FR3060680B1 - TORQUE TRANSMISSION MODULE FOR EQUIPPING MOTOR VEHICLE TRANSMISSION - Google Patents

Abstract

Torque transmission module (1) intended to equip a motor vehicle transmission, and comprising a double-clutch mechanism (10) arranged to rotate about an axis (O), a flange (12) and a cover (11) defining between them a chamber (3) housing the mechanism (10), the flange (12) and the cover (11) respectively comprising a first and second peripheral edges (123, 113) intended to be applied against each other , the first and second peripheral edges (123, 113) each comprising at least one hole (115, 125) for fastening the axially aligned module (1) participating in fixing said module (1) to said transmission, the flange (12) comprises at least a first actuating part (180) and a second closure part (190) and which together define the chamber (3), the first actuating part (180) and the second closure part (190) being connected by at least one holding device (500).

Description

Torque transmission module for equipping a motor vehicle transmission

The field of the present invention is that of transmissions for a motor vehicle. The invention relates more specifically to the field of torque transmission modules for equipping a motor vehicle transmission.

Such a torque transmission module is intended to form part of a transmission, in particular for a motor vehicle or for a so-called industrial vehicle, the latter being for example a truck, a public transport vehicle, or an agricultural vehicle. .

Known from the prior art such torque transmission modules comprising a double-clutch mechanism generally wet multidisc type, said mechanism being intended to be mounted on a gearbox of a motor vehicle.

Torque transmission modules are more particularly known comprising a double-clutch mechanism configured to be rotated about an axis. This dual-clutch mechanism commonly includes a first and a second clutch respectively associated with a first and second shaft. Such a mechanism is generally contained in a volume delimited collectively by a clutch flange, or said clutch housing, and a cover forming an outer casing of the clutch mechanism. These torque transmission modules can be mounted by their outer casing on a gearbox housing of a motor vehicle.

The document FR 3,026,153 describes such a torque transmission module in which the cover and the clutch flange are interconnected by a series of first fasteners. The torque transmission module is completely housed in a clutch bell and connected thereto via the tightening of a series of second fastening screws. The series of first and second fixing screws is regularly distributed about the axis on the periphery of the clutch housing. The clutch bell is then mounted on a crankcase of a combustion engine by a series of third fastening screws.

The document also describes the one-piece clutch flange comprising a support portion housing an oil dispensing device for actuating the double clutch mechanism and a generally bell-shaped closure portion having an edge outer device is intended to bear against the lid.

However, such a module has several disadvantages. A first disadvantage relates to the realization of such a torque transmission module. Indeed, the clutch flange has the disadvantage of being made of a solid material such as cast iron. Such a flange has the disadvantage of being expensive and bulky. In addition, this material contributes to increasing the mass of the transmission and therefore the overall mass of the motor vehicle.

Such a clutch flange also has a disadvantage in its implementation. Indeed, this flange clutch can be achieved by a molding process. Such a method, however, has several disadvantages. Firstly, during mass production, the impression used to mold the pre-formed clutch flange is limited to a predetermined number. In addition, the pre-formed clutch housing includes burrs and further requires being dimensioned so that it can be assembled on the clutch mechanism. This adjustment in dimension is then carried out by a machining process and is intended to machine in particular the surfaces of the clutch flange ensuring a mechanical connection with the cover, the elements of the clutch mechanism or with the vehicle transmission. automobile.

A clutch flange as defined also has the disadvantage of being rigid in operation. Indeed, the clutch flange is made hyperstatic by its clamp against the clutch bell with the second fixing screws. In operation, such a hyperstatic assembly has the effect of generating mechanical vibrations that can disrupt the clutch mechanism in its operation.

In addition, such a flange, by its hyperstatic assembly, has the effect of creating bending points weakening its structure. In addition, the axial support of the flange on the housing and the centering supports of the flange on the housing may not be realized when geometry defects exist.

Finally, such a flange clutch has the disadvantage of being difficult to assemble. Indeed, it is necessary to use a large number of fixing screws to achieve this assembly.

The present invention aims to overcome at least one of the aforementioned drawbacks and to provide a torque transmission module having a simplified flange that can be assembled easily and can overcome the problems of hyperstatic mounting. For this purpose, the subject of the invention is a torque transmission module intended to equip a motor vehicle transmission, said module comprising: a mechanism with double clutches being arranged to rotate about an axis; a flange and a cover defining between them a chamber housing the double clutch mechanism, the flange and the cover respectively comprising a first peripheral edge and a second peripheral edge intended to be applied against each other, the first and the second peripheral edges each comprising at least one axially aligned fixing hole participating in the attachment of said module to said transmission, characterized in that the flange comprises at least a first actuating part and a second closure part distinct from one another and which delimit together the chamber, the first actuating part and the second closure part being connected to each other. one and the other by at least one holding device.

With these latter features, it is possible to provide a flange which at least one of the parts, namely the first actuating part or the second closure part, can be made of a different material. For example, the first actuating part may be made of a material such as cast iron or steel, while the second closure part may be made of a material such as an aluminum alloy or a sheet that may have flexibility.

It is then possible to reduce the mass of the transmission module and thus contribute to reducing the overall weight of the motor vehicle.

Another advantage of the invention relates to the embodiment of the flange of the torque transmission module. In this case, the first actuating part and the second closing part are produced by different manufacturing processes. For example, the first actuating part can be made by molding, while the second closure part can be made by stamping. In this way, it is possible to simplify the manufacture of the flange without requiring a particular machining process of the first peripheral edge of the flange or at least. The invention also makes it possible to overcome the problems of hyperstatic assembly. Indeed, the holding device of the invention can avoid flange bending areas when it is derived from material and monobloc.

The term "holding device" means any mechanical device that can keep two parts together. Such a holding device can provide a flexible mechanical connection, that is to say allowing a degree of freedom of at least one piece relative to the other,

Alternatively, a holding device may designate any mechanical device that can hold two pieces together. Such a holding device can provide a rigid mechanical connection, that is to say not allowing a degree of freedom of a room relative to the other,

In all cases, the term "holding device" means a mechanical device of the two parts that can be mounted or disassembled.

Such a holding device has the effect of ensuring a simplified assembly of the two parts forming the flange. This holding device also has the advantage of being simply dismountable.

In addition, the holding device of the invention can authorize at least one degree of freedom. In this way, it is possible to make the connection less rigid between the support portion of the flange and the closing portion of the flange.

There is no risk of hyperstatic mounting on the transmission case.

Another advantage of the particular features of the invention relates to the assembly of the flange on a support of the transmission of a motor vehicle, such as a gearbox housing. Indeed, for example, when the holding device allows a degree of freedom in a radial direction with respect to the axis as defined according to the invention, it is then possible to make the second piece of closure of the mobile flange in translation. in the same direction. This mobility in translation can then facilitate the assembly of the flange on a gearbox housing while allowing a good crushing of the seals in contact with the gearbox housing.

