DE10307064A1 - Improved power transmission arrangement for a motor vehicle, with an electric machine arranged therein - Google Patents

Abstract

The invention relates to a power transmission arrangement for a motor vehicle, comprising DOLLAR A - a coupling for connecting a rotary drive member (24) driven by an internal combustion engine to a rotary drive member (26) for coupling to a transmission, said drive member (24) and this output member (26 ) about axes which run essentially parallel to an axial direction (X), DOLLAR A - a module (42) which comprises a carrier (44) which carries an electric machine rotor (50) which rotates about an axis essentially parallel to the axial direction , DOLLAR A - first connecting means (54), which connect two members formed from the carrier (44) or a stationary housing (56), and DOLLAR A - second connecting means (58), two from the drive member (24) or links existing to the rotor (50), these second connecting means (58) transmitting the torque between the drive member (24) and the red or (50) elements involved, DOLLAR A, the first (54) or the second (58) connecting means permitting radial relative movement between the links which connect them, DOLLAR A and all of which are involved in the transmission of the torque between the drive link ( 24) and the rotor (50) involved elements of the second connecting means (58) are angularly rigid under the effect of the application of this torque which rotates the rotor (50).

Description

The present invention relates to an improved one Power transmission arrangement for a motor vehicle, in which an electric machine is arranged.

• - eine Kupplung zur Verbindung eines durch eine Brennkraftmaschine angetriebenen Drehantriebsglieds mit einem Drehabtriebsglied zur Kupplung an einem Getriebe, wobei sich dieses Antriebsglied und dieses Abtriebsglied um im Wesentlichen parallel zu einer Axialrichtung verlaufende Achsen drehen,
• - ein Modul, das einen Träger umfasst, der einen sich um eine im Wesentlichen parallel zur Axialrichtung verlaufende Achse drehenden Rotor einer Elektromaschine trägt,
• - erste Verbindungsmittel, die zwei aus dem Träger bzw. einem stationären Gehäuse gebildete Glieder verbinden, und
• - zweite Verbindungsmittel, die zwei aus dem Antriebsglied bzw. dem Rotor gebildete Glieder verbinden, wobei diese zweiten Verbindungsmittel an der Übertragung des Drehmoments zwischen dem Antriebsglied und dem Rotor beteiligte Elemente umfassen,

wobei die ersten oder die zweiten Verbindungsmittel eine radiale Relativbewegung zwischen den Gliedern, die sie verbinden, gestatten. From the prior art, in particular according to FR-A-2 803 452 (FR-9 916 641), a power transmission arrangement for a motor vehicle of the type is already known, which comprises the following:

• a coupling for connecting a rotary drive element driven by an internal combustion engine to a rotary drive element for coupling to a transmission, this drive element and this output element rotating about axes running essentially parallel to an axial direction,
• a module which comprises a carrier which carries a rotor of an electric machine which rotates about an axis which runs essentially parallel to the axial direction,
• - First connecting means which connect two members formed from the carrier or a stationary housing, and
• second connecting means which connect two members formed from the drive member or the rotor, these second connecting means comprising elements involved in the transmission of the torque between the drive member and the rotor,

the first or the second connecting means permitting radial relative movement between the links which connect them.

In FR-A-2 803 452 carries the one that forms an electrical machine module Module simultaneously the rotor and a stator of this machine. The Electrical machine module thus forms a whole, which is before assembly of the module are pre-assembled in the power transmission arrangement can. Thanks to this pre-assembly of the module, it can be between the rotor and the stator has a greatly reduced air gap, thereby promoting the performance of the electric machine. Since the Electric machine can be operated as a motor or as a generator, it allows various functions to be guaranteed, such as a function as a starter or alternator.

Furthermore, in the FR-A-2 803 452 the stationary housing through a firmly connected to a gear housing Coupling housing formed. The carrier of the electrical machine module is by first connecting means rigidly attached to the clutch housing. Out this is why these first connecting means ensure at least in a plane running perpendicular to the axis of rotation of the rotor a rigid connection between the carrier and the stationary Clutch housing.

Finally, the drive link in FR-A-2 803 452 is replaced by a Internal combustion engine driven. The drive link is through in one Housing of the internal combustion engine means rotatably guided, while the rotor of the moving machine through from the carrier of the Electric motor and thus means carried by the clutch housing is rotatably guided.

Between the axes of rotation of the drive member and the Electrical machine rotor should get the best possible alignment. There the drive member and the electric machine rotor, however different, in different housings, namely the Clutch housing and the engine housing, housed funds can be performed when installing the power transmission assembly due to the dimensional deviations of the different elements perfect alignment between the axes of rotation of the drive element and of the electric machine rotor can be obtained.

To this misalignment of the axes of rotation of the drive member and Compensating electrical machine rotors include those in the FR-A-2 803 452 proposed second connection means (which the Connect the drive link and the electric machine rotor) Torque transmission element made of elastomer, which is in a perpendicular to the Axis of rotation of the rotor extending plane is elastically deformable, so that in particular a radial relative movement between the Drive member and the electric machine rotor is permitted.

However, the torque transmission element deforms Elastomer in the direction of application of this torque (Torsional elasticity about the axis of rotation of the rotor) elastic. This can be done under lead to the introduction of rotor resonances under certain operating conditions, if the frequency of the vibrations of the internal combustion engine (2nd Order) and the natural frequency of the rotor-elastomer element system (Mass-spring) match.

In addition, the aging of the Torque transmission element made of elastomer due to the relatively high temperature surrounding environment (especially the electric machine forms an exothermic Link) and by the actual heating of the material due to the Hysteresis of this material can be undesirably accelerated. The aging of the elastomer changes the elasticity of the Torque transmission element and thus the natural frequency of the Rotor elastomer element system.

The object of the present invention is therefore an inexpensive Manufactured and easy to handle power transmission assembly to create the kind mentioned above in a structurally simple manner no longer the aforementioned dangers of resonance formation and of aging.

This object is achieved according to the invention by an arrangement Claim 1 solved. Advantageous refinements and developments the invention result from the dependent claims.

It is essential in the solution according to the invention that all of the Transmission of the torque between the drive member and the Rotor elements involved in the second connection means when creating of the torque driving the rotor in a rotationally rigid manner or are rotationally rigid.

The main advantage is that it is with this Power transmission arrangement not to an angled or rotary Relative rotation of the second connecting means and therefore not too Signs of resonance and no signs of aging. Therefore the arrangement according to the invention is particularly safe and durable.

In addition, the second connection means allow the transmission a large torque even with clear radial, angular and / or axial positioning errors of the rotor relative to the Drive member.

The power transmission arrangement according to the invention is simpler Construction inexpensive to manufacture and easy to assemble.

It is particularly advantageous if the second connecting means at least in a perpendicular to the axis of rotation of the rotor Level a rigid connection between the drive link and the Ensure rotor.

It is also particularly advantageous if the first connecting means comprise at least one clamping member, which by axial clamping cooperates with a clamped member, this Clamp member and this clamped member of the two through the first Lanyards connected respective links are worn.

It is also particularly advantageous if the clamped member with the carrier is firmly connected and at least one elongated Recess includes, through which a fixed with the stationary housing connected axial pin extends with a radial clearance, wherein the clamping member is firmly connected to the stationary housing Area for clamping the clamped member and a elastic element, in particular a spring washer of the diaphragm spring type, includes that under axial compression between the clamped limb and a shoulder of the axial pin acts.

It is also particularly advantageous if the first connecting means at least one of a plug-in member and a receiving member existing pair include, by the two by the first Connection means connected respective links are worn, wherein the plug member housed in the receiving member and by a radial deformable, ring-shaped elastic mass that radially between the Plug member and the receiving member is arranged with this Receiving member is connected.

It is also particularly advantageous if the first connecting means at least in a perpendicular to the axis of rotation of the rotor Level between the support and the stationary housing a rigid Ensure connection.

It is also particularly advantageous if the second connecting means comprise a clamping member, which by axial clamping with a clamped member cooperates, this clamping member and this clamped link with the two through the second Connection means connected respective links are rotatably connected.

It is also particularly advantageous if the clamping member with the Drive member is rotatably connected and the clamped member with the rotor is rotatably connected.

It is also particularly advantageous if the clamping member is replaced by a Cover is supported to support a clutch membrane.

It is also particularly advantageous if the clamping member two ring-shaped clamping jaws clamping clamped member, at least one of which is axially movable, and means for elastic return of each movable jaw to the other Jaw that is under axial compression between this movable jaw and an axially fixed, annular seat Act.

• - Mittel zur radialen Positionierung jeder beweglichen Klemmbacke bezüglich des entsprechenden Sitzes,
• - Mittel zur drehfesten Verbindung jedes beweglichen Klemmbacke mit dem entsprechenden Sitz und
• - Mittel zur axialen Führung jeder beweglichen Klemmbacke.

It is also particularly advantageous if the second connecting means comprise the following:

• Means for radially positioning each movable jaw with respect to the corresponding seat,
• - Means for the rotationally fixed connection of each movable jaw with the corresponding seat and
• - Means for axially guiding each movable jaw.

It is also particularly advantageous if the clamping member has two Movable jaws includes two axially fixed annular Seats are assigned, the radial positioning means, the means for non - rotatable connection and the means for axial rotation in each of the jaws include formed circumferential notches, wherein the jaws on the two axially fixed seats connecting axial webs are pushed.

• - eine Federscheibe der Tellerfederart, die unter Komprimierung zwischen dem axial festgelegten Sitz und der beweglichen Klemmbacke wirkt, und
• - Mittel zur drehfesten Verbindung der Federscheibe mit dem axial festgelegten Sitz.

It is also particularly advantageous if the means for elastically returning each movable jaw to the other jaw comprise the following:

• - A spring washer of the disc spring type, which acts under compression between the axially fixed seat and the movable jaw, and
• - Means for the rotationally fixed connection of the spring washer with the axially fixed seat.

It is also particularly advantageous if the means for rotationally fixed Connection of the spring washer to the axially fixed seat comprise at least one axial circumferential nose of the disc, which in a axially fixed seat trained complementary recess is inserted.

It is also particularly advantageous if the clamped member is one radial flange of a first end of an axial bushing, wherein this clamped flange, especially made of plastic consists of two axially opposite sides, preferably are each covered with a friction lining.

It is also particularly advantageous if the second connecting means Means for axially pushing the axial bushing onto the rotor and for the rotationally fixed connection of this socket with this rotor.

