WO2019154618A1

WO2019154618A1 - Transmission device for a hybrid vehicle

Info

Publication number: WO2019154618A1
Application number: PCT/EP2019/051449
Authority: WO
Inventors: Gilles Lebas; Emmanuel Commeine
Original assignee: Valeo Embrayages
Priority date: 2018-02-12
Filing date: 2019-01-22
Publication date: 2019-08-15
Also published as: FR3077857B1; FR3077857A1

Abstract

The invention relates to a torque transmission device (1) for a motor vehicle, comprising: a torque input element (2); a torque output element (3); a clutch (6) that selectively couples, by friction, the torque input elements (2) and the torque output elements (3); a member (8) for actuating the clutch (6), which comprises a piston (15) moving along an axis B, an actuating rolling bearing (16), and a force-transmission member (17), the force-transmission member (17) being supported on a holding element (23); and a housing (22) arranged so as to at least partially house the above-mentioned elements, a supporting rolling bearing (24). being positioned between the holding element (23) of the force-transmission member (17) and the housing (22), the actuating rolling bearing (16) and the supporting rolling bearing (24) being arranged axially successively along the axis B, and the supporting rolling bearing (24) being provided with an annular notch (70).

Description

Transmission device for a hybrid vehicle

The present invention relates to the field of transmissions for motor vehicles. It relates in particular to a torque transmission device intended to be arranged in the drive train of a motor vehicle, between an internal combustion engine and a gearbox.

It relates more specifically to a torque transmission device for a hybrid type of motor vehicle in which a rotating electrical machine is disposed in the drive chain.

In the state of the art, it is known hybrid motor vehicles comprising a torque transmission device disposed between an internal combustion engine and a gearbox, a rotating electrical machine and a clutch for coupling or uncoupling in rotation a crankshaft of the internal combustion engine to a rotor of the rotating electrical machine. Thus, it is possible to shut down the internal combustion engine at each stop of the vehicle and restart it with the rotating electric machine. The rotating electrical machine can also constitute an electric brake or bring a surplus of energy to the internal combustion engine to assist or prevent it from stalling. When the internal combustion engine is in operation, the electric machine can act as an alternator. The rotating electrical machine can also drive the vehicle independently of the internal combustion engine.

Such a rotating electrical machine may be in line with the torque transmission device, that is to say that the axis of rotation of the rotor of the rotating eclectic machine coincides with the axis of rotation of the transmission device. couple. Alternatively, the electric machine rotating member may be offset relative to the torque transmission device, that is to say that the axis of rotation of the rotor of the rotating electrical machine is offset from the axis of rotation of the torque transmission device.

In the current developments of hybrid vehicles, it is necessary to implement the rotating electrical machine torque transmission device without this does not impact the axial compactness and radial torque transmission device. One of the conditions for the proper functioning of the torque transmission device is the actuation of the clutch which is conventionally performed by an actuating member comprising an axially displaceable piston and a rotary stop made by means of a bearing.

This actuator is conventionally called a "CSC" (Concentric Slave Cylinder) type actuator. Several problems are related to these actuating members of the clutch, namely to transmit an optimal actuating force without losses but also ensure optimal stroke of the piston without impacting the axial and radial dimension of the torque transmission device.

The invention aims to overcome the aforementioned problems by benefiting from a torque transmission device to reconcile the requirements of axial and radial compactness while ensuring optimum transmission of effort between the actuating member and the clutch.

The invention achieves this, in one of its aspects, by means of a torque transmission device, in particular for a motor vehicle, comprising:

a torque input element capable of being coupled in rotation to a crankshaft 15 of an internal combustion engine;

a torque output element capable of being coupled in rotation to at least one input shaft of a gearbox and / or to an electric machine rotating, the torque input member being pivotable relative to the torque output member about an axis of rotation A,

a clutch selectively and frictionally coupling the torque input and torque output elements,

an actuating member of the clutch comprising a piston moving along an axis B parallel to the axis of rotation A, an actuating bearing and a force transmission member for transmitting an actuating force from the piston towards the clutch, the force transmission member being supported on a holding element,

a housing arranged to at least partially enclose the torque input element, the torque output element, the clutch and the actuating member of the clutch, a support bearing is positioned between the holding member of the force transmitting member and the housing, the actuating bearing and the bearing support axially follow each other along the axis B and the support bearing is provided with an annular notch.

