FR2830590A1 - Hybrid vehicle twin clutch transmission assembly with rotating electrical machine, in which crankshaft extension and gear shaft are in a supporting and centering relationship relative to each other - Google Patents

Abstract

The crankshaft (10) has an extension (35) whose end and that of the main gear shaft (11) are in a supporting and centering (38,48) role relative to each other The transmission assembly includes two clutches (20,60) and an electrical machine (80) fitted between the engine and its gearbox. Each of the clutches has a clutch mechanism (21,61) associated with a friction disk (22,65) and the electric machine. The clutch mechanisms are integral with the machines rotor (81). The friction disk (22) of the first clutch mechanism (21) is integral in rotation with the engine crankshaft (10). The friction disk (65) of the second clutch mechanism (61) rotates with the main gear shaft (11).

Description

<Desc / Clms Page number 1>

 The present invention relates to a transmission assembly comprising two clutches and an electric machine, in particular for a motor vehicle.

 More specifically, it relates to a transmission assembly, in particular for a motor vehicle, comprising two clutches and an electric machine and disposed between the internal combustion engine of the vehicle and its gearbox, each of the clutches comprising a clutch mechanism associated with a friction disk and the electrical machine being constituted by a rotor and a stator, the clutch mechanisms being integral in rotation with the rotor of the electric machine and the friction disc associated with the first clutch mechanism being rotationally secured to one another the crankshaft of the internal combustion engine, while the second friction disc associated with said second clutch mechanism is integral in rotation with the input shaft of the gearbox.

 Such an assembly makes it possible, for example, after disengaging the two clutches, to stop the internal combustion engine and restart it by inertia and / or by operating the electric motor machine, which, when it is driven mechanically by the engine, can run as a generator.

 Such an assembly is for example of the type described in document FR-2 797 230.

 It is an object of the present invention to provide a transmission assembly of the above kind which is simple to make, compact, has few parts and solves the problem of relative alignment of the ends of the crankshaft and the shaft. gearbox entry, problem all the more important as the axial distance engine-gearbox is large.

 According to the invention, a transmission assembly of the above kind is characterized in that the crankshaft is extended in an extension whose end and that of the input shaft of the gearbox are in a supporting relationship and centering with respect to each other.

<Desc / Clms Page number 2>

 Advantageously, the extension of the crankshaft or the input shaft of the gearbox at the end carries a cooperating nose, with the interposition of a bearing, with a housing at the end of the input shaft of the gearbox or the extension of the crankshaft.

 Preferably, the friction disk associated with the first clutch mechanism is integral in rotation with the crankshaft via the extension thereof.

 Advantageously, the extension of the crankshaft carries external grooves which cooperate with internal grooves of a hub provided with a flange that includes the friction disc.

 Advantageously, the rotor of the electric machine is rotatably connected to the first clutch mechanism via a drum.

 Preferably, the drum is integral in rotation with the cover of the first clutch mechanism; the cover is fixed by its inner periphery frontally at the end of the drum; the drum and the lid are in one piece; the drum has a U-shaped annular body whose bottom extends radially generally and the flanges axially, the outer flange being extended axially and radially so that the lid of the mechanism is formed which is assembled peripherally with the reaction plate; ; the columns are crimped in the bottom of the drum; the drum holder has at least one opening for the passage of a crimping tool.

 Advantageously, the bottom of the drum has a redent defining an annular groove, which redent present at least one opening for the passage of a thrust tool.

 According to another embodiment, the drum is integral with the reaction plate of the first clutch; the drum is of C-shaped section and has an axially extending outer cylindrical wing in which is centered a circumferential rim of the reaction plate; the rim is extended along axial studs to which the lid is fixed.

 Advantageously, the reaction plate is common to both clutches.

 Preferably, the drum is carried by a drum-carrier by means of bearings.

<Desc / Clms Page number 3>

 Preferably, a disengagement device being provided for controlling each of the two clutches, at least one of the disengaging devices is of the concentric type.

 Advantageously, the disengaging device provided for controlling the first clutch is of the concentric type and comprises two parts in piston cylinder relationship defining a working chamber of variable volume supplied with hydraulic fluid by a channel dug in the drum holder; preferably, the fixed part of the variable volume chamber is carried by the drum-carrier, the disengaging device extending axially to the right of said drum-carrier; advantageously, the disengaging device and the drum-carrier surround the extension of the crankshaft.

