Mounted oil supply hub and triple wet clutch with this mounted oil supply hub

Description

[0001] The present invention relates to an assembled oil supply hub and a triple wet clutch comprising this assembled oil supply hub.

[0002] The present invention relates to the field of torque transmission chains for motor vehicles, in particular those arranged between a heat engine and a gearbox.

[0003] The invention relates more specifically to a triple wet clutch for a hybrid type motor vehicle in which a rotating electric machine is disposed in the torque transmission chain.

[0004] In the prior art, hybrid vehicles are known to include a wet dual-clutch mechanism positioned between an internal combustion engine and a gearbox, a rotating electric machine, and a disconnect clutch and an actuation mechanism for this disconnect clutch. This mechanism allows the rotation of a crankshaft of the internal combustion engine to be coupled or uncoupled from a rotor of the rotating electric machine. Thus, it is possible to shut off the internal combustion engine each time the vehicle stops and restart it using the rotating electric machine. The rotating electric machine can also act as an electric brake or provide additional power to the internal combustion engine to assist it or prevent it from stalling. When the internal combustion engine is running, the electric machine can function as a generator.The rotating electric machine can also provide vehicle drive independently of the internal combustion engine.

[0005] Such a rotating electric machine can be in line with the wet double clutch mechanism, i.e. the axis of rotation of the rotor of the rotating electric machine is coincident with the axis of rotation of the clutches as described in document EP 2 517 915. Alternatively, the rotating electric machine can be offset from the wet double clutch mechanism, i.e. the axis of rotation of the rotor of the rotating electric machine is offset from the axis of rotation of the wet double clutch mechanism.

[0006] Current developments in automotive hybridization require torque transmission systems that integrate an electrical power source without compromising the axial compactness of said transmission system. Due to the presence of wet clutches, a triple wet clutch system was designed to supply fluid to the various clutches without altering the overall dimensions of the torque transmission system. This pursuit of axial compactness is the basis of the invention.

[0007] The architecture of a triple wet clutch must be increasingly compact, and it is sometimes difficult to accommodate all the components. For example, due to the presence of the rotating electric motor, the disconnect clutch and its actuating piston must be positioned in one space on the engine side, and the dual wet clutch mechanism in another space on the gearbox side. This presents several challenges, particularly regarding the fluid supply to the clutch and its actuating element. In document EP 2 517 915, the oil supply channels are arranged through a radially extending central flange that separates the two spaces reserved for the disconnect clutch and the dual wet clutch mechanism. The oil supply channels are complex to manufacture. This triple wet clutch architecture is also very axially bulky.[Other triple wet clutches are known from documents JP2015214988A and CN109322940 A.].

[0008] The invention aims to improve the existing design by benefiting from a triple wet clutch allowing to reconcile the requirements of axial compactness while ensuring a good supply of fluid to the clutches and their actuating pistons.

[0009] To this end, the invention proposes, according to one of its aspects, an assembled oil supply hub for a triple wet clutch comprising a central hub with axis of rotation X, said central hub comprising: a cylindrical portion, a flange extending radially from the cylindrical portion, a first annular cavity disposed on the side of the flange and arranged to receive an actuating piston for a first clutch, a second annular cavity disposed on the same side of the flange as the first annular cavity and arranged to receive an actuating piston for a second clutch, a third annular cavity disposed radially beyond the other two annular cavities and arranged to receive an actuating piston for an additional disconnect clutch, and at least one oil supply channel formed in the central hub passing through the cylindrical portion and / or the flange, and opening into one of the annular cavities said assembled oil supply hub comprising an annular piece attached to the flange of the central hub, said annular piece attached forming in part the first annular cavity and / or the second annular cavity [, the annular piece attached is an input disc holder of the first clutch and / or the second clutch, the free end of the annular piece attached having a groove and the other end being fixed to the flange].

[0010] Thanks to this assembled oil supply hub architecture, the annular cavities associated with the clutches are concentric and arranged radially in the same plane. The oil supply channels for the various cavities are arranged in the same plane, passing through the flange, thus facilitating their integration within the triple wet clutch and their manufacturing. The axial footprint of such an assembled oil supply hub is therefore reduced.

