72 which mesh with grooves 73 complementary to the first driven shaft A1. The outer disk carrier 66 generally has an "L" shape whose inner radial end, opposite to the toothing 67, is integral with the outlet hub 70. Preferably, the outer disk carrier 66 and the outlet hub 70 are fastened together by welding, alternatively by riveting. The friction discs 64 each comprise on their axially opposite radial faces, respectively front and rear, a friction lining 74.
    [0040] The multi-disk assembly of the first clutch El comprises flanges 76 which are provided at their inner radial periphery with a set of teeth 78 to rotate them with an inner disk carrier 80.
    [0041] The inner disk carrier 80 has at its radial outer end an axial portion having an external toothing 82 which, complementary, meshes with the internal teeth 78 of each of the flanges 76 to bind them in rotation without play. The inner disk carrier 80 comprises radial (not shown) radial holes distributed circumferentially in said axial portion provided with the toothing 82 and intended to be traversed by the oil introduced into the multi-disk assembly of the first clutch El. The friction discs 64 are, unitarily, axially interposed between two flanges 76 successive. Each of the friction lining 74 of one of the friction discs 64 cooperates in the engaged position with one of the radial faces of the flanges 76 arranged axially on either side, in front and rear, of said friction disc 64.
    [0042] The multi-disk assembly of the first clutch El comprises axially a flange 76 at each of its ends, respectively a front flange 76 whose front radial face is intended to cooperate in the engaged position with the fingers 54 forming the actuating portion of the piston 30 and a rear flange 76 whose rear radial face is intended to cooperate with the face 59 of the reaction element 58 of the reaction means 60. The first clutch El comprises elastic return means to automatically return the piston 30 in the disengaged position, corresponding to an open state of the clutch.
    [0043] Preferably, the elastic return means of the piston 30 are formed by spring washers, such as "Onduflex" type washers (registered trademark).
    [0044] The spring washers are interposed axially between the flanges 76 and arranged radially inside the friction discs 64, below the friction linings 74. Each spring washer is axially in abutment against the rear radial face of a flange 76 and against the radial face before another flange 76 axially adjacent. The elastic return means axially urge the flanges 76 and in doing so facilitates the release of the friction discs 64 and the return of the piston 30 to the disengaged position.
    [0045] In variant not shown, the piston return means of a clutch are formed by at least one spring which is for example arranged radially between the axis 0 and the inner disk carrier 80 to automatically return the piston 30 to the disengaged position .
    [0046] To directly transmit the input power, the wet dual-clutch mechanism 20 comprises connecting means which, for the first clutch E1, axially link without play at least the veil 18 drive, the inner disk carrier 80 and the reaction means 60.
    [0047] When, in a variant, the driving veil 18 and the balancing piston 50 are made in two separate parts, the connecting means advantageously also advantageously link said balancing piston 50 axially without play with the driving veil 18, the inner disk carrier 80 and the reaction means 60. The balancing piston 50 of the first clutch El being formed by the driving veil 18, the mechanism 20 has one less piece with advantages including a lower cost, simplification and increased axial compactness.
    [0048] Preferably, the connecting means are made by riveting by means of rivets 85. In variant not shown, the connecting means are made by welding, in particular by laser welding by transparency.
    [0049] The driving veil 18 comprises stampings 86 which, circumferentially distributed, protrude axially rearwards with respect to the rear radial face of the veil 18 forming the driving piston 50 balancing.
    [0050] The stampings 86 each surround a hole intended to be traversed axially by one of the rivets 85 forming said connecting means. Preferably, the rivets 85 forming the connecting means are common to the first clutch El and the second clutch E2 which will now be described. Alternatively, the mechanism 20 comprises at least two sets of separate rivets to form the connecting means, first rivets associated with the first clutch E1 and second rivets associated with the second clutch E2.