 Preferably, the disengaging device provided for controlling the second clutch is of the concentric type and comprises two parts in cylinder-piston relationship defining a variable volume chamber fed with hydraulic fluid; advantageously, the disengaging device extends axially between the friction disc associated with the second clutch and the gearbox; preferably, the disengaging device and the drum carrier surround the input shaft of the gearbox.

 Advantageously, at least one of the friction discs is of the rigid type.

 Preferably, at least one of the friction discs is of the torsion damper type.

 Advantageously, at least one of the clutch mechanisms comprises a wear compensating device.

 To better understand the object of the invention will now be described, by way of examples, purely illustrative and not restrictive, embodiments shown in the accompanying drawings.

 In these drawings: - Figure 1 is an axial partial sectional view of an assembly according to the invention; - Figure 2 is a view similar to Figure 1 showing a variant; - Figure 3 is an axial partial sectional view showing another variant of an assembly according to the invention; - Figure 4 is a view similar to Figure 3 showing a variant.

<Desc / Clms Page number 4>

 Referring to FIG. 1, it can be seen that a transmission assembly, arranged between an internal combustion engine, which is seen at the end of the crankshaft, and a gearbox, of which the shaft is shown in FIG. input, comprises a first clutch 20, a second clutch 60 and an electric machine 80.

 The first clutch 20 comprises a clutch mechanism 21, said first mechanism, associated with a friction disk 22, and a reaction plate 23.

 The first clutch mechanism 21 comprises a cover 24, a pressure plate 25 and a diaphragm 26.

 The lid 24 is metallic, here in stamped sheet; it has a bottom, holed centrally, generally of transverse orientation, perpendicular to the axis of the assembly, provided at its outer periphery with an annular rim 27 for fixing; the lid 24 thus has the overall shape of a flat plate.

 A clutch comprises clutch means associated with disengaging means; these may be disengagement levers that can act on axially acting helical springs constituting the engaging means; alternatively, the release levers are constituted by fingers belonging to the central portion of a workpiece whose outer periphery is axially elastic, or devoid of axial elasticity and acting on a Belleville washer forming the clutch means.

 Here, the clutch and disengagement means belong to one and the same piece, the diaphragm 26, which comprises a peripheral portion in the form of a Belleville washer extended internally by a central portion divided into radial fingers by blind slots opening internally in a central opening that the diaphragm 26 whose form, in the free state, is frustoconical. The slots open at their outer periphery in enlarged orifices forming the bottom of the slots.

 The fingers of the diaphragm 26 form disengaging levers and thus the declutching means, while the Belleville-shaped washer-shaped peripheral portion of the diaphragm 26 constitutes the engagement means of the clutch, said orifices being implanted at the inner periphery of the clutch. Belleville washer from the diaphragm 26.

<Desc / Clms Page number 5>

 The disengaging means are provided to counteract at will the action of the clutch means under the action of a clutch release bearing 28 belonging to a disengagement device 29 of the concentric type, to reduce the axial size.

 As described in document US Pat. No. 5,141,091, the clutch abutment 28 can belong to a concentric clutch device with cable control, this abutment then being mounted on a part driven in translation and fixed in rotation, said part being in nut screw relationship with a driving piece fixed in translation and mobile in rotation. The driving part carries a pulley on which the control cable is wound. For more details, reference is made to US-A-5 141 091.

 Alternatively, the driving part is controlled by a transverse electric motor.

 Here, the concentric disengaging device 29 is of the hydraulic type and comprises two parts in piston cylinder relation, namely a fixed part 30 delimiting an axially oriented blind annular cavity 31, and a piston 32 mounted axially movable relative to the fixed part.

 This piston 32 carries the release stop 28 and enters the cavity 31 to define therewith a working chamber of variable volume, the cavity 31 communicating via a channel 33, dug in a drum holder 40, the role of which will appear hereinafter, with a pipe connected to a master cylinder actuated by a clutch pedal or an electric motor actuator controlled according to predetermined programs by a computer. The working chamber is therefore allowed to be pressurized or depressurized, the control fluid filling said chamber usually being oil. The fixed part 30 could be in one piece moldable material.

