• 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 wet clutch mechanism (E1, E2) for a torque transmission system, in particular for a motor vehicle, comprising: - a torque input disk carrier (10, 20) driven in rotation by a shaft driving, - a torque output disc holder (16, 26) rotated by a driven shaft, - a multi-disc assembly, - an axially movable piston (30, 80) which is driven in motion by means of a chamber control unit (32, 36) with which is associated a balancing chamber (34, 38) delimited by a balancing cover (40, 90, 140), said movable piston axially releasing the multi-disk assembly in a disengaged position. under the action of an elastic washer (50) arranged axially between the mobile piston and the balancing lid, and wherein a first bearing washer supported by the movable piston and a second support washer supported by the lid Balancing are in direct contact with the spring washer (50).
    公开号:FR3056660A1
    申请号:FR1659137
    申请日:2016-09-27
    公开日:2018-03-30
    发明作者:Laurent Caumartin；Nicolas Depoilly；Rabah Arhab；Herve RIBOT；David Delplace
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    (57) The invention relates to a wet clutch mechanism (E 1, E2) for a torque transmission system, in particular for a motor vehicle, comprising:
    - a torque input disc carrier (10, 20) driven in rotation by a driving shaft,
    - a torque output disc holder (16, 26) driven in rotation by a driven shaft,
    - a multi-disc set,
    - an axially movable piston (30,80) which is controlled to move by means of a control chamber (32, 36) with which is associated a balancing chamber (34, 38) delimited by a balancing cover ( 40, 90, 140), said movable piston coming to release axially in a disengaged position the multidisc assembly under the action of an elastic washer (50) disposed axially between the movable piston and the balancing cover, and in which a first support washer supported by the movable piston and a second support washer supported by the balancing cover are in direct contact with the elastic washer (50).
    S Λ Αί M U
    Zi 35 3Î 33 Ώ ii
    Wet clutch mechanism
    The present invention relates to a wet clutch mechanism for a torque transmission system.
    Such a clutch mechanism is intended to constitute part of a torque transmission system, in particular for a motor vehicle or for a so-called industrial vehicle, the latter being for example a heavy goods vehicle, a public transport vehicle, or an agricultural vehicle.
    The present invention relates more particularly to a wet double clutch mechanism movable in rotation about a main axis of rotation, which is controlled to selectively couple a driving shaft of an internal 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 of the multi-disc type, each of said first and second clutches comprising at least one axially movable piston which is controlled in displacement by means of a control chamber with which is associated a balancing chamber delimited at least by a balancing cover, said piston coming to clamp axially in a engaged position a multi-disc assembly against reaction means, said multi-disc assembly comprising flanges and also friction discs linked in rotation via an output disc port to one said first and second led trees.
    Document DE1 02007009964A1 describes such a wet double clutch mechanism in which the second clutch is arranged radially inside the first clutch. The axially movable piston of the second wet clutch is controlled to move by means of a control chamber with which is associated a balancing chamber delimited by a balancing cover. The movable piston alternately clamps the multidisc assembly axially in a engaged position against reaction means and releases axially in a disengaged position the multidisc assembly under the action of an elastic washer disposed axially between the movable piston and the cover d 'balancing.
    The successive actuation of the movable piston causes an alternating movement of the elastic washer on these supports. In the engaged position, the supports of the elastic washer on the movable piston and the balancing cover move axially, and in the disengaged position, the supports of the washer move away. The kinematics of the supports of the elastic washer generate a relative radial displacement between the elastic washer and the contact surfaces of the two associated supports, which promotes the wear of these support zones. Repeated actuation of this spring washer throughout the life of the wet clutch mechanism increases wear on these bearing areas.
    In addition, the actuating piston and the balancing cover are made of a material capable of forming by stamping but which has a relatively low hardness compared to the elastic washer, which also promotes wear of the zones. support.
    Such a wear phenomenon induces a shift in the positioning of the elastic washer and modifies the load value applied by said washer so that the release of the friction discs within the multi-disc assembly during disengagement can be disturbed. Improper release of the friction discs can lead to premature wear of the friction discs, the increase of a resistant torque within the wet clutch mechanism and consequently increase the fuel consumption of the motor vehicle.
    The object of the present invention is in particular to propose a wet clutch mechanism for a torque transmission system making it possible to solve at least some of the drawbacks of the prior art.
    To this end, the invention provides a wet clutch mechanism for a torque transmission system, in particular for a motor vehicle, comprising around at least one axis:
    - a torque entry disc holder arranged to be linked in rotation to a driving shaft,
    - a torque output disc holder arranged to be linked in rotation to a driven shaft,
    a multi-disc assembly comprising flanges linked in rotation to the input disc holder, or respectively to the output disc holder, and includes friction discs linked in rotation to the output disc holder, or respectively to the input disc holder ,
    - An axially movable piston which is controlled to move by means of a control chamber with which is associated a balancing chamber delimited at least by a balancing cover, said movable piston alternately clamping axially in a engaged position. multidisk assembly against reaction means and release axially in a disengaged position the multidisk assembly under the action of an elastic washer disposed axially between the movable piston and the balancing cover, and in which a first support washer supported by the movable piston and a second support washer supported by the balancing cover are in direct contact with the elastic washer, said first and second support washers extending radially on the internal faces of the balancing chamber.