[0011] This assembled oil supply hub, according to the invention, offers the advantage of reduced manufacturing costs thanks to the use of an added annular component. This added annular component allows for the formation of annular cavities at a lower cost compared to machining, since it can be formed, for example, by stamping. This added annular component can also perform other functions within the triple wet clutch, such as serving as a disc carrier or supporting helical springs.

[0012] According to one embodiment, the assembled oil supply hub may include a drive cover arranged to be driven in rotation by an electric machine, the drive cover forming part of the third annular cavity.

[0013] Preferably, the drive cover can be attached to the outer circumference of the central hub flange. This simplifies the shape of the central hub, and the material of the drive cover can be chosen to be different from that of the central hub.

[0014] Advantageously, the drive cover can surround the outer edge of the flange. This makes it possible to arrange the annular cavities associated with the three clutches radially in the same plane.

[0015] Preferably, the oil supply channels can open onto the outer edge of the flange and be sealed by the drive cover. This allows a portion of the oil supply channels to be sealed without the need for additional expensive components.

[0016] The invention may exhibit one or more of the features described below, either combined or taken independently of each other: The oil supply channels may be distributed angularly around the cylindrical portion; the added annular part may include at least one inner and / or outer cylindrical bearing surface for supporting an actuating piston seal; the added annular part may form the annular cavity of one of the first or second clutches and includes an inner cylindrical bearing surface and an outer cylindrical bearing surface for supporting the seals of the same actuating piston; the added annular part may include an inner cylindrical bearing surface and an outer cylindrical bearing surface for supporting the seals of the actuating pistons of the first and second clutches; the added annular part may include an inner cylindrical bearing surface and an outer cylindrical bearing surface for supporting the seals of the actuating pistons of the cut-off clutch and the first clutch; theThe added annular part may have a U-shaped cross-section in a plane passing through the X-axis; the cylindrical portion may include an external cylindrical bearing surface that partially forms the second annular cavity of the second clutch. The added annular part may be attached by welding to the flange of the central hub, for example, by laser welding or laser beam welding, with the weld bead positioned radially above and / or below the outlet of the oil supply channel opening into the annular cavity. The added annular part may also be attached by riveting to the flange of the central hub. The added annular part may be an annular plate from one of the elastic return elements of the first clutch or the cut-off clutch, the free end of the added annular part having one face bearing on helical springs and the other end being fixed to the flange. The annular cavities ofThe cut-off clutch, the first clutch and the second clutch can follow each other radially as they approach the X axis. The added annular part can include at least one orifice forming part of the oil supply channel of the annular cavity.

[0017] Such an assembled oil supply hub, whether based on one of the characteristics described above in combination or independently, offers the advantage of reduced manufacturing costs thanks to the use of an added annular component. This added annular component allows for the formation of annular cavities at a lower cost compared to machining, since it can be formed, for example, by stamping. This added annular component can also perform other functions within the triple wet clutch, such as serving as a disc carrier or supporting helical springs. The axial dimensions of such an assembled oil supply hub are thus reduced.

[0018] The invention also relates, according to another aspect, to a triple wet clutch for a torque transmission system comprising: a multi-disc type disconnect clutch, controlled to selectively couple a drive shaft to an electric machine, a first clutch and a second clutch respectively of the multi-disc type, controlled to selectively couple the electric machine and / or the drive shaft to a first driven shaft and a second driven shaft, the first and second clutches being arranged radially one above the other, the triple wet clutch being notable in that it includes an assembled oil supply hub incorporating all or part of the features mentioned above, said assembled oil supply hub supplying oil to the control chambers of the disconnect clutch, the first clutch and the second clutch.

[0019] Thanks to this triple wet clutch architecture, the clutches are concentric and arranged radially in the same plane. The axial footprint of such a triple wet clutch within a torque transmission system or torque transmission chain is thus reduced.

[0020] Preferably, the first clutch can be actuated by means of a first actuating piston, which is axially movable relative to the first annular cavity of the central hub between an engaged and disengaged position of the first clutch. The first actuating piston is steered by means of a control chamber partially delimited by the added annular piece. In this way, the control chamber of the first clutch is contained within the first cavity, and the pressurized oil supply is thus delivered as close as possible to the assembled oil supply hub, thereby reducing leakage within the triple wet clutch.

