ES2310657T3 - ASSEMBLY OF ROTATING ELECTRIC MACHINE FOR AUTOMOBILE VEHICLES. - Google Patents

Abstract

The invention relates to a rotating electrical machine assembly (2) for a motor vehicle. The invention comprises a rotor (6) surrounded by a stator (5) which is solidly connected to a spacer (61) that is disposed between the casing (62) of the engine of the motor vehicle having a crankshaft (11) and a dome (14). The invention is characterised in that the dome (14) is used to house the casing (3) of a hydrokinetic coupling device comprising an axially-projecting centring nozzle (30) with a closed free end. Moreover, the invention is characterised in that a first drive unit (12) connects the crankshaft (11) of the engine of the vehicle to a hollow rigid support (13) bearing the rotor (6) and in that a second drive unit (15, 4) is connected to the casing (3) of the hydrokinetic coupling device. The invention is further characterised in that: said two drive units (12, 15) are interconnected by means of a link comprising complementary forms (241, 341) consisting of an axially-oriented contour (241) which is supported by the first drive unit (12)and which co-operates in a complementary manner with an axially-oriented counter contour (341) which is supported by the second drive unit (15, 4), and in that the contour and the counter contour penetrate the support.

Description

Rotating electric machine assembly for motor vehicles

Technical Field of the Invention

The present invention relates to an assembly of rotating electric machine mounted on the transmission line of movement between the internal combustion engine of a vehicle automobile and a motion gearbox comprising this motor vehicle

State of the art

This machine comprises, in a known manner, a fixed stator surrounding a rotor with the presence of an air gap between the inner periphery of the stator and the outer periphery of the rotor, as described in the document FR-A-2,782,355.

In this document, the machine's rotor is carried by a steering wheel of solidarity drive in rotation with the internal combustion engine crankshaft. This flyer is in solidarity with the reaction plate of a friction clutch that It comprises a friction disk, called clutch friction, provided with an internally grooved hub for connection in rotation with the input shaft of a gearbox manual or robotic control. The friction clutch is an element of cutting and starting the motor of the motor vehicle.

In the clutch engaged position, the movement is transmitted from the crankshaft to the input shaft of the case of speeds, while in the clutch removed position, a cut is made in the transmission of movement between the crankshaft and said input shaft to change the ratio of speeds. When the gearbox is in a position of neutral, the vehicle's engine can be started because it is not He transmitted no movement to the wheels of the vehicle. Is the same With an automatic transmission transmission case.

In this case, the input tree connects to a hydrokinetic coupling apparatus.

More specifically, as seen in the Figure 1, a hydrokinetic coupling apparatus 1 comprises a adjusted annular housing 3 comprising two parts 300 and 301 connected between them by means of a welding cord 303. A 300 of these parts have pallets for the formation of a thrust wheel, while the other part 301 carries, by a part, axially protruding and internally covered covers 31 threaded for connection with a rotating connection arm with the crankshaft of the vehicle and, on the other hand, a centering pin 30 protruding for centering with respect to the crankshaft.

Inside the crankcase set 3 full of oil is a vane turbine wheel 210 fixed, here by riveting, in an internally grooved bucket 211 for its rotating connection with input shaft 201 of the box Automatic motion transmission, as seen in 340 the sump. A bell 14 is fixed tightly in this crankcase 340. The vanes of the turbine wheel 210 face the paddles of the thrust wheel 300 so that when the crankcase 3 It is driven in rotation by the crankshaft, the thrust wheel 300 rotates the wheel of turbine 210 and shaft 201 in rotation oil circulation between the vanes. This circulation of oil causes a slight swelling of the crankcase 3. Wheels 210, 300 they belong, in a known way, to a torque converter, of so that the apparatus 1 also comprises a reaction wheel 220 connected to a reaction sleeve 222 by means of a freewheel 221. In addition, a blocking clutch 200 called here is provided "Lock-up." This clutch comprises a piston 203 that carries a friction liner 204 and is connected by a 205 torsion damper or rigidly, to a hub 211.

Knowing this, particularly after vehicle start, at a certain or predetermined speed clutch 200 is pressed; the lining 204 is pressed then between the piston 203 and the transverse wall facing the part 301 to eliminate the phenomenon of sliding between Wheels 300, 210 and thus reduce vehicle consumption.

The bell 14 is intended to be fixed on the crankcase of the internal combustion engine of the vehicle and presents for this effect a flange with steps 141 for mounting elements of fixing, such as fixing screws, with the interposition in this crankcase most often of a brace.

In this type of embodiment, pin 30 is closed at its free end and cannot therefore be crossed by a led tree, as described in figure 12 of EP document A 0 901 923.

In figure 12 of this document the assembly is axially uncomfortable.

Object of the invention

A problem arises then to mount of compact way the rotor of the rotating electric machine in the motion transmission line between the engine crankshaft internal combustion of the motor vehicle and the crankcase Hydrokinetic coupling.

The present invention aims at solve this problem in a simple and economical way.

According to the invention, a machine assembly rotating electric for a motor vehicle comprising a rotor surrounded by a stator integral to an interposed brace between the crankcase of the internal combustion engine of the vehicle car, which features a crankshaft and a bell, is characterized due to the fact that the bell serves as housing for the crankcase fitting of a hydrokinetic coupling apparatus comprising a centering pin that protrudes axially and is closed in its free end, due to the fact that a first actuator connects the crankshaft of the internal combustion engine of the motor vehicle with a rigid support that carries the rotor of the electric machine rotating, due to the fact that a second actuator is connected to the crankcase of the hydrokinetic coupling apparatus, due to the fact that the two actuators are connected to each other by a cooperative connection of forms comprising an outline of axial orientation carried by the first cooperating actuator of complementary way with an opposite contour of axial orientation carried by the second actuator, due to the fact that the support rigid is hollow and because of the fact that the contour and the opposite contour penetrate inside the support.