The torque transmission module according to the invention may advantageously comprise at least one of the improvements below, the technical characteristics forming these improvements being able to be taken alone or in combination: the first actuating part forms part of a system of actuating at least one of the clutches; the first actuating part forms part of a system for actuating the two clutches; the first actuating part is a casing of the actuating system, the latter comprising at least one actuator arranged to slide in the casing of the actuating system and exert a force on at least one of the clutches; the first actuating part comprises a cylindrical centering surface configured to center the torque transmission module on a vehicle transmission; the first actuating part is connected to a clutch support via at least one support bearing; the second closure part comprises the first peripheral edge; advantageously the first peripheral edge extends radially outwards with respect to the axis; the second closure part is concave seen from the chamber, the chamber being mainly defined by the concavity of the second closure part; the first peripheral edge is configured to secure said module to said transmission, said first peripheral edge is axially offset on the front portion of the torque transmission module; advantageously, the first peripheral edge is configured to fasten said module to said transmission detachably; the holding device allows an axial displacement of the second closure part relative to the first actuating part. Preferably, the amplitude of the axial displacement allowed by the second closure part with respect to the first actuating part is of the order of 1 to 5 mm; advantageously, the holding device allows axial displacement of the second closure part in a direction parallel to the axis; advantageously, the holding device allows at least one degree of freedom of the second closure part relative to the first actuating part; advantageously, the holding device allows a degree of freedom of the second closure part relative to the first actuating part in an axial direction parallel to the axis; advantageously, the degree of freedom of the second closure part in an axial direction allows the axial displacement; advantageously, the holding device comprises at least one bending element allowing axial deformation with respect to the axis; advantageously, the bending element is constituted by the spring washer; the second closure member is held axially by the holding device and the holding device allows a radial displacement of the second closure member relative to the first actuating part; advantageously, the holding device allows a radial displacement of the second closure part relative to the first actuating part; advantageously, the holding device allows a degree of freedom of the second closure part relative to the first actuating part in a radial direction perpendicular to the axis; advantageously, the degree of freedom of the second closure part in a radial direction allows the radial displacement of the second closure part with respect to the first actuating part; a radial clearance is provided between the first actuating part and the second closure part; advantageously, the radial clearance is formed by the radial displacement; the radial clearance is formed between an inner diameter of the second closure member and an outer diameter of the first actuating member; an axial clearance is provided between the first actuating part and the second closure part; the holding device allows axial displacement and radial displacement of the second closure part with respect to the first actuating part; advantageously, the holding device allows a first degree of freedom of the second closure part with respect to the first actuating part in an axial direction parallel to the axis and allows a second degree of freedom of the second closure part by relative to the first actuating part in a radial direction perpendicular to the axis; advantageously, the first degree of freedom of the second closure member in an axial direction allows the axial displacement relative to the first actuating part and the second degree of freedom of the second closure part in a radial direction allows the radial displacement relative to the first actuating part; advantageously, a radial clearance is provided between the first actuating part and the second closure part to ensure the radial displacement while the axial displacement is authorized by the axial deformation of the bending element; the holding device comprises at least one inner fixing screw and / or rivet ensuring a fixed holding of the second closure part against the first actuating part; the holding device makes it possible to carry out at least one plane bearing of the second closure part against the first actuating part; the plane support is achieved by the support of the second closure part against the first actuating part seen from the chamber; the plane support is achieved by the support of the second closure part against the first actuating part seen from outside the chamber; advantageously, the first actuating part comprises first internal fixing holes configured to face second internal fixing holes of the second closure part, the first internal fixing holes and the second internal fixing holes are configured to receive internal fixing screws; advantageously each of the centers of the first internal fixing holes and the second internal fixing holes merges with a straight line parallel to the axis: advantageously, the first internal fixing holes, the second internal fixing holes form in the assembled state a internal fastening member of the torque transmission module; advantageously the first peripheral edge comprises first module fixing holes configured to be opposite tapped holes of a gearbox housing of the transmission; advantageously the second peripheral edge comprises second fixing holes of the module configured to face the first fixing holes of the module disposed on the first peripheral edge, the first and second mounting holes of the module are configured to receive fixing screws of the module; advantageously, the first fixing holes of the module and the second mounting holes of the module form in the mounted state a fixing member of the torque transmission module; the plane support is formed in part by a radially inner edge of the second closure part bearing against a stop of the first actuating part; advantageously, the radially inner edge is defined with respect to a direction perpendicular to the axis; advantageously, the abutment comprises the first internal fixing holes and the peripheral edge comprises the second internal fixing holes; the radially inner edge of the second closure piece bears against the first stop of the first actuating part and against a second stop secured to the first actuating part; the second closure part comprises at least one cylindrical axial bearing, the cylindrical axial bearing being arranged to abut against a circumferential axial coupling zone of the transmission, the cylindrical axial bearing being of shape in correspondence of the docking zone circumferential axial; advantageously, the cylindrical axial scope is defined with respect to a direction parallel to the axis; a first sealing device is configured to be disposed between a radial bearing zone of the second closure piece and a radial docking zone of the transmission, the radial bearing zone being of shape corresponding to the zone of radial docking; advantageously, the first sealing device is a flat seal; the radial bearing zone and the cylindrical axial bearing surface of the second closure part are delimited by the same joining edge; the abutment or first abutment is formed by a shoulder of the first actuating part and the second abutment is formed by a stop ring disposed on the first actuating part; advantageously, the stop ring is an open ring, more advantageously, the stop ring is a circlip; the abutment or first abutment is formed by a stop ring disposed on the first actuating part and the second abutment is formed by a shoulder of the first actuating part; the stop or first stop is formed by a first stop ring disposed on the first actuating part and the second abutment is formed by a second stop ring disposed on the first actuating piece; the second closure part is prestressed under load by an elastic washer; advantageously, the holding device comprises the spring washer; advantageously, the spring washer is disposed between the first stop and the inner peripheral edge; the spring washer comes to press the radially inner edge against the stop; advantageously, the spring washer comes to press the radially inner edge against the first stop; the spring washer comes to press the radially inner edge against the second stop; the radially inner edge of the second closure member bears against the first stop of the first actuating part, the spring washer bearing axially on a second stop secured to the first actuating part; advantageously, the radially inner edge of the second closure member bears against the second abutment of the first actuating part, the spring washer bearing axially on the first abutment secured to the first actuating part; at least one internal fixing screw makes it possible to carry out the flat support; the inner fixing screw is disposed axially from a face of the radially inner edge of the second closure part seen from the chamber; the inner fixing screw is arranged axially on one side of the radially inner edge of the second closure part seen from outside the chamber; advantageously, the second closure part comprises an annular portion in its center delimiting the radially inner edge; a first sealing device is configured to be disposed between the cylindrical axial bearing surface of the second piece of the second closure part and a circumferential axial coupling zone of the transmission, the cylindrical axial bearing being of shape in correspondence of the zone; circumferential axial docking; advantageously, the first sealing device is an O-ring; a second sealing device is configured to be disposed between the first actuating part of the flange and the transmission; a second sealing device is configured to be disposed between the first actuating part of the flange and the transmission; a locking device ensures a locking in rotation of the first actuating part of the flange relative to the second closure part of the flange; the locking device consists of a fluted shape of the first actuating part in correspondence with a fluted shape of the second closure part; the second closure part is axially centered on the first actuating part; the first actuating part is an aluminum alloy and the second closing part is a metal sheet; the second closure piece is an aluminum alloy and the first actuating piece is a metal sheet; the metal sheet is an alloy of aluminum or steel; advantageously, the metal sheet is obtained by press stamping; the clutches are wet; the clutches are arranged radially one above the other; alternatively, the clutches are arranged axially one in front of the other; the flange, the clutches and the cover form a pre-assembled subassembly; advantageously, an angular positioning device ensures the positioning of the second closure part relative to the first actuating part so as to position the first internal fixing holes opposite the second internal fixing holes; advantageously, the angular positioning device is formed by at least one indexing pin connecting the first actuating part to the second closure part; advantageously, the angular positioning device is formed by at least one indexing pin connecting the first actuating part to the second closure part; advantageously, the angular positioning device comprises an indexing hole facing the indexing pin; advantageously, the indexing hole is formed on the first actuating piece and the indexing pin is formed on the second closure piece. The invention also relates to a transmission for a motor vehicle, comprising at least one gearbox housing of a transmission and a torque transmission module as described above.

The transmission according to the invention may advantageously comprise at least one of the improvements below, the technical characteristics forming these improvements can be taken alone or in combination: the first sealing device is disposed between the first peripheral edge of the second piece closing the flange and the gearbox housing; the second sealing device is disposed between the first actuating part of the flange and the gearbox housing; the first sealing device is disposed between the radial bearing zone of the second closure part and the radial docking zone in correspondence of the gearbox housing; the second sealing device is disposed between the first actuating part of the flange and the gearbox housing. The invention also relates to a method of assembling a torque transmission module according to the invention on a transmission of a vehicle, the method comprising the following steps: a. a positioning step of bringing the second closure member closer to the first actuating member; b. a holding step of holding the second closure part at least partly against the first actuating part by means of the holding device so as to form the flange; c. an assembly step of arranging the clutches in the chamber; d. a closing step of closing, by means of at least one fixing hole of the module, the chamber by applying the second peripheral edge of the cover against the first peripheral edge of the flange.

