FR3005902A1 - PRE-ASSEMBLED MODULE FOR A TRANSMISSION ASSEMBLY FOR A HYBRID VEHICLE AND METHOD FOR MOUNTING A TRANSMISSION ASSEMBLY - Google Patents

Abstract

The invention relates to a pre-assembled module for a transmission assembly for a motor vehicle intended to be arranged between an engine block and a gearbox comprising: - a support element (16) provided with fastening elements to the engine block and / or the gearbox; - a clutch abutment, mounted on said support member (16) for actuating a clutch (1), motor side; an intermediate shaft movable in rotation, comprising a splined end intended to cooperate with a hub of a friction disk of said clutch (1), on the motor side, said intermediate shaft cooperating with the support element via a bearing supporting and guiding in rotation the intermediate shaft relative to the support member (16); - An electric machine comprising an outer stator supported by the support member and a rotor have a central opening through which the intermediate shaft passes, said rotor being mounted to rotate with said intermediate shaft; and a reaction plate of a clutch (2), on the gearbox side, integral in rotation with said intermediate shaft.

Description

The invention relates to the field of transmissions for a motor vehicle. It relates in particular to a pre-assembled module for a transmission assembly intended to be disposed between an internal combustion engine and a gearbox of a motor vehicle. It relates in particular to a transmission assembly for a hybrid-type automobile vehicle in which an electric machine is arranged in the transmission chain between the engine and the gearbox. BACKGROUND ART Transmission assemblies for a hybrid motor vehicle, comprising two clutches and an electric machine, are arranged between the internal combustion engine of the vehicle and its gearbox. Such an assembly is, for example, described in document FR 2 830 589. Each of the clutches comprises a friction disk, a clutch abutment, a reaction plate and a clutch mechanism, comprising a mobile mounted pressure plate. axially with respect to said reaction plate between an engaged position in which the friction disk is clamped between said pressure and reaction plates and a disengaged position. Both clutches are arranged on both sides of the electric machine. The mechanism of a first clutch, arranged on the engine side, is configured to be associated with the crankshaft of the internal combustion engine. The friction disc of the first clutch is rotatably mounted to an intermediate shaft which is attached to a rotor support hub of the electric machine. The mechanism and the reaction plate of the second clutch, disposed on the gearbox side, are mounted integral in rotation with said rotor support hub and the friction disc of said second clutch is intended to cooperate with an input shaft of a gearbox. gearbox. The clutch, on the engine side, thus makes it possible to couple in rotation the crankshaft of the combustion engine to the rotor of the electric machine and the clutch, on the gearbox side, makes it possible to couple the rotor to the input shaft. of the gearbox. Thus, one can cut the internal combustion engine at each stop and restart it through the electric machine. The electric machine can also constitute an electric brake or bring a surplus of energy to the combustion engine to assist or prevent it from stalling. When the engine is running, the electric machine acts as an alternator. The assembly of such a transmission assembly is complex in particular in that the assembly of the elements of the transmission assembly requires numerous operations taking place on the assembly lines of the gearbox with the engine block. . SUMMARY An idea underlying the invention is to facilitate the assembly of a transmission assembly 10 associating two clutches and an electric machine. To do this, according to one embodiment, the invention proposes a pre-assembled module for a transmission assembly for a motor vehicle intended to be disposed between an engine block and a gearbox, comprising: a support element provided with fasteners to the engine block and / or the gearbox; a clutch abutment mounted on said support member for actuating a clutch on the engine side; an intermediate shaft movable in rotation, comprising a splined end intended to cooperate with a hub of a friction disc of said clutch, on the motor side, said intermediate shaft cooperating with the support element via a bearing bearing and guiding in rotation the intermediate shaft relative to the support member; an electric machine having an outer stator supported by the support member and a rotor have a central opening through which the intermediate shaft passes, said rotor being rotatably mounted to said intermediate shaft; and a reaction plate of a clutch, on the gearbox side, integral in rotation with said intermediate shaft. Thus, the assembly of the transmission assembly is facilitated because a portion of the elements of the transmission assembly is provided as a pre-mounted module manipulable and transportable. According to embodiments, such a pre-assembled module may comprise one or more of the following features: the intermediate shaft cooperates with the support element via a bearing, the support element comprising a bore cylindrical housing of said limited bearing, motor side, by a radial axial bearing bearing surface and the intermediate shaft having, on the gearbox side, a shoulder defining a radial axial bearing bearing surface. - The bearing comprises an outer ring coupled axially to the support member and an inner ring coupled axially to the intermediate shaft. - The inner ring is coupled axially to the intermediate shaft by press fitting and / or by locking members - the outer ring is coupled axially to the support member by press fitting and / or by locking members. the rotor is mounted to rotate with the intermediate shaft by means of a sheet metal support hub, said hub comprising an axial rotor support skirt and an annular radial sail carrying the clutch reaction plate; , gearbox side. - The intermediate shaft comprises a flange and the rotor support hub has an inner flange, extending radially inwardly of the axial skirt, fixed to said flange of the intermediate shaft. the module comprises a clutch, on the gearbox side, said clutch comprising, in addition to the reaction plate integral in rotation with the intermediate shaft, a friction disc comprising a splined hub intended to cooperate with complementary splines of a gear shaft; an inlet of the gearbox and a pressure plate, integral in rotation with the reaction plate, and mounted axially movable with respect to said reaction plate between an engaged position in which the friction disc is clamped between said pressure plates and reaction and a disengaged position. - The support member is provided with through holes for the passage of fasteners. - The stator is fixed by shrinking or clamping force on the support member. According to one embodiment, the invention also relates to a method for mounting a transmission assembly for a motor vehicle between an engine block and a gearbox, said method comprising: a step of mounting a clutch, engine, on the engine block; a step of assembling a pre-assembled module mentioned above; a mounting step of the module pre-mounted on the gearbox housing or on the engine block; and a step of assembling the gearbox and the engine block, the gearbox and the engine block being fixed to each other via the pre-assembled module. Such a method is particularly simple to implement because a large part of the elements of the transmission assembly is delivered on the assembly lines of the transmission and the engine block in the form of a pre-assembled module. In addition, such a method can be implemented on assembly lines by requiring only very few modifications of the assembly process. According to embodiments, such a method may comprise one or more of the following characteristics: the support element is provided with through-fixing holes for the passage of fixing screws, the pre-mounted module being mounted on the housing of the gearbox before the assembly of the gearbox and the engine block, the assembly step of the pre-mounted module on the gearbox housing including the introduction of screws into a first group of orifices of the gearbox; attachment to secure the pre-mounted module on the gearbox housing and the step of assembling the gearbox and the engine block comprising inserting screws into a second group of mounting holes for fixing the pre-mounted module on the engine block. the support element is provided with through-fixing holes for the passage of fixing screws and the pre-mounted module is mounted on the engine block before the assembly of the gearbox and the engine block, the step for mounting the pre-mounted module on the gearbox casing comprising inserting screws into a first group of fixing holes in order to fix the pre-assembled module on the engine block and the assembly step of the gearbox and the engine block comprising the introduction of screws into a second group of fixing holes for fixing the module pre-mounted on the gearbox housing the support element is provided with through fixing holes for the passage of fasteners and wherein the fasteners are studs having two threaded ends.