    [0051] The second clutch E2 of the wet double clutch mechanism 20 of the transmission system 10 is of similar design to that of the first clutch E1, the second clutch E2 being of multidisc type. Advantageously, reference will be made to the need for the description of the second clutch E2 to the detailed description of the first clutch El given previously. The second clutch E2 comprises a piston 90 which is axially movable, here from the rear to 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 20. The piston 30 of the first clutch E1 and the piston 90 of the second clutch E2 of said wet double clutch mechanism 20 move axially in opposite directions to pass for example from the disengaged position to the engaged position. The piston 90 of the second clutch E2 is controlled in displacement by means of a control chamber 92 delimited axially by a rear face of an inner radial portion of the piston 90 and by the radial front face of a closure piece 94. The control chamber 92 is selectively supplied with oil by the bore 29 passing radially through the second hub 25B and connected to one of the channels 24 for supplying the control shaft 22. The closure piece 94 has at its radially outer end sealing means 96 which cooperate with an inner face of an axial portion of the piston 90 and, at its radial inner end, sealing means 98 which cooperate with a surface 100 external of the second hub 25B. The surface 100 associated with the second clutch E2 is located axially behind the reaction means 60 arranged between said clutches E1 and E2, axially opposite the surface 40 associated with the piston 30 of the first clutch El. Preferably, the closing piece 94 is associated with a bearing piece 102 which is axially locked by a stop ring 104 mounted in a groove 105 of the second hub 25B.
    [0052] The piston 90 comprises at its radially inner end sealing means 106 which cooperate with the external surface 100 of the second hub 25B, when the piston 90 is moved axially between the disengaged positions and engaged by the pressurization of the chamber 92 of ordered.
    [0053] Like the closing piece 34 for the first clutch El, the closure piece 94 is shaped, generally between its radial ends carrying the sealing means 96 and 98, to come axially to cooperate with the rear radial face of the piston 90.
    [0054] The control chamber 92 is associated with a balancing chamber 108 delimited by at least one balancing piston 110. The balancing chamber 108 is fed by one of the oil supply channels 24 through the bore 28 formed in the second hub 25B. Compared with the balance piston 50 of the first clutch El formed by the sail 18 drive, the balancing piston 110 of the second clutch E2 is a separate part. The balancing chamber 108 is delimited axially by the rear radial face of the balancing piston 110 and by the front radial face of the piston 90. The sealing of the balancing chamber 108 is provided radially outward by means 112 which are carried by the piston 90 and which cooperate with the inner face of an axial portion of the balancing piston 110. The inner radial portion of the piston 90 extends radially between the control chamber 92, situated axially behind, and the equilibrium chamber 108 located axially forwardly. The piston 90 of the second clutch E2 has, at its outer radial end, an actuating portion 115 formed by a boss which extends axially forwardly towards a multi-disk assembly of the second clutch E2.
    [0055] The actuating portion 115 of the piston 90 of the second clutch E2 is circumferentially continuous, alternatively discontinuous. The actuating portion formed by the fingers 54 of the piston 30 of the first clutch El and the actuating portion 115 of the piston 90 of the second clutch E2 of said mechanism 20 are located radially on the same radius centered on the axis 0 of the system 10 Advantageously, the actuating portions of the pistons 30 and 90 are located on the same radius centered on the axis 0 as the summit portion of the bosses 63 and 65 forming support faces 59 and 61 of reaction. The piston 30 of the first clutch E1 and the piston 90 of the second clutch E2 each apply a clamping force to the multi-disk assembly associated with them in the axial direction but in an opposite direction, as opposed to the reaction taking place on the reaction elements 58 and 62. The multi-disk assembly of the second clutch E2 comprises friction discs 114 which are rotatably connected to the second shaft A2 led by an outer disk carrier 116 forming the output element of the clutch E2. The outer disk carrier 116 comprises at the outer radial periphery an axial extension 151 which is provided with an internal gearing 117 intended to cooperate with an external toothing 118 that each friction disk 114 comprises. The outer disk carrier 116 has radial holes distributed circumferentially in said axial portion provided with the toothing 117 and intended to be traversed by the oil introduced into the multi-disk assembly of the second clutch E2. The outer disk carrier 116 is rotatably linked by meshing with the friction discs 114 and by a splined connection with said second driven shaft A2. The outer disk carrier 116 has an axially extending outlet hub 120 which has radially inside the grooves 122 which mesh with complementary grooves 123 of the second driven shaft A2. Preferably, said disk carrier 116 and outlet hub 120 are fastened together by welding, alternatively by riveting.
    [0056] The friction discs 114 each comprise on their axially opposite radial faces, respectively front and rear, a friction lining 124. In the example of FIGS. 1 and 2, the outer disk carrier 116 is housed inside the outer disk carrier 66. More specifically, the disk carrier 116 is housed inside the first portion 141, 143, 147 of the axial extension 131 (FIGS. 3A, 4A, 6A).