Thanks to the actuators, the rotor support and to the contours, a simple and fast assembly is obtained, allowing to obtain a precise air gap between the stator and the rotor.

This assembly is also axially compact, because of the fact that the contour and the opposite contour They penetrate the rigid support.

More specifically it is mounted on board, by a part, the first actuator equipped with the rotor and the contour on the crankshaft of the motor vehicle and, on the other hand, the second actuator equipped with the opposite contour on the crankcase of the hydrokinetic coupling apparatus. Then it is done a telescopic type assembly between the contour and the contour opposite, being one of these contours of the male type and another of the female type This telescopic assembly is done by approximation relative axial of the crankcase of the hydrokinetic coupling apparatus and the hood with respect to the crankcase of the vehicle's engine. After this assembly, quickly and simply fits the male contour In the female contour.

These contours are for example of the type of multiple teeth or grooves; the protrusions of one of the contours that penetrate in a complementary manner in the gaps of the other contour. Protruding teeth or hollow grooves that have advantageously a trapezoidal contour. Alternatively these Contours are of the polygonal type. Alternatively, these contours They have one or two chamfers.

It will be appreciated that the crankcase of the hydrokinetic coupling apparatus, in particular, the pin closed from this one, and the crankshaft. The bell is also unchanged and The rotor can have the radial height required for a good result of rotating electric machine.

Advantageously, the second actuator is axially flexible to filter, in particular, vibrations axial and absorb deformations, in particular swelling, in operation of the coupling housing hydrokinetic

Advantageously, to reduce axial volume of the assembly, the contour and the opposite contour are established so least for the most part inside the bracket so hollow

According to other features of the invention:

For reduction of mass, axial volume, in particular, of the support, and the formation of a housing for the contour and the opposite contour, the support being rigid in shape hollow and presenting on its outer periphery an annular skirt of axial orientation that constitutes a mounting area for the rotor;

For cost reduction and reduction of the number of parts, said support constitutes a first part of the first actuator, being only one that has with the first actuator;

To better support the rigid support and the rotor, the first actuator is rigid and comprises a second part center of transversal orientation with respect to the axis of axial symmetry comprising said assembly;

In a simple and economical way, the contour belongs to an annular projection of axial orientation integral with central way with the second part of the first actuator;

In a simple and economical way, the contour opposite belongs to an annular extension of axial orientation, which it has a fixing collar that protrudes radially from the central part of the second actuator;

To reduce the number of pieces and the time of final assembly, the second actuator consists radially of a protruding collar resulting from an annular orientation extension axial bearing the opposite contour; fixing said collar on the crankcase of the hydrokinetic coupling apparatus, so that the extension forms a single piece with the second actuator;

For a good centering, the extension is mounted centered on the centering pin of the coupling apparatus hydrokinetic;

To absorb crankcase deformations of the hydrokinetic coupling apparatus, the second actuator is axially flexible and fixed on its outer periphery over solidarity clamping covers of the crankcase hydrokinetic coupling or directly on said crankcase for use of an apparatus of the normal type and dampen the axial vibrations;

To facilitate the assembly of the assembly, it produce centering covers respectively between the support  and the internal combustion engine crankcase of the motor vehicle and the bell;

To get an even more precise air gap between the stator and the rotor, a centering sheet is produced between the support and a joint extension with the second actuator; the extension having the opposite contour while a bearing is interposed, such as a ball bearing, radially between a hub integral with the centering sheet and the extension;

To better filter the vibrations, the contour belongs to a torsion damper provided with elastic means of circumferential action;

The torsion damper is connected to the rigid support

The contour is thus rigidly linked or elastic to the first actuator.

Brief description of the drawings

The attached description illustrates the invention taking into account the attached drawings, in which:

- Figure 1 is an axial section view partial of a hydrokinetic coupling apparatus conventional;

- Figure 2 is an axial sectional view of a rotating electric machine assembly according to the invention before of the hood assembly of the hydrokinetic coupling device in the crankcase of the internal combustion engine of the vehicle car;

- Figure 3 is a view similar to Figure 2 after mounting the coupling device hood with the internal combustion engine crankcase motor vehicle;

- Figures 4, 5-6, 7-8, 9 are views similar to figures 2 and 3 for respectively a second, a third and a fourth example of embodiment according to the invention.

Description of preferred embodiments of the invention

In the illustrated figures the elements similar will be indicated with the same reference numbers. By Simplicity grounds are shown in Figures 2 to 9 a part of the fitted crankcase 3 of the hydrokinetic coupling apparatus (the which carries the centering pin 30 protruding axially) and a part of bell 14.

In the first embodiment according to the invention of figures 2 and 3, is indicated by the number of reference 2 an axially interleaved rotating electric machine between the internal combustion engine of a motor vehicle and a Hydrokinetic coupling apparatus coupled with the shaft entry, described in figure 1, of an automatic box of motion transmission, which comprises this vehicle car.

The rotating electric machine 2 is here from asynchronous type and comprises a stator 5 surrounding a rotor 6. The Stator and rotor are coaxial annular and have a known way a body or core in the form of a package of plates. The rotor body 6 is shaped to mount a squirrel cage 60, while the body of the stator 5 comprises slots, for example semi-closed, for mounting electrical conductors placed to form the windings of 8 induced machine. These conductors belong to windings classic threads or consist of bars, for example of pins in U shape, as described in the document US-A-2,928,963, the machine being of the polyphasic type. In a known way, the windings of induced 8 cross the body of stator 5 and present that they protrude from the outside of the stator body heads called monkeys. From the same way, the squirrel cage 60 extends protruding to the two sides of the rotor body 6.

Stator 5 is carried internally by a ring support 61 internally provided with a housing of 6002 cooling for the circulation of a carrier fluid of heat, which is the cooling fluid of the vehicle's engine, allowing to evacuate the heat and cool the stator. Fixing stator on the inner periphery of the support 61, for example, performed by immobilization.

