• 专利附录
  • 专利说明
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    • 专利摘要:
    The invention relates to a double wet clutch (1) comprising a first and a second clutch (4, 5) each comprising: - a multi-disc assembly (10, 11) axially movable between a disengaged position and an engaged position; and - a force transmission member (25, 38) which is movable in translation along the X axis so as to move the multi-disc assembly (10, 11) from its disengaged position to its engaged position; said double wet clutch (1) further comprising a control system (21) having a housing (41), a first and a second annular chamber (43, 44), concentric about the X axis and a first and a second annular pistons (45, 46) which are axially slidably mounted respectively within the first and second annular chambers (43, 44); said double clutch having first and second abutment surfaces (59, 61) which are respectively adapted to limit the movement of the force transmitting member (25, 38) of the first and second clutches (4, 5) by direction of the multi-disk assemblies (10, 11) in the event of malfunction or end of life of the double clutch.
    公开号:FR3049024A1
    申请号:FR1652227
    申请日:2016-03-16
    公开日:2017-09-22
    发明作者:Arnaud Dole；Francois Thibaut
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    DOUBLE WET CLUTCH WITH SAFETY BITS TO LIMIT THE PISTON RUN OF THE CONTROL SYSTEM
    TECHNICAL FIELD The invention relates to the field of transmissions for a motor vehicle. The invention relates more particularly to a double wet clutch intended to be arranged, in a transmission chain of a motor vehicle, between an engine block and a gearbox comprising two input shafts.
    Technological background
    A wet double clutch comprises an input hub intended to be secured in rotation to a flywheel attached to the crankshaft of the engine and two clutches each having an inlet disk holder rotatably connected to the input hub, a disk holder an output shaft rotatably connected to one or both of the input shafts of a gearbox and a multi-disk assembly for transmitting torque between the input disk carrier and the disk carrier of output of said clutch when said clutch is in its engaged position. One of the input shafts of the gearbox, rotatably connected to the output disk carrier of one of the clutches, corresponds to the odd gearbox ratios while the other input shaft is connected in rotation to the output disk carrier of the other clutch, corresponds to even reports. Thus, to effect a shift, one of the clutches is moved from its engaged position to its disengaged position while the other clutch is moved from its disengaged position to its engaged position. Such a double clutch thus makes it possible to change speed ratio without breaking torque.
    It is known, for example from document DE102014212805, double wet clutches which are actuated by means of a hydraulic control system comprising, a housing, intended to be fixed on the gearbox, having two concentric annular chambers and two annular pistons. axially movable respectively in one and the other of the two annular chambers. Each of the pistons carries a rotating stop which is in abutment against a force transmission member cooperating with one or the other of the two clutches so as to move said clutch between a disengaged position and a position engaged during the movement of the piston. inside its respective annular chamber. Such a control system limits the drag torque and therefore provides satisfactory energy consumption performance.
    For safety reasons, it is necessary to limit the stroke of the pistons towards the clutches to ensure that said pistons can not escape from their respective chamber in the event of abnormal operation of the double wet clutch, for example in case of overpressure in the annular or end-of-life chambers of the double clutch, when the friction linings of the multi-disk assemblies are worn out. Indeed, failing that, the expulsion of one of the pistons out of his room is likely to cause failures and / or damage to the double wet clutch and / or the gearbox.
    There are certainly hydraulic control systems in which a circlip, which is mounted in a groove placed near the end of the chamber, is able to limit the movement of the piston to prevent it from escaping from bedroom. However, such an arrangement increases the complexity and the cost of the hydraulic control system.
    Such a double clutch is not fully satisfactory. summary
    An idea underlying the invention is to solve the disadvantages of the prior art by providing a double wet clutch that is simple and reliable.
    According to one embodiment, the invention provides a double wet clutch intended to be arranged in a motor vehicle chain, between a motor having a crankshaft and a gearbox comprising two input coaxial shafts extending in a direction X axis, said double wet clutch comprising a first and a second clutch which are respectively able to transmit a torque of the crankshaft towards one and the other of the two input shafts of the gearbox, each of the first and second clutches comprising: - an input disk carrier for coupling in rotation to the crankshaft; an output disk carrier intended to be coupled in rotation to one or the other of the two input shafts of the gearbox; a multi-disk assembly comprising at least one friction disc integral in rotation with one of the inlet and outlet disk carriers and at least two plates respectively arranged on either side of each friction disk, integral in rotation on the other hand input and output disc carriers, the friction disc and the platens being movable axially between a disengaged position and an engaged position in which said platens pinch said friction disc so as to transmit a torque between the input disk carrier and the output disk carrier; and - a force transmitting member which is movable in translation along the axis X so as to move the multiisque assembly from its disengaged position to its engaged position; said double wet clutch further comprising a control system comprising: a housing for attachment to the gearbox and having first and second annular chambers concentric about the X axis; the first annular chamber being located radially outside the second annular chamber; and - first and second annular pistons which are respectively axially slidably mounted within the first and second annular chambers; the first and second annular pistons each carrying a first and a second rotary stop cooperating respectively with the force transmission member of the first and second clutch in order to move said clutch between its disengaged position and its engaged position; said double clutch having first and second abutment surfaces which are respectively adapted to limit the movement of the force transmitting member of the first and second clutches towards the multi-disc assemblies, the first and second abutment surfaces being respectively placed at an axial distance Y1 of the force transmitting member of the first clutch when the first clutch is in the disengaged position and at an axial distance Y2 of the force transmission member of the second clutch when the second clutch is in the disengaged position ; the axial distance Y1 being less than an axial dimension of the first annular chamber and greater than a stroke of the first piston corresponding to a displacement of the first clutch from its disengaged position to its engaged position; the axial distance Y2 being less than an axial dimension of the second annular chamber and greater than a stroke of the second piston corresponding to a displacement of the second clutch from its disengaged position to its engaged position.