BRIEF DESCRIPTION OF THE DRAWINGS The invention will be better understood, and other objects, details, features and advantages thereof will become more clearly apparent from the following description of several particular embodiments of the invention, given solely for the purposes of the invention. illustrative and not limiting, with reference to the accompanying drawings. - Figure 1 is a view, in axial section, of a transmission assembly having two clutches and an electric machine and intended to be disposed between an internal combustion engine and a gearbox. FIG. 2 is a view, in axial section, of a hydraulically-controlled clutch abutment for actuating the clutch, on the engine side. - Figure 3 is a partial view, in perspective, on the motor side, a stator support member of an electric machine having a housing for receiving a clutch abutment. - Figure 4 is a perspective view of a clutch abutment. FIG. 5 is a view, in axial section, of the housing of the stator support element of FIG. 3. FIGS. 6 to 8 are views, in axial section, showing the successive stages of mounting of the stop in Figure 9 is a perspective view showing the locking tabs in a radially inwardly bent position in which the protuberances are in the released position. and extend out of their respective locking recesses. - Figure 10 is a sectional view of a clutch abutment and a stator support member according to another embodiment. FIG. 11 is a perspective view illustrating a clutch attached to the engine block and a pre-assembled module capable of forming a transmission assembly according to FIG. 1. FIG. 12 is a perspective view, on the engine side of the engine, transmission assembly of FIG. 1. - FIGS. 13, 14 and 15 are views, in axial section, of a transmission assembly comprising two clutches and an electric machine according to a second, a third and a fourth embodiments. . - Figure 16 is a partial view, in axial section, of a transmission assembly comprising two clutches and an electric machine and equipped with a dust flange disposed between the electric machine and the clutch, gearbox side. FIG. 17 is an exploded perspective view of the stator and the dust flange of the electrical machine of FIG. 16. FIG. 18 is a perspective view of the stator and flange of FIG. 17 when assembled. . - Figure 19 is a perspective view illustrating a stator of an electric machine according to one embodiment. FIG. 20 is a perspective view of one of the coils of FIG. 19. FIG. 21 is a partial front view of a rotor of an electric machine according to one embodiment. Detailed description of embodiments. In the description and the claims, the terms "external", "internal", "forward", "back" and the "axial" and "radial" orientations will be used to denote, according to the definitions given in the description, elements of the transmission assembly. By convention, the "radial" orientation is directed orthogonally to the X axis of rotation of the set determining the "axial" orientation. The "circumferential" or "tangential" orientation is directed orthogonal to the X axis of the assembly and orthogonal to the radial direction.

The terms "external" and "internal" are used to define the relative position of one element relative to another in the radial direction, with reference to the X axis, an element close to the axis is thus qualified as internal as opposed to an outer member located radially periphery. The terms "forward" and "backward" are used to define the relative position of one element relative to another in the axial direction, a member close to the engine being referred to before as opposed to an element close to the designated rear speeds. Referring to FIG. 1, there is shown a transmission assembly, intended to be disposed between a combustion engine and a gearbox, which comprises a clutch 1, on the engine side, a clutch 2, on the gearbox side, and an electric machine 3 comprising a stator 8 and a rotor 9. The clutch 1, on the motor side, makes it possible to couple or uncouple in rotation the crankshaft of the combustion engine, not shown, to the rotor 9 of the electric machine 2. The clutch 2, on the gearbox side, makes it possible to couple or uncouple in rotation the rotor 9 of the electric machine 3 to an input shaft of the gearbox, not shown. The assembly is therefore able to transmit a torque between the crankshaft of the engine and the input shaft of the gearbox. The electric machine 3 is a reversible rotary electric machine of the alternator-starter type or of the motor-generator type. In starter mode, the clutch 1, motor side, is engaged and the electric machine 3 allows the start of the engine. In alternator mode, the electric machine 3 can recharge a battery of the vehicle and / or power organs or equipment consuming energy when the engine is running. It is further configured to recover energy when braking the vehicle. The electric machine 3 can in particular be configured to stop the engine, for example, at a red light or in the caps, and then restart it (Stop and Go function in English). In one embodiment, it is capable of providing a surplus of power to prevent the motor stalls 30 (boost function in English). Furthermore, the electric machine 3 is able to drive the vehicle at least a short distance, the clutch 1, motor side, then disengaged and the engine stopped.

The clutch 1, on the engine side, comprises a reaction plate 32 carried by a flywheel intended to be mounted on the crankshaft, a friction disc 33 and a clutch mechanism comprising a cover 4 fixed on the reaction plate 32, a pressure plate 5 and a diaphragm 6. The friction disk 33 comprises a splined hub cooperating with splines formed on an intermediate shaft 7. The pressure plate 5 is connected in rotation to the lid 4 by tangential tongues, not illustrated, axial-action elastics allowing axial movement of the pressure plate 5 with respect to the reaction plate 32.