 The fixed part 30 comprises here, for reduction of the radial space, two coaxial parts, namely, an outer body surrounding a metal guide tube longer axially than the outer body. The bottom of the cavity 31 is delimited by a transverse flange belonging to the guide tube assembled to the outer body by means of an intermediate connecting piece. A static seal is provided between the outer body and the guide tube carrying

<Desc / Clms Page number 6>

 its free end a stop to limit the movement of the piston 32 when the disengaging device 29 is not mounted on the drum carrier 40.

 A preloading spring 34 acts between the outer body of moldable material and the clutch release bearing 28 to maintain it in constant abutment on the disengaging means 26.

 The clutch abutment 28 comprises a ball bearing with a profiled rotating ring for point contact with the inner ends of the fingers of the diaphragm 26 and a non-rotating ring coupled axially to the piston 32, which thus carries the abutment 28.

 Here, the outer ring of the bearing is rotating, while the inner ring of the bearing is fixed in rotation and has at its inner periphery a radial flange bearing on a front shoulder of the piston 32, said flange being pressed on said shoulder by a washer. elastic axial action, here in the form of Belleville washer, bearing on the piston. The stop 28 has a flag shape so that the inner ring of the ball bearing is intended to surround the front end of reduced diameter of the outer body to reduce the axial size, knowing that the outer body is intended to be fixed on an inner rim of the drum support 40, directly, with the aid of ears, or indirectly, using a matching sole and a bayonet mount.

 Here, the outer body has attachment lugs and the stop 28 is of the self-centering type because it can move radially in contact with the shoulder of the piston under the control of the spring washer axial action.

 A non-referenced protection bellows is provided for a good sliding of the piston 32.

 In any case, the clutch device 29 is of the concentric type because it is intended to be traversed by an extension 35 of the crankshaft 10. The device 29 thus surrounds the extension 35.

 The clutch mechanism 21 is associated with the friction disc 22.

 The friction disk 22 carries at its outer periphery at least one friction lining intended to be clamped between two plates under the action of the clutch means 26.

 The friction lining is secured to a support coupled here rigidly in rotation to the extension 35.

<Desc / Clms Page number 7>

 This extension 35 therefore passes through the disengaging device 29 and carries the friction disc 22 via external splines which it has and which cooperate with internal splines of a hub provided with a collar 36 whose outer periphery is secured here, by rivets 37, to the inner periphery of the friction disk 22. According to the invention, the end 48 of the extension 35 is shaped as a received nose in a blind bore 38 formed in the end of the input shaft 11 of the gearbox, with the interposition of a bearing.

 Of course, the opposite is possible, that is to say that the nose can be carried by the shaft 11 and the pilot blind bore formed at the end of the extension 35.

 The support of the friction disc 22 may be embedded in the liner. Here, two identical fittings are arranged axially on either side of the axially elastic support, being fixed thereto by gluing; this makes it possible to reduce the axial bulk, the dead thickness of the linings for the riveting operation being eliminated, when, as a variant, the linings are fixed to the support by riveting, the support being shaped at its outer periphery to be axially elastic and gradually crushed. Here, for example, the friction linings can be glued directly into the central zones of the tripod blades described in document FR-A-2693778 to which reference may be made for more details.

 The lining of the friction disc 22 is adapted to be clamped between the pressure plate 25 of the first clutch mechanism 21 and the reaction plate 23.

 The reaction plate 23 is carried peripherally by the cover 24 to which it is attached, by means of screws 41.

 Of course, a flywheel can be added, carried by the crankshaft as shown in Figures 3 and 4.

 When the first clutch 20 is tightened, the assembly connected to the crankshaft, in particular the reaction plate of this clutch, constitutes a steering wheel.

 According to a variant not shown, the friction disc 22 radially carries, beyond the linings, a ring of inertia always thus integral in rotation with the crankshaft 10.

<Desc / Clms Page number 8>

 The cover 24 is fixed by its inner periphery at the end of the drum 39, here frontally by screws 42.

 The pressure plate 25 has an annular projection of axial orientation directed towards the bottom of the cover 24 for contact with the outer periphery of the Belleville washer of the diaphragm 26; this boss is split and molded with the pressure plate 25.