    Thus, the reliability of the double clutch is ensured because the first and second stop surfaces make it possible to prevent the first and second pistons from escaping from their respective annular chamber in the event of malfunction or end of life of the double clutch and this without requiring the addition of a resilient stop circlip at the ends of the chambers of the hydraulic control system.
    In particular, the safety stop function can be exerted by existing components of the double clutch, which simplifies the manufacture of the double clutch and reduce costs.
    Finally, since the axial distances Y1 and Y2 are defined with respect to elements of the double clutch which are external to the hydraulic control system, this can be standardized so that it applies to different models of double clutch, the axial distances Y1 and Y2 defining the maximum stroke of the pistons being adapted to each of the dual clutch models.
    According to other advantageous embodiments, such a double wet clutch can have one or more of the following characteristics.
    The axial dimension of the first annular chamber corresponds to a measurement taken parallel to the X axis between the bottom and the front end of the first annular chamber. More particularly, the axial distance Y1 is less than the maximum stroke likely to be performed by the first piston inside the first annular chamber without it escaping from the first annular chamber.
    The axial distance Y1 corresponds to the sum of the axial stroke of the first piston corresponding to a displacement of the first clutch between its disengaged position and its maximum engaged position when the friction lining is new and a wear threshold of the assembly. friction linings of the first clutch.
    The axial dimension of the second annular chamber corresponds to a measurement taken parallel to the X axis between the bottom and the front end of the second annular chamber. More particularly, the axial distance Y2 is less than the maximum stroke likely to be performed by the second piston inside the second annular chamber without it escaping from the second annular chamber.
    The axial distance Y2 corresponds to the sum of the axial stroke of the second piston corresponding to a displacement of the second clutch between its disengaged position and its maximum engaged position when the friction lining is new and a wear threshold of the assembly. friction linings of the second clutch.
    According to one embodiment, each input or output disk carrier comprises a cylindrical fluted skirt; each friction disk or plate being axially movably mounted on the cylindrical corrugated skirt of one of the output or inlet disk carriers and integrally rotated therewith; one of the input disk carriers having a support portion directed radially inwardly from an edge of its cylindrical corrugated skirt directed toward the control system; said support portion having a radially inner edge cooperating with a guide bearing in rotation of the double clutch about the X axis.
    According to one embodiment, the force transmission member of each of the clutches has an outer periphery equipped with a plurality of fingers having an axial orientation and each passing through the support portion through an opening and for pressing against the multi-disk assembly of said clutch.
    According to one embodiment, the first abutment surface is formed on the support portion in an area which is located radially outside the force transmission member of the second clutch. Also, according to an advantageous variant, the force transmission member of the first clutch comprises, radially outside the force transmission member of the second clutch an axial recess in the direction of the first abutment surface.
    According to one embodiment, the second surface is formed on the support portion.
    According to one embodiment, the support portion has an outer zone having a radial orientation and an inner zone that is folded in a direction opposite to the control system, within the multi-disk assemblies.
    According to an alternative embodiment, the second abutment surface is formed in the outer zone of the support portion.
    According to another variant embodiment, the second abutment surface is formed in the internal zone of the support portion.
    According to one embodiment, the support portion has a shoulder cooperating with the guide bearing in rotation of the double clutch. According to a variant, the second abutment surface is formed on the shoulder.
    According to one embodiment, the housing comprises an inner tube extending axially about the axis X, radially inside the first and second annular chambers and providing an internal space for the passage of the two input shafts. of the gearbox, the inner tube extending axially towards the two clutches beyond the first and the second annular chambers.
    According to one embodiment, the support portion is rotatably mounted on the inner tube via the guide bearing.
    According to one embodiment, the second abutment surface is formed on the inner tube.
    According to an alternative embodiment, the inner tube comprises an annular groove inside which projects radially an inner periphery of the force transmission member of the second clutch, said annular groove having an edge forming the second abutment surface.
    According to another embodiment, the second abutment surface is provided on the rotational guide bearing of the double clutch.
    Advantageously, when the first and second clutches are in their disengaged position, the force transmission members of the first and second clutches are spaced apart by a minimum axial distance Y3 which is greater than the axial distance Y1, which allows to avoid undesirably actuating the second clutch via the actuating member of the first clutch when the friction linings thereof are worn.
    According to one embodiment, the inner tube extends axially towards the two clutches beyond the first and the second annular chambers.
    According to one embodiment, the inner tube is made of material, that is to say formed integrally with the housing.
    According to one embodiment, the inner tube has at least one channel for passing a cooling fluid for conducting said cooling fluid to the clutches. Thus, the clutch cooling circuit is integrated with the hydraulic system for controlling the double clutch, which makes it possible to reduce the number of components of the wet double clutch, to reduce its size and contributes to increasing the standardization of its components.
    The passage channel of a cooling fluid has an outlet opening opening axially beyond the rotating abutment of the second annular piston irrespective of the position of said second annular piston between its rest position and its active position. Therefore, the circulation of the cooling fluid is particularly effective due to the proper axial positioning of the outlet orifice, which ensures a powerful cooling of the double clutch. In particular, since the passage of the cooling fluid opens out beyond the stroke of the annular pistons between their active position and their rest position, effective cooling of the clutches is ensured regardless of the position of the clutches and in particular when they are closed. positioned at the point of licking and that the cooling requirements are the most important.
    According to one embodiment, the inner tube comprises a plurality of cooling fluid passageways distributed circumferentially around the X axis, which ensures efficient and homogeneous cooling. According to one embodiment, the passageways of the cooling fluid are equitably distributed around the X axis.
    According to one embodiment, the two clutches are arranged radially one inside the other, which limits the axial size of the double clutch.
    According to one embodiment, the input disk carriers are arranged radially outside the outlet disk holder of their respective clutch.