    This wet clutch mechanism according to the invention has the advantage, thanks to the axial interposition of the first and second support washers, of reducing the wear of the elastic washer and of the contact interfaces carried by the piston. mobile and the balancing cover. In other words, the balancing cover and the movable piston are no longer subjected directly to the wear generated by the relative radial displacement of the elastic washer.
    Preferably, the first and second support washers comprise contact surfaces with the elastic washer having a surface hardness greater than the surface hardness of their respective support.
    When designing the wet clutch mechanism, according to this aspect of the invention, it becomes possible to define the material suitable for the contact surfaces opposite the elastic washer and to select the level of surface hardness of the contact surfaces in depending on the geometry and material of the spring washer. In this way, the wear of the contact surfaces of the first and second support washers is reduced.
    The invention may have one or other of the characteristics described below, combined together or taken independently of one another.
    - The multi-disc assembly includes flanges linked in rotation to the input disc holder and friction discs linked in rotation to the output disc holder.
    - The multi-disc assembly includes flanges linked in rotation to the output disc holder and friction discs linked in rotation to the input disc holder,
    The first and second support washers are interposed axially between the elastic washer and their respective support.
    - The first and second support washers are annular.
    - The first and second support washers are made of pressed sheet metal.
    - The first support washer is separate from the movable piston.
    - The second support washer is separate from the balancing cover.
    - The contact surfaces of the first and second support washers are parallel.
    - The contact surfaces of the first and second support washers are perpendicular to the axis of rotation of the wet clutch mechanism.
    - The first and second support washers are formed of adjacent segments extending around the circumference of their respective support.
    - The elastic washer is annular in shape.
    - The elastic washer is of the BelleviIle type.
    - The elastic washer has fingers which extend radially from the inner and / or outer periphery of the annular shape arranged to bear on the contact surfaces of the first and second support washers.
    - The ends of the fingers are rounded.
    - The first and second support washers comprise means for stopping in rotation.
    - In one embodiment of the invention, the rotation stop means are extrusions of material from the movable piston and / or the balancing cover which penetrate into orifices arranged in the first and / or the second washer support.
    These rotational stop means have the advantage of avoiding relative angular displacement of the parts therebetween under the action of vibrations internal to the wet clutch mechanism, further reducing wear on the contact surfaces of the first and second support washers and spring washer.
    - As a variant, the means for stopping in rotation are lugs made from material from the first and / or from the second support washer which penetrate into orifices provided in the movable piston and / or the balancing cover.
    - The holes in the balancing cover are through holes.
    - The openings in the movable piston and / or the balancing cover are form stamped.
    - The balancing cover has a bearing surface on the input disc holder, formed on the shaped stampings and offset axially relative to the contact surface of the elastic washer for the radial passage of oil between the balancing cover and the input disc holder.
    - The balancing cover comprises shaped stampings, capable of receiving the means for stopping rotation of the second support washer, delimiting, between two circumferentially consecutive stampings, radial passages of oil between the balancing cover and the input disc holder.
    - The shaped stamps are distributed angularly around the axis of rotation of the wet clutch mechanism.
    - The legs are arranged on the inner periphery of the first and / or the second support washer.
    - The legs are arranged on the outer periphery of the first and / or the second support washer.
    In this way, the pressure balancing function of the balancing chamber is carried out simply, without any additional manufacturing cost.
    - In another embodiment of the invention, the rotation-stopping means are produced by an assembly of the bayonet type of the second support washer on the balancing cover.
    - The bayonet type assembly includes several lugs formed in the balancing cover which engage by rotation in notches arranged in the second support washer.
    - The notches are formed from the inner periphery of the second support washer and extend circumferentially in the plane of said washer.
    - The pins are formed by stamping the balancing cover.
    - The lugs extend axially in the direction of the second support washer and each comprise a lateral support face arranged to come into abutment with each of the notches of the second support washer.
    - The lateral support faces of the lugs come into contact with the inside of the notches after the second support washer has been rotated relative to the balancing cover.
    The bayonet-type assembly of the second bearing washer on the balancing cover has the advantage of simplifying the mounting of the wet clutch mechanism.
    Advantageously, at least one of the contact surfaces of the first and second support washers has a heat treatment to increase the surface hardness of said at least one contact surface.
    Advantageously, at least one of the contact surfaces of the first and second support washers has a surface treatment for tribological use to facilitate the sliding of the elastic washer with respect to said at least one contact surface.
    - As a variant, at least one of the contact surfaces of the first and second support washers has a surface coating for tribological use to facilitate the sliding of the elastic washer with respect to said at least one contact surface.
    - Advantageously, the second annular support washer has centering tabs of the elastic washer disposed on the outer periphery of said annular shape.
    According to one of its aspects, the invention also relates to a wet double clutch mechanism for a torque transmission system, in particular for a motor vehicle, comprising at least a first clutch and a second clutch incorporating all or some of the characteristics mentioned above. .
    Advantageously, the first and second clutches are arranged radially one above the other.
    - As a variant, the first and second clutches are axially juxtaposed.