It is also particularly advantageous if the means for axial Push the axial bushing onto the rotor and towards the non-rotating one Connecting this bushing to this rotor axial, complementary, protruding and protruding grooves which on one the hub of the Rotor forming part and at a second end of the axial bushing are trained.

It is also particularly advantageous if the projecting grooves Hub of the rotor or the axial bushing with axially converging Ends are provided, the mutual angular positioning of the complementary grooves of this rotor hub and this bush favor that for axially pushing the complementary grooves suitable is.

It is also particularly advantageous if the hub of the rotor unites Ring to hold the complementary grooves radially in nested position.

• - ein erstes und ein zweites Kupplungsglied, die mit dem Antriebsglied bzw. dem Rotor drehfest verbunden sind, und
• - ein Zwischenglied, das mit dem ersten bzw. dem zweiten Kupplungsglied durch zwei Verbindungen verbunden ist, die Radialtranslationsbewegungen entlang im Wesentlichen senkrecht zueinander verlaufenden Achsen gewährleisten.

It is also particularly advantageous if the second connecting means comprise an Oldham coupling, which contains the following:

• - A first and a second coupling member which are rotatably connected to the drive member and the rotor, and
• an intermediate member which is connected to the first and the second coupling member by two connections which ensure radial translation movements along axes which are essentially perpendicular to one another.

It is also particularly advantageous if the first coupling member forms a cover for supporting a clutch membrane.

It is also particularly advantageous if the intermediate member is divided by two Sliding connections with essentially perpendicular to each other extending axes with the first and the second coupling member is connected, the two sliding connections through by the Intermediate pegs are formed which are in from the first and the second coupling member worn ears are attached.

It is also particularly advantageous if the second connecting means Means for axially sliding the second coupling member onto the Rotor and for the rotationally fixed connection of this second coupling member embrace with this rotor.

It is also particularly advantageous if the means for axial Sliding the second coupling member onto the rotor and to rotationally fixed connection of this second coupling member with this rotor axial, complementary, projecting and projecting grooves comprise, which are fixed to a part forming the hub of the rotor connected wreath and on a peripheral contour of the second Coupling member are formed.

It is also particularly advantageous if the projecting grooves of the Hub ring of the rotor or the second coupling member with axial converging ends are provided which are mutual Angular positioning of the complementary grooves of this hub ring and favor this second coupling member, the axial Interlocking the complementary grooves is suitable.

It is also particularly advantageous if the intermediate member is divided by two Pairs of diametrically opposed tabs with the first or the second coupling member is connected, the tabs in Run essentially transversely to the axial direction and are elastically deformable that each pair of tabs has a radial relative movement of the Intermediate link and the coupling link to which this pair is connected, allowed.

It is also particularly advantageous if the second connecting means ring-shaped claw coupling links and Receiving claw coupling members include the two through the second Connecting means connected to each other in a rotationally fixed manner, wherein the claw coupling member has teeth that in the complementary notches of the receiving claw coupling member radial play and angular play are inserted.

It is also particularly advantageous if the Plug claw coupling member of a part forming the hub of the rotor and that Pick-up claw coupling member from a cover to support one Coupling membrane is worn.

It is also particularly advantageous if the dog clutch teeth in the Essentially axial and the complementary dog clutch notches run essentially radially.

It is also particularly advantageous if the second connecting means Means for resiliently retrieving the pawl coupling members and receiving claw coupling members in a relative angular position include in which the dog clutch teeth with the contours of Claw coupling notches are not in angular contact.

It is also particularly advantageous if the means for elastic Retrieve include at least a pair of spring leaves from that Pick-up claw coupling member to be worn and on a tooth of the plug claw coupling member opposing forces perform angular retrieval.

It is also particularly advantageous if the means for elastic Retrieve spring leaves included by that Pick-up claw coupling member to be worn and between two successive notches of the receiving claw coupling member are, each spring leaf is provided with two ends, each with the successive teeth of the plug claw coupling member interact.

It is also particularly advantageous if the means for elastic Retrieve an annular spring leaf that includes crenellated around the circumference and radial parts for angular Clamping the dog clutch teeth and peripheral parts to Fastening the spring leaf on the receiving claw coupling member limited.

It is also particularly advantageous if the peripheral parts of the Spring leaf in axial half-cutouts of the receiving claw coupling member are attached.

It is also particularly advantageous if the second connecting means a first and a second annular torque transmission member comprise with the two through the second connecting means connected respective links are rotatably connected, the first torque transmission member has a radially outer contour comprises formed on the projecting and projecting axial grooves are with a radial game and an angle game with complementary axial grooves on a radially inner contour of the second Torque transmission member are designed to cooperate.

It is also particularly advantageous if the first and the second Torque transmission member from a the hub of the rotor forming part or a cover for supporting a clutch membrane be worn.

It is also particularly advantageous if the second connecting means Means for angular braking of the ice and the second Include torque transmission member with respect to each other.

It is also particularly advantageous if the angular braking means unite comprise elastically radially deformable ring, which of one of the Torque transmission members is worn and preferably with one Plastic ring that is different from the other one Power transmission members is worn, cooperating through friction.

It is also particularly advantageous if the friction ring of the second Torque transmission member is carried and projecting and protruding axial grooves containing the protruding and recessed axial grooves of the second Extend the torque transmission link in the axial direction.

It is also particularly advantageous if the projecting grooves of the Friction rings are provided with axially converging ends, one mutual angular positioning of the complementary grooves on the one hand the first torque transmission member and on the other hand the Friction rings and the second torque transmission member favor that for axially pushing the complementary grooves suitable is.

It is also particularly advantageous if the second connecting means comprise a first support for clamping members, which are angular this carrier are distributed, and a second carrier for clamped Links that are angularly distributed on this second support, wherein each clamping member by substantially transverse to the axis of rotation of the Rotary clamping with a corresponding one clamped member cooperates, this first and second carrier connected to the two by the second connecting means Links are connected in a rotationally fixed manner.

It is also particularly advantageous if the first and the second Carrier with the drive member or the rotor are rotatably connected.

It is also particularly advantageous if the first carrier for Clamping members form a cover for supporting a clutch membrane, the second carrier from a part forming the hub of the rotor will be carried.

It is also particularly advantageous if the first carrier is angular contains distributed leaves, each with two essentially axial curved ends are provided, each clamping member by two Ends of two consecutive sheets is delimited, whereby these two ends are elastically deformable so that they Form jaws.

It is also particularly advantageous if the clamped members by essentially axial, firmly connected to the second carrier thin noses are formed by essentially radial Areas are limited.

It is also particularly advantageous if the second connecting means two diametrically opposed pairs of plug sectors and Recording sectors include, the plug-in sector and the recording sector each pair with those connected by the second connecting means two respective links are connected in a rotationally fixed manner, the Mating sector and the receiving sector of a pair by radial Sliding together interact, the plug-in sector and / or the Recording sector of each pair is elastically deformable so that the plug-in sector and the receiving sector by angular Clamp together.

It is also particularly advantageous if the plug sector and Recording sector of a pair with the rotor or the drive member rotatably are connected.

It is also particularly advantageous if the recording sectors are elastically deformable angularly, the angular ends each plug sector by in a part forming the hub of the rotor trained notches are limited.

It is also particularly advantageous if each recording sector passes through a leaf is delimited, which is provided with ends which in the Are essentially radially bent and elastically deformable at an angle, so that they form angle jaws.

It is also particularly advantageous if the recording sectors of one with a lid to support a clutch membrane connected carriers are worn.

It is also particularly advantageous if the plug-in angle sectors and Acquisition angle sectors each run essentially by 90 °.

It is also particularly advantageous if between those in contact standing, angular ends of the plug sectors and the Recording sectors are arranged rolling.

It is also particularly advantageous if the rolling means one by one rotatable on each substantially parallel to the axis of rotation of the rotor include angled end of the plug sectors attached ring, each end of the blades on a corresponding rotatable Ring supports.

• - ein erstes und ein zweites ringförmiges Drehmomentübertragungsglied, die mit den beiden durch die zweiten Verbindungsmittel verbundenen jeweiligen Gliedern drehfest verbunden sind, und
• - gespaltene Kupplungsringe mit im Wesentlichen parallel zur Drehachse des Rotors verlaufenden Drehachsen, die radial zwischen dem ersten und dem zweiten ringförmigen Drehmomentübertragungsglied angeordnet und in in den ringförmigen Flächen ausgebildeten komplementären Aussparungen gegenüber diesem ersten und zweiten ringförmigen Drehmomentübertragungsglied untergebracht sind.

It is also particularly advantageous if the second connecting means comprise the following:

• - A first and a second annular torque transmission member, which are rotatably connected to the two respective members connected by the second connecting means, and
• - Split clutch rings with axes of rotation running essentially parallel to the axis of rotation of the rotor, which are arranged radially between the first and the second annular torque transmission element and are accommodated in the annular surfaces in complementary recesses with respect to this first and second annular torque transmission element.

It is also particularly advantageous if the first and the second Torque transmission member from a the hub of the rotor forming part or a cover for supporting a clutch membrane be worn.

• - einen ersten Träger für im Wesentlichen axiale erste Kupplungsfinger, die auf diesem ersten Träger winkelförmig verteilt sind, und einen zweiten Träger für im Wesentlichen axiale zweite Kupplungsfinger, die auf diesem zweiten Träger winkelförmig verteilt sind, wobei dieser erste und dieser zweite Träger mit den beiden durch die zweiten Verbindungsmittel verbundenen Gliedern drehfest verbunden sind,
• - mindestens einen Metalldraht, der die ersten und die zweiten Kupplungsfinger durch Verschlingung mit diesen Fingern miteinander verbindet.

It is also particularly advantageous if the second connecting means comprise the following:

• a first carrier for essentially axial first coupling fingers, which are angularly distributed on this first carrier, and a second carrier for essentially axial second coupling fingers, which are angularly distributed on this second carrier, this first and this second carrier with the two links connected in a rotationally fixed manner by the second connecting means,
• - At least one metal wire that connects the first and the second coupling fingers by intertwining them with these fingers.

It is also particularly advantageous if the metal wire has a loop forms, which alternate along their contour the radially inner and outer indentations, which are pushed together by those of the interact with both carriers of the clutch fingers, limited.

It is also particularly advantageous if the second connecting means comprise two axially abutting coupling metal wires.