Advantageously, in the positioning step, the first internal fixing holes are arranged facing the second internal fixing holes.

Advantageously, in the positioning step, the second closure piece is brought closer to the first actuating part from an axial end of the first part defined by the cylindrical centering surface.

Advantageously, in the positioning step, the second closure piece is brought closer to the first actuating part from an axial end of the first part opposite the cylindrical centering surface. Other features, details and advantages of the invention will emerge more clearly on reading the description given below as an indication in relation to drawings in which: FIG. 1 illustrates a sectional view of a first mode embodiment of a torque transmission module according to the invention, wherein the flange comprises a first actuating part and a second closure part and where, in particular, the holding device allows axial displacement of the second part closing with respect to the first actuating part; FIG. 2 illustrates a sectional view of a second embodiment of a torque transmission module according to the invention in which, in particular, the holding device allows both an axial displacement and a displacement. radial of the second closure part relative to the first actuating part; FIG. 3 illustrates a sectional view of a third embodiment of a torque transmission module according to the invention in which in particular the holding device ensures a fixed retention of the second closure part with respect to the first actuating part;

In the remainder of the description and in the claims, the following terms will be used without limitation and in order to facilitate understanding: "front" AV or "rear" AR in the direction relative to an axial orientation determined by the main O axis of rotation of the transmission system, the "rear" designating the part to the right of the figures, the side of the transmission, and "the front" designating the left side of the figures, the side of the engine; and "inner / inner" or "outer / outer" with respect to O-axis and in a radial orientation, orthogonal to said axial orientation, "the interior" designating a proximal portion of the O-axis and "the exterior" designating a distal part of the axis O; and

The clutch mechanism of the torque transmission module illustrated in FIG. 1 will first be described. It should be noted that the clutch mechanisms of each of the embodiments are identical and can be described in a manner similar to the embodiment of Figure 1 as detailed below.

Thus, as illustrated in FIG. 1, the exemplary embodiment of the torque transmission module 1 is intended to equip a transmission of a motor vehicle. For this, the torque transmission module is mounted on a gearbox housing 2 of a motor vehicle. The torque transmission module comprises a cover 11 and a flange 12 forming together a chamber 3 containing a double clutch mechanism 10.

The torque transmission module 1 comprises a double-clutch mechanism 10 preferably of the wet double-clutch type, and preferably still in a so-called radial position, a first clutch 100 being located on the outside with respect to a second clutch 200. dual clutch mechanism 10 is integrated on a transmission chain comprising a transmission, not shown in Figure 1, the transmission being coupled in rotation to the double clutch mechanism 10. In general, the double clutch mechanism 10 is arranged to be able to couple in rotation an unillustrated input shaft to a first transmission shaft A1 or alternatively to a second transmission shaft A2 via respectively the first clutch 100 or the second clutch 200.

In the context of the invention, the input shaft is rotated by at least one crankshaft of an engine, for example a heat engine not shown in Figure 1; and the first and second transmission shafts A1, A2 are intended to be coupled in rotation to the transmission such as for example a gearbox of the type fitted to motor vehicles.

Preferably, the first transmission shaft A1 and the second transmission shaft A2 are coaxial. More particularly, the second transmission shaft A2 takes the form of a hollow cylinder inside which the first transmission shaft Al can be inserted.

As illustrated in Figure 1, the first clutch 100 and the second clutch 200 are advantageously multi-disk type. Each multi-disk clutch comprises on the one hand a plurality of first friction elements 101, 201, such as, for example, coupling disks, integrally connected in rotation with the input shaft, and on the other hand a plurality of second friction elements 102, 202, such as for example friction discs, integrally connected in rotation to at least one of the transmission shafts A1, A2.

Optionally, the plurality of first friction elements 101, 201 consist of friction discs integrally connected in rotation with the input shaft, and the plurality of second friction elements 102, 202 consist of flanges integrally connected in rotation to at least one of the transmission shafts A1, A2.

The first transmission shaft A1 is rotatably coupled to the input shaft and driven by it in rotation when the first clutch 100 is configured in a so-called engaged position for which the plurality of first friction elements 101 is rotatably coupled to the plurality of second friction elements 102. Alternatively, the first transmission shaft A1 is rotatably decoupled from the input shaft when the first clutch 100 is configured in a so-called disengaged position for which the plurality of first friction elements 101 is rotatably decoupled from the plurality of second friction elements 102.

Similarly, the second transmission shaft A2 is rotatably coupled to the input shaft and rotated by it when the second clutch 200 is configured in an engaged position for which the plurality of first friction elements 201 is coupled. in rotation to the plurality of second friction elements 202. Alternatively, the second transmission shaft A2 is rotatably decoupled from the input shaft when the second clutch 200 is configured in a so-called disengaged position for which the plurality of first elements friction device 201 is rotatably decoupled from the plurality of second friction elements 202.

In the dual clutch mechanism 10 shown in FIG. 1, the first clutch 100 is arranged to engage odd gear ratios and the second clutch 200 is arranged to engage the even gear ratios and the reverse gear of the gearbox. Alternatively, the ratios supported by said first clutch 100 and second clutch 200 can be respectively reversed.

The first clutch 100 and the second clutch 200 are arranged to alternately transmit a so-called input power - a torque and a rotational speed - of the input shaft, to one of the two transmission shafts A1, A2, according to the respective configuration of each clutch 100 and 200 and via an inlet web 109.

The clutches 100 and 200 are arranged not to be simultaneously in the same engaged configuration. On the other hand, the first and second clutches 100, 200 can simultaneously be configured in their disengaged position.

We will now describe in more detail the double clutch mechanism housed in the chamber 3.

As shown in FIG. 1, the double-clutch mechanism 10 comprises an input element which is rotatably coupled on the one hand to the input shaft and on the other hand to the input web 109 in order to transmit the power - the torque and the rotational speed - generated at the motor at one of the clutches 100, 200 of the double clutch mechanism 10. Preferably, the input element of the double clutch mechanism 10 comprises a hub 150, preferably in rotation about the axis O. On its lower elongation, the input hub 150 is connected in rotation and / or axially to the input shaft, possibly via a damping device not shown such as a double damping flywheel for example.

On its outer elongation, the inlet hub 150 is coupled to the inlet web 109, and more particularly at a lower end and located forwardly of said inlet web 109. Preferably, the entry web 109 and the input hub 150 are integral, for example fixed by welding and / or riveting.

On the side of its upper end, the inlet web 109 is rotatably connected to the first clutch 100 via an inlet disk carrier 106, the inlet disk carrier 106 being rotatably connected to the web input 109, preferably by cooperation of shapes, for example by grooves.

The first and second clutches 100 and 200 are controlled by an actuating system 300 which is arranged to be able to configure them in any configuration between the engaged configuration and the disengaged configuration.

The actuating system 300 comprises: a first actuator 320 arranged to configure the first clutch 100 in a configuration between the engaged configuration and the disengaged configuration; a second actuator 330 arranged to configure the second clutch 200 in a configuration between the engaged configuration and the disengaged configuration; a housing 181 in which are housed at least a portion of the first and second actuators 320, 330.

Preferably, the first and second actuators 320 and 330 are of the hydraulic cylinder type. The first and second actuators 320, 330 may each comprise an annular piston, each annular piston being coaxial with the axis O and developing an axial movement to configure the corresponding clutch. In this case, the actuating system 300 also comprises a hydraulic fluid supply channel for each actuator 320, 330. Preferably, the hydraulic fluid is a pressurized fluid, for example oil.

The first actuator 320 is connected to the first clutch 100 via a part of a first decoupling bearing 140 and secondly of a first force transmission member 105. The first decoupling bearing 140 is arranged for transmitting axial forces generated by the first actuator 320 to the first force transmission member 105.

The first force transmission member 105 is arranged to transmit an axial force to the first clutch 100 via its upper elongation, said upper elongation extending axially forward to be able to spread or squeeze the first friction elements 101 against the second elements friction 102 on the one hand, and against an external reaction means 103 of the inlet web 109 on the other hand.