    According to one embodiment, the input disk carriers of the two clutches are rotatably mounted about the X axis on the inner tube of the control system via a bearing. Thus, the input disk carriers being supported on the control system, intended to be fixed on the gearbox, the bearing is mounted on a stable and rigid element which is not subjected to axial movements and / or radial, which ensures a stability of the double clutch and a greater reliability of the bearing. In addition, the bearing being mounted on an inner tube having a relatively small diameter, the diameter of the bearing is limited, which reduces its cost, especially if it is a rolling bearing.
    According to one embodiment, the bearing is a rolling bearing.
    According to one embodiment, the rolling bearing comprises an inner ring which is mounted around the inner tube, an outer ring mounted inside an inlet disk holder housing of one of the clutches and the bodies. rollers interposed between the inner ring and the outer ring.
    According to one embodiment, the inner ring is retained on the inner tube in a direction opposite to the control system by an elastic ring which is mounted in a groove on the inner tube.
    According to another embodiment, the ring is retained by a shoulder formed directly on the inner tube.
    According to one embodiment, the inner tube is secured axially with the housing so that the axial clutch forces exerted by the annular pistons are taken directly by the housing.
    According to one embodiment, the rolling bearing is angular contact.
    According to one embodiment, the bearing is mounted on a bearing surface of the inner tube, said bearing surface being positioned, in the direction of the two clutches, beyond the races of the first and second annular pistons between their rest position and their position. active position, at least as long as the friction linings of the multi-disk assemblies are not worn.
    According to one embodiment, the output disk carriers are fixed to an outlet hub or formed integrally with it, said output hub having grooves cooperating with complementary grooves formed at the end of one either of the input shafts of the gearbox.
    According to one embodiment, the cylindrical skirts of the output disk carriers are connected to their respective output hub by a radial portion which extends radially inwardly from an edge of said cylindrical skirt directed in one direction. opposite to the hydraulic control system.
    According to one embodiment, the multi-disk assembly of one of the clutches is disposed radially inside the multi-disk assembly of the other clutch and the bearing is disposed radially inside the multi-disk assemblies of the clutches.
    According to one embodiment, the multi-disk assembly of one of the clutches is disposed radially inside the multi-disk assembly of the other clutch, the bearing which supports the input disk carriers being arranged radially at the other end. the interior of the multi-disk assemblies of the clutches and the support portion having an inner zone which is folded in a direction opposite to the hydraulic control system, within the multi-disk assemblies.
    According to one embodiment, each of the force transmission members comprises an inner portion having an axial recess towards the two clutches inside which are at least partially housed the first and second annular pistons of the control system. Such an arrangement also contributes to increasing the axial compactness of the double clutch.
    According to one embodiment, the double clutch comprises an inlet hub comprising splines intended to cooperate with complementary splines of an element attached to the crankshaft of the engine, such as a flywheel. The input disk carriers are attached to the input hub, for example via an inlet web.
    According to one embodiment, the input disk carriers are arranged radially outside the outlet disk holder of their respective clutch.
    According to one embodiment, the invention also provides a motor vehicle comprising a double clutch of the aforementioned type.
    BRIEF DESCRIPTION OF THE DRAWINGS The invention will be better understood, and other objects, details, features and advantages thereof will become more clearly apparent from the following description of several particular embodiments of the invention, given solely for the purposes of the invention. illustrative and not limiting, with reference to the accompanying drawings. - Figure 1 is a half-sectional view of a double wet clutch according to a first embodiment. - Figure 2 is a half-sectional view of a double wet clutch according to a second embodiment. - Figure 3 is a half-sectional view of a double wet clutch according to a third embodiment. - Figure 4 is a half-sectional view of a double wet clutch according to a fourth embodiment.
    Detailed description of embodiments
    In the description and the claims, the terms "external" and "internal" as well as the "axial" and "radial" orientations will be used to designate, according to the definitions given in the description, elements of the double clutch. By convention, the "radial" orientation is directed orthogonally to the X axis of rotation of the double clutch determining the "axial" orientation and, from the inside towards the outside away from said axis, the orientation " circumferential "is orthogonal to the X axis and orthogonal to the radial direction. The terms "external" and "internal" are used to define the relative position of one element relative to another, with reference to the X axis, an element close to the X axis is thus described as internal by opposition an outer member located radially peripherally. Furthermore, the terms "rear" AR and "front" AV are used to define the relative position of one element relative to another in the axial direction, an element intended to be placed close to the engine being designated by before and an element intended to be placed close to the gearbox being designated by the rear.
    In connection with Figure 1, there is a dual clutch 1 which is intended to be disposed between an engine block and a gearbox. Such a double clutch 1 is intended to transmit a torque of the crankshaft of the heat engine selectively to one or the other of the two shafts 2, 3 coaxial input of the gearbox. The shaft 2, inside, passes through the housing of the gearbox and extends longitudinally along the axis X. The shaft 3, hollow, also passes through the housing of the gearbox and surrounds the inner shaft 2. The double clutch 1 comprises two clutches 4, 5 which are each intended to temporarily couple the crankshaft of the engine to one of the shafts 2, 3 input of the gearbox. One of the input shafts 2, 3 of the gearbox corresponds to certain gear ratios, for example the odd-speed gears and the reverse gear, and the other corresponds to the other gears, for example example even gear ratios. Thus, to effect a change of speed ratio, one of the clutches 4, 5 is moved from its engaged position to its disengaged position while the other clutch 4, 5 is moved from its disengaged position to its engaged position, so that the engine torque is progressively transferred from one to the other of the clutches 4, 5. Such a double clutch 1 thus makes it possible to change the speed ratio, without breaking the torque, that is to say while maintaining the transmission engine torque to the wheels of the vehicle.
    The double clutch 1 comprises an inlet hub 6 which has external splines intended to cooperate with complementary splines formed on an element fixed to the crankshaft of the heat engine, such as a flywheel, single or double, not shown.