Thus, the pressure plate 5 is movable, relative to the reaction plate 32, between an engaged position in which the friction disc is clamped between said pressure and reaction plates 5 and a disengaged position. In the engaged position, the clutch 1 is engaged and the torque is transmitted from the crankshaft to the intermediate shaft 7 via the first clutch 1. The diaphragm 6 is in contact, on the one hand, at its inner periphery, with an abutment. clutch 100 and, secondly, with a boss of the pressure plate 5. The diaphragm 6 urges the pressure plate 5 towards the reaction plate 32. To disengage the clutch 1, the clutch stop 100 moves axially the inner periphery of the diaphragm forwards so as to tilt the diaphragm 6. Thus, the load exerted by the diaphragm 6 on the pressure plate 5 decreases so that the pressure plate 5 is biased backwards. under the action of elastic tangential tongues. The clutch 2, on the gearbox side, comprises a reaction plate 10, integral in rotation with the intermediate shaft 7, a friction disc 11 and a clutch mechanism comprising a cover 12, fixed on the reaction plate 10 , a pressure plate 13, axially movable relative to the reaction plate 10 between an engaged position and a disengaged position, and a diaphragm 14. The clutch 2, gearbox side, is also equipped with elastic tangential tongues connecting the plate pressure 13 in rotation to the lid 12.

The friction disc 11 is equipped with a splined hub intended to cooperate with splines formed at the end of the input shaft of the gearbox, not shown. A clutch abutment 15 makes it possible to tilt the diaphragm 14 in order to disengage the clutch 2.

In order to ensure a heat dissipation of the calories generated locally by friction of the friction linings of the clutch discs 3, 11 on the pressure plates 5, 13 and reaction plates 32, 10 of the clutches 1, 2, said pressure plates 5 , 13 and reaction 32, 10 are typically made of cast iron. The reversible rotary electric machine 3 comprises an outer stator 8 and an inner rotor 9. The outer stator 8 of the electric machine surrounds the inner rotor 9. An annular gap gap 300 extends between the inner periphery of the stator 8 and the external periphery of the rotor 9. The rotor 9 has a central opening allowing passage of the intermediate shaft 7. The stator 8 is carried by a support member 16 which is, on the one hand, intended to be fixed on the engine block and, secondly, intended to be fixed on the casing 17 of the gearbox. The support member 16 is inserted between the transmission case and the engine block and is arranged to allow attachment of the gearbox to the engine block. In other words, the support member forms, in a way, a spacer between the engine block and the casing 17 of the gearbox. The support member 16 has an outer peripheral wall 18 whose inner surface is of cylindrical shape in order to cooperate with the outer periphery of the stator 8. The mounting of the stator 8 in the support member 16 can be made by hooping or by clamping by force. The support member 16 also has an internal web 19, extending forwardly of the stator 8 and the rotor 9 and forming a partition wall between the clutch 1, on the motor side, on the one hand and the electric machine 3, on the other hand. The distance between the internal web 19 and the rotor 9 is optimized so as to avoid induced power losses resulting in power reductions of the electric machine.

The support element 16 also defines a housing 201 extending inside the rotor 9 and within which extends, at least partially, the clutch stop 100 of the clutch 1, motor side. Such an arrangement makes it possible to optimize the axial space requirement of the assembly. The housing 201 is defined by an axial skirt 205 and a bottom 212 of radial orientation. The bottom 212 is provided with a bore 202 allowing the passage of the intermediate shaft 7.

Furthermore, an axial flange 211 extends from the bottom 212 of the housing, towards the rear, and forms with the rear face of the bottom 212 of the housing 201, a cylindrical bore housing a bearing 20. In other words , the bottom 212 of the housing 201 limits, on the engine side, the cylindrical housing bore of the bearing 20 and defines a radial bearing surface before the bearing 20.

The bearing 20 cooperates, moreover, with the intermediate shaft 7, with the aid of a shoulder which defines a rear bearing surface of the bearing 20. The bearing 20 thus allows the centering of the intermediate shaft 7 with respect to In one embodiment, not shown, the forward end of the intermediate shaft 7 mounts in the crankshaft of the engine via a pilot bearing mounted in a cavity of the crankshaft nose. The bearing 20 comprises an outer ring, an inner ring and rolling bodies extending between said outer and inner rings. The outer ring is coupled axially to the support member 16 while the inner ring is coupled axially to the intermediate shaft 7. Thus, the bearing is axially fixed relative to the support member 16, on the one hand , and to the intermediate shaft 7, on the other hand. In addition, such a mounting of the bearing 20 makes it possible to hold the intermediate shaft 7 axially with respect to the support element 16. In order to axially couple the inner and outer rings, they can be force-fitted or glued together. . Alternatively, it is also possible to use one or more locking members, such as elastic rods or circlips, not shown. To do this, the intermediate shaft 7 is equipped with a fixing groove extending in front of the bearing 20. During a fixing operation of the bearing 20, a locking member such as a rod or a circlip is arranged, by elastic deformation, in a fixing position, in said fixing groove, so as to limit the axial displacement of the bearing 20, forwards.