The first force transmission member 105 takes the form of a corrugated sheet axially curved forwardly at its outer radial end. More particularly, the first force transmission member 105 collaborates with the first clutch 100 via a plurality of axial extension spans 1051 forming upper fingers 1051 which allow the friction elements 101 to be pushed forward. , 102 of the first clutch 100 under the effect of an axial movement towards the front of the first actuator 320. By way of non-limiting example, the first force transmission member 105 can be obtained by stamping.

The first force transmission member 105 comprises an upper radial extension surface 1052 located behind the upper fingers 1051. The upper radial extension area 1052 extends radially from the first clutch 100 to the interior of the second clutch 200.

An intermediate axial extent of extension 1053 extends the upper radial extension range 1052 under the second clutch 200 towards the front of the dual clutch mechanism 10.

Finally, the first force transmission member 105 comprises an inner radial extension portion 1055 connected to the intermediate axial extension reach 1053 via a curved zone 1054. The rear face of the radial extension portion 1055 is in contact with a front face of the first decoupling bearing 140 connected to the first actuator 320.

The external reaction means 103 is integral with the inlet web 109. Preferably, the external reaction means 103 is derived from material of the inlet web 109; alternatively, the external reaction means 103 is fixed integrally to the entry web 109 by any fastening means, such as for example by riveting or welding.

The external reaction means 103 has a shape complementary to that of the first or second friction elements 101, 102, so as to allow a frictional coupling of the first and second friction elements 101, 102 when the first actuator 320 exerts an axial force forward to configure the first clutch 100 in its engaged position. Conversely, when the first force transmission member 105 is pushed backwards by resilient return elements which will be described later, then the first friction elements 101 separate from the second friction elements 102, then decoupling said friction elements and thus to configure the first clutch 100 in its disengaged configuration.

The external reaction means 103 has in particular external splines which cooperates with corresponding inner grooves of the input disk carrier 106.

The first clutch 100 is adapted to be rotatably coupled to the first transmission shaft A1 via a first output disk carrier 104 forming an output member of said first clutch 100. More particularly, the first disk carrier of Outlet 104 is rotatably coupled to the second friction members 102 at its upper end on the one hand, and on the other hand to a first output hub 170 at its lower end.

The first output disk carrier 104 comprises on its outer radial periphery an axial elongation 107 which is provided with a toothing intended to cooperate with a complementary toothing on each second friction element 102, and more particularly to the inner radial periphery of each second friction element 102 of the first clutch 100. The first output disk carrier 104 is thus coupled in rotation by meshing with the second friction elements 102 of the first clutch 100.

At its lower radial end, the first output disk carrier 104 is connected to the first output hub 170, preferably fastened together by welding or riveting.

The first output hub 170 has radially inside axial splines arranged to cooperate with complementary splines located on the first transmission shaft Al, so as to achieve a coupling rotation.

A radial bearing 195 is interposed between the first output hub 170 and the inlet hub 150 to withstand the radial forces of the inlet hub 150 and / or the inlet web 109 despite the different speeds of rotation respectively turn the input shaft and the first drive shaft Al.

Similarly, the second clutch 200 of the dual clutch mechanism 10 is similar in design to that of the first clutch 100.

The second actuator 330 is connected to the second clutch 200 via on the one hand a second decoupling bearing 240 and secondly on a second force transmission member 205. The second decoupling bearing 240 is arranged for transmitting axial forces generated by the second actuator 330 to the second force transmission member 205.

The second force transmission member 205 is located axially between the input disk carrier 106 and the first force transmission member 105.

The second force transmission member 205 is arranged to transmit an axial force to the second clutch via its upper elongation, said upper elongation extending axially forwardly and through an opening 108 arranged in the disk carrier. inlet 106 to be able to move or squeeze the first friction elements 201 against the second friction elements 202 on the one hand, and against an inner reaction means 203 on the other hand.

The second force transmission member 205 takes the form of a corrugated sheet and is curved axially forward at its outer radial end. More particularly, the second force transmission member 205 collaborates with the second clutch 200 via a plurality of axial extension lands 2051 forming inner fingers 2051 which allow the friction elements 201 to be pushed forward. , 202 of the second clutch 200 under the effect of an axial movement towards the front of the second actuator 330. By way of non-limiting example, the second force transmission member 205 can be obtained by stamping.

The second force transmission member 205 comprises an upper radial extension surface 2052 located behind the upper fingers 2051. The upper radial extension range 2052 extends radially from the second clutch 200 to the interior of the second clutch 200, and more particularly outside the range of intermediate axial extension 1053 of the first force transmission member 105.

An intermediate axial extension surface 2053 extends the upper radial extension range 2052 under the second clutch 200 toward the front of the dual clutch mechanism 10. The intermediate axial extension surface 2053 is located radially within the second clutch 200 and outside the upper radial extension range 1052 of the first force transmission member 105. More particularly, it is located inside the input disk carrier 106.

Finally, the second force transmission member 205 comprises an inner radial extension portion 2055 connected to the intermediate axial extension surface 2053 via a radial extension surface 2054. The rear face of the central portion 205 inner radial extension 2055 is in contact with a front face of the second decoupling bearing 240 connected to the second actuator 330.

The internal reaction means 203 is integral with an axial extension portion 206 facing forward and secured to the input disk carrier 106, fixed to the input disk carrier 106 by any means, such as for example by welding or riveting. Alternatively, the inner reaction means 203 and the input disk carrier 106 are made of material. The external reaction means 203 has a shape complementary to that of the first or second friction elements 201, 202, so as to allow a friction coupling of the first and second friction elements 201, 202 when the second actuator 330 exerts an axial force forward to configure the second clutch 200 in its engaged position. Conversely, when the second force transmission member 205 is pushed back by resilient biasing elements which will be described later, then the first friction elements 201 separate from the second friction elements 202, then decoupling said friction elements 201, 202 and thus to configure the second clutch 200 in its disengaged configuration. By way of nonlimiting example, the external reaction means 203 may take the form of a ring with a toothing on the outer periphery and a central support groove which extends axially rearwardly.

The second clutch 200 is intended to be rotatably coupled to the second transmission shaft A2 via a second output disk carrier 210 forming an output element of said second clutch 200. More particularly, the second disk carrier of outlet 210 is rotatably coupled to the second friction members 202 at its upper end on the one hand, and secondly to a second output hub 220 at its lower end.

The second output disk carrier 210 comprises on its outer radial periphery an axial elongation 207 which is provided with a toothing intended to cooperate with a complementary toothing on each second friction element 202, and more particularly to the inner radial periphery of each second friction element 202 of the second clutch 200. The second output disk carrier 210 is thus coupled in rotation by meshing with the second friction elements 202 of the second clutch 200.

At its lower radial end, the second output disk carrier 210 is connected to the second output hub 220, preferably fixed together by welding or riveting. Furthermore, an axial bearing 160 is interposed between the first output disk carrier 104 and the second output disk carrier 210 in order to be able to transmit an axial force between the two output disk carriers 104, 210 which can rotate at different speeds. different speeds when the first and second clutches 100, 200 are configured in a different configuration.

The second outlet hub 220 comprises radially inside the axial splines arranged to cooperate with complementary splines located on the second transmission shaft A2, so as to perform a coupling in rotation.

The first and second clutches 100, 200 respectively comprise resilient return elements not shown in FIG. 1. The elastic return elements are arranged to generate a return force oriented axially towards the rear in order to automatically push back the first and the second. actuator 320, 330 to the rear. More particularly, the elastic return elements axially urge the first and respectively the second force transmission members 105, 205 rearwards in order to facilitate the spacing of the first friction elements 101, 201 with respect to the second friction elements 102. , 202 of the first and second clutch 100, 200 respectively by pushing the first and the second actuator 320, 330 towards rarrière.

We will now describe in more detail the lid and the flange and the mechanical connections between them.