    The dual clutch 1 is intended to be housed in a clutch housing, not shown, which is fixed on the gearbox. The clutch housing is closed forward by means of a closing cap, not shown, which is guided in rotation on the outer cylindrical surface of the inlet hub 6 by means of a bearing, not shown. The closure cap carries at its outer periphery an annular seal which cooperates with the inner surface of the clutch housing to seal the double clutch 1.
    The double clutch 1 also comprises an inlet web 7 which is welded to the inlet hub 6 or formed integrally therewith. The entry web is rotatably connected to an input disk carrier of each of the two clutches 4, 5.
    The two clutches 4, 5 each comprise a multidisk assembly 10, 11, that is to say an axial stack of friction discs and trays. The multi-disk assemblies 10, 11 of one and the other of the two clutches are arranged radially one inside the other, so as to limit the axial size of the double clutch 1.
    The first clutch 4, that is to say the clutch whose multi-disk assembly 10 is radially outside that of the other clutch 5, comprises an inlet disk carrier 8 which is fixed on the 7. To this end, the inlet web 7 has on its outer periphery an external toothing 12 which cooperates with an internal toothing 13 formed on the inner surface of the inlet disk holder 8 of the first clutch 4 of FIG. in order to join the inlet web 7 in rotation to said inlet disk carrier 8. Furthermore, the inlet web 7 is retained axially rearwardly relative to the inlet disk carrier 8 of the first clutch 4 by means of a stop ring 14. The stop ring 14 is for example an elastic coupling rod which is housed in a groove formed at the front end of the inlet disk holder 8 of the first clutch 4.
    The first clutch 4 also includes an output disc holder 15 which is attached to or integrally formed with an outlet hub 16. The output hub 16 is splined and cooperates with complementary splines formed on the outer periphery of the end of one of the input shafts of the gearbox, here the inner shaft 2. Thus, the output hub 16 of the output disk carrier 15 is integral in rotation with the inner shaft 2. The output hub 16 has, at the front, on its outer periphery a shoulder defining an axial bearing surface for a bearing 17. The bearing 17 also cooperates with a shoulder formed on the inner periphery of the inlet hub 6 and defining an axial bearing surface for said bearing 17. The bearing 17 thus ensures the axial positioning of the output disk carrier 15 the first clutch 4 with respect to the inlet web 7. The bearing 17 is for example a rolling bearing.
    The inlet disk holder 8 comprises a cylindrical skirt 18 of axial orientation in which is provided an internal toothing and a support portion 19 of annular shape which extends radially inwards from the rear end of the cylindrical skirt 18. The support portion 19 and the cylindrical skirt 18 may be formed in one piece, in the same sheet, as in the embodiment shown, or be formed of two separate pieces attached to each other. 'other. The inlet disk holder 8 is rotatably mounted on the hydraulic control system 21 via a bearing 20, described in more detail below, which cooperates on the one hand with the control system 21 and on the other hand with the radially inner edge of the support portion 19. Advantageously, in order to limit the axial size of the double clutch, the support portion 19 of the input disk carrier 8 comprises an outer portion 19a which has a radial orientation and is disposed at the rear of the multi-disk assemblies 10, 11 of the two clutches 4, 5 and an inner portion 19b which is folded forward and thus extends radially inside the multi-disk assemblies 10, 11.
    The output disc holder 15 comprises a cylindrical skirt 22 of axial orientation which is arranged radially inside the cylindrical skirt 18 of the input disc holder 8 and in which is provided an external toothing. The outlet disc holder 15 also has a radially oriented portion 23 which extends radially from the front end of the cylindrical skirt 22 of the output disc holder 15 to the outlet hub 16. The multi-disc assembly 10 comprises a plurality of annular plates, of steel for example, which are integral in rotation with the input disk holder 8 and axially slidably mounted relative to said input disk holder 8. To this end, each plate comprises on its external periphery an external toothing which is in engagement with the internal toothing formed on the internal face of the cylindrical skirt 18 of the input disc holder 8. The multi-disc assembly 10 further comprises a plurality of friction discs which are each interposed between two plates and are integral in rotation with the output disk carrier 15 with an axial translation freedom. To do this, each friction disc has on its inner periphery an internal toothing which is engaged with the external toothing carried by the cylindrical skirt 22 of the output disc holder 15. Each friction disc has friction linings disposed on each of its faces, front and back. The multi-disk assembly 10 is supported forwards against a reaction zone formed on the inlet web 7. The reaction zone is, in the embodiment shown, formed with the aid of an annular rim 24 formed in the vicinity of the outer periphery of the inlet web 7. Furthermore, the plate disposed at the rear end of the multi-disk assembly 10 cooperates with a force transmission member 25. The force transmission member 25 is slidably mounted axially and cooperates with the hydraulic control system 21, described in more detail later, which is adapted to axially slide the force transmission member 25 forward to move the first clutch 4 from its disengaged position towards its engaged position. The force transmission member 25 is constituted by a metal sheet which comprises, at its outer periphery, a plurality of fingers 26 having an axial orientation which are regularly distributed around the axis X. Each finger 26 passes through the support portion 19 of the input disk carrier 8 in favor of a dedicated opening, not shown. Each finger 26 thus bears against the plate disposed at the rear end of the multi-disk assembly 10 of the first clutch 4.
    To move the first clutch 4 from its disengaged position to its engaged position, the force transmission member 25 is moved forward so that each of the friction discs is clamped between two plates and the torque is thus transmitted between the input disk carrier 8 and the output disk carrier 15 and therefore between the crankshaft of the engine and the input shaft 2 of the gearbox. Conversely, when the force transmission member 25 is no longer forced forward, the friction discs and trays find their disengaged position in which they are spaced axially from each other. In order to facilitate the return of the friction discs and plates to their disengaged position, corrugated elastic washers, not shown, are interposed between the plates. In each gap between two adjacent plates, a spring washer is disposed radially outside the friction disc located in said gap.