In the same way, the support member 16 may have a fixing groove extending at the rear of the bearing 20 and adapted to receive a locking member. The locking member is arranged by elastic deformation in the fixing groove of the support member 16 and limits the axial displacement of the bearing 20 rearwardly. In an intermediate embodiment, one of the outer and inner rings is force-fitted or glued while the other ring is held axially by a locking member housed in a groove. The support member 16 is, for example, metallic. It may in particular be of moldable material, for example being made of aluminum or an aluminum-based alloy. It is preferably in non-magnetic material. In one embodiment, the support member 16 has a cooling circuit 21 for cooling the stator 9. For this, it is possible to produce, by sand molding, an annular shape in the outer peripheral wall 18. This circuit The cooling circuit 21 has an inlet and an outlet for circulating a coolant. Alternatively, as illustrated in Figures 13, 14 and 15, it is also possible to obtain such a cooling circuit by means of a reported tube. The rotor 9 is supported by a hub 22. The hub 22 comprises an axial skirt 26 for supporting the rotor 9. The axial skirt 26 has, on its outer surface, a radial shoulder 27 defining a bearing surface of the rotor 9. The rotor 9 comprises a pack of sheets. It is mounted by shrinking on the outer surface of the axial skirt 26. Thus, the sheet metal pack is mounted by fitting onto the outer surface of the axial skirt 26 until it contacts the radial shoulder 27. In another In one embodiment, the rotor 9 can be force-fitted onto the outer surface of the axial skirt 26. The hub 22 further includes an annular radial web 28 extending aft of the stator 8 and the rotor 9 and carrying the reaction plate 10 of the clutch 2, gearbox side. The reaction plate 10 is fixed to the annular radial web 28 outside the annular zone of friction of the reaction plate 10, intended to cooperate with the friction linings of the friction disc 11 in the engaged position. The reaction plate 10 is here fixed on the annular radial web 28, in an outer peripheral zone, extending radially beyond the friction zone. The reaction plate 10 is fixed at an axial distance from the electric machine 3. A space is thus provided between the reaction plate 10 and the electric machine 3. The axial skirt 26 has an axial portion 29 extending between the shoulder radial support 27 of the rotor and the annular radial web 28 so as to define a gap between the annular web 28 and the rotor 9. In other words, the connection area of the annular web 28 to the axial skirt 26 is shifted 10 axially with respect to the rotor 9 so as to avoid magnetic leakage. The annular web 28 has a cambered portion 30 extending between two annular planar portions. This arched portion 30 notably makes it possible to confer on the annular web 28 a flexibility allowing the rotor 9 to be decoupled in flexion from the reaction plate 10. The hub 22 for supporting the rotor 8 is fixed to the intermediate shaft 7. To do this, the rear end of the intermediate shaft 7 comprises a collar 23 bearing axially against an internal flange 25 formed in the hub 22 and extending radially inwardly of the axial skirt 26. Rivets 24 allow to fastening the collar 23 of the intermediate shaft 7 and the inner flange 25 of the hub 22. Thus, the rotor 9 is centered with respect to the support element 16 and therefore with respect to the stator 8 via the bearing 20. The hub 22 is made of sheet steel or iron. The realization of said hub 22 made of sheet metal makes it possible, on the one hand, to facilitate the shrinking of the rotor 9 on the hub 22 and, on the other hand, to limit the conduction of the calories produced by friction by the clutch 2 towards the rotor 9. In order to limit the conduction of the calories generated by the friction of the clutch 2, it is also possible to provide an additional layer of low thermal conductivity material disposed at the interface between the annular radial web 28 and the reaction plate. The additional layer may be a plastic layer, based on polyphenylene sulfide or polyamide 6-6, for example, or a sheet of "DMD" type paper made of a polyester film and a non-woven coating. impregnated fabric covering each of the faces of the polyester film. With reference to FIGS. 2 to 10, a clutch abutment 100 for actuating the clutch 1 on the engine side, as well as its assembly inside the housing 201, will now be described in detail. the support member 16. The clutch abutment 100 is a fluid-controlled abutment. This fluid may be a hydraulic fluid or a pneumatic fluid. The control fluid 10 is usually oil. In one embodiment, the stop may also be an electrically operated stop. The abutment 100 is concentric with the axis X and traversed by the intermediate shaft 7. The stop 100 comprises two parts in piston cylinder relation, that is to say a fixed part 160, delimiting a blind annular cavity of axial orientation, and a piston 162 mounted axially movable relative to the fixed portion 160. The piston 162 enters the cavity to define therewith a working chamber 161 of variable volume. The cavity communicates through a channel with a connection arrival to a fluid supply pipe connected to a master cylinder. The master cylinder is actuated by an electric motor actuator or a pressure / volume generator controlled according to predetermined programs by a computer. The working chamber 161 is therefore allowed to be pressurized or depressurized. In the embodiment shown, the fixed part 160 of the abutment 100 comprises a guide tube 167 and an outer body 101 surrounding the guide tube 167. The guide tube 167, for example a metal tube, defines the annular cavity in FIG. which the piston 162 is movable and thus guides the piston 162. The guide tube 167 is assembled to the body 101. The guide tube 167 is traversed by the intermediate shaft 7. Alternatively, the fixed portion 160 may be in a single piece of molding material, plastic for example, the body 101 then defining the annular cavity in which the piston is movable 162.

The clutch abutment 100 is here of the self-centering type. It comprises a ball bearing 163 with a rotating ring 164 profiled for a point contact with the inner ends of the fingers 165 of the diaphragm 6 and a non-rotating ring 166 coupled axially to the piston 162. For more details on the self-centering of the stop see for example document FR-A2619880. A sealing bellows 169 extends between the body 101 and the non-rotating ring 166. In a variant, the stop is of pulled type, the stop 100 then acting by pulling on the fingers of the diaphragm. In one embodiment, the clutch abutment 100 is provided with a position sensor for controlling the position of the piston 162 relative to the body 101. The position sensor may be a sensor integrated in the piston or installed in the control actuator of the clutch abutment 100. With reference to FIGS. 3 to 5, we will describe the housing 201 of the support member 16, intended to receive at least partially the clutch abutment 100, of clutch 1, motor side. As mentioned above, the housing 201 is defined by a bottom 212 and an axial skirt 205. The bottom 212 is pierced by a bore 202 allowing the passage of the intermediate shaft 7. The axis of the bore 202 is coaxial with the X axis of rotation of the set. The axial skirt 205 comprises a recess 203 to allow the passage of a connection piece 103 to a control fluid supply pipe of the abutment 100. Moreover, the internal veil 19 of the support element 16 comprises a recess 204 for the passage of the fluid supply pipe of the clutch abutment 100. The recess 204 dedicated to the passage of the control pipe 25 is slightly oversized relative to the diameter of the supply pipe. To facilitate the establishment of the clutch abutment 100, the axial skirt 205 includes guide grooves 206 for cooperating with elastic locking tabs 106, described below. The guide grooves 206 are parallel to a generatrix of the axial skirt 205.

In one embodiment, the guide grooves 206 also serve as keys to allow only one angular position of mounting of the clutch stop 100 in the housing 201. Thus, the guide grooves 206 can position angularly the clutch abutment 100 relative to the housing 201 so as to position the connection piece 103 of the clutch abutment 100 vis-à-vis its respective recess 203. To achieve this result, the angular distribution of the grooves 206 is irregular. In other words, there are at least two different angular distances between two adjacent grooves 206.

To facilitate the insertion of the elastic locking lugs 106 into the housing 201, the front end of the longitudinal edges of the grooves 206 may comprise chamfers making it possible to make up a positioning difference of a few degrees during the insertion of the elastic locking tabs. 106 in the grooves 206. Similarly, the grooves 206 has a greater width and / or depth at their front end than at their rear end to facilitate the insertion of the locking tabs 106. In such an arrangement, the variations of the slope of the longitudinal edges or the radially outer edge may be linear or non-linear. The axial skirt 205 also has cavities 207 to accommodate a protrusion 107 carried by a resilient tab 106 locking. The cavities 207 extend here in the bottom of the guide grooves 206. In order to maintain the clutch abutment 100 angularly and to avoid any rotation of the clutch abutment 100 relative to the housing 201 due to the drag torque of the bearing. stop, the housing 201 is provided near its bottom 25 tangential stops 208 for cooperating with the elastic tabs 106 locking. In the embodiment, the abutment surfaces of the tangential abutments 208 bordering each groove are parallel in pairs and symmetrical with respect to a median plane passing through the axis X. At the entrance of the axial skirt, the formed ridge Between the axial skirt 205 and the inner veil 19 is broken by a fillet 210. In another embodiment, the ridge is broken by a chamfer. These arrangements make it easier to insert the clutch stop 100 inside the housing 202.