    Another subject of the invention, according to another of its aspects, is a wet double clutch mechanism for a torque transmission system, in particular for a motor vehicle, comprising around at least one axis O:
    - a torque entry disc holder designed to be linked in rotation to a driving shaft,
    a first clutch and a second clutch respectively of the multi-disc type, controlled to selectively couple said shaft leading to a first driven shaft and to a second driven shaft, each of said first and second clutches comprising at least one axially movable piston which is controlled in displacement by means of a control chamber with which is associated a balancing chamber delimited at least by a balancing cover, said piston coming to clamp axially in a engaged position a multidisc assembly against reaction means and to release axially in a position disengaged the multi-disc assembly under the action of an elastic washer disposed axially between the movable piston and the balancing cover, said multi-disc assembly comprising friction discs and flanges driven in rotation by the entry disc holder of couple, in at least one of the balancing chambers, a first support washer supported by the pi mobile ston and a second support washer supported by the balancing cover are in direct contact with the elastic washer, said first and second support washers extending radially on the internal faces of the balancing chamber
    All or part of the features mentioned above also applies to this other aspect of the invention.
    The invention will be better understood on reading the description which follows, given solely by way of example and made with reference to the appended drawings in which:
    Figure 1 is an axial sectional view of a wet double clutch mechanism according to a preferred embodiment of the invention;
    FIG. 2 is a detail view in perspective and cut away of the wet double clutch mechanism of FIG. 1.
    Figure 3 is a perspective and cutaway view of the balancing cover and the second support washer of the first clutch of Figure 1;
    Figure 4 is a perspective and cutaway view of the movable piston and the first support washer of the first clutch of Figure 1;
    Figure 5 is a perspective and cutaway view of the balancing cover and the second support washer of the second clutch of Figure 1;
    ίο Figure 6 is an axial sectional perspective view of a wet double clutch mechanism according to a second preferred embodiment of the invention;
    Figure 7 is a detailed and cutaway view of the wet double clutch mechanism of Figure 6;
    Figure 8 is a perspective and cutaway view of the movable piston and the first support washer of the first clutch of Figure 6;
    Figure 9 is a perspective and cutaway view of the second clutch input disc carrier, the balancing cover and the second first clutch support washer in Figure 6.
    In the following description and claims, the terms "front >> or" rear >> depending on the direction relative to an axial orientation determined by the axis will be used without limitation and in order to facilitate understanding thereof. Main O of rotation of the motor vehicle transmission and the terms "interior / internal >> or" exterior / external >> with respect to the axis O and in a radial orientation, orthogonal to said axial orientation.
    There is shown in Figures 1 to 6 a first embodiment of a double wet clutch mechanism 1 for the torque transmission system, in particular of a motor vehicle, having a main axis O of rotation.
    The wet double clutch mechanism 1 comprises around the axis O at least one input element which is linked in rotation to a driving shaft (not shown). The input element is located at the rear of the wet double clutch mechanism 1.
    Preferably, the entry element of the mechanism 1 comprises at least one entry veil 4 which is linked in rotation to a entry hub 2.
    The entry veil 4, generally having an "L" shape, comprises a portion of radial orientation and a portion of axial orientation. The radial orientation part of the web 4 and the inlet hub 2 are integral, preferably fixed together by welding.
    The hub 2 is arranged radially inside with respect to the web 4.
    The input hub 2 is for example linked in rotation via the grooves 3 to the output of a damping or damping device (such as a double damping flywheel, etc.) whose input is linked, notably by means of an engine flywheel, to the driving shaft formed by a crankshaft which is driven in rotation by an engine fitted to the motor vehicle.
    The entry veil 4 has, at its external radial end of axial orientation, teeth 5 which extend radially outwards and which are supported on an entry disc holder 10.
    The wet double clutch mechanism 1 is controlled to selectively couple said shaft leading to a first driven shaft A1 and to a second driven shaft A2.
    Preferably, the first driven shaft A1 and the second driven shaft A2 are coaxial.
    The wet double clutch mechanism 1 comprises a first clutch E1 and a second clutch E2, which are respectively of the multi-disc type.
    The multi-disc assembly of the first clutch E1 comprises flanges 12 linked in rotation to the input disc holder 10 and friction discs 14 linked in rotation to an output disc holder 16. The friction discs 14 are, individually, axially interposed between two successive flanges 12.
    The output disc holder 16 is linked in rotation by engagement with the friction discs 14 and by a splined connection with said first driven shaft A1.
    The outlet disc holder 16 generally has an "L" shape, the inner radial end of which is secured to a grooved outlet hub 17.
    Preferably, the outlet disc holder 16 and the outlet hub 17 are fixed together by welding, alternatively by riveting.
    The multi-disc assembly of the second clutch E2 comprises flanges 22 linked in rotation to an input disc holder 20 and friction discs 24 linked in rotation to an output disc holder 26.
    The input disc holder 20 is rotationally integral with the input disc holder 10. The input disc holders 10 and 20 are fixedly connected by means of a clutch hub 8. The clutch hub 8 is common to the first and second clutch E1 and E2.
    The output disc holder 26 of the second clutch E2 is linked in rotation by meshing with the friction discs 24 and by a splined connection with said second driven shaft A2.
    The outlet disc holder 26 generally has an "L" shape, the inner radial end of which is secured to a grooved outlet hub 27.
    Preferably, the outlet disc holder 26 and the outlet hub 27 are fixed together by welding, alternatively by riveting.