This axial orientation support 61 is set in the outer periphery, interposing the bell 14 axially between the crankcase 62 of the internal combustion engine of the motor vehicle and hood 14 housing the apparatus of hydrokinetic coupling This bell 14, as seen in Figure 1 is in solidarity with the crankcase of the automatic transmission box motion transmission The vehicle's engine comprises a tree directed in the form of a crankshaft 11, whose free end 111 is conforms to raise, on the outside of the crankcase 62, a first drive actuator 12 connecting crankshaft 11 with a bracket rigid 13 bearing the rotor 6 of the machine 2. This support 13 It has a hollow shape to reduce the axial volume of the way described below.

Here, the actuator 12 is rigid and is the same in all figures 2 to 9. This actuator 12 raises, here in its outer periphery, the support 13 for the rotor 6. The actuator 12 and the support 13 are annular. The axial axis of symmetry of crankshaft 11 aligns with that of the input shaft, of the type driven, automatic transmission transmission case visible in figure 1, so that an axis of X-X axial symmetry constituting the axis of rotation of the crankshaft 11, of the driven shaft of the automatic transmission motion transmission and rotor 6.

The bell 14 surrounds the crankcase 3, here metallic, of the hydrokinetic coupling apparatus. Some screws do not visible guarantee the fixing of bracket 61. These screws they have a head that rests on a radial edge, which presents bell 14 at its free end. The screws cross the edge of bell 14 in favor of steps 141 of figure 1 and the support to screw on the threads of the crankcase 62 and tighten the support between bell 14 and crankcase 62. Thus, it is intended that the centering covers 161 of the support 61 carried in the figures illustrated, by support 61, or in an alternative respectively by the bell 14 and by the crankcase 62 of the engine of the vehicle, here at the rate of two decks 161 diametrically opposed carried by the support or respectively by the crankcase 62 and the bell 14. In an alternative, support 61 has only one, the crankcase 62 or bell 14. In an alternative, it is devoid of cooling housing In an alternative, it is of the type described in figure 21 of the document FR-A-2,782,355, which is done Reference for more details.

The cooling housing 6002 of the support 61 is in the form of a channel, inside which a fluid circulates heat carrier This channel is connected to an inlet tube and a outlet pipe connected here to the engine cooling fluid of the vehicle, as described in the embodiment of the Figures 14 and 15 of the document FR-A-2,782,355, which is done Reference for more details.

The support 61, the stator 5 and the rotor 6 are of annular shape, being mounted coaxially.

There is an annular radial air gap 7 between the internal periphery of the stator 5 and the outer periphery of the rotor 6.

This machine 2 is axially interposed between the crankcase 62 of the vehicle engine and crankcase 3 of the hydrokinetic coupling, that is, between the engine block of the motor vehicle and crankcase 3, here in embedded sheet.

The rigid support 13 presents externally in Figures 2 to 9 an annular skirt of axial orientation. The support 13 is, in this embodiment, only one conducted with the actuator 12. In an alternative, the support 13 is fixed of rigid way, for example by welding, in the first driver type 12 actuator. In all cases, support 13 it is rigidly integral with the actuator 12 and constitutes, in the outer periphery of actuator 12, a first annular part of axial orientation of this axially directed projecting towards the crankcase 3.

The outer periphery of the support 13 constitutes in favor of its skirt an axial orientation mounting projection for rotor 6, here mounted by immobilization on said outgoing. For this purpose the outer periphery of the support 13 advantageously presented, as seen in the embodiment from figures 6 to 9, a stop flange for the sheet package of the rotor 6 at its axial end as close as possible to the crankcase 62 of the vehicle's engine. In an alternative, fixing the package of rotor plates 6 on the mounting projection of the support 13 it is carried out by means of a groove mounting with axial locking by coupling with the other end of the sheet package. In a Alternatively, this assembly is done by welding or by means of a assembly with the help of screws mounted between leather and meat, such as for example in figure 26 of the document FR-A-2,782,355. It is the same assembly of the stator on the inner periphery of the strut 61. The rotor 6 is  it therefore mounts on its internal periphery on the mounting projection of the support. It will be taken into account that the winding 8 referred to in the stator 5 is adjacent to the crankcase 62.

The actuator 12 has a second part annular cross-orientation in the form of a fixing disc 140 equipped with holes (not referenced) for the passage of fasteners 145 of actuator 12 to crankshaft 11. The disk 140 rigidly connects the crankshaft 11 to the support 13 and is radially directed towards the X-X axis. This disc 140 extends perpendicular to the X-X axis and is connects with its outer periphery at the axial end of the bracket 13, with the outer periphery globally in the form of a skirt, the most possible close to the motor 62. In figures 2 to 9, the disk of fixation 140 is thicker than support 13.

This support 13 extends opposite from the disc 140 and thus extends axially towards the crankcase 3. The Second axial end of the sleeve 13 is free.

In figures 2 and 3, the fasteners 145 consist of screws.

In Figures 2 to 7, the support 13 has a constant thickness on the outside of disk 140 and is globally tubular

In figures 8 and 9, the thickness of the support 13 It is not constant in the manner described below. So, the ribs may be provided to reinforce the connection between the support 13 and disk 140.

In all cases and in all figures, the squirrel cage 60 is set radially outside the actuator 12 which is adjacent to the crankcase 62.

The actuator 12 carries a third part 240 provided with a contour 241, here of axial orientation, for the cooperative connection of shapes with an opposite contour 341, here axial orientation, which belongs to a part 4 mounted centered on the outer periphery of the centering pin 30 Closed crankcase free 3. Part 4 is annular and oriented axial. The piece 4 axially extends the protruding pin 30 axially, to use a crankcase 3 of the normal type and consisting therefore in an axial extension mounted centered on the pin 30 of the crankcase 3. Extension 4 is here cylindrical, while that the hollow support 13 delimits a housing in which it penetrates the opposite contour 341.