It is also particularly advantageous if the first carrier of one of the Hub of the rotor forming part is worn and the second carrier forms a cover for supporting a clutch membrane.

• - zwei komplementäre Hauptträger, von denen einer mit dem Antriebsglied und der andere mit dem Rotor drehfest verbunden ist,
• - komplementäre axiale Verzahnungen, die an einem ersten Hauptträger und an einem von dem zweiten Hauptträger getragenen Nebenträger ausgebildet sind, wobei der Nebenträger an dem zweiten Hauptträger axial gleitend angebracht und mit diesem zweiten Hauptträger drehstarr verbunden ist,
• - ein elastisches Glied mit axialer Wirkung, das von dem zweiten Hauptträger getragen wird und den Nebenträger in Position zum axialen Ineinanderschieben der komplementären Verzahnungen belastet.

It is also particularly advantageous if the second connecting means comprise the following:

• two complementary main carriers, one of which is connected to the drive member and the other to the rotor in a rotationally fixed manner,
• complementary axial toothings which are formed on a first main carrier and on a secondary carrier carried by the second main carrier, the secondary carrier being axially slidably mounted on the second main carrier and connected to this second main carrier in a rotationally rigid manner,
• - An elastic member with axial action, which is supported by the second main carrier and loads the secondary carrier in position for axially pushing the complementary teeth.

It is also particularly advantageous if each toothing has teeth is provided, each bounded by two converging edges are and in complementary recesses of the other toothing are to be inserted, each recess having a generally "V" - has a shape that is characterized by the converging flanks of the adjacent teeth is limited.

It is also particularly advantageous if the flanks of a tooth have a greater convergence than that of the flanks to a pointed end of this tooth converge, causing the tooth to enter the complementary deepening is facilitated.

It is also particularly advantageous if the module also has a carried by the same carrier as the rotor Contains electrical machine stator.

A better understanding of the invention will be obtained by reading the following description, which is given only as an example and is based on related to the drawings. In it show:

Figure 1 is an axial section half view of a power transmission arrangement for a motor vehicle according to a first embodiment of the invention.

Fig. 2 is a view of a variant embodiment of the machine support to the stationary housing of the power transmission arrangement according to the first embodiment of the invention connecting the first connecting means;

Fig. 3 is an axial sectional view of a power transmission arrangement for a motor vehicle according to a second embodiment of the invention;

Fig. 4 is a detailed view of the encircled part 4 of Fig. 3;

Fig. 5 is a view along arrow 5 of Fig. 4, showing axial, complementary, projecting and projecting grooves formed on a part forming the hub of the rotor and at one end of an axial bushing before sliding this bushing on this hub;

FIG. 6 shows a view similar to FIG. 3 of a power transmission arrangement for a motor vehicle according to a third embodiment of the invention;

FIG. 7 is an exploded, perspective view of the second means for connecting the power transmission arrangement shown in FIG. 6, which connect the drive member and the rotor;

Is a perspective view of a variant of an Oldham coupling of the power transmission assembly 8 in Figures 6 and 7..;

. Fig. 9 is a view similar to Figure 3 of a power transmission arrangement for a motor vehicle according to a fourth embodiment of the invention;

Fig. 10 is a view along arrow 10 of Fig. 9 showing a dog clutch tooth and dog clutch notch which are complementary;

FIG. 11 is a perspective view of two ring-shaped claw coupling members, a plug and a receiving member, of the power transmission arrangement shown in FIG. 9;

FIG. 12 is a view similar to FIG. 11 of an embodiment variant of the means for resiliently returning the annular dog coupling plug member and dog coupling receiving member to a predetermined relative angular position;

FIG. 13 is a perspective view along arrow 13 of FIG. 12;

Fig. 14 is a cross-sectional view of the ring-shaped dog coupling male and female member shown in Figs. 12 and 13;

Fig. 15 and 16 are views similar to Figures 3 and 4 a force transmission assembly for a motor vehicle according to a fifth embodiment of the invention.

Figure 17 is a perspective detail view showing an axial groove of a torque transmitting member of the second connecting means of the power transmission assembly shown in Figures 15 and 16..;

FIG. 18 is a perspective view of the drive member and the rotor connecting the second connecting means of a power transmission device according to a sixth embodiment of the invention;

FIG. 19 is a perspective, exploded view of the second connecting means shown in FIG. 18;

. FIG. 20 is a view similar to Figure 19 of a power transmission device according to a seventh embodiment of the invention;

Fig. 21 is an axial sectional view of the second connection means shown in Fig. 20;

. Fig. 22 and 23 are views similar to Figures 18 and 21 of a force transfer system according to an eighth embodiment of the invention;

Fig. 24 and 25 are views similar to Figures 20 and 21 of a power transmission device according to a ninth embodiment of the invention.

Fig. 26 is a schematic view of means integrated in the second connecting means, which allow changes in the axial position with respect to the drive member and the rotor to be effectively taken into account.

In Fig. 1, a power transmission assembly has been shown for a motor vehicle according to a first embodiment of the invention, which is designated by the general reference numeral 20.

The power transmission arrangement 20 comprises a clutch 22 , which connects a rotary drive member 24 , which is driven by an internal combustion engine of a vehicle, to a rotary drive member 26 . The latter forms a shaft for coupling to a transmission.

The drive member 24 and the driven member 26 , which are essentially coaxial, are to rotate about axes running essentially parallel to an axial direction represented by the axis X in the figures.

The clutch 22 comprises an engine flywheel 28 which is fastened to the drive member 24 in a manner known per se. Furthermore, the clutch 22 comprises a friction disk 30 , which is connected to the driven member 26 via conventional means 32 for the rotationally fixed connection. These coupling means 32 allow axial displacements of the friction disk 30 parallel to the axis X.

The disk 30 is provided with conventional friction linings 34 .

Furthermore, the clutch 22 comprises a pressure plate 36 which is connected in a rotationally fixed manner to a cover 38 which is firmly connected to the engine flywheel 28 . The connecting means of the pressure plate 36 to the cover 38 comprise tabs, not shown, in a conventional manner, which connect the plate 36 to the cover 38 . These tabs allow axial displacements of the pressure plate 36 parallel to the X axis.

A conventional membrane 40 for controlling the displacements of the pressure plate 36 rests on the cover 38 . In a manner known per se, the membrane 40 has a radially inner part 401 which interacts with a conventional control stop (not shown) and a radially outer part 40 E which is intended to cooperate with the pressure plate 36 .

The linings 34 of the friction disk 30 are to be clamped between the engine flywheel 28 and the pressure plate 36 in such a way that they connect the drive member 24 and the driven member 26 to one another.

Furthermore, the power transmission arrangement 20 comprises a module 42 , the so-called electric machine module, which comprises an annular carrier 44 carrying an electric machine 46 . This machine 46 , which can be operated as a motor or as a generator, is provided with a stator 48 and a rotor 50 . The stator 48 is fixed to the carrier 44 . The rotor 50 is rotatably guided with conventional rolling means 52 , which are arranged between an annular, axial wall 44 A of the carrier and the rotor 50 , about an axis which substantially coincides with the axis X.

The first connecting means 54 connect the carrier 44 to a stationary housing 56 which is fixedly connected to the transmission housing or forms this transmission housing.

Second connecting means 58 connect the drive member 24 and the rotor 50 .

In the first embodiment of the invention, the second connecting means 58 ensure, at least in a plane running perpendicular to the axis of rotation of the motor 50 , a rigid connection between the drive member 24 and this rotor 50 . In Fig. 1, the second connecting means 58 are connecting link 50 constituting line schematically shown in particular by a clutch cover 38 and the rotor. It should be noted that this cover 38 is fixedly connected to the drive member 24 by the engine flywheel 28 .

The first connecting means 54 comprise a substantially radial wall 44 B of the carrier 44 , which contains at least one elongate recess 59 through which a screw 60 , which forms an axial pin, extends with a radial play and an angular play. The screw 60 screwed into the stationary housing 65 is firmly connected to the former.

The radial wall 44 B of the carrier forms a clamped member which cooperates by tightening with a clamping member described below.

The clamping member comprises a surface 62 formed on the stationary housing 56 or fixedly connected thereto for clamping the radial wall 44 B and an elastic element 64 , in particular a spring washer of the diaphragm spring type, which is traversed by the screw 60 and with axial compression between the radial wall 54 and a shoulder 66 formed by the head of the screw 60 acts.

It is thus understood that in the embodiment shown in FIG. 1, the clamped member is carried by the carrier 44 , while the clamping member is carried by the stationary housing 56 . Alternatively, the clamp member could be carried by the bracket 44 and the clamped member could be carried by the stationary housing 56 .

Thanks to the axial clamping of the radial wall 44 B of the carrier, the first connecting means 54 allow a radial relative movement between the carrier 44 and the stationary housing 56 . Thus, the first connecting means 54 allow the alignment errors of the axes of rotation of the drive member 24 and the rotor 50 to be compensated for by radial relative displacement between the carrier 44 carrying the rotor 50 and the stationary housing 56 when the power transmission arrangement is assembled. This displacement forces the rotor 50 to align with the drive member 24 .

The alignment error is corrected once and for all when the power transmission assembly 20 is installed or the first rotation of the rotor 50 , the carrier 44 consequently remaining immobile with respect to the stationary housing 56 when the power transmission assembly is in operation.

FIG. 2 shows an embodiment variant of the first connecting means 54 connecting the carrier 44 and the stationary housing 56 .

In this variant, the radial wall 44 B provided with at least one elongated recess 59 forms a receiving member through which the screw 60 forming a plug member extends.

The radial wall 44 B is connected by an annular elastic mass 68, which is arranged radially between the contour of the elongate recess 59 and the screw 60 with the screw 60th The mass 68 is arranged axially between two seats formed by the surface 62 of the stationary housing 56 and the shoulder 66 formed by the head of the screw 60 .

According to the variant shown in FIG. 2, the first connecting means 54 allow a radial relative displacement between the carrier 44 and the stationary housing 56 in an analogous manner to the first connecting means 54 shown in FIG. 1.

In FIGS. 3 to 24, a power transmission assembly 20 according to other embodiments for a motor vehicle of the invention has been illustrated. In these figures, the elements that are analogous to those of FIGS. 1 and 2 are represented by identical reference numerals.

In the other embodiments of the invention, which are described below, the first connecting means 54 ensure a rigid connection between the carrier 44 and the stationary housing 56, at least in a plane perpendicular to the axis of rotation of the rotor 50 .