[0021] Preferably, the second clutch can be actuated by means of a second actuating piston, which is axially movable relative to the second annular cavity of the central hub between an engaged and disengaged position of the second clutch. The second actuating piston is steered by means of a control chamber partially defined by the added annular component. In this way, the control chamber of the second clutch is contained within the second cavity, thus ensuring that the pressurized oil supply is delivered as close as possible to the assembled oil supply hub, thereby reducing leakage within the triple wet clutch.

[0022] According to one embodiment, the actuating pistons are annular and may include added O-rings.

[0023] According to another embodiment, the actuating pistons are annular and may include overmolded seals.

[0024] Advantageously, the multi-disc assembly of the first clutch can be arranged radially between the first and third cavities of the assembled oil supply hub. This allows for the utilization of the available internal space within the triple wet clutch, thereby reducing the axial footprint.

[0025] Advantageously, the multi-disc assembly of the second clutch can be arranged radially between the first and second cavities of the assembled oil supply hub. This allows for the utilization of the available internal space within the triple wet clutch, thereby reducing the axial footprint.

[0026] Preferably, the multi-disc assembly of the first clutch can be actuated by a first force transmission element, the first force transmission element being a stamped sheet metal part bearing on the actuating piston of the first clutch.

[0027] In one embodiment, the free end of the second clutch actuating piston, which bears against the multi-disc assembly, is positioned radially between the first and second cavities. This allows for the utilization of the available internal space within the triple wet clutch, thereby reducing the axial footprint.

[0028] Preferably, the three annular cavities of the cut-off clutch, the first clutch and the second clutch can be oriented in the same axial direction, in particular towards the driving shaft.

[0029] According to one embodiment, the oil supply channel can be made by drilling successive channels within the assembled oil supply hub, said channels opening into each other and arranged to supply pressurized fluid to the clutch control chamber.

[0030] According to one embodiment, the fluid can be oil, for example gearbox oil.

[0031] According to one embodiment, the triple wet clutch may further include a rotational cut-off clutch about the X axis, selectively coupling by friction an input element, rotationally linked to a driving shaft, to an assembled oil supply hub suitable for rotationally coupling to a first driven shaft of the gearbox or a second driven shaft of the gearbox.

[0032] According to one embodiment, the triple wet clutch may further comprise a first clutch and a second clutch respectively of the multi-disc type, controlled to selectively couple the electric machine and / or the driving shaft to a first driven shaft of the gearbox and to a second driven shaft of the gearbox via the assembled oil supply hub.

[0033] Preferably, the disengagement clutch can be the one located radially on the outside, i.e., furthest from the X-axis of rotation of the wet triple clutch. The second clutch can be the one located radially on the inside, i.e., closest to the X-axis of rotation of the wet triple clutch.

[0034] According to one aspect of the invention, the actuating piston of each clutch can be controlled by an internal position sensor controlling the clutch, or by measuring the hydraulic pressure when the clutch is closed, or by measuring the volume of fluid injected, or by measuring a displacement quantity when the clutch is closed.

[0035] According to one embodiment, the drive cover includes an electrical connection area suitable for being rotationally linked with an electrical machine rotating around an axis parallel to the axis of rotation X.

[0036] Preferably, the drive cover may include a groove arranged to receive the multi-disc assembly of the cut-off clutch, said groove being formed from the same material as the drive cover or attached to the drive cover.

[0037] Advantageously, the drive cover may include a toothed ring suitable for being rotationally linked with an electrical machine rotating around an axis parallel to the axis of rotation X.

[0038] According to one aspect of the invention, the electrical connection zone is axially offset from the disconnect clutch and / or the first and second clutches. The electrical machine is then said to be "off-line".

[0039] This arrangement allows the electric motor to be positioned according to the available space within the vehicle's torque transmission chain. Specifically, this arrangement avoids having to position the electric motor axially following the clutches, which would negatively impact axial compactness. Similarly, this arrangement avoids having to position the electric motor radially beyond the clutches, which would negatively impact radial compactness.

[0040] Alternatively, a chain or belt can be used to connect the rotating electrical machine to the electrical connection area.

[0041] Alternatively, the drive cover can be used to define a rotor support for an electrical machine rotating around its axis of rotation. The electrical machine is then said to be "in-line".

[0042] Preferably, the drive cover may include an electrical connection area suitable for being rotationally linked with an electrical machine rotating around an axis concentric to the axis of rotation X.