Finally, the bottom 212 of the housing 201 comprises a bearing face 209 allowing axial support of the clutch abutment 100. FIG. 4 is a perspective view of an exemplary embodiment of a clutch abutment 100 illustrating means for fixing the clutch abutment 100 in the housing 201. The body 101 or housing is provided with resilient tabs 106 for locking. An elastic tab 106 includes a proximal body-connecting end 101 and a free distal end. The resilient tab 106 is L-shaped and includes a radially-oriented portion 108 extending from its proximal end and an axially-oriented portion 110. The proximal body-connecting end 101 is located proximate to the body. of the rear end of the body 101 and the axially oriented portion 110 extends forward, that is to say in a direction opposite to the bottom 212 of the housing 201. The elastic tab 106 is provided with a protrusion 107 adapted to cooperate with a respective locking cavity 207. The protuberance 107 extends radially outwardly from the axially oriented portion 110. The resilient tab 106 thus formed has a radial bending capacity around the junction between the radially oriented portion 108 and the Axial orientation portion 110. This radial flexibility of the resilient tab 106 allows the protrusion 107 to move radially. Thus, during assembly of the clutch abutment 100 on the support member 16, the elastic tab 106 deforms radially inwardly by contacting the protrusion 107 with the axial skirt 205 and is then biased towards the outside, towards a locking position, when the protrusion 107 is housed in its respective cavity 207. Note that the body 101 is advantageously made of a material adapted to give the elastic tabs 106 a sufficient capacity for elastic deformation. For example, the body 101 may in particular be made of plastic, such as polyamide 6-6 optionally supplemented with fillers. Furthermore, the resilient tabs 106 are arranged to allow an operator to unlock the attachment of the clutch stop 100 to extract it from its housing 201, during a maintenance operation for example. To do this, the protrusion 107 extends in a medial portion of the elastic tab 106. Thus, a radially inward support on the free distal end of the elastic tab 106 moves the protrusion 107 of its locked position, in Which it extends inside the locking cavity 207, to a released position in which it extends radially out of the cavity 207. In other words, the distal portion of the elastic tab 106 which extends beyond the protrusion 107 constitutes an unlocking tab 105 allowing an operator to act on the radial movement of the tab 106. Thus, this operator can easily unlock the clutch stop 100 to be able to 201. In the embodiment shown, the protrusion 107 has a tooth shape. The rear face 117 is inclined to facilitate the insertion of the clutch abutment 100 into the housing 202. The inclination with respect to the X axis is preferably less than 45 °. The front face 127, on the side of the distal end, also has an inclination whose function will be detailed in Figure 9. The inclination of the front face 127 relative to the axis X is preferably greater than 45 °. Finally, the body 101 includes a connection piece 103 for connection to a control fluid supply of the clutch stop 100. In this embodiment, the control is carried out using a pneumatic fluid. or hydraulic conveyed by a pipe, here a flexible or rigid supply pipe 104. The body 101 includes a shoulder 109 for axially supporting the clutch abutment 100 against the bottom 212 of the housing 201. The body 101 also includes a cylindrical reduction 102 cooperating with the bore 202 formed in the bottom 212 of the housing 212. The reduction serves to position the clutch abutment 100 on the support element 16. To ensure this centering, this cylindrical reduction 102 is coaxial with the reference axis X. FIGS. 6 to 8 represent the three steps of mounting the clutch stop 100.

In a first step, the clutch abutment 100 is presented facing the housing 201, respecting the keying performed by the elastic tabs 106 and the grooves 206. When the protrusion 107 comes into contact with the support member 16, the leave 210, at the entrance of the housing 202, bears on the front face 117 5 of the protuberance. The inclination of the front face 117 of the protrusion 107 combined with the shape of the fillet 210 allows the elastic lug 106 to be progressively deformed so as to fold down the distal end towards the central axis of the abutment 100 and to favor the insertion of this abutment. this. The shape of the inlet of the housing as well as the inclination of the front face 117 of the protuberance 107 thus contribute to facilitating insertion without the need for operator pressure on the elastic tabs 106. In a second step, the clutch stop 100 is pushed along the reference axis X to the bottom of the housing 201 so that the cylindrical reduction 102 enters the bore 202, then the shoulder 109 bears on the face of the housing. 209. To facilitate the insertion of the cylindrical reduction 102 into the bore 202, the cylindrical reduction and the bore 202 comprise complementary tapered chamfers. During this insertion phase, the lug 106 remains in the radially bent position, under the force exerted by the bottom of the groove 206 of the axial skirt 205. During the last step, when the clutch stop 100 has reached 20 its mounted position, abutting against the bottom 212 of the housing, the protrusion 107 is vis-à-vis the cavity 207. The tab 106, thanks to its elasticity, finds its rest form and the protrusion 107 enters the cavity 207 ensuring an axial immobilization of the clutch abutment 100. In other words, the locking lug 106 serves to clutch the clutch abutment 100 in the housing 201 of the support member 16. In this position, the radial orientation portion 108 bears against the tangential abutment 208 to angularly maintain the clutch abutment 100. The tangential stop 208 makes it possible to prevent the angular retention from taking place between the protuberance 107 and its cavity 207 because , considering u positioning of the protrusion 107, a tangential force exerted at the protuberance would generate a lever arm effect and, therefore, a twist at the base of the resilient tabs 106 to break them.