In FIGS. 3 to 5, a power transmission arrangement 20 has been described according to a second embodiment of the invention.

In this case, the carrier 44 is rigidly attached to the stationary housing (not shown) by means of conventional means, in particular including screws 70 , only one of which is shown in FIG. 3.

It should be noted that the stator of the electrical machine 46 is not shown in FIG. 3 for the sake of simplicity.

With reference in particular to FIGS. 3 and 4, it can be seen that the second connecting means 58 in the second embodiment of the invention comprise a clamping member 72 which cooperates with a clamped member 74 by axial clamping. The clamping member 72 is carried by the clutch cover 38 . For this reason, the clamping member 72 is rotatably connected to the drive member, not shown in FIGS . 3 to 5. The clamped member 74 is rotatably connected to the rotor 50 .

As an alternative, the clamping member 72 could be connected in a rotationally fixed manner to the rotor 50 , the clamped member 74 then being connected in a rotationally fixed manner to the drive member.

In the example shown, the clamping member 72 comprises two axially movable, annular clamping jaws 76 , which clamp the clamped member 74 . Furthermore, the clamping member 72 comprises means for resiliently returning the clamping jaws 76 to one another, which act under axial compression between each clamping jaw 76 and an axially fixed, corresponding annular seat 78 .

The seats 78 are connected to one another by generally cylindrical axial webs 80 . It should be noted that one of the seats 78 is formed on the clutch cover 38 .

The means for resiliently returning the clamping jaws 76 to one another preferably comprise two spring washers 81 of the diaphragm spring type, which act under respective compression between a clamping jaw 76 and a corresponding seat 78 .

The clamping jaws 76 each include circumferential notches 82 pushed onto the webs 80 . The notches 82 and the webs 80 , which have complementary shapes, simultaneously form means for the radial positioning of the clamping jaws 76 with respect to the seats 78 , means for the rotationally fixed connection of the clamping jaws 76 with the seats 78 and means for axially guiding the clamping jaws 76 .

Each spring washer 81 comprises at least one axial peripheral lug 84 which is inserted into a complementary recess 86 formed in the corresponding seat 78 in order to connect this spring washer 81 to its corresponding seat 78 in a rotationally fixed manner.

As an alternative to this, the clamping member 72 could also have only a single movable clamping jaw 76 , the other clamping jaw 76 being fixed axially.

The clamped member 74 preferably forms a radial flange of a first end of an axial bushing 88 .

The clamped member 74 has two opposite axial surfaces, which are preferably each covered with a friction lining 90 .

The clamped member 74 is made of plastic, for example, and the jaws 76 are made of metal, for example. Alternatively, the materials of the clamped member 74 and jaws 76 may be reversed.

The axial bushing 88 is connected by means for axially pushing this bushing 88 onto the rotor 50 and for non-rotatably connecting this bushing 88 to this rotor 50 with the latter. These means for axially sliding on and for non-rotatable connection preferably comprise axial, complementary, projecting and projecting grooves 92 , 94 , which on one part forming the hub 96 of the rotor 50 (the hub 96 is directly connected to the rolling means 52 ) and on a second End of the axial bushing 88 are formed.

The projecting grooves 92 of the hub 96 of the rotor are preferably provided with axially converging ends 92 E, which favor mutual angular positioning of the complementary grooves 92 , 94 of this hub 96 and this bushing 88 , which is suitable for axially pushing the complementary grooves 92 , 94 into one another ,

It should be noted that the hub 96 of the rotor 50 carries a ring 98 for radially holding the complementary grooves 92 , 94 in a pushed-together position.

Optionally, the second end of the bushing 88 provided with the grooves 94 has axial slots which promote the pushing of the bushing 88 onto the hub 96 .

In the second embodiment of the invention, the alignment between the axes of rotation of the drive member 24 and the rotor 50 takes place by radially displacing the clamped member 74 between the clamping jaws 76 of the clamping member 72 . This shifting occurs every revolution of the drive member 24 .

The friction parameters between the clamp member 72 and the clamped member 74 are conventionally calculated by those skilled in the art to allow transmission of the torque provided by the drive member, while the relative radial displacement between the clamped member 74 and the clamp member 72 allows for limited force becomes.

It should be noted that all elements of the second connecting means 58 , which are involved in the transmission of the torque between the drive member 24 and the rotor 50 , are not elastically deformable under the effect of the application of this torque when the power transmission arrangement is in operation. In particular, all elements of the second connecting means 58 , which are involved in the transmission of the torque between the drive member 24 and the rotor 50 , are angularly rigid under the effect of the application of this torque, which drives the rotor 50 in rotation. The angular stiffness of the elements involved in the transmission of the torque is such that the frequency for exciting the internal combustion engine to its highest rotational speed is of the order of 2, since it results from the successive combustions, below the natural frequency of the rotor elements involved in the torque transmission System remains. For this reason, the dangers of introducing rotor resonances mentioned at the beginning of this work are avoided.

It should also be pointed out that the second connecting means 58 ensure a connection between the drive member 24 and the rotor 50 without an elastic radial component. In particular, all elements of the second connecting means 58 , which are involved in the transmission of the torque between the drive member 24 and the rotor 50 , are not radially deformable under the effect of this torque, which rotates the rotor 50 .

Finally, it should be pointed out that the complementary axial grooves of the bushing 88 and the hub 96 of the rotor make it possible to remedy changes in the relative axial position of the clutch cover 38 and the rotor which result from the dimensional deviations of the elements forming the power transmission arrangement 20 , to accomplish. The grooves thus allow the transmission to come into contact with the motor by being pushed together in the area of the second connecting means 58 .

The second connecting means 58 thus allow the transmission of a relatively large torque while permitting noticeable relative radial, angular and axial positioning errors of the rotor 50 and the clutch cover 38 .

In Figs. 6 and 7, a force transfer assembly 20 has been illustrated for a motor vehicle according to a third embodiment of the invention.

In this case, the second connection means 58 comprise an Oldham coupling 100 .

The clutch 100 includes a first clutch member, which is formed, for example, by the clutch cover 38 , and an annular second clutch member 102 , which is connected to the rotor 50 in a rotationally fixed manner.

In addition, the clutch 100 comprises an intermediate member 104 for torque transmission, which is connected to the first 38 and the second clutch member 102 by means of two sliding connections with the axes T1, T2 running essentially perpendicular to one another.

The generally annular link 104 has radial pins 106 slidably mounted in ears 108 carried by the first 38 and second 102 coupling members. The pins 106 and the ears 108 form two sliding connections with the axes T1, T2 (see in particular FIG. 7).

The circumferential contour of the second coupling member 102 is provided with axial, projecting and protruding grooves 110 , which interact with complementary axial grooves 112 formed in a ring 114 fixedly connected to the rotor hub 96 . These complementary, axial grooves 110 , 112 form means for axially pushing the second coupling member 102 onto the rotor 50 and for non-rotatably connecting this second coupling member 102 to this rotor 50 .

In an analogous manner to the previously described second embodiment of the invention, the projecting grooves of the hub ring 114 or of the second coupling member 102 are provided with axially converging ends which promote mutual angular positioning of the complementary grooves 110 , 112 of this second coupling member 102 and this ring 114 , which are used for axial insertion of the complementary grooves 110 , 112 is suitable.

In the third embodiment of the invention, alignment between the axes of rotation of the drive member and the rotor is according to the conventional operation of the Oldham clutch 100 .

It should be noted that all elements of the second connecting means 58 according to the third embodiment of the invention, which are involved in the transmission of the torque between the drive member 24 and the rotor 50 , are not elastically deformable under the effect of the application of this torque when the power transmission arrangement is in operation are. In particular, all the connecting means 58 involved in the transmission of the torque between the drive member 24 and the rotor 50 are angularly rigid under the effect of the application of this torque which rotates the rotor 50 . For this reason, the dangers of introducing rotor resonances mentioned at the beginning of this work are avoided. It should also be pointed out that the second connecting means 58 ensure a connection between the drive member 24 and the rotor 50 without an elastic radial component. In particular, all elements of the second connecting means 58 involved in the transmission of the torque between the drive member 24 and the rotor 50 are not radially deformable under the effect of the application of this torque which rotates the rotor 50 .

Finally, it should be noted that the complementary axial grooves 110 , 112 of the second coupling member 102 and the ring 114 allow remedial action for changes in the relative axial position of the clutch cover 38 and the rotor 50 , which result from dimensional deviations of the elements forming the power transmission arrangement 20 surrender to create.

A variant of the Oldham coupling 100 is shown in FIG. 8.

In this case, the intermediate member 104 has a generally disc-shaped shape and contains four substantially axial lugs 115 . These tabs 115 are each provided with a tangential alignment tab 115 '. Each tab 115 'has a first end, which is fastened to a nose 115 , for example by a rivet, in such a way that it is rotationally rigidly connected to the intermediate member 104 , and a second end which is connected to the first 38 or second 102 coupling member, on. A first pair of diametrically opposed tabs 115 'are connected to the first 38 coupling member. A second pair of diametrically opposed tabs 115 'is connected to the second 102 coupling member.

The tabs 115 'are resiliently deformable so that each pair allows radial relative movement of the link 104 and the link 38 , 102 of the coupling to which that pair is connected. The two radial movements of the two pairs of tabs 115 'correspond to radial translational movements along axes which are essentially perpendicular to one another. The coupling 100 thus makes it possible to compensate for misalignments between the axes of rotation of the drive member 24 and the rotor 50 , as a result of which great torsional rigidity is ensured.

The arrangement of the coupling member 100 according to this variant thus has the advantage that it allows the intermediate member 104 to be displaced without friction and thus without wear.

More generally, this principle can be implemented by a rigid intermediate member 104 of different shapes, which is flexibly connected to the coupling members 38 and 102 along two vertical, radial directions.

In FIGS. 9 to 11, a power transmission arrangement 20 has been shown for a motor vehicle according to a fourth embodiment of the invention.

In this case, the second connecting means 58 comprise an annular plug-in claw coupling member 116 which is carried by the rotor hub 96 and an annular receiving claw coupling member 118 which is carried by the clutch cover 38 .

Thus, in the example shown in FIGS . 9 to 11, the plug claw coupling member 116 and the receiving claw coupling member 118 are connected in a rotationally fixed manner to the rotor 50 and the drive member, which is not shown in these FIGS. 9 to 11. As an alternative, the plug-in claw coupling member 116 could be connected in a rotationally fixed manner to the drive member, in which case the receiving claw coupling member 118 would then be connected in a rotationally fixed manner to the rotor 50 .