    The first driven shaft A1 is driven in rotation when said first clutch E1 is closed and the second driven shaft A1 is driven in rotation when said second clutch E2 is closed, said first and second driven shafts A1, A2 being respectively connected to a gearbox gears fitted to the motor vehicle.
    In the wet double clutch mechanism 1, the first clutch E1 is used, for example, both for starting and engaging odd gears and the second clutch E2 then takes care of even and reverse gear, alternatively the gears supported by said first clutch E1 and second clutch E2 are reversed.
    As illustrated in FIG. 1, the first clutch E1 is arranged radially above the second clutch E2.
    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 pass from the open state to the 'closed state.
    The wet double clutch mechanism 1 is hydraulically controlled by means of a pressurized fluid, generally oil.
    To selectively control the change of state of the first clutch E1 and of the second clutch E2 of the double clutch mechanism 10, the control device manages the supply of pressurized oil to the mechanism 1. The control device is connected to the hub 8 d 'clutch which comprises oil supply channels 84, for example four in number as shown in FIG. 1.
    The oil supply channels 84 consist of axial bores and communicating radial bores, the axial bores being connected by their front ends to the gearbox casing, not shown. The radial holes are directed towards the control chambers and the balancing chambers of the first and second clutches E1, E2.
    The clutch hub 8 has two radial holes 86 and 87 located axially at the front and which are associated respectively with the control chamber and the balancing chamber of the first clutch E1. The clutch hub 8 also has two holes 88 and 89 located axially at the rear and which are associated respectively with the control chamber and the balancing chamber of the second clutch E2.
    The first clutch E1 of the multi-disc type comprises a piston 30 which is axially movable, here from front to rear, between a disengaged position and a engaged position which correspond respectively to the open and closed states of the first clutch E1.
    Advantageously, the piston 30 comprises, at its external radial end supports 31 which extend axially towards the rear. The supports 31 come to bear on the end plate 12 of the multi-disc assembly of the first clutch E1. In the example shown in Figure 1, the supports 31 form a continuous ring.
    As shown in FIGS. 1 and 2, the piston 30 is controlled to move by means of a control chamber 32 delimited axially by a front face of an internal radial part of the piston 30 and by a rear radial face of a closing part 10. As illustrated in FIG. 1, the input disc port 10 of the first clutch E1 constitutes an example of closing part of the control chamber 32.
    The input disc holder 10, generally having an “L” shape, has a portion of radial orientation and a portion of axial orientation. The radial orientation part of the input disc carrier 10 and the clutch hub 8 are integral, preferably fixed together by welding.
    The input disc holder 10 also carries on the rear radial face a seal holder 13 added by welding. The seal holder 13 has at its external radial end sealing means which cooperate respectively with an internal face of an axial part of the piston 30.
    The piston 30 has at its internal radial end sealing means 31 which cooperate with the external axial surface 81 of the clutch hub 8, when the piston 30 is moved axially between the disengaged and engaged positions by the pressurization of the control room 32.
    The input disc holder 10 has, between its two radial ends, a concave portion 19 which cooperates with the front radial face of the piston 30 axially opposite. This concave portion 19 comprises an annular flat surface which serves as a front axial stop for the movable piston 30.
    The control chamber 32 is supplied with oil by means of the bore 86 which passes radially through the clutch hub 8, the bore 86 placing said control chamber 32 in communication with one of the oil supply channels 84.
    The chamber 32 for controlling the piston 30 of the first clutch E1 is associated with a balancing chamber 34 delimited at least by a balancing cover 40.
    The piston 30 of the first clutch E1 extends radially and is disposed axially between the control chamber 32, located axially at the front, and the balancing chamber 34, located axially at the rear. The piston 30 is concentric with the input disc holder 1 0.
    In the first embodiment illustrated in FIG. 1, the balancing cover 40 is inserted into a recess arranged on the input disc holder 20 and comes to bear on an annular wall of the input disc holder 20. The annular wall 21 is in the present case disposed on the radially internal part of the input disc holder 20.
    The balancing cover 40 is a separate part from the input disc holder 20 of the second clutch E2.
    The input disc holder 20 therefore performs a dual function, of transmitting the input power for the second clutch E2 on the one hand, and of supporting the balancing cover 40 in the operation of the first clutch E1, of somewhere else.
    This example is in no way limiting, and the balancing cover can come to bear on other components constituting the wet clutch mechanism.
    The balancing cover 40 has a general shape of revolution around the axis O. The balancing cover 40 comprising an external cylindrical wall 41 connected to an annular wall 42 of radial extension. The balancing cover 40 also includes a central opening to allow it to be mounted around the clutch hub 8.
    The balancing chamber 34 of the first clutch E1 is delimited axially by the front face 43 of the annular wall 42 of the balancing cover 40 and by the rear face 35 of the internal radial part of the piston 30. These faces 35 and 43 define the internal faces of the balancing chamber.
    The balancing chamber 34 is supplied with oil through the hole 87 that the clutch hub 8 includes.
    The balancing chamber 34 is sealed radially outside by sealing means which are carried by the piston 30 and which cooperate with the external cylindrical wall 41 of the balancing cover 40.
    The piston 30 is controlled to clamp axially, in the engaged position, said multidisk assembly of the first clutch E1 against reaction means 18. The reaction means 18 are interposed axially between a portion of the entry web 4 and a friction disc 14 at the end.