    [0057] Figures 7A and 7B, the outer disk carrier 66 and the outer disk carrier 116 are arranged relative to each other with a clearance "J". This set "J" is calculated so that the toothing 67 of the outer carrier 66 can slide frictionlessly on the toothing 117 complementary to the outer carrier 116 at the time of assembly. The clearance "J" is measured perpendicularly between an internal face 154 of the toothing 67 of the second portion 142 of the axial extension 131 of the outer disk carrier 66 and an outer face 155 of the toothing 117 of the axial extension 151 of the record holder 116 outside. In other words, the radius R2 of the second portion 141 is calculated to be reduced to a value just sufficient to create the clearance J and allow the frictionless passage of the outer disk carrier 66 on the outer disk carrier 116. The multi-disk assembly of the second clutch E2 comprises flanges 126 which are provided at their inner radial periphery with a set of teeth 128 to rotate them with an inner disk carrier 130.
    [0058] The inner disc carrier 130 has at its outer radial end an axial portion having an external toothing 132 which meshes with the internal toothing 128 of each of the flanges 126 to rotate them in play-free rotation. The inner disc carrier 130 has radial holes. distributed circumferentially in said axial portion provided with the toothing 132 and intended to be traversed by the oil introduced into the multi-disk assembly of the second clutch E2. The friction discs 114 are, unitarily, axially interposed between two flanges 126 consecutive.
    [0059] Each of the friction lining 124 of one of the friction discs 114 cooperates in the engaged position with a radial face of one of the two flanges 126 located axially on either side.
    [0060] The multi-disk assembly of the second clutch E2 comprises axially a flange 126 at each of its ends, respectively a rear flange 126 whose rear radial face is intended to cooperate, in the engaged position, with the actuating portion 115 of the piston 90 and a front flange 126 whose front radial face is intended to cooperate with the rear face 61 of the reaction element 62. The second clutch E2 comprises elastic return means 134 for automatically returning the piston 90 to the disengaged position, corresponding to an open state of the clutch. Preferably and as for the first clutch El, the elastic return means 134 of the piston 90 are formed by spring washers, such as washers of the type "Onduflex" (registered trademark). To directly transmit the input power, the wet dual-clutch mechanism 20 comprises connecting means which, for the second clutch E2, axially link without play at least the balancing piston 110, the inner disk carrier 130 of the second clutch E2 and said reaction means 60. Advantageously, the connecting means of the second clutch E2 are made by riveting. Preferably, said connecting means of the second clutch E2 are formed by rivets 85 common with the first clutch E1 so that said connecting means are formed by the only rivets 85. As shown in FIG. The double wet clutch mechanism 20 is axially connected between the piston 30 of the first clutch E1 and the piston 90 of the second clutch E2. The connecting means axially link without play at least said drive web 18, the inner disc carrier 80 of the first clutch El, the inner disc carrier 130 of the second clutch E2 and said at least one hub carrying the reaction means 60 formed by the reaction elements 58 and 62.
    [0061] In this embodiment, the rivets 85 bind axially without play and in rotation the first hub 25A and the second hub 25B. The rivets 85 forming the connecting means enable the driving web 18 to be simultaneously connected both to the first clutch E1 and to the second clutch E2 of the mechanism and to directly transmit the input power delivered to the system 10 by the drive shaft. Preferably, the connecting means formed by the rivets 85 are used to secure the balancing piston 50 of the first clutch El here formed by the web 18 and the balancing piston 110 of the second clutch E2. Advantageously, said connecting means also axially link without play the balancing piston 50 of the first clutch El and the balancing piston 110 of the second clutch E2 of the mechanism 20. The reaction elements 58 and 62 are interposed axially between the door discs 80 inside the first clutch E1 and the disk carrier 130 inside the second clutch E2 to directly transmit the input power to the mechanism 20. As the veil 18 forming the piston 50 balancing the first clutch El , the balancing piston 110 of the second clutch E2 comprises stampings 136 which each surround a hole 138 for passage of one of the rivets 85 forming the connecting means. When, alternatively, the balancing piston 50 is a separate piece of the sail 18 drive, the balancing piston 50 is then advantageously also axially linked without play by the rivets 85 to be held in position. The connecting means formed by the rivets 85 do not, however, impede the circulation of the oil, radially from the inside to the outside, intended in particular to lubricate the friction linings 74 and 124 of the clutches E1 and E2. the stampings 86 of the web 18 forming the balancing piston 50, like the stampings 136 of the balancing piston 110, are circumferentially discontinuous. As shown in FIG. 2, there exists, thanks to the stampings 86, an axial clearance between the rear radial face of the balancing piston 50 formed by the web 18 and the front radial face of the inner disk carrier 80 enabling