In figures 2 and 3, as well as in figures 4 at 7, the third part 240 is a solid orientation projection axial and annular, whose axis of axial symmetry is the axis X-X The protrusion 240 is directed axially towards the crankcase 3 being positioned centered on disc 140. The projection 240 has grooves 241 on its outer periphery, which is that is, an external profile of multiple teeth, which constitute the contour mentioned above, performing an alternation of teeth and slots In an alternative, contour 241 is an outline of hexagonal profile with a profile of external lobes, such as a Profile sold under the "TORX" brand. Internal contour opposite 341 is the same.

In the illustrated figures, contour 241 and the opposite contour 341 are axially oriented and consist of grooves or in a teeth with multiple teeth. One of the contours 241, 341 has protrusions (teeth) that penetrate from complementary way in some holes (the grooves) of the other contour 341, 241. The protrusions and the gaps have a shape here trapezoidal In these illustrated figures, the hollow support delimits a housing inside which the contour 241 and the opposite contour 341 for reducing the axial dimension of the assembly according to the invention.

More specifically, the support 13 delimits with the second part 140 of the actuator a cavity into which they penetrate the contours 241, 341.

The rigid actuator 12 is here a single driver; its parts 140, 240, 13 are obtained economically, for example by molding. The first actuator is metallic here. In an alternative, the support 13 and / or the projection 240 are placed with a rigid fixation on the fixing disc 140, for example by welding or riveting.

Thus, to return lighter to actuator 12, alternatively the projection 240 is provided centered in a hole blind. Alternatively, the central hole of the boss 240 is transverse, so that the second part 140 of the actuator 12 It consists of a centrally perforated ring.

It will be noted that in Figures 2 to 5 the support 13 is axially longer than rotor 6 and than boss 240. In Figures 6 and 7, the support 13 is longer than the rotor 6 and more short than axial projection 240. In all cases, the contour 241 and the opposite contour 341 are advantageously established by less for the most part inside the rotor 6 under it.

The inner periphery of the support is not machined 13.

The actuator 12 extends radially in the inside the air gap 7 of the electric machine 2, which is favorable for the reduction of the axial dimension of the assembly of the machine. The disc 140 centrally has a gap 212 annular to the level of its face turned towards the crankcase 62 of the vehicle's engine. An annular flange 213 of axial orientation is thus defined which outwardly delimits the hole 212, and that allows to center the actuator 12 on the crankshaft 11. It is the same in all figures, since that the crankshaft is not modified.

More specifically, the free end 111 of the crankshaft 11 is radially shaped outgoing ring diameter superior to the current part of the crankshaft, and presents some slightly drilled holes for screw mounting 145. This ring 111 is cut at its free end for formation, on the one hand, of an annular projection centering projection axial for the flange 213 of the actuator 12 and, on the other hand, of a transverse support projection for actuator disc 140 12, globally of transverse orientation with respect to the axis X-X The actuator 12, provided with the support 13 in the which rotor 6 is fixed, is simply fixed previously on the crankshaft, that is, before mounting bell 14 to crankcase 62. Thanks to the centering boss of end 111 and the flange 213, a precise air gap 7 is obtained between the periphery external rotor 6 and internal periphery of stator 5.

The crankshaft 11 is here of the normal type, of so that its end 111 centrally presents a cavity centering blind 112 to receive the pin 30 of the crankcase 3 in a assembly of the classic type without electric machine 2. It will be taken in note that the centering cavity 112 is delimited by a chamfer of entrance to facilitate in a classic assembly the adjustment of the pin 30 in cavity 112.

The extension 4 is in figures 2 to 7 of form tubular and presents at one of its ends as close as possible to the crankcase 62, at said free end, a chamfer 43 to avoid any interference with the screw heads 145 and, in consequently, reduce the axial dimension of the assembly that includes the machine 2 axially sandwiched between the casings 62, 3. The other axial end of extension 4 has, on the one hand, internally a decrease in diameter for the formation of a cylindrical centering boss 42 on the outer periphery of the centering pin 30 of the coupling device hydrokinetic and, on the other hand, an annular collar provided with slightly drilled holes for fixing a screw 245 with the interposition of the central part of transverse orientation of a second actuator 15 between the head of the screws 245 and the collar 41.

The inner periphery, that is, the part central, of the actuator 15 is in contact with the face of the collar 41 turned towards the crankcase of the vehicle; screw heads 245 also turning towards the crankcase 62.

Extension 4 is therefore in solidarity with the second actuator 15 by means of screws 245, which pass through the actuator 15 provided with holes for this purpose.

It will be taken into account that a little axial play is present between this actuator 15 and the winding 8 and the cage 60 of the machine 2.

The internal mandrel of extension 4 presents here an intermediate portion of smaller diameter for the formation of the overhang 42, as well as a first portion and a third portion arranged axially on each side of intermediate portion 42.

The first portion comprises contour 341 cited above and extends axially between the free end of the extension 4 and intermediate portion 42. The third portion is extends to the level of the collar 41 in its lower part.

It will be taken into account that pin 30 is coupled with the crankcase 3 and presenting a change in diameter in its free end for the formation of a centering projection for the outgoing 42 of the extension. The pin is cylindrical in shape, being axial orientation and closed at its free end. Alternatively, pin 30 is fixed, for example by welding, on the crankcase 3.

In all cases, the crankcase 3 is waterproof.

Extension 4 presents on its outer periphery three portions of increasing diameter, namely a smaller portion diameter that extends above (outside) the contour 341, an intermediate portion of larger diameter that extends over above the projection 42 and finally a portion of larger diameter  constituted by the outer periphery of the collar 41. The portion intermediate is delimited by the orientation collar 41 transverse and serves as a centering projection on the inner periphery of the second actuator 15 centrally drilled for this purpose.