    In order to limit the axial size of the double clutch 1, the force transmission member 25 comprises at its inner portion an axial recess 28 forwards inside which is, at least partly, housed the system. hydraulic control 21.
    The second clutch 5, that is to say the clutch whose multi-plate assembly 11 is disposed radially inside that of the other clutch 4, has a structure similar to the first clutch 4. The second clutch 5 comprises an inlet disk carrier 9 integral in rotation with the inlet web 7. To do this, the inlet disk carrier 9 of the second clutch 5 is fixed, for example by welding, to the support portion 19 of the door input disk 8 of the first clutch 4. The input disk carrier 9 comprises a cylindrical skirt 29 of axial orientation which is arranged radially inside the cylindrical skirt 22 of the output disk carrier 15 of the first clutch. 4. The cylindrical skirt 29 has an internal toothing.
    The second clutch 5 also includes an outlet disk carrier 30 which is attached to or is integrally formed with an outlet hub 31. The outlet hub 31 has internal splines which cooperate with complementary splines formed on the outer periphery of the end of one of the input shafts of the gearbox, here the outer shaft 3. In order to ensure the axial positioning of the output disk carrier 30, a first axial bearing 32 is interposed between the output hub 16 of the first clutch 4 and the output hub 31 of the second clutch 5 and a second axial bearing 33 is interposed between the hub of output 31 of the second clutch 5 and an inner tube 42 of the hydraulic control system 21.
    The outlet disc holder 30 comprises a cylindrical skirt 34 of axial orientation, arranged radially inside the cylindrical skirt 29 of the inlet disc holder 9 and having external toothing. The outlet disc holder 30 also has a radially oriented portion 35 which extends radially from the front end of the cylindrical skirt 34 of the output disc holder 30 to the outlet hub 31. The multi-disc assembly 11 of the second clutch 5 comprises a plurality of annular plates having a structure similar to that of the annular plates of the first clutch 4. Each plate has on its outer periphery an external toothing which cooperates with the complementary toothing formed on the internal face of the cylindrical skirt 29 of the input disc holder 9. The multi-disc assembly 11 further comprises a plurality of friction discs which have a structure similar to those of the first clutch 4 and are mounted integral in rotation with the output disc holder 30 and sliding axially on it. To do this, each friction disc has on its inner periphery an internal toothing which is in engagement with the external toothing formed on the cylindrical skirt 34 of the output disc holder 30. Each friction disc is interposed between two plates.
    The plate disposed at the front end of the multi-disk assembly 11 cooperates with a reaction member 36. The reaction member 36 is in turn held forward by means of a stop ring 37 which is attached to the input disk carrier 9 of the second clutch 5, at the front end of its cylindrical skirt 34.
    The second clutch 5 is actuated by means of a force transmitting member 38 which, on the one hand, cooperates with the plate disposed at the rear end of the multi-disk assembly 11 of the second clutch 5 and, on the other hand , cooperates with the hydraulic control system 21 which is able to slide axially forwardly so as to move the second clutch 5 from its disengaged position to its engaged position. The force transmitting member 38 here consists of a metal sheet which comprises at its outer periphery a plurality of axially oriented fingers 39 regularly distributed around the axis X. Each finger 39 passes through a dedicated opening formed in the support portion 19 of the input disk carrier 8 of the first clutch 4 and is thus in abutment against the plate disposed at the rear end of the multi-disk assembly 11 of the second clutch 5.
    To move the second clutch 5 from its disengaged position to its engaged position, the force transmitting member 38 is moved forwardly so that each of the friction discs is clamped between two platens and the torque is thereby transmitted between the input disk carrier 9 and the output disk carrier 30 and therefore between the crankshaft of the engine and the external shaft 3 input of the gearbox.
    In order to limit the axial size of the double clutch, the force transmission member 38 comprises at its inner portion an axial recess 40 forwards inside which is, at least partly, housed the hydraulic system order 21.
    The double clutch 1 further comprises a hydraulic control system 21 for actuating the two clutches 4, 5. The hydraulic control system 21 comprises a housing 41 which is fixed against a wall of the gearbox, not shown. The housing 41 has an inner tube 42 extending axially about the axis X and providing an internal space through which pass the shafts 2, 3 input of the gearbox. The inner tube 42 is made of material with the casing 41. The casing 41 also has first and second concentric annular chambers 43, 44 arranged radially outside the inner tube 42. First and second pistons 45, 46 of annular shape are respectively movably mounted in axial translation inside the first and second chambers 43, 44.
    The housing 41 further has, for each of the first and second chambers 43, 44, a channel 47, 48 for supplying pressurized fluid opening into said chamber 43, 44 so as to allow its supply of fluid. Each of the channels 47, 48 is connected to a hydraulic circuit equipped with a pump. The first and second chambers 43, 44 are thus intended to be supplied with fluid to cause the piston 45, 46 to move forward from its rest position to its active position.
    Each of the first and second pistons 45, 46 carries a rotary stop 49, 50 which is fixed to the end of said piston 45, 46. Each rotary stop 49, 50 comprises a first ring which is fixed to the piston 43, 44, a second ring bearing against one of the force transmission members 25, 38 and rolling bodies, such as balls, interposed between the two rings.
    The inner tube 42 extends axially forwardly beyond the first and second chambers 43, 44. Furthermore, beyond the stroke of the first and second pistons 45, 46 corresponding to the displacement of the first and second clutches 4 5 of their disengaged position towards their engaged position, the inner tube 42 has a cylindrical bearing surface 51 on which is mounted the bearing 20 supporting the input disk carriers 8, 9 of the clutches 4, 5. The bearing 20 is here a rolling bearing comprising an inner ring which is mounted around the cylindrical bearing surface 51 of the inner tube 42, an outer ring which is mounted inside a housing 52 formed at the radially inner edge of the portion support 19 of the inlet disk holder 8 of the first clutch 4 and the rolling bodies, such as balls, interposed between the outer ring and the inner ring. The rolling bearing is angular contact. The housing 52 has, rearwardly a shoulder 53 for retaining the outer ring backwards. Furthermore, the inner ring is held forward by an elastic ring 54 of the "circlip" type which is mounted in a groove in the inner tube 42, in front of the cylindrical bearing surface 51.