 The inner periphery of the Belleville washer of the diaphragm 26 is pivotably mounted or pivotally mounted between a primary bearing here from the bottom of the cover 24 by stamping and a secondary support constituted by the heads of the columns secured to the cover 24. The columns pass axially through the enlarged openings of the diaphragm 26.

 The pressure plate 25 is rotatably connected to the cover 24 by axially acting tangential tangential tongues 43 permitting axial movement of the pressure plate 25 with respect to the cover 24 itself connected to the reaction plate 23; the tabs 43 are connected to the cover 24 by rivets 44 and radial projecting lugs of the pressure plate 25 also by rivets 45.

 As will have been understood, the tongues 43 exert an elastic return action of the pressure plate 25 in the direction of the bottom of the lid 24 and the pressure plate 25 has a friction face frontally for contact with the concerned lining of the disk. 22 while the reaction plate 23 has a friction face frontally for contact with the friction linings of the disc 22.

 Normally, the clutch is engaged and the engine torque is transmitted from the driving shaft or crankshaft 10 to the friction disc 22 of the first clutch 20. In this position, the Belleville washer of the diaphragm 26, constituting the clutch means of the clutch, is in contact, on the one hand, at its inner periphery with the primary support, and, on the other hand, at its outer periphery with the boss of the pressure plate 25. The diaphragm 26 thus urges the pressure plate In the direction of the plate 23 so that the friction linings of the friction disc 22 are clamped between the pressure and reaction plates 23.

<Desc / Clms Page number 9>

 The reaction plate 23 is thus rotated as well as the cover 21 and the drum 39.

 In this position, the piston 32 of the clutch device 29 is in the retracted position, the upper part of Figure 1, and the cavity 31 is depressurized. When the cavity 31 is pressurized, the piston 32 moves to the right, the lower part of FIG. 1, and thus causes the clutch release stop 28, which then acts by pushing on the fingers of the diaphragm 26, to rotate the diaphragm 26 -this. The diaphragm 26 then leaves its primary support to rely on its secondary support. In this case, the load exerted by the diaphragm 26 on the pressure plate 25 decreases and then vanishes, the pressure plate 25 then following the movement of the diaphragm 26 under the return action of the tongues 43. The friction linings are then released and the clutch disengaged. The motor torque is not transmitted.

 When the cavity 31 is depressurized, the diaphragm 26 returns the piston 32 back and the linings are tightened.

 The drum carrier 40 has a skirt 55 which carries the drum 39 by means of bearings 47.

 The rotor 81 comprises a bundle of plates, made of soft iron, mounted by shrinking on the outer periphery of the drum 39 having at its end a flange 56 forming a stop for the rotor 81. The sheet is then hot-mounted by fitting onto the outer periphery of drum 39 to contact with flange 56.

 It will be noted that, according to this arrangement, the electric machine is on a large radius, which is favorable from the point of view of its efficiency.

 The ring-shaped sheets thus form an axially oriented ring mounted by hooping on the drum 39.

 The sheets can be isolated by oxidation or provided with insulators.

 The stator 82 is formed, similarly to the rotor 81, from a pack of annular sheets of soft iron, reconstituting an axially oriented ring. Notches are made in the sheets for passage of electrical windings 83,84, the rotor 81 and the stator 82 being shown schematically.

<Desc / Clms Page number 10>

 By injecting a controlled electric current into the stator windings, the electrical machine 80 is converted into a starter for the internal combustion engine of the vehicle, the clutch 20 being tightened.

 For this, it is necessary to provide a control device of the electronic type.

The machine is here of the asynchronous electric motor type. Of course, the electric machine may be synchronous electric motor type or other.

 In general, when the engine is running, the machine acts as an alternator. The internal combustion engine can be shut down at each stop and restarted by the machine. The machine can constitute an electric brake and bring a surplus of energy to the internal combustion engine to assist it or to prevent it from stalling; we can also filter the vibrations.

 For more details, see W098 / 105882.

 Alternatively, the rotor 81 is fixed to the outer periphery of the drum 39 by means of splines or by cone-fitting. In all cases, the rotor 81 is integral in rotation as well as axially with the drum 39, the cover 21 and the reaction plate 23.