Thanks to this architecture, the support bearing is held axially between the holding element and the casing without the intervention of a fastening means such as a circlip, which guarantees the actuator a longer stroke. important and therefore optimized for the transmission of the actuating force from the piston to the clutch.

Annular notch means any type of unhooked in a piece of revolution that can be likened to a groove or a shoulder.

According to one aspect of the invention, the support bearing is composed of an inner ring in contact with the housing and an outer ring in contact with the holding member, the annular notch of the support bearing is located on the outer ring. The notch is preferably machined.

According to another aspect of the invention, the holding element comprises an outgrowth cooperating with the annular notch of the support bearing. According to a feature of the invention, the actuating bearing is also provided with an annular notch.

According to yet another aspect of the invention, the actuating bearing is composed of an inner ring in contact with the piston and an outer ring in contact with the force transmission member, the annular notch of the actuating bearing is located on the outer ring. The notch is preferably machined.

According to another aspect of the invention, the force transmission member comprises an excrescence cooperating with the annular notch of the actuating roller.

According to one characteristic of the invention, the force transmission member comprises a thrust bushing and a diaphragm, the protuberance being located on the thrust bushing.

According to another aspect of the invention, the thrust bushing is forcibly mounted on the outer ring of the actuating bearing.

According to another aspect of the invention, the diaphragm is in contact with the holding member.

According to the invention, the actuating bearing and the bearing support are located radially at the same distance from the axis A.

According to an additional feature of the invention, the actuating bearing and the bearing support are ball bearings.

The invention will be better understood, and other objects, details, features and advantages thereof will appear more clearly in the following description of a particular embodiment of the invention, given solely for illustrative purposes and not limiting, with reference to the appended figures.

FIG. 1 is a sectional view of the torque transmission device according to the invention, - Figure 2 is a sectional view of the torque transmission device according to a second embodiment of the actuating member.

In connection with FIG. 1, a torque transmission device 1 comprising a torque input element 2, coupled in rotation to a crankshaft V of an internal combustion engine (not shown), an output element of FIG. torque 3, rotatably coupled to an input shaft of a BV gearbox.

The torque input member 2 is rotatably coupled to the crankshaft V of the internal combustion engine by fastening means 30 in the form of a screw. Ten screws are required to attach the torque input member 2 to the small V-ring V of the internal combustion engine.

The torque output element 3 is also coupled to a rotating electrical machine via a first connecting means 102 in the form of a chain.

The torque output member 3 has a ring gear 50 on its outer periphery. The ring gear 50 is in contact with the chain. The torque input member 2 pivots relative to the torque output member 3 about an axis of rotation A.

An elastic return member 5 acts against rotation of the torque output member 3 with respect to the torque input member 2. The resilient biasing member 5 is a coil spring.

A clutch 6 selectively and frictionally couples the torque input 2 and torque output elements 3. An intermediate element 7 is arranged between the elastic return member 5 and the clutch 6 to transmit the torque.

An actuating member 8 of the clutch 6 moves along an axis B parallel to the axis of rotation A. The elastic return member 5 and the clutch 6 radially follow each other along an axis R perpendicular to the axis of rotation A.

The actuating member 8, the torque input member 2 and the torque output member 3 succeed one another axially along the axis B.

The elastic return member 5 and the clutch 6 are stacked radially close to the axis of rotation A. The axis R is perpendicular to the axis of rotation A and cuts at the same time elastic return 5 and the clutch 6.

The elastic return member 5, the clutch 6 and the actuating member 8 radially follow each other along the axis R.

The elastic return member 5, the clutch 6 and the actuating member 8 are stacked radially close to the axis of rotation A. The axis R is perpendicular to the axis of rotation A and cut to both the elastic return member 5, the clutch 6 and the actuating member 8.