In the mounted position, the distal end of the elastic tabs 106 protrudes axially from the axial skirt 205. Such an arrangement facilitates the unlocking operations. As a variant, the elastic tab 106 is shorter and does not protrude outside the housing 201. This arrangement is notably achieved in the event of a problem of space. For disassembling the clutch abutment 100, with reference to FIG. 9, it is necessary to exert a radial force 199 on the distal tongue end 105 of the elastic tabs 106 from the outside of the abutment 100 towards its central axis. so as to move the protuberances 107 to their released position in which they extend outside their cavity 207. The front face 127 of the protrusion 107 has an inclination which facilitates the unlocking when a radial force 199 is exerted. Once the stop is no longer immobilized in its housing 201 by the protuberances 107, it is sufficient to extract it by pulling it forwardly of the axial skirt 205. FIG. 10 represents another embodiment of the function centering and support of the body 101 relative to the housing 201. In FIG. 9, the elements identical to those of FIGS. 3 to 9 bear the same reference number. The modified analog elements have the same reference number increased by 40. In this embodiment, the bottom 212 of the housing 201 comprises a shoulder forming a centering bore 255 and a radial bearing surface 249 of the axial body 141 of the abutment 100. The outer casing 142 of the body 141 of the clutch abutment 140 is cylindrical to ensure the centering function with the bore 255 present at the bottom 212 of the housing 201. As for the previous embodiment, the envelope 142 cylindrical and the bore 255 are coaxial with the X axis of the assembly. To ensure the axial stop, the body 141 comprises at its rear end, a bearing surface 149 which abuts on the bottom of the bore 249. FIGS. 11 and 12 illustrate the method of mounting a set of transmission.

The clutch 1, on the engine side, is fixed on the engine block 34. To do this, the flywheel carrying the reaction plate 32 is fixed on the crankshaft of the combustion engine via screws and then the mechanism and the disc of the engine. friction 33 of the clutch 1, motor side, are mounted on the flywheel. Alternatively, it is also possible to pre-mounted a module comprising a flywheel, a clutch mechanism and a friction disc 33 and to mount said module on the crankshaft of the combustion engine. Furthermore, a module comprising at least one support member 16, the clutch stop 100 for actuating the clutch 1, the motor side, the intermediate shaft 7, an electric machine 3 and the reaction plate of the clutch 2, gearbox side, is pre-assembled. The pre-assembly of such a module facilitates assembly of the assembly during assembly of the transmission with the engine block. In the embodiment shown, the pre-mounted module further comprises the mechanism, that is to say the lid 12, the pressure plate 13, and the diaphragm 14, as well as the friction disk 11 of the clutch 2, 15 speed gearbox side. This pre-assembled module is manipulable and easily transportable, the elements of said module being fixed axially and centered relative to each other, in particular by means of the bearing 20. The support element 16 has through-fixing orifices 35. said support member 16 from side to side. These fastening orifices 35 open in relation to orifices 36 formed in the casing 17 of the gearbox and in relation to orifices, not shown, formed on the engine block or on a spacer connection to the engine block. Thus, fastening screws, not shown, are inserted through said orifices 35, 36 so as to secure the gearbox, the pre-assembled module and the engine block. In one embodiment, the pre-mounted module is pre-positioned on the engine block, by means of pins or centering sleeves, for example, and then the housing 17 of the gearbox is attached against the support element. 16 and the screws are inserted through the orifices 36 of the housing, the orifices 35 of the support member 16 and orifices of the engine block in order to secure the assembly.

In an alternative embodiment, it is also possible to pre-position the pre-mounted module on the casing 17 of the gearbox and then report the gearbox and the pre-mounted module on the engine block. In another embodiment, a first group of fixing holes 35 may be used for the passage of screws intended to fix the pre-mounted module on the gearbox while a second group of fixing orifices 35 may be used for the passage of screws for attaching the pre-mounted module to the engine block 34. In one embodiment, it is also possible to use studs having two threaded ends to allow mounting of the module pre-mounted on the casing 17 of the gearbox via the first end of said studs and on the engine block 34 via the second end of said studs. As shown in FIGS. 13, 14 and 15, the friction discs 11, 33 are advantageously equipped with torsion dampers 37. Typically, such a torsion damper 37 comprises two guide washers integral in rotation with a disc of support of the friction linings and forming the input element of the damper. The guide washers are arranged on either side of a web forming the output element of the damper. Elastic members with circumferential action, such as helical springs, are mounted in accommodating windows, facing each other, in the guide washers and in the web. The ends of the coil springs bear against the radial edges of the housing windows so that said helical springs are able to transmit a torque between the guide washers and the web. The friction discs 11, 33 may also be equipped with a pre-damper 38 for filtering vibrations generated by the combustion engine acyclisms at the idling speed. Such pre-dampers, in particular shown in FIGS. 14 and 15, have small coil springs with lower stiffness than the springs of a main damper.

In the embodiment shown in FIG. 13, the reaction plate 32 of the clutch 1, on the engine side, constitutes the secondary mass 39 of a double damping flywheel. The double damping flywheel has a primary flywheel 38 and a secondary flywheel 39, coaxial, rotatable relative to each other in favor of a bearing such as a ball bearing. The primary flywheel 38 is intended to be fixed on the crankshaft of the heat engine, for example by means of screws. The primary flywheel 38 and the secondary flywheel 39 are coupled in rotation by means of damping means. The damping means are typically helical springs 40 circumferentially disposed in an annular chamber formed in the primary flywheel 38 and filled with a lubricating agent. The coil springs 40 are supported at their ends on bosses of the side walls of the annular chamber and on radial tabs of an annular web 41 fixed by rivets to the secondary flywheel 39. In addition, FIG. 13 illustrates a range of clutch 42 rotatable to move the stopper of the clutch 2, gearbox side. In the embodiment of FIG. 14, the reaction plate 32 of the clutch 1, on the engine side, is fixed to a flexible annular plate 43 which is intended to be fastened to the crankshaft of the engine, via screws for example . A Belleville washer acts between the reaction plate 2 and the flexible plate 43. Such a flywheel is commonly referred to as a flexible flywheel and serves to dampen the excitations in the axial direction of the crankshaft. In the embodiment of Figure 15, the reaction plate 32 of the clutch 1, motor side is carried by a rigid flywheel intended to be fixed on the crankshaft of the engine. Note that in the embodiments of Figures 1 and 15, the flywheel has, on its outer periphery a ring gear 44 for cooperating by meshing with the pinion of a starter. Such a starter may be used, in a manner complementary to the electric machine 3, to start the thermal combustion engine, in particular in very cold weather, as described in the document FR 2 797 472, to which reference will be made for more information. subject.