Referring also to Figure 1, there is shown the torque transmission module 1 formed in part by the cover 11 and the flange 12 together defining the chamber 3 housing the double clutch mechanism 10 as described above. The flange 12 comprises a first actuating part 180 and a second closure part 190. The cover 11 is circular in shape with a revolution and an axis O; it is delimited by a second inner radial contour 110 and a second outer radial contour 111. The second inner radial contour 110 delimits an annular section 112 through which the inlet hub 150 of the double clutch mechanism 10 can emerge. The second radial contour outside 111 delimits the outer end of a second peripheral edge 113 in correspondence of a first peripheral edge 123 of the flange 12. Second extensions 114 extend radially outwardly relative to the axis O from the second contour external radial 111 of the cover 11. The second extensions 114 are, in a plane transverse to the axis of rotation O as illustrated in Figure 1, of rounded shape. The second extensions 114 are intended to receive screws 116 for fixing the module 1 through the second holes 115 for fixing the module 1 formed in the center of each second extension 114.

The second fixing holes 115 of the module 1 and the screws 116 for fixing the corresponding module 1 partially form a member for fastening the module 117. The term "module fastener" means each of the second holes 115 for fixing the module. of cover 11 in correspondence with first holes 125 for fixing the module of the flange 12 and configured to receive respectively a screw 116 for fixing the module 1, taken collectively. In other words, the fixing member of the module 117 is formed by all the second holes 115 for fixing the module 1 cooperating with the first holes 125 for fixing the corresponding module 1.

There is also shown an angular indexing device 13 formed by at least one indexing pin 130 disposed on the second peripheral edge 113 of the lid 11. As will be described later, the indexing pin 130 extends into an axial direction parallel to the axis O so as to be housed without displacement in respectively an indexing hole 132 formed in correspondence on the flange 12. However, the invention is not limited to an indexing pin, the angular indexing device 13 could advantageously comprise two indexing pins 130.

In practice, the indexing pin 130 ensures a positioning of the cover 11 on the flange 12 in a predetermined angular position as will be described later.

The angular indexing device 13 as formed by the indexing pin 130 thus allows radial and angular positioning of the cover 11 on the flange 12.

The lid 11 comprises a corrugated section delimited by the second outer radial contour 111 and the second inner radial contour 110 as defined above. A second extension 114 of the cover 11 as shown extends beyond the second outer radial contour 111 and includes a second fixing hole 115. The cover 11 conforms by its shape to an inlet veil 109 of the double-clutch mechanism 10. The annular section 112 of the cover 11 comprises a first rim 118 extending radially outwards with respect to the axis O and successively a second edge 119 extending axially relative to the axis O in the direction of the clutches 100, 200. The second edge 119 is intended to receive together a first seal 4 sealing. As shown, the first seal 4 ensures a sealing contact between the inlet hub and the cover 11 so as to prevent the flow of a hydraulic fluid from the chamber 3 to the outside.

The flange 12 comprises a first inner radial contour 120 delimiting an annular portion 191 of the second closure member 190 and a first outer radial contour 121. As shown, the flange 12 is bell-shaped or concave seen from the chamber 3. It will be understood that the chamber 3 is predominantly defined by the concavity of the second closure part 190. In the embodiment illustrated in FIG. 1, the flange 12 is radially supported by the first internal radial contour 120 against a support of FIG. The first external peripheral edge 121 delimits a first peripheral edge 123 disposed opposite the second peripheral edge 113 of the lid 11. The flange 12 comprises a plurality of first extensions 124 corresponding to the second extensions 114. of the cover 11 to allow the attachment of the cover 11 on the flange 12 via the pins first holes 125 fixing the module 1 of said flange 12 cooperating with the second holes 115 for fixing the module 1 of the lid 11. As shown, a first extension 124 of the flange 12 extends radially outwardly beyond the first outer radial contour 121. The first extension 124 comprises a first fixing hole 125 in correspondence with one of the second holes 115 for fixing the module 1 of the cover 11.

A second seal 5 is disposed between the cover 11 and the flange 12 to prevent the flow of hydraulic fluid along the first and second peripheral edges 123, 113 from the chamber 3. More particularly, the second sealing gasket 5 is configured to bear against the first peripheral edge 123 as well as against each of the first and second extensions 124, 114. The second gasket 5 is then shaped in correspondence with the first or second peripheral edge 123, 113 and each of the first and second extensions 124, 114.

The first peripheral edge 123 of the flange 12 and the second peripheral edge 113 of the cover 11 respectively comprise a first bearing zone 128 and a second bearing zone 118 facing one another. The first bearing zone 128 and the second bearing zone 118 are intended to each bear against the second seal 5.

The angular indexing device 13 is represented by the indexing pin 130 formed from the cover 11. The indexing pin 130 is formed in the second peripheral edge 113 of the cover 11 as previously described. In general, the indexing pin 130 can be made by stamping or molding, for example. The flange 12 comprises at least the indexing hole 132 formed on the first peripheral edge 123 and which is intended to receive the indexing pin 130. The indexing pin 130 assumes a solid circular shape extending axially with respect to the axis O to the flange 12 from the second peripheral edge 113.

To assemble the cover 11 on the flange 12, the cover 11 is arranged axially with respect to the axis O so that the second peripheral edge 113 of the cover 11 is opposite the first peripheral edge 123 of the flange 12. The cover 11 is then angularly positioned about the axis O so that the indexing pin 130 is respectively opposite the indexing hole 132. In other words, the cover 11 is rotated about the axis O and relative to the flange 12 until the indexing pin 130 is respectively opposite the indexing hole 132.

The pin 130 and the indexing hole 132 together form the angular indexing device 13.

When the cover 11 is assembled on the flange 12, the first peripheral edge 123 is applied against the second peripheral edge 113 via the second seal 5. The indexing pin 130 of the second peripheral edge 113 is then inserted into the indexing hole 132 of the first peripheral edge 123 of the flange 12.

Thanks to these angular positioning steps, it is possible to guarantee positioning in correspondence of the first and second holes 115, 125 for fixing the module 1 of the fastener of the module 117. The first bearing zone 128 of the flange 12 and the second bearing zone 118 of the lid 11 are then substantially perpendicular to each other.

This particular positioning has the effect of allowing the second seal 5 to ensure good contact sealing between the first bearing zone 128 of the flange 12 and the second bearing zone 118 of the cover 11, and in particular to avoid leakage of a hydraulic fluid in the torque transmission module 1 and in particular for lubricating the clutch mechanism 10.

Screws 116 for fixing the module 1 are intended to be inserted in the first and second holes 115, 125 for fixing the module 1 respectively of the flange 12 and the cover 11 to be housed in tapped holes 21 of the gearbox housing 2 In the mounted state, each of the first and second holes 115, 125 for fixing the module 1 is configured to receive a screw 116 for fixing the module 1, as described, so as to hold the cover 11 and the flange 12 tightly. together against transmission case 2.

A first sealing device 6 is configured to be disposed between the first peripheral edge 123 of the flange 12 and the transmission case 2. The tightness of the torque transmission module 1 is ensured by the crushing of the second seal 5 sealing and first sealing device 6 when the fastening screws 116 of the module 1 are inserted into the threaded holes 21 of the gearbox housing 2.

Note also that the flange 12 and the cover 11 have a section of thickness different from one another.

In the same way, the indexing pin 130 can be obtained by stamping or molding during the design of the cover 11, for example.

The indexing pin 130 makes it possible to obtain an angular positioning of the lid 11 with respect to the flange 12, and particularly of the second peripheral edge 113 with respect to the first peripheral edge 123. Thanks to this angular positioning of the lid 11, it is possible to also determine the radial position of the cover 11 relative to the axis O, and therefore with respect to the first seal 4. Consequently, it is thus possible to ensure a good seal between the annular section 112 of the cover 11 and the inlet hub 150 of the double clutch mechanism 10. This prevents a bad contact of the first seal 4 with the lid 11 that can generate a leakage of the hydraulic fluid out of the torque transmission module 1.

In FIG. 1 particularly, there is shown a housing of the gearbox housing 2 intended to partially receive the torque transmission module 1. As assembled, the double clutch mechanism 10 comprises a cylindrical centering bearing 182 s extending axially with respect to the axis O towards the outside of the chamber 3 delimited by the flange 12. The cylindrical centering surface 182 is in the gearbox case 2 by means of a cylindrical zone of the casing of gearbox 2, the axial end of the cylindrical centering centering bearing surface 182 bears against the gearbox case 2 by means of a second sealing device.

The first and second sealing devices 6, 7 are configured and dimensioned so as to allow axial retention of the torque transmission module 1 with respect to the axis O.