The second actuator 15 is fine and consists here on a plate, disk-shaped, fixed on its outer periphery on the crankcase 3. In Figures 2 and 3, the actuator 15 presents on its outer periphery an outer ring axially displaced in crankcase direction 3 relative to the central part of the actuator 15, and in this embodiment, it has an axial offset of the external ring to fix it directly by welding on the metal housing 3, so that the presence of the covers 31 of figure 1 is not mandatory. Alternatively, the ring external is fixed by welding on the covers 31, of so that these are not inevitably coupled, and the actuator is, in one embodiment, flat. The lag  axial of the external ring of the actuator 15 makes it possible to avoid interference with the winding 8 of the stator 5 and, consequently, reduce axial dimension.

Alternatively, the covers 31 and fixing of the outer ring of the actuator 15 is carried out on the crankcase 3, similar to the embodiments of the Figures 6 to 9, with the help of fasteners indicated by reference number 45 in these figures 6 to 9, so that the screws, fixed by screwing on the covers slightly perforated 31 protrude axially at the periphery external of the crankcase 3 in the manner mentioned above.

The transverse orientation actuator 15 in This case thus presents some external and internal periphery holes for, respectively, the passage of screws 45 and 245

In figures 6 to 9 the outer periphery of the second actuator 15 moves axially in the direction of the crankcase 62 with respect to the central part of the actuator.

The second actuator 15 is in all cases axially flexible, to absorb axial vibrations and crankcase deformations 3 due, in particular, to inflation of This one in operation.

It will be taken into account that the diameter of the projection cylindrical centering 42 of the extension features a chamfer of input for pin 30, whose outer periphery is in contact intimate with the diameter of the projection 42 of the element of centered.

The 4 multifunction extension is one piece Economical and simple manufacturing. Extension 4, on the one hand, participates in obtaining a precise air gap 7 and, on the other part, allows, in combination with projection 240 and support 13 hollow in outer periphery in the form of a skirt, better occupy the available space in the center of the assembly and the crankcase 3. In In effect, the crankcase 3 has an annular depression 36 in the periphery  external of its pin 30. Moreover, this depression for establish in this collar 41, on which the height depends on the height of this depression, the height less than this. It shrinks like this the axial dimension, the collar 41 being placed approximately in the bottom of depression 36. This collar 41 is split into grooves in the Figures 2 and 3 and is continuous in the other figures.

Alternatively (figures 6 to 9), the part actuator center 15 is in contact with the collar face 41 turned towards crankcase 3 and, more specifically, towards the bottom of annular depression 36. In this case, the screw heads 245 are placed approximately at the bottom of depression 36.

Alternatively, as seen in the Figures 4 and 5, the collar 41 of the extension is fixed directly on the outer edge 37 of depression 36, for example by welding, which is performed between this edge 37 and the periphery collar 41. Collar 41 comes into contact locally the bottom of depression 36. Collar 41 is then the actuator of extension 4, which reduces the number of pieces. This type of realization is applicable to the other embodiments of the invention.

In Figures 2 to 7, extension 4 is placed in the annular cavity delimited by the support 13, constituting the disk 140 the bottom of the cavity, and the central projection 240. The assembly is easy, since after mounting bell 14 with the crankcase 62, the female grooves 341 of axial orientation are placed  of extension 4 on the axial grooves male grooves complementary to projection 240, so that extension 4 is linked in rotation through a cooperative connection of forms with the first actuator 12 of the conductor type, and is connected to the crankcase 3 by the second actuator 15 of the driven type.

Well understood, you can reverse the structures Thus, alternatively, the slots 341 are of the type male, being provided on the outer periphery of extension 4, while slots 241 are of the female type, which are provided in a cylindrical central hole, blind or through, of the projection 240 axial orientation. This type of embodiment is visible in figures 8 and 9. In this case, extension 4 is solid and presents at its axial end adjacent to collar 41 a blind annular hole 400 for the formation of the annular projection 42 of axial orientation that cooperates in centering with the periphery external of pin 30. In these figures 8 and 9, slots 241 belong to a torsion damper in the manner described to continuation.

The diametral dimension of machine 2 depends, in particular, the applications and the power of it. Is the same as the axial length of the machine 2 and, consequently, of extension 4. Thus, there is an axial play between the protrusion 240 and pin 30, as seen in figure 3, so that the length and dimensions of slots 241, 341 are calculated in consequence. Thus, movements are also taken into account crankshaft axial; All that depends on the applications.

Thanks to the 12, 15 drilled actuators of centered way, to support 13, projection 240 and extension 4, you get a precise air gap 7 and as small as possible, so as a good mechanical behavior of the crankshaft. The results of machine 2 are increased, axial vibrations are filtered well  generated by the crankshaft and the operating deformations of the crankcase 3.

In a known way, a crankcase of oil 163 in the lower part of the crankcase 62. This crankcase oil 163 is provided with a protruding transverse edge 164 provided with an opening 165 to allow, in a classic assembly without rotating machine 2, access to the fixing elements of the crankcase connection plate 3 to crankshaft 11. Thanks to the invention reduces the final assembly time, since it couples the opposite contour 341 of the extension 4 integral in rotation with the crankcase 3 with the contour 241 of the projection integral with its own actuator 12 attached to the crankshaft, so that it is no longer used the opening 163.

Machine 2 has several functions. It constitutes an alternator-shaped current generator for the elements of vehicle consumption and also a start for the vehicle. It allows you to stop the vehicle's engine at a traffic light and return it to boot then. It also allows to avoid an engine draft of the vehicle, providing additional energy for this purpose. The machine in one embodiment works with a motor electric auxiliary, for example, to drive the air conditioning device compressor when the vehicle is stopped at a traffic light and with the internal combustion engine arrested.

The armature windings 8 are to be, in particular, connected to an electronic management unit and command that receives information regarding rotation speed of the crankshaft 11 or of the crankcase 3 and that of the input shaft of the automatic box.

All machine functions are described, for example in the documents FR-A-2,782,355 and WO 98/05882, at which reference is made.