    The first clutch E1 comprises elastic return means for automatically returning the piston 30 to the disengaged position, corresponding to an open state of the clutch. In this position, the piston 30 axially releases the multidisk assembly which then no longer transmits torque in the direction of the first driven A1 shaft.
    As illustrated in FIGS. 1 and 2, the elastic return means of the piston 30 are formed by an elastic washer 50 disposed axially between the movable piston 30 and the balancing cover 40. The elastic washer 50 is a Belleville type spring exerting an axial load between the internal faces 35 and 43 of the balancing chamber 34.
    In order to limit the wear of the supports of the elastic washer and of the associated counter-supports, support washers 60a and 70a are interposed axially between the elastic washer 50 and the internal faces 35 and 43 of the balancing chamber 34.
    A first support washer 60a supported by the movable piston 30 is in direct contact with the elastic washer 50. The first support washer 60a extends radially on the internal face 35 of the balancing chamber 34.
    A second support washer 70a supported by the balancing cover 40 is in direct contact with the elastic washer 50. The second support washer 70a extends radially on the internal face 43 of the balancing chamber.
    The elastic washer 50 is of annular shape and comprises fingers 52 which extend radially from the inner periphery of the ring 51. The ends of the fingers are of rounded shapes.
    Alternatively, the spring washer may have fingers which extend radially from the outer periphery of the ring.
    In order to limit wear, the first support washer 60a comprises a contact surface 61a with the elastic washer 50 which has a surface hardness greater than the surface hardness of the piston 30.
    Likewise, the second support washer 70a comprises a contact surface 71a with the elastic washer 50 which has a surface hardness greater than the surface hardness of the balancing cover 40.
    For example, the support washers 60a and 70a can be produced by press cutting or obtained by machining.
    The increase in surface hardness can come either from the choice of the material of the support washer such as for example a low alloy steel, or by the application of a heat treatment on the contact surface of the support washer. . For example, the heat treatment can be carbonitriding or carburizing carried out on a steel support washer.
    The surface hardnesses of the support washers are measured according to standard measurement protocols of the "ROCKWELL" hardness or "BRINELL" hardness type. These measurement protocols use a non-deformable indenter which leaves an imprint in the material to be tested. The dimensions of the imprint are measured to deduce the hardness.
    The first and second support washers 60a and 70a are annular and made of pressed sheet metal. The contact surfaces 61a and 71a of the first and second support washers are parallel and perpendicular to the axis of rotation O.
    Alternatively, the first and second support washers can be formed from adjacent segments extending around the circumference of their respective support.
    Alternatively also, the contact surfaces of the first and second support washers may not be parallel to each other.
    As illustrated in FIGS. 3 and 4, the first and second support washers 60a and 70a comprise means for stopping in rotation relative to their respective support.
    For the support washer 60a, the rotational stop means are lugs 62 made from the material of said first support washer which penetrate into orifices 33 arranged in the movable piston. In this case, three legs 62 are arranged on the outer periphery of the first support washer and distributed at 120 °.
    The orifices 33 arranged in the piston 30 are shaped stampings.
    For the support washer 70a, the rotational stop means are lugs 72a made from the material of said second support washer which penetrate into orifices 45 arranged in the balancing cover 40. The lugs 72a are arranged on the inner periphery of the second support washer 70a.
    The orifices 45 arranged in the balancing cover 40 are stamped in shape distributed angularly around the axis of rotation of the wet clutch mechanism.
    The balancing cover 40 has a bearing surface on the input disc holder 20, formed on the form stampings 45 and offset axially relative to the front face 43 of the annular wall 42 of the balancing cover 40 The axial offset between these two parallel faces creates a radial passage of oil between the balancing cover 40 and the inlet disc holder 20 and allows oil circulation, radially outward, at the stamped form. The means for stopping the second support washer 70a in rotation delimit, between two circumferentially consecutive stampings, radial passages of oil between the balancing cover 40 and the input disc holder 20.
    As illustrated in FIG. 3, the second support washer 70a of annular shape comprises centering tabs 73a of the elastic washer 50 disposed on the outer periphery of the annular shape.
    The second clutch E2 of the wet double clutch mechanism 1 is similar in design to that of the first clutch E1, the second clutch E2 being of the multi-disc type.
    Advantageously, reference will be made, if necessary, to the description of the second clutch E2 in the detailed description of the first clutch E1 given previously.
    The second clutch E2 comprises a piston 80 which is axially movable, here from the front to the rear, between a disengaged position and a engaged position corresponding respectively to the open and closed states of the second clutch E2.
    The piston 30 of the first clutch E1 and the piston 80 of the second clutch E2 of said wet double clutch mechanism 1 move axially in the same direction to pass for example from the disengaged position to the engaged position.
    Advantageously, the piston 80 comprises, at its external radial end, supports 81 which extend axially towards the rear. The supports 81 come to bear on the end flange 22 of the multi-disc assembly of the second clutch E2. In the example shown in Figure 1, the supports 81 form a continuous ring.
    As shown in FIGS. 1 and 2, the piston 80 is controlled to move by means of a control chamber 36 delimited axially by a front face of an internal radial part of the piston 80 and by a rear radial face of a closing part 20. As illustrated in FIG. 1, the input disc port 20 of the second clutch E2 constitutes an example of a closing part of the control chamber.