 Of course, it is possible to fix the rotor 81 on the drum 39 by means of screws bearing on a fixing washer, passing through the bundle of sheets in a manner similar to that described in document DE-C-3 227 810. Elastic elements can also be used.

 The stator 82 is fixed here by shrinking at its outer periphery on a not shown casing such as the bell of the second clutch. Any other form of attachment such as screwing is possible.

 It will be appreciated that the method of fastening by hooping promotes the reduction of the radial size.

 The drum support 40 constitutes the hub of the rotor 81; it surrounds the crankshaft 10 and carries the seal.

 Of course, the clutch 20 may be equipped with a wear compensating device to compensate in particular the wear of the friction liners and maintain the diaphragm in a constant position when the clutch is engaged.

 In FIG. 1, the clutch 20 is of the pushed type because the stop 28 acts by pushing centrally on the diaphragm 26. In a variant, the clutch is

<Desc / Clms Page number 11>

 pulled type. In this case, the stop is coupled to a docking piece acting behind the diaphragm and passing through the central opening of the diaphragm.

 The disengagement operation is performed by pulling, via a docking piece, on the fingers of the diaphragm.

 In this case, the peripheral portion of the Belleville washer of the diaphragm is in contact, at its outer periphery, with a bearing carried by the cover and its inner periphery with the boss of the pressure plate. For more details, reference is made, for example, to document FR-A-2 606 477 also showing a wear-compensating device; As a result, the boss of the pressure plate 25 can be movable relative to the pressure plate 25 to compensate for wear of the friction liners, circumferentially acting springs acting between the pressure plate 25 and the boss, ramps varying the axial distance between the boss and the pressure plate 25.

 The reaction plate 23 is intended to cooperate also with a friction disc associated with the clutch mechanism 61 of the second clutch 60.

 The mechanism 61 comprises a cover 62 secured by its outer periphery to the reaction plate 23.

 A pressure plate 63 is coupled to the cover 62 by tangential tabs 64.

 The reaction plates 23 and pressure 63 are intended to clamp together the lining of a friction disc 65 whose hub 66 is integral with the input shaft 11 of the gearbox through longitudinal grooves.

 Thus, the reaction plate 23 is intended to be disengageably connected to the input shaft 11 of the gearbox.

 Here, circumferentially acting torsion damping means are arranged kinematically between the lining of the friction disc 65 and its hub 66; these torsion damping means comprise circumferentially acting elastic means and axially acting friction means.

 Here, the torsion damping means comprise a main damper and a secondary damper.

<Desc / Clms Page number 12>

 Such an arrangement is well known by itself and will not be described in detail.

 As seen in the figure, the elastic means are coil springs 67,68 extending ciconferentially, and the friction means comprise friction washers.

 For more details on the friction disc 65, see document FR-A-2 792 698.

 As for the first clutch 20, the second clutch 60 is diaphragm 69 and push type; for the operation of this clutch, there is provided a release device 71, similar to the clutch device 29 associated with the first clutch 20; the clutch is shown engaged in the upper right half of the figure and disengaged in the lower right half of the figure.

 Here, the second clutch 60 comprises a wear-compensating device 75 of the type described in document FR-A-2 739 158; thanks to this device also the stroke of the stop of the disengagement device 71 is reduced.

 The machine 80 can be used to synchronize the speed of the shafts 10 and 11 to facilitate shifting. It is in this case that the stop associated with the disengagement device 71 is operated by a receiver whose transmitter is operated by an actuator controlled by a computer receiving information from sensors receiving the speed of the shafts 10 and 11.

 Of course, any type of electrical machine with axial or radial magnetic flux may be suitable. The machine 80 may be of the asynchronous type, in the abovementioned manner, synchronous with a magnet in the air gap or buried, with flux switching with single or hybrid magnets with excitations by stator windings, with brushless claws, with variable reluctance, single or double excitation, cross flow with Vernier effect.

 The electric machine may be of the synchronous type with a ring-brush system.

 FIG. 2 shows an assembly similar to that of FIG. 1 except that here the reaction plate 123 is fixed directly to the drum 139.