The assembly of the rotating electric machine 2 of figures 2 and 3 refers to the previous formation of two assemblies, namely, on the one hand, mounting on end 111 of the crankshaft 11 of the first actuator 12 provided with the projection 240 of contour 241 and rotor 6 on the outer periphery of support 13 and, on the other hand, the assembly of contour extension 4 341 opposite on the crankcase 3. This last assembly comprises the following stages:

a) mounting extension 4 on pin 30 by axial coupling of the projection 42 on the outer periphery of pin 30 and fixing of the inner periphery of the second actuator 15 on collar 41 with the help of screws 245 or other fasteners;

b) fixation of the external periphery of the second actuator 15 on the crankcase by welding or on the covers 31 by welding or screw support preferably prefabricated on the actuator 15.

The embodiment of figures 4 and 5 is more simple, since the extension that constitutes the second actuator 15 is performed in a single fixing operation on the crankcase 3. Mounting the extension of figures 6 to 9 on the crankcase 3 will be described below.

In figures 2 to 9, the one part is mounted tie 61 on the crankcase 62 with the help of the covers 161, carried by the shoulder 61 or alternatively by the crankcase 62, and, on the other hand, the actuator 12, provided with the rotor 6 and the projection 240, on the crankshaft 11, which makes it easier by the consequently the assembly, since the tie rod is carried by the crankcase 62, so that bell 14 is less heavy.

An axial approach is then made relative of bell 14 with respect to engine housing 62 with axial coupling in the holes of the hood 14 of the decks 161, preferably diametrically opposite, referred to by tie rod 61 and axial contour coupling opposite 341 of the axial extension 4 to the contour 241 of the projection axial 240.

Finally, the strap 61 is fixed on the bell 14 and crankcase 62 with the help of screws or bolts not represented.

In an embodiment not shown, assembles the assembly of the strut assembly 61 and the stator 5 on the bell 14 by axial coupling of the strap 61 on the centering covers 161, preferably diametrically opposite, carried by bell 14 or shoulder 61.

It will be taken into account that part of the axial play within the coupling device hydrokinetic, so that the crankcase 3 can move axially

Thus, centering covers 161 are carried by the crankcase 62, 3 or the strap 61. Alternatively, a series of the covers are carried by the strap and the other series by one of crankcase elements 62 or bell 14. All combinations are possible; the covers 161 that penetrate a complementary calibrated step preferably provided with a entrance chamfer.

Preferably, the collar 41 has minus a centering pin that penetrates a hole complementary to actuator 15 for the placement of this actuator 15 on extension 4 and to facilitate then fixing screws 245.

Also, the end 111 of the crankshaft 11 it has, in one embodiment, at least one pin of centered that penetrates in a complementary way in a hole in the disk 140 of actuator 12 for mounting this actuator 12 on end 111 and facilitate the mounting of screws 145. The pins are housed in associated holes for the formation of positioning slots. Any other is possible shape of the positioning slots, which form adjustment means angular between the pieces in question.

Screws 245 and 145 are mounted here on a average circumference of the same diameter. It will be taken into account that brake discs can be associated with screws 145 and 345, as seen for example in figures 6 to 9.

Alternatively, instead of screws 45, 145, 245 can use nuts that are screwed respectively on threaded stems that protrude axially from the covers 31, free end 111 of the crankshaft and collar 41.

The fixations mentioned above are detachable Alternatively, screws 145 and / or 245 are replaced by non-removable fasteners, for example by riveting or welding.

Alternatively, one of the fixings 45, 145, 245 is removable and the others cannot be disassembled.

Alternatively, none of the fixings are They can disassemble.

Alternatively, actuator fixing 12 on end 111 is done with the help of a single screw central.

In Figures 6 to 9, the outer periphery of the rotor 6 extends over a diameter circumference globally equal to the average diameter of the circumference of placement of screws 45 and covers 31.

Alternatively, the outer periphery of the rotor 6 extends over a circumference of diameter smaller than average diameter of the screw placement circumference 45 and of covers 31. In Figures 2 and 3 it is extended radially on the outer periphery of the rotor 6, which extends on a circumference of diameter smaller than the average diameter of the outer peripheral ring of the second actuator 15. In all cases, the rotor 6 is placed, at least for the most part, in the bottom (the inside) of the average diameter of the placement circumference of screws 45 and covers 31 or of the outer peripheral ring of the second actuator 15, of so that the rotor inertia is reduced, as well as the mass of the support 13.

In figures 6 to 9, the crankcase 3 carries a receiver 32, for example to pick up the rotation speed of the crankcase 3 and, consequently, of the crankshaft 11 or to regulate the vehicle ignition or for vehicle engine control car. Receiver 32 is associated with a sensor that sends information to the electronic command and management unit of stator windings 8 5. It can be the same in the other figures.

In these figures 6 to 9, the air gap 7 is Even more accurate.

More specifically, the strap 61 is mounted centered on a centering flange 600 that extends transversely with respect to the X-X axis of symmetry axial assembly according to the invention.

This flange 600 is drilled centrally for the step of extension 4 and presents on its outer periphery 601 calibrated holes for mounting covers 161 of centered solidarity with the strap 61. Alternatively, in the way cited above, the covers are carried by bell 14 or by bell 14 and tie 61.

Thus, the flange also has other holes not visible for the passage of the fastener fasteners 61 to bell 14.

In its inner periphery this flange 600 it has a cylindrical hub 602 of axial orientation directed towards the crankcase 62 and, consequently, towards the free end of the extension 4.

The hub 602 is extends more axially than the extension 4. The inner periphery of hub 602 serves as a projection of assembly for a radially produced bearing 603, that is, interposes radially between the outer periphery of the extension 4 and the inner periphery of the cube 602.

The bearing 603 is, in one embodiment, a smooth transport. In figures 6 to 9 it is a bearing from balls to a row of balls; alternatively, two rows of balls.