    The outer diameter of the cylindrical bearing surface 51 is smaller than the internal bore of the force transmitting member 38.
    It is furthermore observed that the inner tube 42 of the hydraulic control system 21 comprises a plurality of channels 55 for the passage of a cooling fluid, such as gearbox oil, intended to ensure the cooling and lubrication of the multi-disk assemblies 10, 11. The channels 55 are equitably distributed around the X axis.
    Each channel 55 extends axially between an inlet orifice 56 opening at the rear face of the housing 41 of the hydraulic control system and an outlet orifice 57 opening at the front end of the inner tube 42. The orifices input 55 are connected to a hydraulic circuit equipped with a pump. The outlet orifices 57 are regularly distributed around the X axis and open radially inside the multi-disk assemblies 10, 11. The outlet orifices 57 are directed radially outwards in order to guide the cooling fluid radially towards the outside. In the illustrated embodiment, the outlet orifices 57 open axially at a portion of the inner tube extending beyond the cylindrical bearing surface 51 on which is 20. The coolant then passes between the input disk carriers 8, 9 and the output disk carriers 15, 30.
    In order to allow oil to flow from the outlet ports to the outside of the double clutch, passing through the multi-disk assemblies 10, 11, the cylindrical skirts 29, 34 of the inlet and outlet disk carriers 9, 30 of the second clutch 5 and the cylindrical skirts 18, 22 of the inlet and outlet disc holders 8, 15 of the first clutch 4 have radial orifices 58. In FIG. 1, only the orifices 58 of the exit disc holder 30 of the second clutch 5 are visible.
    The double clutch comprises two safety abutment surfaces 59, 61 which are respectively able to limit the movement of the force transmission member 25, 38 of the first and second clutches 4, 5 forward under certain abnormal conditions. operation of the double clutch, or at the end of its life.
    In the embodiment shown in FIG. 1, the first abutment surface 59 is formed at the level of the external zone 19a of the support portion 19, in a region radially outside the force-transmitting member 38. of the second clutch 5. Furthermore, the force transmission member 25 comprises, at its outer periphery, a recess 60 forwards which is disposed at an axial distance Y1 of the first abutment surface 59 when the first piston 45 is in its rest position and the first clutch 4 in its corresponding disengaged position.
    The axial distance Y1 is greater than the axial stroke of the first piston 45 - and therefore of the force transmission member 25 - which corresponds to a displacement of the first clutch 4 between its disengaged position and a maximum engaged position when the trims friction discs are new or have not reached a wear threshold. The maximum engaged position corresponds to the position of the first clutch 4 for which it is able to transmit its maximum torque. Therefore, in normal operation, the force transmission member 25 of the first clutch 4 does not abut against the first abutment surface 59. Conversely, the axial distance Y1 is smaller than the axial dimension of the first annular chamber 43. More precisely, the axial distance Y1 is smaller than the maximum stroke that can be performed by the first piston 45 without it escaping from the first annular chamber 43. Thus, whatever the malfunction may be. being met by the double clutch, the first piston 45 can not escape from the first annular chamber 43.
    Advantageously, the axial distance Y1 corresponds to the sum of the axial stroke of the first piston 45 corresponding to a displacement of the first clutch 4 between its disengaged position and its maximum engaged position when the friction lining is new and a threshold of maximum wear of the set of friction linings of the first clutch 4. In other words, the axial distance Y1 is necessarily less than the sum of the axial stroke of the first piston 45 corresponding to a displacement of the first clutch 4 between its disengaged position and its maximum engaged position when the friction linings are new and the total thickness of all the friction linings of the first clutch 4.
    Furthermore, we observe in Figure 1 that the axial distance Y1 is necessarily less than the minimum axial distance Y3 between the two force transmission members when they are both in a position corresponding to a disengaged state of their respective clutch . Thus, the force transmission member 25 is not likely to press forward on the other force transmission member 38 because, in case of wear of the friction linings of the first clutch 4 and displacement forwardly of the force transmitting member 25, it will meet the first abutment surface 59 before the axial distance Y3 is completely overtaken.
    The second abutment surface 61 is formed on the rear face of the shoulder 53 formed on the inner periphery of the support portion 19. The second abutment surface 61 is disposed at an axial distance Y2 of the force transmission member 38 of the second clutch 5. The characteristics of the axial distance Y2 are similar to that of the axial distance Y1.
    Thus, the axial distance Y2 is: - greater than the axial stroke of the second piston 46 which corresponds to a displacement of the second clutch 5 between its disengaged position and a maximum engaged position when the lining of the friction discs are new or have not reaches a wear threshold; - less than the maximum stroke likely to be performed by the second piston 46 without it escaping from the first annular chamber 44; and - corresponds to the sum of the axial stroke of the second piston 46 corresponding to a displacement of the second clutch 6 between its disengaged position and its maximum engaged position when the friction lining is new and a wear threshold of the assembly friction pads of the second clutch 5 from which the second clutch 5 is no longer able to function properly.
    Figure 2 illustrates a double wet clutch 1 according to a second embodiment. This embodiment differs from the embodiment of Figure 1 only in that the inner periphery of the support portion 19 is devoid of shoulder. Therefore, on the one hand, the outer ring of the rolling bearing 20 is force-fitted inside the housing 52 formed at the radially inner edge of the support portion 19. On the other hand, the second surface of stop 62 able to limit the movement of the force transmitting member 38 of the second clutch 5 forwards under certain abnormal conditions of operation of the double clutch, or at the end of its life is provided on the rear face of the 20. The rolling bearing 20 is here disposed at an axial distance Y2 of the force transmission member 38 when the latter is in its position corresponding to a disengaged state of the second clutch 5. The characteristics of the distance axial Y2 are identical to those described in relation to Figure 1.