<Desc / Clms Page number 13>

 More specifically, the drum 139 has a C-shaped section whose concavity is directed towards the reaction plate 123; it has an outer cylindrical wing 140 extending axially in which is centered a circumferential flange 57 of the reaction plate 123. Locally, the rim 57 is extended along axial pads 58 to which the cover 24 of the mechanism 21 is fixed by screws.

 Axial screws 59 solidarize the reaction plate 123 to the drum 139: they pass axially through the rim 57 and are screwed into the bottom of the drum 139 with a C-shaped section.

 It is on the outer cylindrical surface of the flange 140 of the drum 139 that the rotor 81 of the electric machine 80 is mounted.

 Here, the friction disk associated with the first clutch mechanism 21 is of small diameter and comprises two disks 22 placed on either side of an intermediate plate 73 integral in rotation with the reaction plate 123, while being able to move axially with respect to it, thanks to splines provided at its outer periphery which cooperate with splines formed at the inner periphery of the flange 57.

 As can be seen, the assembly of the mechanism 21 and associated disks 22 is situated axially under the wing 140 of the drum 139, that is to say under the rotating machine 80.

 Alternatively, there is only one friction disc 22.

 It should be noted that the clutch 20 wears little because here it is used only to couple the engine to the transmission, the starting of the vehicle being provided through the second clutch 60.

 Referring to Figure 3, there is shown an assembly according to the invention wherein the cover of the first clutch mechanism 21 is in one piece with the drum 239.

 More specifically, the drum 239 has a U-shaped annular body whose bottom 240 extends radially generally and the wings axially, being directed towards the motor; the outer flange of the U is extended axially and radially towards the gearbox so that the cover of the mechanism is formed, to which the reaction plate 23 is peripherally assembled by screws 141.

<Desc / Clms Page number 14>

 The posts 77 for the articulation of the diaphragm 26 of the first clutch 20 are crimped into the bottom 240 of the drum 239; this crimping operation can be performed after mounting, on the drum-holder 40, bearings 47 and their retaining circlips 78,79 axial, through an axial opening 87 formed in the drum-holder 40, for the passage of a crimping tool, which is arranged on a radius corresponding to that of the columns 77; here, these are used for fixing the tangential tabs 43 which solidarize in rotation, with freedom of relative axial displacement, the pressure plate 25 to the cover of the first mechanism, so the drum 239.

 Here, the extension 135 of the crankshaft 10 is not in one piece with it but reported by screws 86; the collar that it has for its attachment is extended radially so as to constitute a flywheel 100.

 FIG. 4 shows a variant of the assembly according to FIG. 3 in which, after having mounted axially against the circlip 78 the assembly constituted by the drum 239, the rotor 81 and the mechanism 21 of the first clutch 20, it is possible to set up the second circlip 79; to do this, centrally the bottom 240 of the drum 239 internally has a redent 74 defining an annular groove 76 facing the bearings 47; the transverse elasticity of the split type circlip 79 is used to wedge it radially in said groove 76, as visible in the lower left half of the figure; openings, here radial slots 85, for example three slots 120, formed in the groove 74 allow the passage of an axial thrust tool which, implemented, causes the circlip 79 to fall into its positioning groove as visible on the upper left half of the figure.

Claims (27)