Here, extension 4 presents a projection of stop (not referenced) on its outer periphery for blocking axial in one direction of the inner ring of bearing 603. The butt protrusion is formed in favor of a diameter variation in the outer periphery of the extension 4. The position of this projection is determined to avoid any interference between the periphery centering flange 600 and extension collar 41 4. Retaining washers (not referenced) are mounted on a throat made in the outer periphery of extension 4 for axial locking in the other direction of the inner ring of the bearing 603.

The cube 602 presents at its most distant end of collar 41 a transverse edge 604 directed towards the shaft X-X and that forms a stop projection to fix axially in one direction the outer ring of the ball bearing 603. In the other axial direction, the outer ring of bearing 603 it is fixed by means of retaining washers (not done reference) mounted on a throat in the periphery internal of the cube 602.

Thus, some washers of retainer to fix the bearing rings 603 axially in Both sense. Alternatively, the edge 604 is fixed by welding on hub 602.

Alternatively, the outer ring of the bearing 603 is one piece with hub 602.

Thanks to bearing 603 and flange 600, the tie 61 and extension 4 are positioned correctly, so that the air gap 7 is even more precise.

The assembly is carried out in the manner mentioned above, by previously mounting the strap 61 on the crankcase 62 and the assembly of the rotor 6, the support 13 and the actuator 12 on the crankshaft.

The actuator 15 is mounted on the collar 41 with the help of screws 245, then the periphery is fixed external of the actuator 15 on the covers 31 with the help of screws 45.

The bearing 603 is mounted on the hub 602, and the inner ring of bearing 603 is then coupled onto extension 4 until it makes contact with the shoulder boss. TO Next, the lock retaining washers of the inner ring of ball bearing 603. Next, it approaches the bell 14 of the crankcase 62, coupling the slots 341 over slots 241 in figures 6 and 7, and finally the bell on the crankcase 62. In figures 8 and 9 the slots 341 in slots 241 belonging to a shock absorber of torsion 700 of circumferential action described below.

Thus, in Figures 6 to 9, advantageously, the angular adjustment means, such as pins resulting from one of bell elements 14 and flange 600 that penetrate into holes calibrated in other elements bell 14 and flange 600, are placed between bell 14 and flange 600 so that the covers 161 can penetrate the holes of the flange 600. The free end of the extension 4 has in figures 6 and 7 a external diameter less than the external diameter of the extension 4 which defines a mounting projection for the outer bearing ring 603

Also in figures 8 and 9 the free end of extension 4 has grooves in its outer periphery male type 341 penetrating into slots 241 of the female type provided on the internal periphery of a projection 2400.

The protrusion 2400 consists here of a cube that presents slots 241 internally.

The 2400 cube is placed inside the support 13 and, consequently, rotor 6. This hub 2400 is of axial orientation and constitutes the output part of the shock absorber torque 700. The inlet portion of the torque 700 It consists of two steering disks 702 arranged to two sides of a bucket flange 701 integral with the bucket 2400. The address disks 702 surround the hub 2400, allowing a relative rotation movement between the hub and the disks of address. In one embodiment, the flange 701 is single piece the bucket 2400. Alternatively, the flange 701 is fixed on its internal periphery by welding or crimping on the hub 2400

Thus, alternatively, a radially produced annular centering movement between the cube and a first of the address discs. This movement also occurs advantageously axially between this first steering disc and the flange 701 and presents for this purpose an annular piece of cross orientation. In this case, the elastic means of axial action, such as a Belleville disk or a wavy disk, is  placed between the second steering disc and the flange 701 to drive a friction disc in contact with flange 701 and actuate the transverse part of the movement between the first disk Steering and flange. Thus, a disk of distribution, linked in rotation with the second disk of direction, for example with the help of axial legs that they penetrate holes in the second steering disc; sayings elastic means of axial action are axially interspersed between the second address disk and the distribution disk, which in a embodiment serves as a support for the friction disk or It constitutes the friction disk. The means of friction and / or of centered they can then intervene between the flange assembly 701 and the hub 2400 and the steering disks 702.

The flange 701 and the steering discs 702 openings face, here windows, for the housing of elastic elements 705 of circumferential action. Here the windows are set tangentially; the edges internal windows that are set tangentially with relation to the same internal circumference. The elements Elastic 705 consist here of spiral springs. Alternatively, at least some of these elements 705 They consist of blocks in elastic material. The windows of the address discs 702 and flange 701 have, in a form of realization, the same size. Alternatively, the elements Elastic 705 are mounted without play in the windows of the discs of address 702, without play in some windows of flange 701 and with play in other windows of flange 701 for an intervention stepped elastic elements 705.

Alternatively, housing openings of the elements 705 open outwards and the elements Elastic 705 are curved springs.

Here, rigid support 13 presents internally 706 reinforcements that connect at one of its axial ends to disk 140 of actuator 12. Reinforcements delimit in its other free axial end a transverse projection to support the outer periphery of a first steering disc 702 integral with The second address disk.

More specifically, the axial braces 704 in cover shape interpose axially between the two discs of address 702. These braces are placed on the outer periphery of the address disks 702 and are each traversed by a screw 703. The head of screw 703 rests on the second address disk 702; its inserted part goes through the second address disc 702, the tie rod in question 704 and the first steering disc 702 to be screwed into a thread made in the respective reinforcement 706. The 703 screws thus guarantee the fixing of the steering discs on reinforcements 706, the first address disc 702 resting on the projections of the reinforcements 706. Thus the projection 2400 is connected so elastic with rigid support 13.

Thanks to the torsion damper they filter the vibrations Alternatively, reinforcements 706 are continuous, although that is less favorable for reasons of increasing weight.

The shock absorber 700 is mounted by placing on the inside the support 13 and the rotor 6 axially between the faces axial end of rotor 6.

It will be taken into account that the first one is simplified actuator 12; disk 140 consisting of a simple ring that it carries on its external periphery the support 13.