As mentioned above, the reaction plate 10 is axially distant from the elements of the electric machine 3, creating an axial space between the reaction plate 10 and the electric machine 3. With reference to FIGS. 16 and 17, a flange will now be described. 301 anti-dust for protecting the electric machine dust particles, especially from the clutch 2 and likely to enter through the aforementioned axial space. These particles are in particular generated during the friction of the friction linings of the friction disk 11 between the reaction plates 10 and pressure plates 13. This flange 301 is intended to prevent dust from accessing the gap gap space 300 between the rotor 9 and the stator 8. In fact, if such particles penetrated into the gap gap space 300, they could damage the rotor 9 and the stator 8 by abrasion by acting as abrasive grains between the stator 8, fixed part and rotor 9, moving part. To avoid this, the flange 301 is disposed in the space between the electric machine 3 and the reaction plate 10 and more particularly between the reaction plate 10, on one side, and the rotor assembly 9 and stator 8, the other. The flange 301 has the form of a washer whose outer periphery and the inner periphery are defined by two concentric circles. The flange 301 is fixed on the stator 8. Its inner periphery extends radially inwardly beyond the annular gap gap 300 so as to cover it. The flange 301 comprises a radially oriented cheek and two lips 302 and 303 which extend axially towards the reaction plate 10. The lips 302 and 303 obstruct the passage of dust in the space between the electric machine 3 and the 10. Advantageously, the axial distance between the end of the lips 302, 303 and the reaction plate 10 or the radial annular web 28 supporting the reaction plate 10, when the annular radial web 28 is disposed between the reaction plate 10 and the electric machine 3 is limited to a functional clearance, typically less than 5 mm. As shown in FIG. 16, the axial distance between the annular radial web 28 and the electric machine 3 is not constant. The distance or axial distance between the annular radial web 28 and the stator 8 is greater than the gap between the annular radial web 28 and the rotor 9. The inner lip 302 is disposed at the rotor 9 in the smallest interval, while the outer lip 303 is positioned in the largest gap at the stator 8. The axial dimension of this outer lip 303 is larger than the dimension of the smallest gap. According to this arrangement, the inner and outer lips 302 and 303 are on either side of the gap gap space 300 and form baffles further obstructing the passage of dust in the space between the reaction plate 10 and the electric machine 3. The flange 301 also comprises a deflector 304 disposed at the outer periphery of the cheek 305 and forming a frustoconical flange, flared outwards, in the direction of the clutch 2. This deflector makes it possible to confine the dust generated by the clutch 2, on the gearbox side, between the gearbox and the electric machine 3. With reference to FIGS. 17 and 18, the attachment of the flange 301 to the electric machine 3 and more precisely to a workpiece will now be described. In this case, the stator 8 is equipped with pins 306 projecting axially from its lateral part, on the gearbox side. The pins 306 are configured to cooperate with holes 307 opening, formed on the flange 301. During the assembly step, the holes 307 and the pins 306 are used to position the flange 301 relative to the stator 8. Thus, the flange 301 is coaxial with the electric machine 3. In one embodiment, the pins 8 are carried by the body of an interconnector, which will be described later, for connecting the coils of the stator 8. 25 The pins 306 are regularly distributed along the gap annular space 300. After the insertion of the flange 301 on the pins 306 of the stator 8, the studs 306 overflow the flange 301 through the holes 307. The attachment is, for example, obtained by an assembly by ultrasonic welding of the pins 306 so as to obtain, at the end 308 of the pins, a head whose dimensions are larger than the diameter of the hole 307. Thus, the flange 301 is maintained, blocked, of non demontab the stator 8. To allow this method of assembly, the pins 306 are made of a hot melt material, such as a thermoplastic. By way of example, the pins may in particular be polyamide 6-6. In one embodiment, the flange 301 is made of a non-magnetic material. For example, the flange 301 may in particular be made of plastic. Such a flange makes it possible to limit magnetic leakage to the reaction plate 10 or to the annular radial web 28 supporting the reaction plate 10 when the annular radial web 28 is disposed between the reaction plate 10 and the electric machine 3.

In another embodiment, the flange 301 constitutes a magnetic shielding screen between the electric machine 3 and the clutch 2, on the gearbox side, able to concentrate the lines of the magnetic field and limit the leakage field. To do this, the flange 301 may in particular be made of a plastic material associated with non-magnetic metal charges such as aluminum particles. Such a flange advantageously has a magnetic susceptibility of less than 1.10-3. FIG. 19 illustrates the stator 8 of an electric machine 3 capable of equipping the transmission assembly. The stator belongs here to a polyphase rotating electric machine. The winding of the stator 8 is equipped with several concentric coils 45, here preformed, and a neutral point, said neutral of the machine, visible for example in Figure 1 of EP 0 831 580. This stator is compact and efficient from point of view of the power of the electric machine. The coils 45 are interconnected with each other using a compact interconnector 46 comprising a plurality of frames, one of which, said neutral frame is connected to the neutral of the rotating electrical machine. This stator 8 comprises an annular body of axis coinciding with the axis X. This body has teeth 47 regularly distributed on the inner periphery and notches 48 open inwards, two notches 48 consecutive being separated by a tooth 47. These teeth 47 are parallel edges in pairs, a strip of material, corresponding to the yoke 53 existing between the bottom of the notches 48 and the outer periphery of the body 49. The body 49 is formed by a stack of annular sheets made of ferromagnetic material, coaxial with the X axis. The sheet package is maintained by means of rivets (not shown) passing axially through the stack of sheets. This stack reduces eddy currents. The stator 8 has an interconnector 46 with U, V and W connection terminals for interconnection with a power connector. As can be seen in FIG. 20, preformed coils 45 forming the winding of the stator 8 are mounted on the teeth 47 of the stator. These coils 45 are made from a wire wound on several turns. The wires consist of an electrically conductive wire, for example a copper and / or aluminum wire, coated with an electrical insulator, such as enamel. The son may be of circular, rectangular or flat-shaped section. The ends 51, 52 of each coil 50 protrude axially from the coil on the same side of the stator 8, corresponding to the rear face of the stator 8. Each coil 45 has a first end 51 called "input" intended to be connected with the others. 15 inputs alternately to belong to one of the phases, each having a respective terminal U, V, W, of the machine and a second end 52 called "output" intended to be connected to the neutral of the electric machine. To do this, the coils 45 are interconnected with each other by means of the interconnector 46. The interconnector 46 comprises in this embodiment four annular-shaped frames extending in a radial plane. The frames are electrically conductive by being for example copper or advantageously another weldable metal material. These frames are stacked axially on each other and electrically isolated from each other. Each frame has on its inner periphery apparent tabs projecting radially inwards from the frame for welding the ends 51, 52 of the stator coils. Preferably, the frames are embedded in a body made of electrically insulating material, such as plastics material. Each phase frame comprises on its outer periphery a connection terminal U, V, W, for interconnection with a power connector (not shown) itself connected to an inverter described for example in the document EP 0 831 580. In a variant, the inverter is controlled by signals as in document FR 2 745 444.