[0043] Advantageously, the electrical connection area of ​​the drive cover arranged to receive an electric motor rotor concentric to the X axis can be axially offset relative to the first clutch and the second clutch.

[0044] This arrangement allows the electric machine to be positioned radially at the clutches, which improves radial compactness.

[0045] According to the invention, the clutches, namely the cut-off clutch, the first clutch, and the second clutch, can be of the multi-disc type. Within the scope of the invention, a multi-disc assembly is an assembly comprising at least one friction disc rotatably fixed to one of the input and output disc carriers, at least two plates respectively arranged on either side of each friction disc, rotatably fixed to the other of the input and output disc carriers, and friction linings arranged between the plates and a friction disc, the clutches describing a disengaged position and an engaged position in which said plates and the friction disc pinch the friction linings so as to transmit a torque between an input disc carrier and an output disc carrier.

[0046] For the purposes of this application, a wet clutch is a clutch that is adapted to operate in an oil bath.

[0047] The invention will be better understood, and other objects, details, features and advantages thereof will become more apparent from the following description of a particular embodiment of the invention, given solely by way of illustration and not limitation, with reference to the accompanying figures. there [ Figure 1 ] represents an axial cross-sectional view of a triple wet clutch according to a first embodiment of the invention. the [ Figure 2 ] represents an isometric view of a triple wet clutch according to the first embodiment of the invention of the [ Figure 1 ]. there [ Figure 3 ] represents an axial cross-sectional view of a triple wet clutch according to a second embodiment of the invention.

[0048] In the following description and claims, the terms "front" or "rear" will be used, without limitation and to facilitate understanding, according to the direction with respect to an axial orientation determined by the main X axis of rotation of the transmission of the motor vehicle and the terms "inside / internal" or "outside / external" with respect to the O axis and along a radial orientation, orthogonal to said axial orientation.

[0049] We have represented on the figures 1 And 2 A first embodiment of an assembled oil supply hub 50 for a triple wet clutch 1. The triple wet clutch 1 is represented within a motor vehicle torque transmission chain by means of a gearbox housing 100 equipped with two driven torque output shafts A1, A2. In relation to the figures 1 And 2 We observe a triple wet clutch 1 comprising: a multi-disc type K0 cutting-off clutch, controlled to selectively couple a shaft driving an electric machine, a first torque output clutch E1 and a second torque output clutch E2 respectively of multi-disc type, controlled to selectively couple the electric machine and / or the shaft driving a first driven shaft and a second driven shaft, the first and second clutches E1, E2 being arranged radially one above the other, and an assembled oil supply hub 50 in the sense of the present invention, said assembled oil supply hub 50 supplying oil to the control chambers of the cutting-off clutch K0, the first clutch E1 and the second clutch E2.

[0050] The assembled oil supply hub 50 comprises a central hub 51 with axis of rotation X, said central hub 51 comprising: a cylindrical portion 52, a flange 53 extending radially from the cylindrical portion 52, a first annular cavity 56 disposed on the side of the flange and arranged to receive an actuating piston for the first clutch E1, a second annular cavity 55 disposed on the same side of the flange as the first annular cavity and arranged to receive an actuating piston for the second clutch E2, a third annular cavity 57 disposed radially beyond the other two annular cavities and arranged to receive an actuating piston for the additional cut-off clutch K0, and oil supply channels 54a, 54b and 54c formed in the central hub 51 passing through the cylindrical portion 52 and the flange 51, and opening separately into the annular cavities.

[0051] The annular cavities 57, 56, 55 of the K0 cut-off clutch, the first clutch E1 and the second clutch E2 are oriented in the same direction, for example in the direction of the driving shaft, i.e. in the direction of the internal combustion engine of the torque transmission chain.

[0052] The triple wet clutch 1 has, around its axis of rotation X, at least one torque input element 2 which is rotationally linked to a driving shaft (not shown). The input element 2 is located at the front of the triple wet clutch 1.

[0053] In the first embodiment, the input element 2, generally L-shaped, comprises a radial orientation portion formed by a torque input shroud 3 and an axial orientation portion formed by a torque input hub 4. The shroud 3 and the hub 4 are integral, preferably joined by welding. The torque input hub 4 is guided in rotation within a housing 101 fixed relative to the torque transmission chain.