Alternatively, the address disks 702 they are integral with the cube 2400 and the flange 701 is integral with 706 reinforcements, for example by screwing with the help of screws 703. Alternatively, the elements are suppressed elastic 705 and flange 701, integral with the 2400 hub, is fixed directly on reinforcements 706 with the help of screws 703. The 2400 cube-shaped projection is thus connected in a manner rigid or elastic, by means of an action torsion damper circumferential, to the rigid support 13. This projection is placed radially inside the rotor 6 and, advantageously, axially between the axial end faces of the rotor.

Alternatively, a connection can be provided elastic between the protrusion 240 and the disc 140; The elements elastics of circumferential action intervene between disc 140 and the protrusion 240 presenting for this purpose some accommodations faces.

The outgoing 240, 2400 is thus linked according to the invention rigidly or elastically with the first actuator 12, that is, disk 140 or support 13.

Alternatively, the cooperative connection of forms 241, 341 extends axially more distantly with respect to disk 140.

For example, this connection extends in greater outside of the support 13.

This solution is less advantageous as it increases the axial dimension, in particular, in the shoulder 61.

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References cited in the description

This list of references cited by the applicant is intended solely to help the reader and not It is part of the European patent document. Although it has been put maximum care in its realization, errors cannot be excluded or omissions and the EPO declines any responsibility in this respect.

Patent documents cited in the description

FR 2782355 A [0002] [0031] [0032] [0037] [0080]

EP 0901923 A [0010]

US 2928963 A [0027]

WO 9805882 A [0080].

Claims (17)

1. Assembly of rotating electric machine (2) for motor vehicles, comprising a rotor (6) surrounded by a stator (5) integral with a tie rod (61) interposed between the crankcase (62) of the internal combustion engine of the motor vehicle which has a crankshaft (11) and a bell (14), characterized in that the bell (14) serves as an adjusted housing for the crankcase (3) of a hydrokinetic coupling apparatus comprising a centering pin (30) protruding axially and closed at its free end, due to the fact that a first actuator (12) connects the crankshaft (11) of the internal combustion engine of the motor vehicle with a rigid support (13) that carries the rotor (6) of the rotating electric machine (2), by the fact that a second actuator (15, 4) is connected to the crankcase (3) of the hydrokinetic coupling apparatus, by the fact that the two actuators (12, 15) are connected between yes through a connection of cooperation of forms (241, 341) comprising an axial orientation contour (241) carried by the first actuator (12) cooperating in a complementary manner with an opposite contour (341) of axial orientation carried by the second actuator (15, 4 ), due to the fact that the rigid support (13) is hollow and due to the fact that the contour (241) and the opposite contour (341) penetrate the
support (13). 2. Assembly according to claim 1, characterized in that the contour (241) and the opposite contour (341) are of the type of multiple teeth or grooves. 3. Assembly according to claim 1 or 2, characterized in that the contour (241) and the opposite contour (341) are mounted at least mostly inside the support (13) hollowly. 4. Mounting according to any one of the preceding claims, characterized in that the rigid support (13) is hollow and comprises an annular skirt with an axial orientation in its outer periphery that constitutes a mounting projection for the rotor (6 ). 5. Assembly according to the preceding claim, characterized in that the rigid support (13) constitutes a first part of the first actuator (12), being a single support with the first actuator (12). 6. Assembly according to any one of the preceding claims, characterized in that the first actuator (12) is rigid and comprises a second central part (140) of transverse orientation relative to the axis of axial symmetry comprising said assembly. 7. Assembly according to the preceding claim, characterized in that the contour (241) is part of an annular projection (240) of axial orientation integral with the second part (140) of the first actuator (12). 8. Assembly according to any one of claims 1 to 6, characterized in that the contour (241) is part of an annular projection (2400) of axial orientation connected to the rigid support (13). 9. Assembly according to the preceding claim, characterized in that the contour (241) forms part of the hub (2400) of a torsion damper (700) connected to the rigid support (13). 10. Assembly according to the preceding claim, characterized in that the torsion damper (700) comprises elastic elements of circumferential action (705) mounted in opposite openings made in steering discs (702) arranged on each side of a hub flange (701) and by the fact that one of the steering disc elements (702) - hub flange (701) is integral with the hub (701), while others of the hub flange elements ( 701) - steering disc (702) are fixed in reinforcements (706), if any continuous, which has the rigid support (13) in its internal periphery. 11. Mounting according to any one of the preceding claims, characterized in that the opposite contour (341) forms part of an annular extension (4) of axial orientation centrally mounted on the centering pin (30) of the apparatus for hydrokinetic coupling (1). 12. Assembly according to the preceding claim, characterized in that the extension (4) has a collar (41) projecting radially for the central part of the second actuator (15). 13. Assembly according to the preceding claim, characterized in that the second actuator (15) is axially flexible and is fixed on its outer periphery on fixing covers (31) in solidarity with the housing (3) of the hydrokinetic coupling apparatus or directly, for example by welding, on said crankcase for the use of an apparatus of the normal type and damping axial vibrations. 14. Assembly according to claim 12, characterized in that the second actuator (41) consists of a collar that protrudes radially from the annular extension (4) of axial orientation bearing the opposite contour (341) and by the fact that the collar (41) is fixed on the crankcase (3) of the hydrokinetic coupling apparatus, so that the extension is in one piece with the second actuator. 15. Assembly according to any one of the preceding claims, characterized in that a centering flange (600) acts between the tie rod and an extension (4) integral with the second actuator (15, 41), due to the fact that the extension carries the opposite contour (341), while a bearing (603), such as a ball bearing, is radially interposed between a hub (602) integral with the centering boss and the extension (4). 16. Assembly according to any one of the preceding claims, characterized in that centering covers (161) act between the tie rod (61), and respectively the crankcase (62) of the internal combustion engine of the motor vehicle and the hood (14). 17. Assembly according to any one of the preceding claims, characterized in that the contour (241) and the opposite contour (341) are mostly installed inside the rotor (6) below it.