The plug claw coupling member 116 contains teeth 120 which are inserted with a radial and an angular play in the complementary notches 122 formed in a radially inner contour of the receiving claw coupling member 118 .

Preferably, the dog clutch teeth 120 are substantially axial and the complementary dog clutch notches 122 are substantially radial.

In order to avoid, in particular, undesirable noise and undesirable vibrations due to the angular play between the teeth 120 and the notches 122 , the second connecting means 58 comprise means for elastically returning the plug-in member 116 and the receiving member 118 into a relative angular position in which the claw coupling teeth 120 with the contours the dog clutch notches 122 are not in angular contact.

These elastic return means include, for example, spring leaves 124 which are carried by the receiving claw coupling member 118 and are each arranged between two successive notches 122 . Each spring leaf 124 is provided with two ends 124 E, each of which interacts with successive teeth 120 of the plug-in claw coupling member 116 . Thus, each dog clutch tooth 120 is subjected to opposing angular retraction forces exerted by the spring blades 124 (see FIG. 10) disposed on both sides of the dog clutch tooth 120 .

In the fourth embodiment of the invention, the alignment between the axes of rotation of the drive member and the rotor occurs due to the double radial and angular play between the complementary teeth 120 and notches 122 .

It should be noted that the elements of the second connecting means 58 according to the fourth embodiment of the invention, which are involved in the transmission of the torque between the drive member 24 and the rotor 50 , are not elastically deformable under the effect of the application of this torque when the power transmission arrangement is in operation are. In operation, the dog clutch teeth 120 are supported directly at an angle on the contour of the dog clutch notches 122 . In particular, all elements of the second connecting means 58 , which are involved in the transmission of the torque between the drive member 24 and the rotor 50 , are angularly rigid under the effect of the application of this torque, which rotates the rotor 50 .

It should also be pointed out that the second connecting means 58 ensure a connection between the drive member 24 and the rotor 50 without an elastic radial component. In particular, all elements of the second connecting means 58 , which are involved in the transmission of the torque between the drive member 24 and the rotor 50 , are not radially deformed under the effect of the application of this torque, which rotates the rotor 50 .

Finally, it should be noted that the dog clutch teeth 120 can slide axially in the dog clutch notches 122 , thereby making it possible to remedy changes in the relative axial position of the clutch cover 38 and the rotor 50 which result from dimensional deviations of the elements forming the power transmission arrangement 20 ,

In Figs. 12 to 14, a variant embodiment of the means for resiliently returning the plug jaw clutch member 116 and the receiving jaw clutch member 118 in the non-contact angular position of the teeth 120 is illustrated with the contours of the depressions 122.

In this case, the spring leaves 124 have been replaced by an annular spring leaf 126 which extends around the circumference to form crenellations. These crenellations limit radial angular clamping parts 126 R of the jaw clutch teeth 120 (see in particular Fig. 12), and peripheral parts 126 T for fastening the spring plate 126 the receiving jaw clutch member 118 (see in particular Fig. 13).

The peripheral parts 126 T of the spring leaf are fastened in axial half-cutouts of the receiving claw coupling member 118 and delimit axial strut parts 128 which alternate angularly with axial tabs 130 of the receiving claw coupling member 118 .

In Figs. 15 to 17, a power transmission assembly 20 is shown for an automotive vehicle according to a fifth embodiment of the invention.

In this case, the second connecting means 58 comprise a first torque transmission element 132 carried by the rotor hub 96 and a second torque transmission element 134 carried by the clutch cover 38 .

These first 132 and second 134 generally ring-shaped torque transmission members are connected in a rotationally fixed manner to the rotor 50 and the drive member (not shown in FIGS. 15 to 17). As an alternative, the first torque transmission element 132 could be connected in a rotationally fixed manner to the drive element, the second torque transmission element 134 in this case being connected in a rotationally fixed manner to the rotor 50 .

The first torque transmission element 132 comprises a radially outer contour, on which axial, projecting and protruding grooves 136 are formed, which have a radial and angular play with complementary, axial grooves 138 which are formed on a radially inner contour of the second torque transmission element 134 , interact.

In order in particular to avoid undesirable noise and undesirable vibrations due to the angular play between the complementary grooves 136 , 138 , the second connecting means 58 comprise means for angularly braking the torque transmission members 132 , 134 relative to one another.

The angle brake means comprise, for example, an elastically radially deformable sealing ring 140 which is carried by the first torque transmission element 132 . This seal 140 cooperates by friction with a ring 142 , preferably made of plastic, which is carried by the second torque transmission member 134 .

As an alternative, the sealing ring 140 could also be carried by the second torque transmission member 134 , in which case the friction ring 52 is carried by the first torque transmission member 132 .

The friction ring 142 includes axial, projecting and projecting grooves 144 , which extend the axial, projecting and projecting grooves 138 of the second torque transmission member 134 in the axial direction.

The protruding grooves 144 of the friction ring 142 are preferably provided with axially converging ends, which mutually angularly position the complementary grooves on the one hand of the first torque transmission element 132 (the grooves 136 ) and on the other hand the friction ring 142 and the second one designed to axially push the complementary grooves 136 , 138 into one another Favor torque transmission member 134 (the grooves 138 and 144 ).

The friction ring 142 made of plastic, which is provided with grooves 144 with an axially converging end, can be easily produced, in particular by molding.

In the fifth embodiment of the invention, the alignment between the axes of rotation of the drive member and the rotor takes place due to the double radial and angular play of the axial, complementary grooves 136 , 138 .

It should be noted that the elements of the second connecting means 58 according to the fifth embodiment of the invention, which are involved in the torque transmission between the drive member 24 and the rotor 50 , are not elastically deformable under the effect of the application of this torque when the power transmission arrangement is in operation. In operation, the complementary grooves 136 , 138 are in direct angular contact with one another. In particular, all elements of the second connecting means 58 , which are involved in the transmission of the torque between the drive member 24 and the rotor 50 , are angularly rigid under the effect of the application of this torque, which rotates the rotor 50 .

Furthermore, it should be pointed out that the elements of the second connecting means 58 , which are involved in the torque transmission between the drive member 24 and the rotor 50 , are not radially deformable under the effect of the application of this torque, which rotates the rotor 50 .

Finally, it should be noted that the complementary grooves 136 , 138 can slide axially one below the other, thereby making it possible to remedy changes in the relative axial position of the clutch cover 38 and the rotor 50 which result from dimensional deviations of the elements forming the force transmission arrangement 20 create.

The drive member and the rotor connecting second connecting means shown in FIGS. 18 and 19 have been shown 58 of a power transmission arrangement for a motor vehicle according to a sixth embodiment of the invention.

In this case, the second connecting means 58 comprise a first carrier for clamping members 146 , which is preferably formed by the cover 38 . The clamping members 146 , for example six, are angularly distributed over the cover 38 .

Furthermore, the second connecting means 58 comprise a second carrier 148 of generally annular shape, which carries clamped members 150 . These clamped members 150 , the number of which corresponds to the number of clamping members 146 , are angularly distributed over the second carrier 148 .

Each clamping member 146 interacts with a clamped member 150 by clamping running essentially transverse to the axis of rotation X of the rotor 50 .

The second carrier 148 is fixedly connected to the rotor hub 96 . Thus, the clamping members 146 in the example shown in FIGS . 17 and 18 are non-rotatably connected to the drive member not shown in these figures, and the clamped members 150 are non-rotatably connected to the rotor.

As an alternative, the clamping members 146 can also be connected in a rotationally fixed manner to the rotor, the clamped members 150 then being connected in a rotationally fixed manner to the drive member.

With particular reference to FIG. 19, it can be seen that the clamping members 146 are formed by sheets 152 attached to the cover 38 by conventional means 154 . These angularly distributed blades 152 are each provided with two essentially axially curved ends 152 E.

Each clamping member 146 is delimited by two ends 152 E of two successive blades 152 , these two ends 152 E being elastically deformable so that they form clamping jaws.

The clamped members 150 are formed by essentially axial, thin lugs firmly connected to the second carrier 148 , which are delimited by essentially radial surfaces.

Although the jaws of the clamping members 146 are resiliently deformable to allow clamping of the clamped members 150 , the rigidity of the clamping jaws of these clamping members 146 is high enough that the natural frequency of the system consisting of the rotor 50 and the clamping members 146 is very far from the excitation frequency the internal combustion engine is removed. For this reason, the angular rigidity of all elements of the second connecting means 58 involved in the torque transmission is sufficient to avoid the dangers of introducing rotor resonances mentioned at the beginning of this work.

In the sixth embodiment of the invention, alignment between the axes of rotation of the drive member and the rotor is accomplished by radial displacement of the clamped members 150 between the jaws of the clamp members 146 . This shift occurs with every revolution of the drive member.

It should be noted that the substantially axial clamped members 150 allow remedial action to be taken for changes in the relative axial position of the clutch cover 38 and the rotor 50 that result from dimensional deviations of the elements forming the power transmission assembly 20 .

In Figs. 20 and 21 the drive member and the rotor connecting second connecting means 58 have been shown of a power transmission device according to a seventh embodiment of the invention.

In this case, the second connecting means 58 comprise two pairs of plug-in sectors 154 and receiving sectors 156 (see in particular FIG. 21). The plug-in sector 154 and the receptacle sector 156 of a pair are connected in a rotationally fixed manner to the rotor 50 and the drive member (not shown in FIGS. 20 and 21). As an alternative, the plug-in sector 154 and the receptacle sector 156 of a pair could be connected in a rotationally fixed manner to the drive member or to the rotor.

The plug sector 154 and the receptacle sector 156 of a pair interact by radially sliding into one another. The plug-in sector 154 and / or the receiving sector 156 of each pair can be deformed elastically at an angle, so that the corresponding plug-in sector is clamped at an angle.

The angular plug-in sectors 154 and the receiving sectors 156 preferably each extend essentially over 90 °.

In the example shown in FIGS . 20 and 21, the plug sectors 154 are formed in the rotor hub 96 . The angular ends of each plug sector 154 are delimited by axially open notches 158 formed in the hub 96 of the rotor.