    The input disc holder 20, having an overall "L" shape, has a radial orientation part and an axial orientation part. The radial orientation part of the input disc carrier 20 and the clutch hub 8 are integral, preferably fixed together by welding.
    The input disc holder 20 also carries on the rear radial face a seal holder 28 added by welding. The seal holder 28 has at its external radial end sealing means which cooperate respectively with an internal face of an axial part of the piston 80.
    The piston 80 has at its internal radial end sealing means 25 which cooperate with the external axial surface 82 of the clutch hub 8, when the piston 80 is moved axially between the disengaged and engaged positions by the pressurization of the control chamber 36.
    The input disc holder 20 has, between its two radial ends, a concave portion 29 which cooperates with the front radial face of the piston 80 axially opposite. This concave portion 29 comprises an annular planar surface which serves as a front axial stop for the movable piston 80.
    The control chamber 36 is supplied with oil via the hole 88 which passes radially through the clutch hub 8, the hole 88 bringing said control chamber 36 into communication with one of the oil supply channels 84.
    The chamber 36 for controlling the piston 80 of the first clutch E2 is associated with a balancing chamber 38 delimited at least by a balancing cover 90.
    The piston 80 of the second clutch E2 extends radially and is disposed axially between the control chamber 36, located axially at the front, and the balancing chamber 38, located axially at the rear. The piston 80 is concentric with the input disc holder 20.
    In the first embodiment illustrated in FIG. 5, the balancing cover 90 has a general shape of revolution around the axis O. The balancing cover 90 comprising an external cylindrical wall 91 connected to an annular wall 92 d 'radial extension. The balancing cover 90 also includes a central opening to allow it to be mounted around the clutch hub 8.
    The balancing chamber 38 of the second clutch E2 is delimited axially by the front face 93 of the annular wall 92 of the balancing cover 90 and by the rear face 85 of the internal radial part of the piston 80. These faces 85 and 93 define the internal faces of the balancing chamber 38.
    The balancing chamber 38 is supplied with oil via the hole 89 that the clutch hub 8 includes.
    The balancing chamber 38 is sealed radially on the outside by sealing means which are carried by the piston 80 and which cooperate with the external cylindrical wall 91 of the balancing cover 90.
    The piston 80 is controlled to clamp axially, in the engaged position, said multidisk assembly of the second clutch E2 against reaction means 39. The reaction means 39 are positioned on the rear end of the input disc holder 20.
    The second clutch E2 comprises elastic return means for automatically returning the piston 80 to the disengaged position, corresponding to an open state of the clutch. In this position, the piston 80 axially releases the multidisk assembly which then no longer transmits torque in the direction of the second driven shaft A2.
    As illustrated in FIGS. 1 and 2, the elastic return means of the piston 80 are formed by an elastic washer 50 disposed axially between the movable piston 80 and the balancing cover 90. The elastic washer 50 is a Belleville type spring exerting an axial load between the internal faces 85 and 93 of the balancing chamber 38.
    In order to limit wear on the supports of the elastic washer and associated counter-supports, support washers 60b and 70b are interposed axially between the elastic washer 50 and the internal faces 85 and 93 of the balancing chamber 38.
    A first support washer 60b supported by the movable piston 80 is in direct contact with the elastic washer 50. The first support washer 60b extends radially on the internal face 85 of the balancing chamber 38.
    A second support washer 70b supported by the balancing cover 90 is in direct contact with the elastic washer 50. The second support washer 70b extends radially on the internal face 93 of the balancing chamber 38.
    The first and second support washers 60b and 70b are annular and made of pressed sheet metal.
    The first support washer 60b comprises a contact surface 61b with the elastic washer 50 which has a surface hardness greater than the surface hardness of the piston 80.
    Likewise, the second support washer 70b comprises a contact surface 71b with the elastic washer 50 which has a surface hardness greater than the surface hardness of the balancing cover 90.
    As illustrated in FIGS. 1, 2 and 5, the first and second support washers 60b and 70b comprise means for stopping in rotation relative to their respective support.
    The means for stopping the first support washer 60b from rotating are extrusions of material 83 from the movable piston 80 which penetrate into orifices 65 arranged in the first support washer 60b. The material extrusions 83 are angularly distributed around the axis of rotation O.
    The support washer 60b is fixed to the piston 80 by pressing extrusions of material 83 in the press.
    For the second support washer 70b, the rotation stop means are tabs 72b made from the material of said second support washer which penetrate into orifices 95 arranged in the balancing cover 90. The tabs 72b are arranged on the inner periphery of the second support washer 70b.
    As illustrated in FIG. 5, the second annular support washer 70b has centering tabs 73b of the elastic washer 50 disposed on the outer periphery of the annular shape.
    The balancing cover 90 has holes 96 opening out, angularly distributed on either side of the orifices 95. The holes 96 create an oil passage between the balancing chamber 38 and the interior of the second clutch E2 and allows an oil circulation necessary for balancing the pressures between the control chamber 36 and the balancing chamber 38.
    There is shown in Figures 6 to 9 a second embodiment of a double wet mechanism substantially similar to the first embodiment.
    The second embodiment will be described below by comparison with the first embodiment, the same reference numerals designate identical parts or parts having similar functions.