    Figure 3 illustrates a double wet clutch 1 according to a third embodiment. This embodiment differs from the embodiment of FIG. 1 only in that the minimum distance between the force transmission member 38 of the second clutch 5 and the support portion 19 is here located at the level of the external zone. 19a of the support portion 19. In other words, the second abutment surface 63 adapted to limit the movement of the force transmission member 38 of the second clutch 5 forward under certain abnormal conditions of operation of the double clutch, or end of life thereof is formed on the outer zone 19a of the support portion 19. The second abutment surface 63 is disposed at an axial distance Y2 of the force transmission member 38 when the latter it is in its position corresponding to a disengaged state of the second clutch 5. The characteristics of the axial distance Y2 are identical to those described in relation to FIG.
    Figure 4 illustrates a double wet clutch 1 according to a fourth embodiment. This embodiment differs from the embodiment of FIG. 1 in that the second abutment surface 64 is able to limit the movement of the force transmission member 38 of the second clutch 5 forward under certain abnormal operating conditions. the double clutch, or end of life thereof is provided on the inner tube 42. To this end, an annular groove 65 is formed on the outer surface of the inner tube 42. The radially inner periphery of the transmission member force 38 protrudes radially inside the annular groove 65.
    In order to allow placing of the force transmission member 38 in a position in which its radially inner periphery projects into the annular groove 65, the inner tube 42 is not integrally formed. and an annular ring is attached and fixed to the rest of the inner tube 42. The annular ring is attached to the front of the housing 41 of the hydraulic system. The annular ring is fixed releasably by means of a press fitting or a weld for example. In this fourth embodiment, the second axial bearing 33 is interposed between the outlet hub 31 of the second clutch 5 and the annular ring attached to the inner tube 42. The cylindrical bearing surface 51 is formed on the annular ring.
    The front edge of the annular groove 65 thus forms the second abutment surface 64. This second abutment surface 64 is located at an axial distance Y2 of the force transmission member 38 when the latter is in its position corresponding to a disengaged state of the second clutch 4. The characteristics of the axial distance Y2 are identical to those described in relation to FIG.
    Although the invention has been described in connection with several particular embodiments, it is obvious that it is not limited thereto and that it comprises all the technical equivalents of the means described and their combinations if they are within the scope of the invention. The use of the verb "to include", "to understand" or "to include" and its conjugated forms does not exclude the presence of other elements or steps other than those set out in a claim.
    In the claims, any reference sign in parentheses can not be interpreted as a limitation of the claim.
    权利要求:
    Claims (14)
    [1" id="c-fr-0001]
    1. Double wet clutch (1) intended to be arranged in a motor vehicle transmission chain, between a motor having a crankshaft and a gearbox comprising two axially-extending coaxial input shafts (2, 3) X, said double wet clutch (1) comprising a first and a second clutch (4, 5) which are respectively capable of transmitting a torque of the crankshaft towards one and the other of the two input shafts (2, 3) of the gearbox, each of the first and second clutches (4, 5) comprising: - an input disk carrier (8, 9) intended to be coupled in rotation to the crankshaft; an output disk carrier (15, 30) intended to be coupled in rotation to one or the other of the two input shafts of the gearbox; a multi-disk assembly (10, 11) comprising at least one friction disc integral in rotation with one of the input and output disk carriers (8, 9, 15, 30) and at least two plates respectively arranged on each side of each friction disk, integral in rotation with the other of the inlet and outlet disk carriers (8, 9, 15, 30), the friction disk and the plates being movable axially between a disengaged position and an engaged position in which said trays pinch said friction disk so as to transmit a torque between the input disk carrier (8, 9) and the output disk carrier (15, 30); and - a force transmission member (25, 38) which is movable in translation along the X axis so as to move the multi-disc assembly (10, 11) from its disengaged position to its engaged position; said double wet clutch (1) further comprising a control system (21) comprising: - a housing (41) intended to be fixed on the gearbox and having a first and a second concentric annular chamber (43, 44) around the X axis; the first annular chamber (43) being located radially outside the second annular chamber (44); and first and second annular pistons (45, 46) respectively axially slidably mounted within the first and second annular chambers (43, 44); the first and second annular pistons (45, 46) each carrying first and second rotational stops (49, 50) cooperating respectively with the force transmission member (25, 38) of the first and second clutch (4, 5). ) to move said clutch (4, 5) between its disengaged position and its engaged position; said double clutch having first and second abutment surfaces (59, 61, 62, 63, 64) which are respectively adapted to limit the movement of the force transmitting member (25, 38) of the first and second clutches (4, 5) towards the multi-disk assemblies (10, 11), the first and the second abutment surface (59, 61, 62, 63, 64) being respectively placed at an axial distance Y1 of the transmission member of force (25) of the first clutch (4) when the first clutch (4) is in the disengaged position and at an axial distance Y2 of the force transmitting member (38) of the second clutch (5) when the second clutch (5) ) is in the disengaged position; the axial distance Y1 being less than an axial dimension of the first annular chamber (43) and greater than a stroke of the first piston (45) corresponding to a displacement of the first clutch (4) from its disengaged position to its engaged position; the axial distance Y2 being less than an axial dimension of the second annular chamber (44) and greater than a stroke of the second piston (46) corresponding to a displacement of the second clutch (5) from its disengaged position to its engaged position.
    [2" id="c-fr-0002]
    A dual wet clutch (1) according to claim 1, wherein each input or output disk carrier (8, 9, 15, 30) has a cylindrical corrugated skirt (18, 22, 29, 34); each friction disk or plate being axially movably mounted on the cylindrical corrugated skirt of one of the output or inlet disk carriers and integrally rotated therewith; one of the input disk carriers (8, 9) having a support portion (19) directed radially inwardly from an edge of its cylindrical corrugated skirt directed towards the control system; said support portion (19) having a radially inner edge cooperating with a bearing (20) for rotating the double clutch about the X axis.