The torque input element 2 is located between the actuating member 8 and the torque output member 3 along the axis B.

The torque input element 2 comprises an additional mass of inertia 49. This additional mass of inertia 49 is located near the elastic return member 5.

The torque output member 3 includes a torque output hub 4 removably attached to the torque input member 2 and the torque output member 3. This removable function facilitates access. to the fastening means 30. A holding bearing 31 is disposed between the torque output member 3 and the torque input member 2. The holding bearing 31 makes it possible to take up the radial forces transmitted by the drive shaft. BV gearbox input and / or the rotating electrical machine. The bearing bearing 31 is of the double row type of balls. More specifically, the bearing bearing 31 is disposed between the torque output hub 4 and the torque input member 2. The bearing bearing 31 is composed of an inner ring in contact with the hub torque output and an outer ring in contact with the torque input element 2. The bearing bearing 31 is blocked axially by two circlips and two shoulders.

The torque output hub 4 comprises means 36 for compensating for radial and / or axial and / or angular misalignment between the torque input element 2 and the torque output element 3 so that the rotation the crankshaft around the axis of rotation A is transmitted to the input shaft of the gearbox BV without constraints. The torque output hub has a fluted orifice for receiving the input shaft of the gearbox BV.

The torque transmission device 1 comprises a housing 22 arranged to at least partially enclose the torque input element 2, the torque output member 3, the elastic return member 5, the clutch 6, the intermediate member 7 and the actuating member of the clutch 8. The housing 22 is wet, that is to say that the aforementioned wrapped components are in an oil mist or partially immersed.

The casing 22 is composed of a front cover 25 situated opposite the internal combustion engine, a rear cover 26 situated opposite the gearbox BV and a central element 27 connecting the front cover 25 and the cover. 26. The front cover 25, the central element 27 and the rear cover 26 are fixed together by fastening means, for example of the screw or rivet type.

Alternatively, the central element 27 may be integrated at least partially in one of the two covers.

The casing 22 is fixed to the internal combustion engine by means of fixing means, for example of the screw or rivet type. Advantageously, the front cover 25 may be fixed to the internal combustion engine by means of fastening means, for example screw or rivet type. The front cover 25 of the housing 22 has a generally "L" shape, the base of the "L" is located on the side of the axis of rotation A. The piston 15 of the actuating member 8 of the clutch is disposed substantially at the base of the "L" of the front cover 25 of the housing 22.

The clutch 6 comprises an input disk carrier integral in rotation with the intermediate element 7, an output disk carrier integral in rotation with the torque output element 3, a multi-disk assembly 11 comprising at least one friction disk integral in rotation with one of the input and output disk carriers, at least two plates respectively arranged on either side of the friction disk, integral in rotation with the other of the input and output disk carriers . The friction disc has on each of its sides friction linings. The gaskets are fixed to the friction discs by gluing, riveting or overmolding.

In variant not shown, the fittings are fixed on the trays.

The clutch 6 may have an engaged position in which said trays pinch the friction disk and its friction liners so as to transmit torque between the input disk carrier and the output disk carrier. The clutch 6 may also have a disengaged position in which said trays do not pinch the friction disk and its friction linings so as not to transmit torque between the input disk carrier and the output disk carrier.

Each input or output disk carrier can synchronize in rotation all the trays or the set of friction discs. The trays and the disks can cooperate with the input and output disk gates on one of their radial periphery by complementarity of form, the trays and the friction discs can for example be fluted. The trays can be integral in rotation with the input disk carrier and the friction disks can be integral with the output disk carrier. Alternatively, the trays can be integral in rotation with the output disk carrier and the friction disks can be integral in rotation with the input disk carrier. The trays are radially inside the input disk carrier with which they are secured in rotation. The friction discs are radially outside the output disc holder with which they are integral in rotation. The clutch has between two and seven friction discs. The clutch preferably comprises four friction discs. The clutch 6 is of the "normally closed" type. The clutch 6 is wet type and is adapted to be supplied with fluid by a hydraulic pump (not shown).