It will be noted that in FIG. 2, the indexing device 13 as described previously has not been represented. However, it will be understood that the embodiment of FIG. 2 may comprise an indexing device 13 as described.

The characteristics common to the various embodiments of the invention have been described. In the remainder of the description, these various embodiments will now be described. In this case, a first embodiment makes it possible to allow axial displacement 502 of the second closure part 190 with respect to the first actuating part 180. A second embodiment makes it possible to authorize, at the same time, an axial displacement and a radial displacement 503 of the second closure part 190 with respect to the first actuating part 180. A third embodiment allows a fixed retention of the second closure part 190 with the first actuating part 180.

Of course, the embodiments illustrated below are in no way limiting and the technical characteristics of each embodiment can be combined with the technical characteristics of the other embodiments.

According to the first embodiment illustrated in FIG. 1, of the invention mentioned above, there is shown the holding device 500 ensuring a maintenance of the second closure part 190 with the first actuating part 180. As illustrated , the first actuating part 180 forms part of an actuating system 300 of each of the clutches 100, 200 of the double clutch mechanism 10, in particular the first actuating part 180 corresponds to the casing 181 of the actuating system 300 of the clutches 100, 200. This housing 181 of the actuating system 300 houses the two actuators 320, 330 respectively configured to engage each of the clutches 100, 200. It will be understood that these actuators 320, 330 have the function of providing an axial force on their respective clutches 100, 200 sliding in the housing 181 of the actuating system 300. The first actuating part 180 extends by Cylindrical centering center 182 in a rearward axial direction, as defined. The cylindrical centering surface 182 is configured to center the torque transmission module 1 on a vehicle transmission, in this embodiment on a gearbox case 2. Indeed, as shown in FIG. actuating member 180 comprises a clearance defined by a first radially extending first clearance face 181A and a second axial extending clearance face 181B in order to avoid contact between the first actuating part 180 and the casing of the gearbox 2 and, consequently, to allow optimal positioning of the first actuating part 180 and therefore of the torque transmission module 1 relative to said casing 2. Thus, the cylindrical centering bearing 182 defines a short centering at the of the distal axial end of said cylindrical centering surface 182 with respect to a centering zone 2 "'of the transmission case 2. The center trage court is delimited by the clearance.

The first actuating part 180 is connected to a clutch support by means of an oblique-contact bearing type support bearing.

In this embodiment, the casing 181 of the actuating system 300 of the first actuating part 180 comprises a shoulder 183 forming a first stop 183. As illustrated, the shoulder 183 is made of material with the casing 181. of the actuating system 300. This shoulder 183 is formed by a protruding portion of the first actuating part 180 extending radially in a direction perpendicular to the axis O. This projecting portion is circular in shape around the O axis. As illustrated, the shoulder 183 is configured to be disposed in the chamber 3.

Alternatively, the first stop 183 is attached to the housing 181 of the actuating system 300 and secured by welding, for example.

The holding device 500 is also formed in part by the support of an annular portion 191 of the second closure member 190 against a support surface 181 ', shown in FIG. 2 or 3, of the housing 181 of the system. for actuating 300 of the first actuating member 180. In this case, it will be understood that the second closure member 190 is disposed on the first actuating member 180 without radial displacement at its radially inner end forming the annular portion. 191.

A stop ring 184 is arranged housed, possibly clamped, in a groove of the housing 181 of the actuating system 300. The stop ring 184 thus forms a second axial stop 184 of the first actuating part 180. second stop 184 is disposed outside the chamber 3, as described above. The second closure piece 190 is disposed by a radially inner edge 192 between the first stop 183 and the second stop 184, as defined.

In a first step, it will be noted that when the torque transmission module 1 is not assembled on the transmission case 2 of the transmission of the vehicle, an elastic washer 501 exerts an axial force on the second closure part 190 sufficient to hold the second closure member 190 against the first actuating member 180, in particular holding a radially inner edge 192 of the second closure member 190 against the second stop 184 of the first actuating member 180.

In a second step, it will be noted that the spring washer 501 can be deformed axially so as to allow axial displacement 502 between the second closure member 190 and the first actuating part 180, an axial clearance is provided between the second piece of closure 190 and the first actuating part 180, in particular between the radially inner edge 192 of the second closure part 190 and the second stop 184 of the first actuating part 180.

Thus, as shown in FIG. 1, the spring washer 501 is disposed between the first stop 183 and the second closure piece 190. More particularly, the elastic washer 501 is disposed in the chamber 3 between the first stop 183 and the edge radially. Inside 192 of the second closure part 190. During the assembly of the module 1 on the gearbox case 2, the axial end of the cylindrical centering surface 182 bears against the second sealing device 7. The spring washer 501 bears axially on the first stop 183 so as to maintain the second closure part 190 by its radially inner edge 192 in a mounting position of the torque transmission module 1 on the gearbox case 2, such as illustrated. The axial displacement 502, as defined above, is then created.

As mentioned above, the second closure part 190 and the first actuating part 180 are arranged relative to each other without radial displacement. In this case, the holding device 500 only allows a degree of freedom corresponding to an axial movement of the second closure member 190 with respect to the first actuating part 180 and corresponding to the axial displacement 502. In the figure 1, there is shown the axial displacement 502 of the axial play that can be provided by the deformation of the spring washer 501 in the mounting position of the torque transmission module 1 on the gearbox case 2. In particular, the position of the radially inner edge 192 of the second closure member 190 with respect to the second stop 184 of the first actuating member 180 is intended to represent the axial displacement 502, as defined.

In this first embodiment, an elastic washer 501 has been described, partly forming the holding device 500 and ensuring that the second closure piece 190 is held in the mounting position, as previously described. However, the invention is not limited to such a spring washer 501.

As mentioned later, the first sealing device 6 is disposed between the first peripheral edge 123 of the second closure piece 190 and the transmission case 2. More specifically, the first sealing device 6 is configured to be arranged between a radial bearing zone 123 'of the first peripheral edge 123 of the second closure piece 190 and a radial docking zone 2' of the gearbox case 2. It will be specified that when the torque transmission module 1 is assembled on the transmission of the vehicle, the first sealing device 6 and the second sealing device 7 are dimensionally configured to ensure their crushing respectively between the first peripheral edge 123 of the second closure member 190, the axial end of the cylindrical centering surface 182 of the first actuating part 180 and the transmission case 2, of so as to ensure a zero axial value chain between the torque transmission module 1 and the gearbox case 2. The hyperstatic mounting of the module 1 on the gearbox case 2 is thus avoided.

Alternatively, the first stop 183, as defined, is disposed outside the chamber 3 while the second stop 184, as defined, is disposed inside the chamber 3. In this case, the washer elastic 501 bears on the second stop 184 to maintain the radially inner edge 192 of the second closure member 190 in the position as shown.

In another variant, according to the configuration of the first mode of configuration, the spring washer 501 is disposed outside the chamber 3 and bears against the second stop 184 to maintain the radially inner edge 192 of the second closure piece 190 in the position, as shown. In this case, the axial displacement 502, as defined in the first embodiment, is formed between the first stop 183 and the radially inner edge 192 of the second closure member 190.

According to a feature of this latter variant, the first stop 183 is disposed outside the chamber 3 while the second stop 184 is disposed inside the chamber 3. In this case, the elastic washer 501 is supported on the first stop 183 to maintain the radially inner edge 192 of the second closure member 190 in the position as shown. The axial displacement 502 is then formed between the second stop 184 and the radially inner edge 192 of the second closure piece 190.

According to a second embodiment of the invention illustrated in Figure 2 and similar to the first embodiment, there is shown the holding device 500 in another configuration ensuring a holding of the second closure part 190 with the first piece of actuation 180.

As illustrated in Figure 2, the housing 181 of the actuating system 300 of the first actuating part 180 comprises a shoulder 183 forming a first stop 183. The shoulder 183 is made of material with the housing 181 of the system in the same way, this shoulder 183 is formed by a projecting portion of the first actuating part 180 extending radially in a direction perpendicular to the axis O. This projecting portion is circular in shape around the axis O. The shoulder 183 is configured to be disposed outside the chamber 3.