[0054] The torque input hub 4 is for example linked in rotation by means of splines formed at the output of a damping device (such as a double flywheel damper, etc.) whose input is linked, in particular by means of a flywheel, to the driving shaft formed by a crankshaft which is driven in rotation by a thermal engine equipping the motor vehicle.

[0055] The torque input veil 3 has, at its external radial end, a groove arranged to receive the multi-disc assembly of the K0 cut-off clutch.

[0056] In the example considered, the triple wet clutch 1 further includes a cut-off clutch K0 selectively coupling by friction the input torque disc 3 and an output disc carrier 81 of the cut-off clutch K0 fixed in rotation with the assembled oil supply hub 50.

[0057] In this first embodiment, the output disc carrier 81 is mounted on a drive cover 80, itself fixed to the assembled oil supply hub 50.

[0058] The K0 cut-off clutch comprises a multi-disc assembly including several friction discs 7, equipped with friction linings, rotationally fixed to the torque input disc 3, several plates 6 respectively arranged on either side of each friction disc 7, rotationally fixed to the output disc carrier 81, the K0 cut-off clutch describing a disengaged position and an engaged position in which said plates 6 and the friction discs 7 pinch the friction linings so as to transmit a torque between the torque input disc 3 and the output disc carrier 81.

[0059] The plates 6 of the multi-disc assembly of the K0 cut-off clutch are rotationally linked to the assembled oil supply hub 50 via a spline and the friction discs 7 are rotationally linked to the input element 2.

[0060] The assembled oil supply hub 50 includes a drive cover 80 attached to the outer circumference of the flange 53 of the central hub 51. The assembled oil supply hub 50 has the function of transmitting the torque within the triple wet clutch 1. For this purpose, the drive cover 80 is rotationally fixed to the output disc carrier 81, in this case by means of a welded connection.

[0061] Alternatively, the drive cover 80 may include a groove arranged to receive the multi-disc assembly of the K0 cut-off clutch, said groove being formed from the same material as the drive cover or attached to the drive cover.

[0062] The drive cover 80 includes an electrical connection area 82 suitable for rotationally linking with a rotating electrical machine. In this case, the electrical machine rotates about an axis parallel to the axis of rotation X. The electrical machine is described as "off-line" because it is not concentric with the drive shaft but aligned along a parallel shaft. The electrical connection area 82 is suitable for direct interaction with a pinion of the rotating electrical machine.

[0063] The electrical connection zone 82 can be in the form of a ring gear suitable for direct or indirect (belt, chain, etc.) engagement with a pinion of the rotating electrical machine (not visible). The ring gear may have helical teeth with a shape complementary to the pinion of the rotating electrical machine.

[0064] The assembled oil supply hub 50 is capable of transmitting torque from two separate sources: thermal and electrical. When the disconnect clutch K0 is closed, the torque from the internal combustion engine can then be transmitted to the coaxial gearbox shafts A1 and A2, depending on whether one of the first clutch E1 or the second clutch E2 is closed.

[0065] The first driven shaft A1 is driven in rotation when said first clutch E1 is closed and the second driven shaft A2 is driven in rotation when said second clutch E2 is closed.

[0066] The multi-disc assembly of the first clutch E1 comprises plates 11 rotationally linked to a disc carrier 10 attached to the assembled oil supply hub 50 and friction discs 12 rotationally linked to an output disc carrier 13. The friction discs 12 are, individually, axially interposed between two successive plates 11.

[0067] The output disc carrier 13 of the first clutch E1 is rotationally linked by meshing with the friction discs 12 and by a splined connection with the first driven shaft A1. The inner radial end of the output disc carrier 13 is fixed to a splined output hub.

[0068] The multi-disc assembly of the second clutch E2 comprises plates 21 rotationally linked to the disc carrier 10 attached to the assembled oil supply hub 50 and friction discs 22 rotationally linked to an output disc carrier 23.

[0069] The output disc carrier 23 of the second clutch E2 is rotationally linked by meshing with the friction discs 22 and by a splined connection with said second driven shaft A2. The inner radial end of the output disc carrier 23 is fixed to a splined output hub.

[0070] In this case, the disc carrier 10 has an external spline 10a which meshes with the multi-disc assembly of the first clutch E1 and an internal spline 10b which meshes with the multi-disc assembly of the second clutch E2. The disc carrier 10 is securely fixed to the central hub 51 by means of a weld bead.