Furthermore, each receiving sector 156 is delimited by a sheet 160 provided with ends 160 E, the ends being essentially radially, elastically deformable in an angular manner so that they form angular clamping jaws which interact with a corresponding plug-in sector 154 .

The sheet 160 is attached to a bracket 164 fixedly connected to the clutch cover 38 by conventional means 162 .

Although the receiving sectors 156 are elastically deformable so that they can clamp the corresponding plug-in sectors 154 , the angular rigidity of the receiving sectors 156 is high enough that the natural frequency of the system consisting of the rotor 50 and the receiving sectors 156 is very far from the excitation frequency of the internal combustion engine ,

In the seventh embodiment of the invention, the alignment between the axes of rotation of the drive member and the rotor takes place in particular by radial displacement of the ends 160 E of the blades in the notches 158 . This shift occurs every revolution of the drive member 24 .

Alternatively, you could arrange 156 rolling means between the contacting angular ends of the plug sectors 154 and recording sectors that replace the rolling contact friction contacts between these sectors 154, 156th

Such rolling means could, for example, comprise a ring which is mounted by means of a sliding or rolling bearing at each angular end of the plug sectors 154 (formed in the rotor hub 96 ) so as to be rotatable about an axis running essentially parallel to the axis of rotation of the rotor. In this case, each end 160 E of the blades is supported on a corresponding rotating ring. By radial displacement in the notches 158 , the ends 160 E of the sheets each roll over a corresponding ring, this ring rotating about its axis with little friction.

It should be noted that the ends 160 E of the blades 160 can slide axially in the notches 158 , thereby allowing for remedial changes in the relative axial position of the clutch cover 38 and the rotor 50 resulting from the elements forming the power transmission assembly 20 to accomplish.

In Figs. 22 and 23 the drive member and the rotor connecting second connecting means 58 are a power transmission arrangement in accordance with an eighth embodiment of the invention.

In this case, the second connecting means 58 comprise a first torque transmission element 166 carried by the rotor hub 96 and a second torque transmission element 168 carried by the clutch cover 38 .

These first 166 and second 168 torque transmission members of generally annular shape are connected in a rotationally fixed manner to the rotor 50 and the drive member, which is not shown in FIGS. 22 and 23. As an alternative, the first torque transmission element 166 could be connected in a rotationally fixed manner to the drive element, the second torque transmission element 168 in this case being connected in a rotationally fixed manner to the rotor.

The second connecting means 58 furthermore comprise split coupling rings 170 with an axis of rotation X1 which runs essentially parallel to the axis of rotation X of the rotor. The rings 170 are arranged radially between the first 166 and the second 168 annular torque transmission members so that they cooperate with the latter like wedge links.

The rings 170 are accommodated in complementary recesses 172 , 174 in the form of annular surfaces opposite the torque transmission members 166 , 168 .

The angular rigidity of the split rings 170 is high, so that the natural frequency of the system consisting of the rotor 50 and the rings 170 is very far from the excitation frequency of the internal combustion engine.

The split rings 170 , on the other hand, have a low radial rigidity, which allows their elastic radial deformation, so that the alignment between the axes of rotation of the drive member and the rotor is favored.

It should be noted that the annular torque transmission members 166 , 168 can slide axially with respect to each other, thereby allowing remedial changes in the relative axial position of the clutch cover 38 and the rotor 50 resulting from dimensional variations of the elements forming the power transmission assembly 20 .

In Figs. 24 and 25 the drive member and the rotor connecting second connecting means 58 are shown a power transmission device according to a ninth embodiment of the invention.

In this case, the second connecting means 58 comprise a first carrier 176 for essentially axial coupling fingers 178 , which are distributed angularly. This generally ring-shaped first carrier 176 is carried by the rotor hub 96 .

The second connecting means 58 further comprise a second carrier, which is formed, for example, by the clutch cover 38 . This cover 38 carries angularly distributed second coupling pins 180 .

Furthermore, the second connecting means 58 comprise at least one metal wire 182 , preferably two metal wires 182 , as shown in FIGS. 24 and 25, which connect the first 178 and second 180 coupling fingers to one another by intertwining them with these fingers 178 , 180 . The two axially abutting metal wires 182 are identical. For this reason, only one of the wires 182 is described below.

With particular reference to FIG. 24, it can be seen that the metal wire 182 forms a loop which alternately delimits radially inner 184 and outer 186 indentations, which interact with the coupling fingers 178 , 180 by being pushed into one another.

The first clutch fingers 178 alternate angularly with the second clutch fingers 180 . The outer indentations 186 cooperate with the first clutch fingers 178 . The inner indentations 184 cooperate with the second clutch fingers 180 .

Three pairs of clutch fingers 178 and 180 have been shown. As an alternative, only two pairs of clutch fingers could be provided, which facilitates radial pivoting.

The angular rigidity of the metal wires 182 is high, so that the natural frequency of the system consisting of the rotor 50 and the wires 182 is very far from the excitation frequency of the internal combustion engine.

However, the radial stiffness of the loop formed by each metal wire 182 is low, which allows elastic radial deformation of each wire 182 and thus promotes the alignment between the axes of rotation of the drive member 24 and the rotor 50 .

It should be noted that the clutch fingers 178 , 180 can slide axially in the indentations 184 , 186 of the wires 182 , thereby remedying changes in the relative axial position of the clutch cover 38 and the rotor 50 that result from dimensional deviations of the elements forming the force transmission arrangement 20 can be.

It can be seen from the advantages of the invention that the second connecting means 58 shown in FIGS. 3 to 25 allow the transmission of a relatively large torque while permitting noticeable relative radial, angular and axial positioning errors of the rotor 50 and the clutch cover 38 .

With regard to the tolerance of the relative axial positioning of the clutch cover 38 and the rotor 50 , FIG. 26 shows means 188 integrated in the second connecting means 58 , which allow the relative axial changes in position to be effectively taken into account during the final assembly of the transmission on the motor. It should be remembered that these changes result from dimensional deviations of the elements forming the power transmission arrangement 20 .

These means comprise two complementary main carriers 190 , 192 , one of which is connected to the clutch cover 38 and the other to the rotor 50 in a rotationally fixed manner. Complementary, axial toothings 194 , 196 are formed on a first main carrier 190 and on a secondary carrier 198 carried by the second main carrier 192 . The secondary carrier 198 is axially slidably attached to the second main carrier 192 and is connected in a rotationally rigid manner to this second main carrier 192 .

An elastic member 200 with axial action, which is carried by the second main carrier 192 , loads the secondary carrier 198 in position for axially sliding the complementary teeth 194 , 196 .

The teeth D of a toothing are preferably delimited by two converging flanks 202 , 204 and are to be inserted into complementary recesses C of the other toothing, the generally "V" -shaped shape of these recesses C being due to the converging flanks 202 , 204 of the adjacent teeth D is limited. The flanks 202 , 204 of a tooth D converge with a greater convergence than that of the flanks towards a pointed end 206 of this tooth, which facilitates the tooth's penetration into the complementary recess. The complementary teeth 194 , 196 ensure a coupling without play, which can generate noise and wear.

When mounting the transmission on the motor, the elastic member 200 maintains a constant pressure between the flanks of the teeth of the complementary teeth, thereby ensuring a play-free connection and compensating for the tolerance of the relative axial positioning of the clutch cover 38 and the rotor 50 .

The angular rigidity of all elements of the second connecting means 58 , which are involved in the torque transmission, is such that the excitation frequency of the internal combustion engine is very far from the natural frequency of the system consisting of the rotor and the elements involved in the torque transmission. The second connecting means 58 shown in FIGS. 3 to 25, on the other hand, have at least two torque transmission elements that can move radially with respect to one another either freely or against a relatively small elastic force, so that the alignment between the axes of rotation of the drive member 24 and the rotor 50 is favored.

Thus, the invention allows compensation for an alignment error between the axes of rotation of the drive member 24 and the rotor 50 while limiting the radial force exerted on the drive member, in particular so that it does not exceed a radial stiffness of 1000 N per mm of displacement.

The invention is not based on those previously described Embodiments limited.

In particular, the carrier 44 of the electric machine is not necessarily formed in one piece.

The electrical machine module preferably forms a whole, which can be preassembled in the power transmission arrangement before the module is installed. If the carrier 44 is made from several parts, however, the electrical machine module can be assembled in several steps during the course of the assembly of the power transmission arrangement.

Furthermore, it could be provided that the rotor and the Stator of the electrical machine carried by different carriers become.

Claims (65)