Alternatively, the first stop 183 is attached to the housing 181 of the actuating system 300 and secured by welding, for example.

In this second embodiment, the annular portion 191 of the second closure member 190 is of greater diameter than the support surface 181 'of the housing 181 of the actuating system 300 of the first actuating part 180, it will be understood that the support surface 181 'is a circular surface of revolution. In this case, it will be understood that radial displacement 503 is formed between the second closure member 190 and the first actuating member 180, more particularly between the annular portion 191 of the second closure member 190 and the support surface 181. of the housing 181 of the actuating system 300. The radial clearance allows a radial displacement 503 between the second closure member 190 and the first actuating part 180.

A stop ring 184 is arranged tight in a groove of the housing 181 of the actuating system 300. The stop ring 184 is then secured to the housing 181 of the actuating system 300. The stop ring 184 forms and a second stop 184 of the first actuating part 180. This second stop 184 is disposed inside the chamber 3. The second closure part 190 is disposed by the radially inner edge 192 between the second stop 184 and the first stop 183.

An elastic washer 501 exerts a sufficient axial force on the second closure member 190 to maintain the second closure member 190 against the first actuating member 180, a radial plane support P is then formed by the support of the radially inner edge 192 the second closure part 190 against the first stop 183 of the first actuating part 180. The radial plane support P makes it possible to stop the second closure part 190 against the first actuating part 180

The second closure part 190 and the first actuating part 180 are arranged relative to one another with the radial displacement 503. A degree of freedom corresponds to at least one radial movement in a direction perpendicular to the axis O of the second closing piece 190 with respect to the first actuating part 180 and authorized by the radial displacement 503. In FIG. 2, the authorized radial displacement 503 is shown between the second closure piece 190 and the first piece actuator 180 in the mounting position of the torque transmission module 1 on the transmission case 2. In particular, the position of the annular portion 191 of the second closure member 190 with respect to the support surface 181 of the housing 181 of the actuating system 300 of the first actuating part 180 is intended to represent the radial displacement 503.

It will be understood that in a mounting phase of the torque transmission module 1 on the transmission case 2, the flange 12 of the torque transmission module 1, particularly the second closure member 190 of the flange 12 can be handled axially and or radially so as to position the torque transmission module 1 on the transmission case 2 in order to ensure the attachment of said module 1 to said casing 2 by the screws 116 for fixing the module 1.

In this second embodiment, an elastic washer 501 has been described, partly forming the holding device 500 and ensuring that the second closure piece 190 is held against the first actuating part 180 made using the support radial plane P defined in this embodiment. However, the invention is not limited to such a spring washer 501. It could in particular, perform the bearing function of the spring washer 501 by a bending member allowing axial deformation relative to the axis O.

Unlike the first embodiment, in this second embodiment, the first sealing device 6 is disposed between the first peripheral edge 123 of the second closure part 190 and the transmission case 2. More precisely, the first sealing device 6 is configured to be disposed between a cylindrical axial bearing surface 123 "of the second closure part 190 and a circumferential axial docking zone 2" of the gearbox case 2. It has also been described previously, the second sealing device 7 configured to be disposed between the first actuating part 180 and the transmission casing 2, more particularly between the cylindrical centering surface 182 of the first actuating part 180 and the transmission casing. 2. It will be specified that in this configuration, when the transmission module is assembled on the transmission of the v vehicle, only the second sealing device 7 is configured in size to ensure its crushing between the cylindrical centering surface 182 of the first actuating part 180 and the gearbox housing 2. It will be understood that, in this mode of realization the first sealing device 6 can be dimensioned independently of the second sealing device 7. Advantageously, the first sealing device 6 is an O-ring. As illustrated in FIG. 2, the first peripheral edge 123 of the second closure piece 190 is in direct abutment against the gearbox case 2, that is to say without intermediate sealing device, so that the radial bearing zone 123 'of the first peripheral edge 123 abuts against the radial docking zone 2' of the gearbox case 2. This configuration has the effect of ensuring a radial plane support P of the second piece of closing 190 against the first actuating part 180. More particularly, the radial plane support P is formed between the radially inner edge 192 of the second closure member 190 and the first stop 183 of the first actuating part 180. note, that in this embodiment the first sealing device 6 is configured to prevent a flow of hydraulic fluid outwardly from a space between the second part closing 190 and the transmission case 2.

As a variant of this second embodiment, the first stop 183 is disposed inside the chamber 3 while the second stop 184 is disposed outside the chamber 3. In this case, the elastic washer 501 is supported on the first stop 183 to maintain the radially inner edge 192 of the second closure member 190 against the second stop 184.

In another variant of this embodiment, the elastic washer 501 is disposed outside the chamber 3 and bears against the first stop 183 to maintain the radially inner edge 192 of the second closure member 190 against the first stop 183.

According to a feature of this latter variant, the first stop 183 is disposed inside the chamber 3 while the second stop 184 is disposed outside the chamber 3. In this case, the elastic washer 501 is supported on the second stop 184 to maintain the radially inner edge 192 of the second closure piece 190 against the second stop 184.

According to a third embodiment of the invention similar to the first embodiment and illustrated in Figure 3, there is shown the holding device 500 in a different configuration ensuring a fixed holding of the second closure member 190 against the first piece actuator 180.

As illustrated in Figure 3, the housing 181 of the actuating system 300 of the first actuating member 180 comprises a shoulder 185 forming a stop. The shoulder 185 is made of material with the housing 181 of the actuating system 300. Similarly, this shoulder 185 is formed by a projecting portion of the first actuating part 180 extending radially in a direction perpendicular to O tax. This protruding portion is circular in shape around the O axis. The shoulder 185 is configured to be disposed inside the chamber 3.

As shown in FIG. 3, the shoulder 185 is of radial dimension sufficient to ensure a stable plane support of the second closure member 190 against the latter, more particularly, a stable plane support of the radially inner edge 192 of the second closure piece. 190 against the latter.

Alternatively, the stop is reported on the housing 181 of the actuating system 300 and secured by welding, for example.

In this third embodiment, the annular portion 191 of the second closure member 190 is supported by its annular portion 191 against the support surface 18Γ of the housing 181 of the actuating system 300 of the first actuating part 180. In this case, it will be understood that the second closure member 190 is disposed on the first actuating member 180 without radial displacement. It will thus be understood that a radial plane support P is formed. As illustrated, the radial plane support P is formed by the support of the second closure piece 190 against the stop, seen from outside the chamber 3.

First internal fixing holes 186 are formed on the abutment. Advantageously, the first internal fixing holes 186 are regularly distributed around the axis O on the circular contour of the abutment. Second internal fixing holes 193 are formed on the radially inner edge 192 of the second closure member 190. Preferably, the second internal fixing holes 193 are regularly distributed about the axis O on the radially inner edge 192 of the second closure piece 190. The first internal fixing holes 186 and the second internal mounting holes 193 are arranged so as to be respectively facing each other when the second closure piece 190 is angularly arranged around the first actuating member 180. In an angular position of the second closure member 190 with respect to the first actuating member 180, internal fixing screws 187 may be inserted into both the first internal fixing holes 186 and the second internal fixing holes 193. These internal fastening screws 187 have the function of keeping fixed the first actuating part 180 and the second closure part 190. As illustrated, these internal fixing screws 187 are inserted in the first internal fixing holes 186 and second internal fixing holes 193 from the outside of the chamber 3.

The first internal fixing holes 186, the second internal mounting holes 193 and the inner fastening screws 187 together form an inner fastener.

The second closure part 190 and the first actuating part 180 are arranged relative to each other without radial displacement and without axial displacement.

In this case, the holding device 500 does not allow any degree of freedom. The second closure piece 190 is then immobile with respect to the first actuating part 180. It will be noted that the stop is recessed axially with respect to the first bearing face 181A forming the clearance of the cylindrical centering bearing surface 182, so as to allow the radial plane support P of the second closure member 190 against the stop and so as to accommodate the inner fastening screws 187 while allowing movement between the inner fastener screw heads 187 and the box cover speeds 2.