The actuating member 8 of the clutch 6 comprises a piston 15 moving along the axis B which is parallel to the axis of rotation A, an actuating bearing 16 and a force transmitting member 17 for transmit an actuating force from the piston 15 to the clutch 6.

The piston 15 is supplied with fluid by an external actuator of electro-hydraulic or electro-hydrostatic type (not shown). The piston 15 of the actuating member 8 of the clutch 6 is controlled in position by force measurement through the power consumption of the electric motor of the external actuator. The piston 15 can have a retracted position in which the piston is close to the front cover 25 and an extended position in which the piston 15 is moved away from the front cover 25. As the clutch 6 is of normally closed type, the retracted position of the piston 15 corresponds to the clutch 6 closed and the extended position of the piston 15 corresponds to the clutch 6 open.

The force transmission member 17 comprises a thrust bushing 18 and a diaphragm 19. The actuating bearing 16 is composed of an inner ring 20 in contact with the piston 15 and an outer ring 21 in contact with the piston. thrust sleeve 18.

The actuating bearing 16 is supported by a cup attached to the piston 15. The force transmitting member 17 can be supported on the an inlet disk carrier via a holding element 23. The diaphragm 19 is in contact with the holding element 23.

A support bearing 24 can be positioned between the holding member 23 of the force transmission member 17 and the casing 22 in order to take up the actuating force of said actuating member 8.

The actuating bearing 16 and the support bearing 24 follow one another along the axis B. The bearing support 24 is provided with an annular notch 70. The annular notch 70 is more precisely a shoulder. In variant not shown, the annular notch 70 may be a groove.

The support bearing 24 is composed of an inner ring 47 in contact with the casing 22 and an outer ring 48 in contact with the holding element 23 of the force transmission member 17. The bearing support 24 is locked axially by a circlip in contact with the inner ring 47. The annular notch 70 of the support bearing is located on the outer ring 48. The annular notch 70 is more precisely a shoulder formed on the outer ring 48. notch or shoulder 70 is formed on one side of the support bearing 24 facing the actuating bearing 16.

The holding element 23 comprises a protrusion 71 which cooperates with the annular notch 70 of the support bearing 24. This form of cooperation between the annular notch 70 and the protrusion 71 makes it possible to ensure axial mounting of the support bearing. 24 without encroaching on the piston stroke 15.

The actuating bearing 16 and the bearing support 24 are located radially at the same distance from the axis A. The actuating bearing 16 and the bearing support 24 are ball bearings.

Thus the distance d represents the stroke traveled by the piston 15 of the actuating member. This race corresponds to the distance separating the actuating bearing 16 of the support bearing 24 when the piston

15 is in its retracted position.

The piston 15 of the actuating member 8 of the clutch 6 is disposed on the housing 22. The piston 15 of the actuating member 8 of the clutch 6 is fixed in rotation by means of an anti-rotation system (not shown) The actuating member 8 of the clutch 6 is provided with a stop (not shown) to limit the output of the piston 15.

The piston 15 of the actuating member 8 of the clutch 6 is disposed on the front cover 25 of the casing 22. The front cover 25 of the casing 22 has an external wall located opposite the internal combustion engine and an inner wall located opposite the clutch 6, the piston 15 of the actuating member 8 of the clutch 6 is disposed on this inner wall.

The inner wall of the housing 22 may comprise two annular walls between which is housed the piston 15 of the actuating member 8 of the clutch 6. The piston 15 and the two annular walls of the housing 22 form an actuating chamber suitable for to be supplied with fluid for moving the piston 15. The actuating chamber is sealed and filled with oil. The piston 15 comprises two seals in order to seal the actuating chamber.

The piston 15 is moved axially by variation of oil pressure in the actuating chamber. The piston has a generally "U" shape.

In Figure 2 is shown a transmission device according to a second embodiment.