1. A power transmission arrangement for a motor vehicle, comprising:
a coupling for connecting a rotary drive member ( 24 ) driven by an internal combustion engine to a rotary drive member ( 26 ) for coupling to a gearbox, said drive member ( 24 ) and this output member ( 26 ) rotating about axes essentially parallel to an axial direction (X) rotate,
a module ( 42 ) which comprises a carrier ( 44 ) which carries an electric machine rotor ( 50 ) rotating about an axis running essentially parallel to the axial direction,
first connecting means ( 54 ) connecting two members formed from the carrier ( 44 ) or a stationary housing ( 56 ), and
second connecting means ( 58 ) connecting two links formed from the drive member ( 24 ) and the rotor ( 50 ), respectively, said second connecting means ( 58 ) being involved in the transmission of the torque between the drive member ( 24 ) and the rotor ( 50 ) Elements include
the first ( 54 ) or the second ( 58 ) connecting means permitting radial relative movement between the links connecting them,
characterized in that all elements of the second connecting means ( 58 ) involved in the transmission of the torque between the drive member ( 24 ) and the rotor ( 50 ) are angularly rigid under the effect of the application of the torque driving the rotor ( 50 ). 2. Arrangement according to claim 1, characterized in that the second connection means (58) at least ensure a rigid connection between the drive member (24) and the rotor (50) in a direction perpendicular to the rotational axis of the rotor (50) plane. 3. Arrangement according to claim 1 or 2, characterized in that the first connecting means ( 54 ) comprise at least one clamping member ( 64 ) which cooperates by axially clamping with a clamped member ( 44 B), this clamping member ( 64 ) and this clamped Link ( 44 B) by the two links ( 44 and 56 ) connected by the first connecting means ( 54 ). 4. Arrangement according to claim 3, characterized in that the clamped member ( 44 B) is fixedly connected to the carrier ( 44 ) and comprises at least one elongate recess ( 59 ) through which there is a fixedly connected to the stationary housing ( 56 ) extends axial pin ( 60 ) with a radial play, the clamping member ( 64 ) having a surface ( 62 ) fixedly connected to the stationary housing ( 56 ) for clamping the clamped member ( 44 B) and an elastic element ( 64 ), in particular one Spring washer and / or a plate spring, which acts under axial compression between the clamped member ( 44 B) and a shoulder ( 66 ) of the axial pin ( 60 ). 5. Arrangement according to claim 1 or 2, characterized in that the first connecting means ( 54 ) comprise at least one pair consisting of a plug-in member ( 60 ) and a receiving member ( 44 B), which of the two are connected by the first connecting means ( 54 ) Links ( 44 and 56 ) are worn, the plug member ( 60 ) housed in the receiving member ( 44 B) and by a radially deformable, annular elastic mass ( 68 ) which radially between the plug member ( 60 ) and the receiving member ( 44 B ) is arranged, is connected to this receiving member ( 44 B). 6. Arrangement according to one of the preceding claims, characterized in that the first connecting means ( 54 ) ensure a rigid connection at least in a plane running perpendicular to the axis of rotation of the rotor ( 50 ) between the carrier ( 44 ) and the stationary housing ( 56 ). 7. The arrangement according to claim 6, characterized in that the second connecting means ( 58 ) comprise a clamping member ( 72 ) which cooperates by axially clamping with a clamped member ( 74 ), said clamping member ( 72 ) and this clamped member ( 74 ) are connected in a rotationally fixed manner to the two members ( 24 and 50 ) connected by the second connecting means ( 58 ). 8. Arrangement according to claim 7, characterized in that the clamping member ( 72 ) is rotatably connected to the drive member ( 24 ) and the clamped member ( 74 ) is rotatably connected to the rotor ( 50 ). 9. Arrangement according to claim 8, characterized in that the clamping member ( 72 ) is carried by a cover ( 38 ) for supporting a coupling membrane ( 40 ). 10. Arrangement according to one of claims 7 to 9, characterized in that the clamping member ( 72 ) two, the clamped member ( 74 ) clamping, annular clamping jaws, at least one of which is axially movable, and means ( 81 ) for resiliently retracting each movable Clamping jaw ( 76 ) to the other clamping jaw ( 76 ), which act under axial compression between this movable clamping jaw ( 76 ) and an axially fixed, annular seat ( 78 ). 11. The arrangement according to claim 10, characterized in that the second connecting means ( 58 ) comprise:
Means ( 80 , 82 ) for radially positioning each movable jaw ( 76 ) with respect to the corresponding seat ( 78 ),
Means ( 80 , 82 ) for non-rotatably connecting each movable jaw ( 76 ) to the corresponding seat ( 78 ) and
Means ( 80 , 82 ) for axially guiding each movable jaw ( 76 ). 12. The arrangement according to claim 11, characterized in that the clamping member ( 72 ) comprises two movable clamping jaws ( 76 ) associated with two axially fixed annular seats ( 78 ), wherein the radial positioning means, the means for non-rotatable connection and the means for comprise axial guidance in each of the clamping jaws ( 76 ) formed circumferential notches ( 82 ) which are pushed onto the axial webs ( 80 ) connecting the two axially fixed seats ( 78 ). 13. Arrangement according to one of claims 10 to 12, characterized in that the means for elastically returning each movable jaw ( 76 ) to the other jaw comprise:
a spring washer ( 81 ), in particular a plate spring, which acts under compression between the axially fixed seat ( 78 ) and the movable clamping jaw ( 76 ), and
Means ( 84 , 86 ) for the rotationally fixed connection of the spring washer to the axially fixed seat ( 78 ). 14. Arrangement according to claim 13, characterized in that the means for the rotationally fixed connection of the spring washer ( 81 ) with the axially fixed seat ( 78 ) comprise at least one axial peripheral lug ( 84 ) of the washer ( 81 ) which is in an axially fixed seat ( 78 ) trained complementary recess ( 86 ) is inserted. 15. Arrangement according to one of claims 7 to 14, characterized in that the clamped member ( 74 ) forms a radial flange of a first end of an axial bushing ( 88 ), said clamped flange, which consists in particular of plastic, two axially opposite sides has, which are preferably each covered with a friction lining ( 90 ). 16. Arrangement according to claims 8 and 15, characterized in that the second connecting means ( 58 ) means ( 92 , 94 ) for axially pushing the axial bushing ( 88 ) onto the rotor ( 50 ) and for non-rotatably connecting this bushing to this rotor ( 50 ). 17. The arrangement according to claim 16, characterized in that the means for axially pushing the axial bushing ( 88 ) onto the rotor ( 50 ) and for non-rotatably connecting this bushing ( 88 ) to this rotor ( 50 ) are axial, complementary, projecting and projecting Include grooves ( 92 , 94 ) formed on a portion forming the hub ( 96 ) of the rotor ( 50 ) and on a second end of the axial bushing ( 88 ). 18. The arrangement according to claim 17, characterized in that the projecting grooves ( 92 , 94 ) of the hub ( 96 ) of the rotor ( 50 ) or the axial bushing ( 88 ) are provided with axially converging ends, which mutually angular positioning of the complementary grooves ( 92 , 94 ) favor this hub ( 96 ) of the rotor ( 50 ) and this bushing ( 88 ), which is suitable for axially pushing the complementary grooves ( 92 , 94 ) into one another. 19. The arrangement according to claim 17 or 18, characterized in that the hub ( 96 ) of the rotor ( 50 ) carries a ring ( 98 ) for radially holding the complementary grooves ( 92 , 94 ) in a pushed-together position. 20. The arrangement according to claim 6, characterized in that the second connecting means ( 58 ) comprise an Oldham coupling ( 100 ) which contains the following:
a first ( 38 ) and a second ( 102 ) coupling member, which are rotatably connected to the drive member ( 24 ) and the rotor ( 50 ), and
an intermediate link ( 104 ), which is connected to the first ( 38 ) and the second ( 102 ) coupling link by two connections, which ensure radial translation movements along axes (T1, T2) which run essentially perpendicular to one another. 21. The arrangement according to claim 20, characterized in that the first coupling member forms a cover ( 38 ) for supporting a coupling membrane ( 40 ). 22. The arrangement as claimed in claim 20 or 21, characterized in that the intermediate member ( 104 ) is connected to the first ( 38 ) and the second ( 102 ) coupling member by two sliding connections with axes (T1, T2) running essentially perpendicular to one another, the two sliding connections being formed by pins ( 106 ) carried by the intermediate member ( 104 ) and slidably mounted in ears ( 108 ) carried by the first ( 38 ) and second ( 102 ) coupling members. 23. The arrangement according to claim 22, characterized in that the second connecting means ( 58 ) means ( 110 , 114 ) for axially pushing the second coupling member ( 102 ) onto the rotor ( 50 ) and for non-rotatably connecting this second coupling member ( 102 ) to it Include rotor ( 50 ). 24. The arrangement according to claim 23, characterized in that the means for axially pushing the second coupling member ( 102 ) onto the rotor ( 50 ) and for non-rotatably connecting this second coupling member ( 102 ) to this rotor ( 50 ) are axial, complementary, projecting and Recessing grooves ( 110 , 114 ), which are formed on a ring ( 114 ) which is fixedly connected to a part forming the hub ( 96 ) of the rotor ( 50 ) and on a peripheral contour of the second coupling member ( 102 ). 25. The arrangement according to claim 24, characterized in that the projecting grooves ( 110 ) of the ring ( 114 ) of the hub ( 96 ) of the rotor ( 50 ) or of the second coupling member ( 102 ) are provided with axially converging ends which provide mutual angular positioning the complementary grooves ( 110 , 114 ) of this ring ( 114 ) of the hub ( 96 ) and this second coupling member ( 102 ) favor, which is suitable for axially pushing the complementary grooves ( 110 , 114 ). 26. The arrangement according to claim 20 or 21, characterized in that the intermediate member ( 104 ) is connected by two pairs of diametrically opposed tabs ( 115 ') to the first ( 38 ) and the second ( 102 ) coupling member, the tabs essentially are transverse to the axial direction and are elastically deformable, so that each pair of tabs ( 115 ') allows radial relative movement of the intermediate member ( 104 ) and the coupling member ( 38 , 102 ) to which this pair is connected. 27. The arrangement as claimed in claim 6, characterized in that the second connecting means ( 58 ) comprise annular plug-in claw coupling members ( 116 ) and receiving claw coupling members ( 118 ) which are connected in a rotationally fixed manner to the links ( 24 and 50 ) connected by the second connecting means ( 58 ) , wherein the male claw coupling member ( 116 ) has teeth ( 120 ) which are inserted into the complementary notches ( 122 ) of the receiving claw coupling member ( 118 ) with a radial play and an angular play. 28. The arrangement according to claim 27, characterized in that the plug claw coupling member ( 116 ) by a part forming the hub ( 96 ) of the rotor ( 50 ) and the receiving claw coupling member ( 118 ) by a cover ( 38 ) for supporting a coupling membrane ( 40 ) becomes. 29. The arrangement according to claim 27 or 28, characterized in that the dog clutch teeth ( 120 ) run essentially axially and the complementary dog clutch notches ( 122 ) run essentially radially. 30. Arrangement according to one of claims 27 to 29, characterized in that the second connecting means ( 58 ) comprise means ( 124 ; 126 ) for elastically returning the male dog coupling members ( 116 ) and female dog coupling members ( 118 ) into a relative angular position in which the dog clutch teeth ( 120 ) do not make angular contact with the contours of the dog clutch notches ( 122 ). 