In the same way as mentioned in the first embodiment, the first sealing device 6 is disposed between the first peripheral edge 123 of the second closure piece 190 and the transmission case 2. More precisely, the first sealing device 6 is configured to be disposed between the radial bearing zone 123 'of the first peripheral edge 123 of the second closure piece 190 and the radial docking zone 2' of the transmission case 2, such as described in the second embodiment. Similarly to the first embodiment, it will be specified that in this configuration, when the transmission module is assembled on the transmission of the vehicle, the first sealing device 6 and the second sealing device 7 are configured in size to ensure their respective crushing between the first peripheral edge 123, the cylindrical centering surface 182 of the first actuating part 180 and the transmission case 2. It will be understood that, in this third embodiment, the first sealing device 6 and the second sealing device 7 are dimensioned axially with respect to each other so as to ensure a zero dimension chain between the torque transmission module 1 and the transmission case 2. Advantageously, the first 6 sealing device is a flat gasket. As illustrated in FIG. 3, the first peripheral edge 123 of the second closure piece 190 is supported by means of the first sealing device 6 against the gearbox case 2. It will be noted that in a manner similar to the first In one embodiment, the first sealing device 6 is configured to prevent outward hydraulic fluid flow from a space between the second closure member 190 and the transmission case 2.

According to this third embodiment, the holding device 500 does not allow any radial displacement and no axial displacement. However, this configuration is intended to particularly allow the realization of the flange 12 in two parts, namely the first actuating part 180 and the second closure part 190, according to different manufacturing processes. In addition, the internal fixing screws 187 make it possible to maintain the second closure piece 190 fixed against the first actuating part 180 and to move bending points that can be created in a junction zone between the second part 190 and the first actuating part 180 when the flange 12 is made in one piece. With a flange 12 in two parts assembled by the inner fixing screws, these bending points are then moved to said screws. Preferably, the second closure member 190 is made of sheet metal and has an axial and radial flexibility.

During the assembly step of the torque transmission module 1, the fastening screws 116 of the module 1 exert a first axial force so as to maintain, in particular, the second closure piece 190 by its first peripheral edge 123 against the gearbox housing 2. It will be noted that when the torque transmission module 1 is assembled on the transmission case 2 by the fastening screws 116 of the module 1, the first sealing device 6 and the second device 7 are crushed between the first peripheral edge 123 of the second closure member 190, the cylindrical centering surface 182 and the transmission case 2.

As a variant of this third embodiment, the internal fixing screws 187 are inserted axially into the first internal fixing holes 186 and the second internal fixing holes 193 from the chamber 3.

As a variant of this third embodiment, the abutment is disposed outside the chamber 3. In this case, the radial plane support P of the radially inner edge 192 of the second closure part 190 against the abutment is realized from room 3.

According to a feature of this latter variant, the internal fixing screws 187 are inserted in the first and second internal fixing holes 186, 193 from the chamber 3.

Advantageously, an angular positioning device 600 separate from the indexing device 13 and internal fixing screws 187 makes it possible to perform an angular positioning of the second closure part 190 by supplying the first actuating part 180.

Advantageously, the angular positioning device 600 can be used in polarization.

Advantageously, the angular positioning device 600 comprises an angular positioning pin formed on the second closure piece 190 and configured to be in correspondence with an angular positioning hole formed on the first actuating part 180.

Advantageously, the annular portion 191 of the second closure piece 190 is of non-circular shape and configured to cooperate with a shape corresponding to the support surface 18Γ of the housing 181 of the actuating system 300 of the first actuating part 180 .

Advantageously, the non-circular shape of the second closure piece 190 and the shape corresponding to the support surface 181 'of the casing 181 of the actuating system 300 of the first actuating part 180 form a locking device in rotation of the first actuating part with respect to the second closure part 190.

Of course, the invention is not limited to the examples that have just been described and many adjustments can be made to these examples without departing from the scope of the invention. In particular, the various features, shapes, variants and embodiments of the invention can be associated with each other in various combinations to the extent that they are not incompatible or exclusive of each other. In particular all the variants and embodiments described above are combinable with each other.

Claims (15)

A torque transmission module (1) for equipping a motor vehicle transmission, said module (1) comprising: a double clutch mechanism (10) being arranged to rotate about an axis (O), a flange (12) and a cover (11) delimiting between them a chamber (3) housing the double clutch mechanism (10), the flange (12) and the cover (11) respectively comprising a first peripheral edge (123) and a second peripheral edge (113) intended to be applied against each other, the first and second peripheral edges (123, 113) each comprising at least one hole (115, 125) for fixing the axially aligned module (1) participating fixing said module (1) to said transmission, the flange (12) comprising at least a first actuating part (180) and a second closure part (190) which are distinct from one another and which delimit together the chamber (3), the first piece of power nt (180) and the second closure part (190) being connected to one another by at least one holding device (500), characterized in that the holding device (500) allows axial displacement (502 and a radial displacement (503) of the second closure member (190) relative to the first actuating member (180). Torque transmission module (1) according to claim 1, wherein the first actuating part (180) forms part of an actuating system (300) of the two clutches (100, 200) and in that the first actuating part (180) is a housing (181) of the actuating system (300), the latter comprising at least one actuator (320, 330) arranged to slide in the housing (181) of the actuating system ( 300) and exert a force on at least one of the clutches (100, 200). A torque transmitting module (1) according to any one of the preceding claims, wherein the first actuating member (180) comprises a cylindrical centering surface (182) configured to center the torque transmission module (1). ) on a vehicle transmission. The torque transmitting module (1) according to any one of the preceding claims, wherein the second closure member (190) comprises the first peripheral edge (123). A torque transmission module (1) according to any one of the preceding claims, wherein the first peripheral edge (123) is configured to secure said module (1) to said transmission, said first peripheral edge (123) is shifted axially on the front portion of the torque transmission module (1). Torque transmission module (1) according to any one of the preceding claims, wherein the holding device (500) makes it possible to carry out at least one plane support (P) of the second closure piece (190) against the first actuating part (180), and in that the plane support (P) is formed in part by a radially inner edge (192) of the second closure part (190) bearing against a stop (185) of the first actuating part (180). 7. Transmission module according to claim 6, wherein the radially inner edge (192) of the second closure member (190) bears against the stop (185), said first stop (185), the first piece of actuation (180) and against a second stop (184) secured to the first actuating part (180). A torque transmitting module (1) according to any one of the preceding claims, wherein the second closure member (190) comprises at least one cylindrical axial bearing (123 "), the cylindrical axial bearing (123") being arranged to bear against a circumferential axial docking zone (2 ") of the transmission, the cylindrical axial bearing (123") being of a shape corresponding to the circumferential axial docking zone (2 "). A torque transmission module (1) according to any one of claims 1 to 7, wherein a first sealing device (6) is configured to be disposed between a radial bearing zone (123 ') of the second closing piece (190) and a radial docking area (2 ') of the transmission, the radial bearing area (123') being of shape in correspondence of the radial docking area (2 '). 10. Torque transmission module (1) according to claim 7, wherein the stop (185), said first stop (185), is formed by a shoulder of the first actuating part (180) and the second stop ( 184) is formed by a stop ring disposed on the first actuating member (180). 11. Torque transmission module (1) according to claim 7, wherein the stop (185), said first stop (185), is formed by a stop ring disposed on the first actuating part (180) and the second stop (184) is formed by a shoulder of the first actuating part (180). 12. Torque transmission module (1) according to any one of the preceding claims taken in combination with any one of claims 6 or 7, wherein the second closure member (190) is prestressed under load by a spring washer (501) and in that the spring washer (501) comes to press the radially inner edge (192) against the stop (185). The torque transmission module (1) according to claim 8, wherein a first sealing device (6) is configured to be disposed between the cylindrical axial bearing (123 ") of the second closure member (190) and a circumferential axial docking zone (2 ") of the transmission, the cylindrical axial bearing (123") being of a shape corresponding to the circumferential axial docking zone (2 "). 14. Torque transmission module (1) according to any one of the preceding claims, wherein a locking device ensures a rotational locking of the first actuating part (180) of the flange (12) relative to the second part. closing (190) the flange (12). A torque transmitting module (1) according to any one of the preceding claims, wherein the flange (12), the clutches (100, 200) and the cover (11) form a preassembled subassembly.