In this second embodiment, the actuating bearing

16 of the actuating member 8 of the clutch 6 is also provided with an annular notch 72. The annular notch 72 is more precisely a shoulder. In variant not shown, the annular notch 72 may be a groove. The actuating bearing 16 is composed of an inner ring 20 in contact with the piston 15 and an outer ring 21 in contact with the force transmission member 17. The annular notch 72 of the operating bearing 16 is located on the outer ring 21.

In this second embodiment, the actuating bearing

16 and the support bearing 24 each have an annular notch 70, 72. The annular notches 70, 72 are axially facing.

The thrust bushing 18 of the force transmission member 17 comprises an outgrowth 73 cooperating with the annular notch 72 of the thrust bearing 16. This form of cooperation between the annular notch 72 and the projection 73 makes it possible to transmit the axial force of the piston 15 without risk of sliding between the outer ring 21 of the actuating bearing 16 and the thrust sleeve 18 of the force transmission member 17.

Thus the distance D represents the stroke traveled by the piston 15 of the actuating member. This stroke corresponds to the distance separating the actuating bearing 16 from the support bearing 24 when the piston 15 is in its retracted position.

Claims

1. Torque transmission device (1), in particular for a motor vehicle, comprising:

a torque input element (2) capable of being rotatably coupled to a crankshaft (V) of an internal combustion engine;

a torque output element (3), able to be coupled in rotation to at least one input shaft of a gearbox (BV) and / or to a rotating electrical machine, the input element of torque (2) being pivotable relative to the torque output member (3) about an axis of rotation A,

- a clutch (6), selectively coupling and friction coupling the torque (2) and torque output (3) input elements,

- an actuating member (8) of the clutch (6) comprising a piston (15) moving along an axis B parallel to the axis of rotation A, an actuating bearing (16) and a transmission member of force (17) for transmitting an actuating force from the piston (15) to the clutch (6), the force transmitting member (17) being in abutment on a hand element (23). )

a housing (22) arranged to at least partially enclose the torque input element (2), the torque output element (3), the clutch (6) and the actuating member (8). ) of the clutch (6), a support bearing (24) is positioned between the holding element (23) of the force transmitting member (17) and the housing (22),

characterized in that the actuating bearing (16) and the support bearing (24) are arranged axially along the axis B and in that the support bearing (24) is provided with an annular notch (70).

2. Torque transmission device (1) according to claim 1, characterized in that the support bearing (24) is composed of an inner ring (47) in contact with the housing (22) and a ring external (48) in contact with the holding member (23), the annular notch (70) of the support bearing (24) is located on the outer ring (48).

Torque transmission device (1) according to one of the preceding claims, characterized in that the holding element (23) comprises a protrusion (71) cooperating with the annular notch (70) of the support bearing ( 24).

4. torque transmission device (1) according to one of the preceding claims, characterized in that the actuating bearing (16) is also provided with an annular notch (72).

5. Torque transmission device (1) according to claim 4, characterized in that the actuating bearing (16) is composed of an inner ring (20) in contact with the piston (15) and a outer ring (21) in contact with the force transmission member (17), the annular notch (72) is located on the outer ring (21).

6. Torque transmission device (1) according to one of claims 4 to 5, characterized in that the force transmission member (17) comprises an outgrowth (73) cooperating with the annular notch (72) actuating bearing (16).

7. Torque transmission device (1) according to claim 6, characterized in that the force transmission member (17) comprises a thrust bushing (18) and a diaphragm (19), the protrusion ( 73) being located on the thrust bushing (18).

8. torque transmission device (1) according to claim 7, characterized in that the thrust bushing (18) is force-fitted on the outer ring (21) of the actuating bearing (16).

9. torque transmission device (1) according to one of claims 7 or 8, characterized in that the diaphragm (19) is in contact with the holding member (23).

Torque transmission device (1) according to one of the preceding claims, characterized in that the actuating bearing (16) and the supporting bearing (24) are located radially at the same distance from the axis A .

1 1. Torque transmission device (1) according to one of the preceding claims, characterized in that the actuating bearing (16) and the bearing support (24) are ball bearings.