31. Arrangement according to claim 29 and 30, characterized in that the means for resiliently returning comprise at least one pair of spring leaves ( 124 ) which are carried by the receiving claw coupling member ( 118 ) and act counter to a tooth ( 120 ) of the plug claw coupling member ( 116 ) Apply angular retraction forces. 32. Arrangement according to claim 31, characterized in that the means for resiliently returning spring leaves ( 124 ) carried by the receiving claw coupling member ( 118 ) and each arranged between two successive notches ( 122 ) of the receiving claw coupling member ( 118 ), each spring leaf ( 124 ) is provided with two ends ( 124 E), which each cooperate with the successive teeth ( 120 ) of the claw coupling member ( 116 ). 33. Arrangement according to claim 29 and 30, characterized in that the means for elastic retrieval comprise an annular spring leaf ( 126 ) which extends in a crenellated manner around the circumference and radial parts ( 126 R) for angular clamping of the dog clutch teeth ( 120 ) and circumferential parts ( 126 T) limited for fastening the spring leaf ( 126 ) to the receiving claw coupling member ( 118 ). 34. Arrangement according to claim 33, characterized in that the peripheral parts ( 126 T) of the spring leaf in axial half-cutouts ( 128 , 130 ) of the receiving claw coupling member ( 118 ) are attached. 35. Arrangement according to claim 6, characterized in that the second connecting means ( 58 ) comprise a first ( 132 ) and a second ( 134 ) annular torque transmission member, which are connected to the two members ( 24 and 50 ) connected by the second connecting means ( 58 ) ) are connected in a rotationally fixed manner, the first torque transmission element ( 132 ) comprising a radially outer contour, on which projecting and projecting axial grooves ( 136 ) are formed, which have a radial play and an angular play with complementary axial grooves ( 138 ) which are connected to a radial inner contour of the second torque transmission member ( 134 ) are formed to cooperate. 36. Arrangement according to claim 35, characterized in that the first ( 132 ) and the second ( 134 ) torque transmission member of a part forming the hub ( 96 ) of the rotor ( 50 ) or a cover ( 38 ) for supporting a clutch membrane ( 40 ) are worn. 37. Arrangement according to claim 35 or 36, characterized in that the second connecting means ( 58 ) comprise means ( 140 , 142 ) for angular braking of the first ( 132 ) and the second ( 134 ) torque transmission member with respect to each other. 38. Arrangement according to claim 37, characterized in that the angular braking means comprise an elastically radially deformable ring ( 140 ) which is carried by one of the torque transmission members ( 132 ) and with a preferably made of plastic ring ( 142 ) which is supported by the other ( 134 ) the torque transmission members are worn, cooperating through friction. 39. Arrangement according to claim 38, characterized in that the friction ring ( 142 ) is carried by the second torque transmission member ( 134 ) and contains projecting and projecting axial grooves ( 144 ) which the projecting and projecting axial grooves ( 138 ) of the second torque transmission member ( 134 ) extend in the axial direction. 40. Arrangement according to claim 39, characterized in that the projecting grooves of the friction ring ( 142 ) are provided with axially converging ends, which mutually angularly position the complementary grooves ( 136 , 138 ) on the one hand of the first torque transmission element ( 132 ) and on the other hand of the friction ring ( 142 ) and the second torque transmission element ( 134 ), which is suitable for axially pushing the complementary grooves ( 136 , 138 ) into one another. 41. Arrangement according to claim 6, characterized in that the second connecting means ( 58 ) a first carrier ( 38 ) for clamping members ( 146 ), which are angularly distributed on this first carrier ( 38 ), and a second carrier ( 148 ) for clamped Links ( 150 ) angularly distributed on this second support ( 148 ) comprise, each clamping member ( 146 ) cooperating with a corresponding clamped member ( 150 ) by essentially transverse to the axis of rotation (X) of the rotor first ( 38 ) and second ( 148 ) beams are rotatably connected to the two links ( 24 and 50 ) connected by the second connecting means ( 58 ). 42. Arrangement according to claim 41, characterized in that the first ( 38 ) and the second ( 148 ) carrier are rotatably connected to the drive member ( 24 ) and the rotor ( 50 ). 43. Arrangement according to claim 42, characterized in that the first carrier for clamping members ( 146 ) forms a cover ( 38 ) for supporting a coupling membrane ( 40 ), the second carrier ( 148 ) from one of the hub ( 96 ) of the rotor ( 50 ) forming part is worn. 44. Arrangement according to one of claims 41 to 43, characterized in that the first carrier ( 38 ) contains angularly distributed blades ( 152 ), which are each provided with two substantially axially curved ends ( 152 E), each clamping member ( 146 ) is delimited by two ends ( 152 E) of two successive blades, these two ends ( 152 E) being elastically deformable so that they form clamping jaws. 45. Arrangement according to one of claims 41 to 44, characterized in that the clamped members ( 150 ) are formed by substantially axial, with the second carrier ( 148 ) fixedly connected lugs, which are delimited by substantially radial surfaces. 46. Arrangement according to claim 6, characterized in that the second connecting means ( 58 ) comprise two diametrically opposed pairs of plug-in sectors ( 154 ) and receiving sectors ( 156 ), the plug-in sector ( 154 ) and the receiving sector ( 156 ) of each pair passing through the two the second connecting means ( 58 ) are connected to members ( 24 and 50 ) connected in a rotationally fixed manner, the plug-in sector ( 154 ) and the receptacle sector ( 156 ) of a pair interacting by radially pushing together, the plug-in sector ( 154 ) and / or the receptacle sector ( 156 ) each pair is elastically deformable at an angle so that the plug-in sector ( 154 ) and the receiving sector ( 156 ) interact by angular clamping. 47. Arrangement according to claim 46, characterized in that the plug-in sector ( 154 ) and receiving sector ( 156 ) of a pair with the rotor ( 50 ) or the drive member ( 24 ) are rotatably connected. 48. Arrangement according to claim 47, characterized in that the receiving sectors ( 156 ) are elastically deformable at an angle, the angular ends of each plug-in sector ( 154 ) being formed by notches ( 158 ) forming part of the hub ( 96 ) of the rotor ( 50 ). be limited. 49. Arrangement according to claim 47 or 48, characterized in that each receiving sector ( 156 ) is delimited by a sheet ( 160 ) which is provided with ends ( 160 E) which are essentially radially bent and elastically deformable at an angle, so that they form angled jaws. 50. Arrangement according to one of claims 47 to 49, characterized in that the receiving sectors ( 156 ) are carried by a carrier ( 164 ) which is fixedly connected to a cover ( 38 ) for supporting a coupling membrane ( 40 ). 51. Arrangement according to one of claims 46 to 50, characterized in that the plug-in angle sectors ( 154 ) and receiving angle sectors ( 156 ) each extend essentially over 90 °. 52. Arrangement according to one of claims 46 to 51, characterized in that rolling means are arranged between the contacting, angular ends of the plug-in sectors ( 154 ) and the receiving sectors ( 156 ). 53. Arrangement according to claim 48 and 52, characterized in that the rolling means comprise a ring which is attached to each angular end of the plug-in sectors ( 154 ) and is rotatable about a rotation substantially parallel to the axis of rotation of the rotor ( 50 ), each end ( 160 E) the blades are supported on a corresponding rotating ring for the system. 54. Arrangement according to claim 6, characterized in that the second connecting means ( 58 ) comprise:
a first ( 166 ) and a second ( 168 ) annular torque transmission member, which are non-rotatably connected to the two members ( 24 and 50 ) connected by the second connecting means ( 58 ), and
split clutch rings ( 170 ) with axes of rotation (X1) substantially parallel to the axis of rotation (X) of the rotor ( 50 ), arranged radially between the first ( 166 ) and the second ( 168 ) annular torque transmission member and in complementary recesses formed in annular surfaces ( 172 , 174 ) opposite this first ( 166 ) and second ( 168 ) annular torque transmission member. 55. Arrangement according to claim 54, characterized in that the first ( 166 ) and the second ( 168 ) torque transmission member of a part forming the hub ( 96 ) of the rotor ( 50 ) or a cover ( 38 ) for supporting a clutch membrane ( 40 ) are worn. 56. Arrangement according to claim 6, characterized in that the second connecting means ( 58 ) comprise:
a first bracket ( 176 ) for substantially axial first clutch fingers ( 178 ) angularly distributed on this first bracket and a second bracket ( 38 ) for substantially axial second clutch fingers ( 180 ) angularly distributed on this second bracket , said first ( 176 ) and this second carrier ( 38 ) being connected in a rotationally fixed manner to the two links ( 24 , 50 ) connected by the second connecting means ( 58 ), and
at least one metal wire ( 182 ) which connects the first ( 176 ) and the second ( 180 ) coupling fingers by intertwining them with these fingers. 57. Arrangement according to claim 56, characterized in that the metal wire ( 182 ) forms a loop which alternately delimits radially inner ( 184 ) and outer ( 186 ) indentations along its contour, which are pushed together by the two carriers ( 176 , 176 , 38 ) interact with the clutch fingers ( 178 , 180 ). 58. Arrangement according to claim 56 or 57, characterized in that the second connecting means ( 58 ) comprise two axially abutting coupling metal wires ( 182 ). 59. Arrangement according to one of claims 56 to 58, characterized in that the first carrier ( 176 ) is carried by a part forming the hub ( 96 ) of the rotor ( 50 ) and the second carrier a cover ( 58 ) for supporting a coupling membrane ( 40 ) forms. 60. Arrangement according to one of claims 6 to 59, characterized in that the second connecting means ( 58 ) comprise the following:
two complementary main carriers ( 190 , 192 ), one of which is connected to the drive member ( 24 ) and the other to the rotor ( 50 ) in a rotationally fixed manner,
complementary axial sets of teeth (194, 196) which are formed on a first main beam (190) and on a carried by the second main carrier (192) secondary beams (198), said secondary beam (198) on the second main support (192) axially slidably attached and connected to this second main support ( 192 ) in a rotationally rigid manner,
an elastic member ( 200 ) with axial action, which is carried by the second main carrier ( 192 ) and loads the secondary carrier ( 198 ) in position for axially sliding the complementary teeth ( 194 , 196 ). 61. Arrangement according to claim 60, characterized in that each toothing ( 194 , 196 ) is provided with teeth (D) which are each delimited by two converging flanks ( 202 , 204 ) and in complementary recesses (C) of the other toothing ( 196 , 194 ), each recess (C) having a generally "V" -shaped shape, which is delimited by the converging flanks ( 202 , 204 ) of the adjacent teeth (D). 62. Arrangement according to claim 61, characterized in that the flanks ( 202 , 204 ) of a tooth (D) converge with a stronger convergence than that of the flanks towards a pointed end ( 206 ) of this tooth, as a result of which the tooth penetrates into the complementary deepening is facilitated. 63. Arrangement according to one of the preceding claims, characterized in that the module also contains an electrical machine stator ( 48 ) which is carried by the same carrier ( 44 ) as the rotor ( 50 ). 64. Arrangement according to one of claims 1 to 62, characterized in that the module also contains an electrical machine stator ( 48 ) which is carried by a separate carrier and the carrier ( 44 ) of the rotor ( 50 ). 65. Arrangement according to one of the preceding claims, characterized in that the carrier ( 44 ) consists of two or more individual parts.