a radial circulation of the oil towards the multi-plate assembly of the first clutch El. Advantageously, oil passages are thus provided to allow an oil flow, radially outwardly, at the connection means formed by the rivets 85. The oil flows radially from the inside to the outside 20 according to arrows shown in particular in FIG. 2, by borrowing radial passages F of oil delimited circumferentially by two consecutive stampings 86 of the web 18 forming the piston 50 of FIG. balancing the first clutch E1 or two circumferentially consecutive stampings 136 of the balancing piston 110 of the second clutch E2. For the first clutch E1, the oil flow then radially traverses holes in the inner disk carrier 80 to circulate between the friction discs 74 and the flanges 76 of the multi-disc assembly of El before passing through the radial holes in the door. -disks 66 outside. For the second clutch E2, the oil flow passes radially through the holes of the inner disk carrier 130 to circulate between the friction discs 114 and the flanges 126 of the multi-disc assembly of E2 before passing through the radial holes of the disk carrier. 116 outside. When the connecting means are made by riveting, the sealing of the equilibrium chamber 48 of the first clutch El is ensured around the holes by contact between a radially flat, annular face which is formed in favor of the stamping. and surround the hole. Once the riveting is performed to axially bind the pieces together, said annular face cooperates with a portion of the planar radial face surrounding the hole of the inner disk carrier 80. The tightness of the equilibrium chamber 108 of the second clutch E2 is ensured around holes by contact between a radially flat annular face which is formed in favor of the stamping 136 and surrounds the hole.
    [0062] Once the riveting has been performed to axially bind the pieces together, said annular face cooperates with a portion of the planar radial face surrounding the hole of the inner disk carrier 130. Openings 158 may also be provided on the axial extension 131 of each of the embodiments of the invention FIGS. 3A, 3B, 4A, 4B, 5, 7A, 7B. An example of such openings 158 is illustrated in Figure 6B. Such openings also contribute to reducing the inertia of the assembly 10.
    权利要求:
    Claims (13)
    [0001]
    REVENDICATIONS1. Mechanism (20) with a double wet clutch for a transmission system (10), in particular for a motor vehicle, comprising around an axis (0) of rotation at least a first clutch (El) and a second clutch (E2) respectively of multi-disc type, the first clutch (El) having at least one first piston (30) and the second clutch (E2) having at least one second piston (90), said first and second pistons (30, 90) being moved axially in the direction opposite to come, in the engaged position, clamping a multi-disk assembly against means (60) of reaction which are interposed axially between the multi-disk assembly of each of said first and second clutches (E1, E2), said multi-disk assembly of the first clutch El and the second clutch E2 respectively comprising friction discs (64, 114) which are rotatably connected respectively to the first shaft Al and to the second shaft A2 led respectively by a disk carrier (66, 11). 6) forming the output element of the clutch (E1, E2), each of said outer disk carriers having a radial extension (135,156) and an axial extension (131,151), the axial extension of at least one one of said outer disk carriers having a radial offset (137).
    [0002]
    2 - Mechanism according to claim 1, wherein the outer disk carrier (116) of the second clutch is housed inside the outer disk carrier (66) of the first clutch, the outer disk carrier of the first clutch comprising said extension axial (131) with the radial offset.
    [0003]
    3 - Mechanism according to one of claims 1 to 2, wherein the axial extension of the outer disk carrier having an axial offset comprises a first portion (141,143,147) and a second portion (142,144,148) each registering respectively in a first cylinder and in a second cylinder, the radius R1 of the first part being greater than the radius R2 of the second part.
    [0004]
    4 - Mechanism according to claim 3, wherein the first portion and the second portion form a single piece.
    [0005]
    5 - Mechanism according to claim 3, wherein the first part and the second part each form a separate part, said parts being connected in rotation, for example by welding or riveting.
    [0006]
    6 - Mechanism according to claim 5, wherein one end of the first portion (143) and one end of the second portion (144) each form a radial flange (145,146), the flange of the first portion and the flange of the second part being rotatably connected to each other.
    [0007]
    The mechanism of claim 5, wherein one end of the first portion (147) and one end of the second portion (148) each form an axially extending peripheral edge (149,150), the peripheral edge of the first portion, and the peripheral edge of the second portion being rotatably connected to each other by superimposition of their respective peripheral edge.
    [0008]
    8 - Mechanism according to one of claims 3 to 7, wherein the radius R2 of the second part is reduced to a value corresponding to a clearance J measured between the two outer disk carriers, at the location of the second part of the axial extension, the clearance J being sufficient to allow the sliding of one of the outer disk carriers on the other of the outer disk carriers during assembly.