    In this second embodiment, the first clutch E1 of the multidisc type comprises a piston 30 movable axially from front to rear, between a disengaged position and a engaged position which correspond respectively to the open and closed states of the first clutch E1.
    As shown in FIGS. 6 and 7, the piston 30 is controlled to move by means of a control chamber 32 delimited axially by a front face of an internal radial part of the piston 30 and by a rear radial face of the disc carrier d 'entry 1 0.
    The piston control chamber 32 of the first clutch E1 30 is associated with a balancing chamber 34 delimited at least by a balancing cover 140.
    The first clutch E1 comprises elastic means for returning the piston 30 formed by an elastic washer 50 disposed axially between the movable piston 30 and the balancing cover 140. The elastic washer 50 exerts an axial load between the internal faces 35 and 43 of the balancing chamber 34.
    In order to limit the wear of the supports of the elastic washer and the associated counter-supports, support washers 160 and 170 are interposed axially between the elastic washer 50 and the internal faces 35 and 43 of the balancing chamber 34.
    The first support washer 160a comprises a contact surface 161 with the elastic washer 50 which has a surface hardness greater than the surface hardness of the piston 30.
    Likewise, the second support washer 170 comprises a contact surface 171 with the elastic washer 50 which has a surface hardness greater than the surface hardness of the balancing cover 140.
    This second embodiment differs in that the multidisk assembly of the first clutch E1 comprises a second support washer 170 supported by the balancing cover 140 by a bayonet type assembly.
    The bayonet-type assembly is another embodiment of a means for stopping the support washer in rotation relative to its respective support.
    As illustrated in FIGS. 7 and 9, the bayonet-type assembly comprises several lugs 141 formed in the balancing cover 140 which engage by rotation in notches 172 arranged in the second support washer 170. The notches 172 are formed from the inner periphery of the second support washer 170 and extend circumferentially in the plane of said washer.
    Each of the notches 172 defines a cavity with a bottom 173 and an outlet opposite the bottom.
    The pins 141 are formed by stamping the balancing cover and extend axially in the direction of the second support washer. Each of the lugs 141 comprises a lateral bearing face 142 arranged to come into abutment with each of the notches 172 of the second bearing washer 170. The lateral bearing faces 142 of the lugs come into contact with the bottom 173 of the notches after rotation of the second support washer relative to the balancing cover. In this way, the mounting of the wet clutch mechanism is simplified.
    As illustrated in FIG. 8, the means for stopping the first support washer 160 from rotating are extrusions of material 83 coming from the movable piston 30 which penetrate into orifices provided in the first support washer 160.
    Furthermore, according to an advantageous variant, the contact surfaces of the first and second support washers may have a surface treatment for tribological use or a surface coating for tribological use to facilitate the sliding of the elastic washer by compared to said at least one contact surface.
    The invention is not limited only to the embodiments which have just been described.
    In an example not described, the first clutch E1 and the second clutch E2 of said wet double clutch mechanism can be axially juxtaposed, the first clutch E1 and the second clutch E2 being arranged axially on either side of the reaction means. In this case, the first clutch E1 can for example be arranged axially at the front on the side of the gearbox and the second clutch E2 can for example be arranged axially at the rear on the engine side.
    权利要求:
    Claims (15)
    [1" id="c-fr-0001]
    1. Wet clutch mechanism (E1, E2) for a torque transmission system, in particular for a motor vehicle, comprising around at least one axis (O):
    - a torque input disk holder (10, 20) arranged to be linked in rotation to a driving shaft,
    - a torque output disc holder (16, 26) arranged to be linked in rotation to a driven shaft,
    - A multi-disc assembly comprising flanges (12, 22) linked in rotation to the input disc holder (10, 20), or respectively to the output disc holder (16, 26), and comprises discs (14, 24 ) friction linked in rotation to the output disc holder (16, 26), or respectively to the input disc holder (10, 20),
    - an axially movable piston (30, 80) which is controlled to move by means of a control chamber (32, 36) with which is associated a balancing chamber (34, 38) delimited at least by a cover balancing (40, 90, 140), said movable piston (30, 80) alternately clamping axially in a engaged position the multi-disc assembly against reaction means (18, 39) and releasing axially in a disengaged position multi-disc assembly under the action of an elastic washer (50) disposed axially between the movable piston and the balancing cover, characterized in that a first support washer (60a, 60b, 160) supported by the piston ( 30, 80) movable and a second support washer (70a, 70b, 170) supported by the balancing cover (40, 90, 140) are in direct contact with the elastic washer (50), said first and second washers bearing extending radially on the internal faces (35, 43, 85, 93) of the balancing chamber.
    [2" id="c-fr-0002]
    2. Clutch mechanism according to claim 1, characterized in that said first and second support washers (60a, 60b, 160, 70a, 70b, 170) comprise contact surfaces (61a, 61b, 161, 71a, 71b, 171) with the elastic washer (50) having a surface hardness greater than the surface hardness of their respective support.
    [3" id="c-fr-0003]
    3. Clutch mechanism according to claim 1 or 2, characterized in that said first and second support washers (60a, 60b, 160, 70a, 70b, 170) comprise means for stopping in rotation relative to their respective support (30, 80, 40, 90, 140).