The electric machine 3 is a synchronous machine. A rotor 9 with permanent magnets for equipping the electric machine is illustrated in FIG. 21. The rotor comprises a body formed of a bundle of sheets 54 stacked in the axial direction. The permanent magnets 55 are implanted radially in the laminations 54 of the laminations 54 at the outer periphery of the rotor 9. The permanent magnets 55 open into the gap 300. In this case, it is referred to as an open-pole permanent magnet rotor. Such a rotor makes it possible to obtain a large useful magnetic flux. In one embodiment, the permanent magnets are ferrite magnets. Several permanent magnets can be mounted in the same opening of the sheet package. Although the invention has been described in connection with several particular embodiments, it is quite obvious that it is in no way limited thereto and that it comprises all the technical equivalents of the means described and their combinations if These are within the scope of the invention. The use of the verb "to include", "to understand" or "to include" and its conjugated forms does not exclude the presence of other elements or steps other than those set out in a claim. The use of the undefined article "a" or "an" for an element or a step does not exclude, unless otherwise stated, the presence of a plurality of such elements or steps. In the claims, any reference sign in parentheses can not be interpreted as a limitation of the claim.

Claims (4)

REVENDICATIONS1. Pre-assembled module for a transmission assembly for a motor vehicle intended to be arranged between an engine block and a gearbox comprising: a support element (16) provided with fastening elements to the engine block and / or the gearbox ; a clutch abutment (100) mounted on said support member (16) for actuating a clutch (1) on the engine side; An intermediate shaft (7) movable in rotation, comprising a splined end designed to cooperate with a hub of a friction disk (33) of said clutch (1), on the motor side, said intermediate shaft (7) cooperating with the support member (16) via a bearing (20) supporting and rotating the intermediate shaft (7) relative to the support member (16); An electric machine (3) comprising an external stator (8) supported by the support element (16) and a rotor (9) have a central opening through which the intermediate shaft (7) passes, said rotor (9) being rotatably mounted to said intermediate shaft (7); and a reaction plate (10) of a clutch (2), on the gearbox side, 20 integral in rotation with said intermediate shaft (7). 2. Pre-assembled module according to claim 1, wherein the intermediate shaft (7) cooperates with the support member (16) via a bearing (20), the support member (16). comprising a cylindrical housing bore of said bearing (20) limited, on the motor side, by a radial axial bearing surface 25 of the bearing (20) and the intermediate shaft (7) comprising, on the gearbox side, a shoulder defining a surface radial bearing axial bearing (20). 3. Pre-assembled module according to claim 1, wherein the bearing (20) comprises an outer ring coupled axially to the support member (16) and an inner ring coupled axially to the intermediate shaft (7). 4. Pre-assembled module according to claim 3, wherein the inner ring and the outer ring are coupled axially by press fitting and / or by locking members. . Pre-assembled module according to any one of claims 1 to 4, wherein the rotor (9) is mounted to rotate with the intermediate shaft (7) via a hub (22) of sheet metal support said hub (22) having an axial skirt (26) for supporting the rotor (9) and an annular radial web (28) carrying the reaction plate (10) of the clutch (2) at the gearbox side. Pre-assembled module according to any one of claims 1 to 5, wherein the intermediate shaft (7) comprises a flange (23) and wherein the hub (22) for supporting the rotor (9) comprises a flange. internal wall (25), extending radially inwardly of the axial skirt (26), fixed to said flange (23) of the intermediate shaft (7). 7. Pre-assembled module according to any one of claims 1 to 6, comprising a clutch (2), gearbox side, said clutch comprising, in addition to the reaction plate (10) integral in rotation with the intermediate shaft ( 7), a friction disk (11) having a splined hub for cooperating with complementary splines of an input shaft of the gearbox and a pressure plate (13), integral in rotation with the reaction plate (10), and mounted axially movable with respect to said reaction plate (13) between an engaged position in which the friction disc (11) is clamped between said pressure and reaction plates (13, 10) and a disengaged position. 8. Pre-assembled module according to any one of claims 1 to 7, wherein the support member (16) is provided with orifices (35) passing through for the passage of fasteners. Pre-assembled module according to one of Claims 1 to 8, in which the stator (8) is fastened by shrinking or force-clamping on the supporting element (16). a transmission assembly for a motor vehicle between an engine block and a gearbox, said method comprising: a step of mounting a clutch (1), on the engine side, on the engine block; a step of assembling a pre-assembled module according to any one of claims 1 to 9; a mounting step of the module pre-mounted on the housing (17) of the gearbox or on the engine block (34); a step of assembling the gearbox and the engine block (34), the gearbox and the engine block (34) being fixed to each other via the pre-assembled module. 11. The mounting method according to claim 10, wherein the support member (16) is provided with fixing holes (35) therethrough for the fixing screw passage and wherein the pre-mounted module is mounted on the casing (17) of the gearbox before the assembly of the gearbox and the engine block (34), the mounting step of the pre-mounted module on the housing (17) of the gearbox comprising the introduction of screws into a first group of fixing holes (35) in order to fix the pre-mounted module on the gearbox casing (17) and the step of assembling the gearbox and the gearbox; engine block (34) comprising the introduction of screws into a second group of fixing holes (35) for fixing the pre-mounted module on the engine block (34). 12. The mounting method according to claim 10, wherein the support member (16) is provided with fixing holes (35) therethrough for the fixing screw passage and wherein the pre-mounted module is mounted on the engine block (34) before the assembly of the gearbox and the engine block (34), the step of mounting the module pre-mounted on the housing (17) of the gearbox comprising the introduction of screw in a first group of fixing holes (35) to fix the pre-mounted module on the engine block (34) and the step of assembling the gearbox and the engine block (34) involving the insertion of screws into a second group of fixing holes (35) for fixing the pre-mounted module to the casing (17) of the gearbox 13. The mounting method according to claim 10, wherein the support member (16) is provided with through-holes (35) for the passage of fasteners and in which the members fasteners are studs having two threaded ends.