Transmission assembly, in particular for a motor vehicle, comprising two clutches (20,60) and an electrical machine (80) arranged between the internal combustion engine of the vehicle and its gearbox, each of the clutches (20,60) comprising a clutch mechanism (21,61) associated with a friction disc (22-122,65-165) and the electrical machine (80) consisting of a rotor (81) and a stator (82), the clutch mechanisms (21, 61) being integral in rotation with the rotor (81) of the electric machine (80) and the friction disk (22-122) associated with the first clutch mechanism (21) being rotationally fast of the crankshaft (10) of the internal combustion engine while the second friction disk (65-165) associated with said second clutch mechanism (61) is rotatably connected to the input shaft (11) of the combustion chamber. characterized in that the crankshaft (10) is extended along an extension (35-135) whose end and that of the input shaft (11) of the gearbox are in a support and centering relationship (38-48) relative to each other.  2. An assembly according to claim 1, characterized in that the extension (35,135) of the crankshaft (10) or the input shaft (11) of the gearbox carries at the end a nose (48) cooperating, with interposition a bearing, with a housing (38) at the end of the input shaft (11) of the gearbox or the extension (35, 135) of the crankshaft.  3. An assembly according to one of claims 1 or 2, characterized in that the friction disk (22-122) associated with the first clutch mechanism (21) is integral in rotation with the crankshaft (10) via the extension (35,135) thereof (10).  4. An assembly according to claim 3, characterized in that the extension (35,135) of the crankshaft (10) carries external grooves which cooperate with internal grooves of a hub provided with a flange (36) that comprises the disc of friction (22-122).  5. An assembly according to one of claims 1 to 4, characterized in that the rotor (81) of the electric machine (80) is integral in rotation with the first mechanism (21) clutch via a drum (39-139-239). <Desc / Clms Page number 16>  6. An assembly according to claim 5, characterized in that the drum (39-239) is integral in rotation with the cover of the first mechanism (21).  7. An assembly according to claim 6, characterized in that the cover (24) is fixed by its inner periphery frontally end of the drum (39).  8. Assembly according to claim 6, characterized in that the drum (239) and the cover are in one piece.  9. An assembly according to claim 8, characterized in that the drum (239) has an annular body with a U-shaped section whose bottom (240) extends radially generally and the wings axially, the outer flange being extended axially and radially so that is formed the cover of the mechanism which is assembled peripherally reaction plate (23).  10. An assembly according to claim 9, characterized in that the columns (77) are crimped into the bottom (240) of the drum (239).  11. The assembly of claim 10, characterized in that the drum holder (40) has at least one opening (87) for the passage of a crimping tool.  12. Assembly according to one of claims 9 to 11, characterized in that the bottom (240) of the drum (239) has a redent (74) defining an annular groove (76), which redent (74) has at least an opening (85) for the passage of a pushing tool.  13. An assembly according to claim 5, characterized in that the drum (139) is integral with the reaction plate (123) of the first clutch (20).  14. An assembly according to claim 13, characterized in that the drum (139) is of C-shaped section and has an outer cylindrical wing (140) extending axially in which is centered a circumferential edge (57) of the tray of reaction.  15. The assembly of claim 14, characterized in that the flange (57) is extended along axial pads (58) to which the cover (24) is fixed. <Desc / Clms Page number 17>  16. An assembly according to one of claims 1 to 15, characterized in that the reaction plate (23,123) is common to both clutches (20,60).  17. An assembly according to one of claims 5 to 16, characterized in that the drum (39-139-239) is carried by a drum holder (40) by means of bearings (47).  18. Assembly according to one of claims 1 to 17, characterized in that a disengagement device (29,71) being provided to control each of the two clutches (20, 60), at least one of the declutching (29,71) is of the concentric type.  19. An assembly according to claims 17 and 18 taken together, characterized in that the disengaging device (29) provided for controlling the first clutch (20) is of the concentric type and comprises two parts in piston cylinder relationship defining a chamber of variable volume work fed with hydraulic fluid by a channel (33) dug in the drum holder (40).  20. An assembly according to claim 19, characterized in that the fixed part of the variable volume chamber is carried by the drum holder (40), the disengaging device (29) extending axially to the right of said portetambour (40). ).  21. An assembly according to claim 20, characterized in that the disengaging device (29) and the drum holder (40) surround the extension (35,135) of the crankshaft (10).  22. An assembly according to one of claims 18 to 21, characterized in that the disengaging device (71) provided for controlling the second clutch (60) is of the concentric type and comprises two parts in cylinder-piston relationship defining a variable volume chamber fed with hydraulic fluid.  23. An assembly according to claim 22, characterized in that the disengaging device (71) extends axially between the friction disk (65- 165) associated with the second clutch (60) and the gearbox.  24. An assembly according to one of claims 22 or 23, characterized in that the disengaging device (71) surrounds the input shaft (11) of the gearbox. <Desc / Clms Page number 18>  25. Assembly according to one of claims 1 to 24, characterized in that at least one of the friction discs (22,165) is of the rigid type.  26. An assembly according to one of claims 1 to 24, characterized in that at least one of the friction discs (65,122) is of the torsion damper type.  27. An assembly according to one of claims 1 to 26, characterized in that at least one of the clutch mechanisms (61) comprises a wear compensating device (75).