    [3" id="c-fr-0003]
    A dual wet clutch (1) according to claim 2, wherein the force transmitting member (25, 38) of each of the clutches (4, 5) has an outer periphery equipped with a plurality of fingers (26, 39) having an axial orientation and each passing through the support portion (19) at an aperture and for pressing against the multi-disk assembly (9, 10) of said clutch (4, 5).
    [4" id="c-fr-0004]
    A dual wet clutch (1) as claimed in claim 2 or 3, wherein the first abutment surface (59) is provided on the support portion (19) in an area which is radially outwardly of the member force transmission device (38) of the second clutch (5).
    [5" id="c-fr-0005]
    A dual wet clutch (1) according to claim 4, wherein the force transmitting member (25) of the first clutch (4) has, radially outwardly of the force transmitting member (38) the second clutch (5) an axial recess (60) in the direction of the first abutment surface (59).
    [6" id="c-fr-0006]
    The dual wet clutch (1) according to any one of claims 2 to 5, wherein the second abutment surface (61, 63) is provided on the support portion (19).
    [7" id="c-fr-0007]
    A dual wet clutch (1) according to claim 6, wherein the support portion (19) has an outer zone (19a) having a radial orientation and an inner zone (19b) which is folded in a direction opposite to the control system. control within the arrays (10, 11).
    [8" id="c-fr-0008]
    The dual wet clutch (1) according to claim 7, wherein the second abutment surface (63) is formed in the outer region (19a) of the support portion (19).
    [9" id="c-fr-0009]
    The double wet clutch (1) according to claim 7, wherein the second abutment surface (61) is provided in the inner region (19b) of the support portion (19).
    [10" id="c-fr-0010]
    10. Double wet clutch (1) according to claim 6 or 9, wherein said support portion (19) has a shoulder (53) cooperating with the bearing (20) for guiding rotation of the double clutch and wherein the second surface stop (61) is provided on the shoulder (53).
    [11" id="c-fr-0011]
    11. Double wet clutch (1) according to any one of claims 1 to 5, wherein the housing (41) comprises an inner tube (42) extending axially about the axis X, radially inside of the first and second annular chambers (43, 44) and providing an internal space for the passage of the two shafts (2, 3) input of the gearbox, the inner tube (42) extending axially towards the two clutches (4, 5) beyond the first and second annular chambers (43, 44); said second abutment surface (64) being provided on said inner tube (42).
    [12" id="c-fr-0012]
    A dual wet clutch (1) according to claim 11, wherein the inner tube (42) has an annular groove (65) within which radially projects an inner periphery of the force transmitting member (38). ) of the second clutch (5), said annular groove (65) having an edge forming the second abutment surface (64).
    [13" id="c-fr-0013]
    13. Double wet clutch (1) according to any one of claims 2 to 5, wherein the second abutment surface (62) is provided on the bearing (20) for guiding the double clutch in rotation.
    [14" id="c-fr-0014]
    A dual wet clutch (1) according to any one of claims 1 to 13, wherein when the first and second clutches (4, 5) are in their disengaged position, the force transmitting members (25, 38). first and second clutches (4, 5) are spaced apart by a minimum axial distance Y3 which is greater than the axial distance Y1.
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    同族专利:
    公开号 | 公开日
    KR20170107927A|2017-09-26|
    FR3049024B1|2019-04-26|
    KR102320702B1|2021-11-02|
    DE102017104949A1|2017-09-21|
    引用文献:
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    DE102010051447A1|2009-11-20|2011-05-26|Schaeffler Technologies Gmbh & Co. Kg|coupling device|
    DE102011115227A1|2010-10-08|2012-04-12|Borgwarner Inc.|Dual clutch assembly|WO2019154618A1|2018-02-12|2019-08-15|Valeo Embrayages|Transmission device for a hybrid vehicle|
    WO2020025362A1|2018-08-03|2020-02-06|Valeo Embrayages|Wet double clutch with a safety stop capable of limiting the travel of a piston of the control system|
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    DE102014212805A1|2013-07-19|2015-01-22|Schaeffler Technologies Gmbh & Co. Kg|Dual clutch assembly|KR101871917B1|2017-11-20|2018-06-27|주식회사 카펙발레오|Dual clutch device for vehicle|
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    KR102073104B1|2018-04-20|2020-02-04|주식회사 카펙발레오|Dual clutch device for vehicle|
    法律状态:
    2017-03-31| PLFP| Fee payment|Year of fee payment: 2 |
    2017-09-22| PLSC| Publication of the preliminary search report|Effective date: 20170922 |
    2018-03-29| PLFP| Fee payment|Year of fee payment: 3 |
    2020-03-31| PLFP| Fee payment|Year of fee payment: 5 |
    2021-03-30| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1652227|2016-03-16|
    FR1652227A|FR3049024B1|2016-03-16|2016-03-16|DOUBLE WET CLUTCH WITH SAFETY BITS TO LIMIT THE PISTON RUN OF THE CONTROL SYSTEM|FR1652227A| FR3049024B1|2016-03-16|2016-03-16|DOUBLE WET CLUTCH WITH SAFETY BITS TO LIMIT THE PISTON RUN OF THE CONTROL SYSTEM|
    DE102017104949.5A| DE102017104949A1|2016-03-16|2017-03-09|WET DOUBLE COUPLING WITH SAFETY INSTRUCTIONS SUITED TO LIMIT THE HAND OF THE PISTONS OF THE CONTROL SYSTEM|
    KR1020170032704A| KR102320702B1|2016-03-16|2017-03-15|Wet double clutch with safety bearings capable of limiting the piston course of a control system|
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