    [4" id="c-fr-0004]
    4. Clutch mechanism according to the preceding claim, characterized in that the rotational stop means are material extrusions (83) from the movable piston (30, 80) and / or the balancing cover (40, 90, 140) which penetrate into orifices (65) arranged in the first and / or the second support washer.
    [5" id="c-fr-0005]
    5. Clutch mechanism according to claim 3, characterized in that the rotational stop means are lugs (62, 72a, 72b) made from the material of the first and / or the second support washer which penetrate in orifices (33, 45, 95) arranged in the movable piston and / or the balancing cover.
    [6" id="c-fr-0006]
    6. Clutch mechanism according to the preceding claim, characterized in that the legs (62, 72a, 72b) are arranged on the inner periphery of the first and / or the second support washer.
    [7" id="c-fr-0007]
    7. Clutch mechanism according to claim 5, characterized in that the legs (62, 72a, 72b) are arranged on the outer periphery of the first and / or the second support washer.
    [8" id="c-fr-0008]
    8. Clutch mechanism according to any one of claims 5 to 7 characterized in that the balancing cover (40) comprise stamped form (45), adapted to receive the means for stopping the second rotation support washer (70a), delimiting, between two circumferentially consecutive stampings, radial passages of oil between the balancing cover (40) and the input disc holder (20).
    [9" id="c-fr-0009]
    9. Clutch mechanism according to claim 3, characterized in that the rotation-stopping means are produced by an assembly of the bayonet type of the second support washer (170) on the balancing cover (140).
    [10" id="c-fr-0010]
    10. Clutch mechanism according to the preceding claim, characterized in that the bayonet-type assembly comprises several lugs (141) formed in the balancing cover (140) which engage by rotation in notches (172) arranged in the second support washer (170).
    [11" id="c-fr-0011]
    11. Clutch mechanism according to any one of the preceding claims, characterized in that the second support washer (70a, 70b) of annular shape comprises centering tabs (73a, 73b) of the elastic washer (50) disposed on the outer periphery of said annular shape.
    [12" id="c-fr-0012]
    12. Clutch mechanism according to any one of claims 2 to 11, characterized in that at least one of the contact surfaces (61a, 61b, 161, 71a, 71b, 171) of the first and second support washers (60a, 60b, 160, 70a, 70b, 170) has a heat treatment to increase the surface hardness of said at least one contact surface.
    [13" id="c-fr-0013]
    13. Clutch mechanism according to any one of claims 2 to 11, characterized in that at least one of the contact surfaces (61a, 61b, 161, 71a, 71b, 171) of the first and second support washers (60a, 60b, 160, 70a, 70b, 170) has a surface treatment for tribological use to facilitate the sliding of the elastic washer with respect to said at least one contact surface.
    [14" id="c-fr-0014]
    14. wet double clutch mechanism (1) comprising at least a first clutch (E1) and a second clutch (E2) according to any one of the preceding claims, said first and second clutch being arranged radially one above the 'other.
    [15" id="c-fr-0015]
    15. Double wet clutch mechanism (1) comprising at least a first clutch (E1) and a second clutch (E2) according to any one of claims 1 to 13, said first and second clutch being axially juxtaposed.
    1/6
    5 43 λ A âo 34 / ' 1
    95 3 33 21 3 / X y, ®- Ά 36
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    同族专利:
    公开号 | 公开日
    FR3056660B1|2019-10-04|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE20310015U1|2003-06-18|2003-08-28|Zf Sachs Ag|Clutch for drive train of motor vehicles includes resetting element guided on radial outer circumference along sealing arrangement to return operating piston to starting position when not activated|
    DE102004012948A1|2004-03-17|2005-10-06|Zf Friedrichshafen Ag|Hydraulic double clutch for motor vehicle transmission has switching drive with clutch housing concentric to drive shafts|
    EP1584830A1|2004-04-10|2005-10-12|BorgWarner Inc.|Clutch device, in particular starting clutch|
    DE102013205611A1|2013-03-28|2014-10-02|Zf Friedrichshafen Ag|Multi-plate clutch arrangement|
    FR3024510A1|2014-08-01|2016-02-05|Valeo Embrayages|CLUTCH DEVICE FOR A MOTOR VEHICLE|EP3581821A1|2018-06-14|2019-12-18|Valeo Embrayages|Multi-plate clutch|
    WO2020114898A1|2018-12-07|2020-06-11|Valeo Embrayages|Spacer device for a wet clutch mechanism and wet clutch mechanism comprising such a spacer device|
    FR3101926A1|2019-10-09|2021-04-16|Valeo Embrayages|"COMPACT WET DOUBLE CLUTCH MECHANISM"|
    法律状态:
    2017-09-29| PLFP| Fee payment|Year of fee payment: 2 |
    2018-03-30| PLSC| Search report ready|Effective date: 20180330 |
    2018-09-28| PLFP| Fee payment|Year of fee payment: 3 |
    2019-09-30| PLFP| Fee payment|Year of fee payment: 4 |
    2020-09-30| PLFP| Fee payment|Year of fee payment: 5 |
    2021-09-30| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1659137A|FR3056660B1|2016-09-27|2016-09-27|WET CLUTCH MECHANISM|
    FR1659137|2016-09-27|FR1659137A| FR3056660B1|2016-09-27|2016-09-27|WET CLUTCH MECHANISM|
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