    [0009]
    9 - Mechanism according to one of claims 1 to 8, wherein the axial extension of the outer disk carrier comprises at least one stiffening means (152,153,157) for stiffening said extension.
    [0010]
    The mechanism of claim 9, wherein said axial extension forms at least one local deformation (152,153) extending in a direction opposite to the axis of rotation.
    [0011]
    11 - Mechanism according to claim 10, wherein the local deformation is at least partially annular.
    [0012]
    12 - Mechanism according to one of claims 9 to 11, wherein the axial extension comprises a fluted peripheral outer surface.
    [0013]
    13 - Mechanism according to one of claims 1 to 12, wherein the axial extension comprises at least one opening (158).
    类似技术:
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    同族专利:
    公开号 | 公开日
    FR3026152B1|2018-03-02|
    CN105443606A|2016-03-30|
    EP2998603B1|2016-10-12|
    CN105443606B|2019-10-18|
    US20160084322A1|2016-03-24|
    KR20160033623A|2016-03-28|
    EP2998603A1|2016-03-23|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    EP1195537A1|2000-10-05|2002-04-10|Ford Global Technologies, Inc., A subsidiary of Ford Motor Company|Transmission double clutch with two input shafts|
    EP1522753A1|2003-10-11|2005-04-13|BorgWarner Inc.|Hydraulic double clutch|
    US20060086586A1|2004-10-26|2006-04-27|Borgwarner Inc.|Dual clutch mechanism for a transmission|
    EP1686277A1|2005-01-27|2006-08-02|Getrag Ford Transmissions GmbH|Dual-clutch with same dimension disks|
    DE10323514A1|2003-05-24|2004-12-23|Dr.Ing.H.C. F. Porsche Ag|Coupling device, in particular multi-plate clutch for a double clutch transmission|
    EP2059689B1|2006-09-15|2015-06-24|Borgwarner Inc.|Flexplate coupling for a wet clutch transmission|
    CN101621502A|2008-06-30|2010-01-06|华为技术有限公司|Method and device for storing and searching routing table|
    US20130153355A1|2011-12-16|2013-06-20|Eaton Corporation|Hydraulic clutch assembly|US9677622B2|2015-02-27|2017-06-13|Avl Powertrain Engineering, Inc.|Clutch with opposite load application|
    EP3252332B1|2016-06-03|2020-02-26|FCA Italy S.p.A.|Motor-vehicle transmission with a double clutch coupling device|
    JP6627804B2|2017-02-26|2020-01-08|トヨタ自動車株式会社|Power transmission device for vehicles|
    DE102017212665A1|2017-07-24|2019-01-24|Zf Friedrichshafen Ag|Coupling device for a motor vehicle transmission|
    FR3070458B1|2017-08-29|2020-01-10|Valeo Embrayages|WET CLUTCH MODULE OF A MOTOR VEHICLE|
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    法律状态:
    2015-09-30| PLFP| Fee payment|Year of fee payment: 2 |
    2016-03-25| PLSC| Publication of the preliminary search report|Effective date: 20160325 |
    2016-09-28| PLFP| Fee payment|Year of fee payment: 3 |
    2017-09-29| PLFP| Fee payment|Year of fee payment: 4 |
    2018-09-28| PLFP| Fee payment|Year of fee payment: 5 |
    2019-09-30| PLFP| Fee payment|Year of fee payment: 6 |
    2020-09-30| PLFP| Fee payment|Year of fee payment: 7 |
    2021-09-30| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1458830|2014-09-18|
    FR1458830A|FR3026152B1|2014-09-18|2014-09-18|DUAL WET CLUTCH MECHANISM FOR A TRANSMISSION SYSTEM|FR1458830A| FR3026152B1|2014-09-18|2014-09-18|DUAL WET CLUTCH MECHANISM FOR A TRANSMISSION SYSTEM|
    EP15181303.7A| EP2998603B1|2014-09-18|2015-08-17|Dual wet clutch mechanism for a transmission system|
    KR1020150131046A| KR20160033623A|2014-09-18|2015-09-16|Double wet clutch mechanism for a transmission system|
    US14/856,756| US20160084322A1|2014-09-18|2015-09-17|Double wet clutch mechanism for a transmission system|
    CN201510598419.6A| CN105443606B|2014-09-18|2015-09-18|Wet-type dual-clutch mechanism for transmission system|
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