[0071] In an alternative not shown, the internal and external splines engaging with the multi-disc assemblies of the E1 and E2 clutches can be distributed over two separate disc carriers attached to the assembled oil supply hub.

[0072] The triple wet clutch 1 is hydraulically controlled via a pressurized fluid, usually oil.

[0073] To selectively control the change of state of the cut-off clutch K0, the first clutch E1, and the second clutch E2, a wet triple-clutch control device manages the pressurized oil supply within separate control chambers. The control device is generally integrated into the gearbox housing 100. The control device is connected to the oil supply hub 50, which has pressurized oil supply channels 54a, 54b, and 54c, for example, three as shown in the diagram. figure 1 . The oil supply channels 54a, 54b and 54c are distributed angularly around the cylindrical portion 52 of the central hub 51.

[0074] Each of the oil supply channels 54a, 54b and 54c consists of substantially radial and axial bores directed towards the control chambers of the cut-off clutch K0, the first and second clutches E1, E2.

[0075] For example, the oil supply channel 54b, located axially at the rear end of the oil supply hub 50, is associated with the control chamber of the second clutch E2. The oil supply channel 54b is formed by drilling successive axial and radial channels within the assembled oil supply hub 50. The channels open into one another and are arranged to supply pressurized fluid to the control chamber of the second clutch E2. The oil supply channel 54b opens into the second annular cavity 55, formed partly by the cylindrical portion 52 of the central hub 51 and partly by an annular insert. In this case, the annular insert on the flange of the central hub 51 is part of the disc carrier 10 of the second clutch E2. The disc carrier 10 and the annular insert of the second cavity 55 form a single unit.

[0076] The second clutch E2 comprises an actuating piston 25 which is axially movable, here from rear to front, between a disengaged position and an engaged position, corresponding respectively to the open and closed states of the second clutch E2. The multi-disc assembly of the second clutch E2 is directly actuated by the second actuating piston 25, which is made from stamped sheet metal. The actuating piston 25 is axially movable relative to the second annular cavity 55 of the central hub 51. The actuating piston 25 is steered by means of a control chamber partially delimited by the attached annular piece 10.

[0077] The oil supply channel 54a, machined in the oil supply hub 50, is associated with the control chamber of the first clutch E1. The oil supply channel 54a is formed by drilling successive axial and radial channels within the assembled oil supply hub 50. The channels open into one another and are arranged to supply pressurized fluid to the control chamber of the first clutch E1. The oil supply channel 54b opens into the first annular cavity 56 formed by an annular insert 41, which has a U-shaped cross-section in a plane passing through the X-axis.

[0078] In this case, the annular insert 41 forming the first cavity 56 comprises an inner cylindrical bearing surface 41a and an outer cylindrical bearing surface 41b for supporting the seals of the first actuating piston 15 of the first clutch E1. The annular insert 41 is the annular plate of an elastic return element 40 of the disconnect clutch K0. The free end of the annular insert 41 has one face bearing against helical springs 42, and the other end is fixed to the flange 53. The annular insert 41 of the first cavity 56 is securely fixed to the central hub 51 by means of concentric weld beads. The weld beads ensure the sealing of the control chamber of the first actuating piston 15.The added annular part 41 includes an orifice forming in part the oil supply channel 54a of the annular cavity 56 allowing the entry of oil into the control chamber.

[0079] The actuating piston 15 of the first clutch E1 is axially mobile, here from rear to front, between a disengaged position and an engaged position which correspond respectively to the open and closed states of the first clutch E1. The multi-disc assembly of the first clutch E1 is actuated by a first force transmission element 16, the first force transmission element 16 being a stamped sheet metal part bearing against the first actuating piston 15.

[0080] As illustrated on the figure 1 The elastic return element 40 of the actuating piston 5 of the K0 disconnect clutch comprises a plurality of helical springs 42 axially interposed between a front wall of the attached annular part 41 and the actuating piston 5 of the K0 disconnect clutch. The elastic return element 40 automatically returns the actuating piston 5 to the disengaged position, corresponding to an open clutch state. The actuating piston 5 is annular and includes overmolded seals.

[0081] The oil supply channel 54c, machined into the oil supply hub 50, is associated with the control chamber of the shut-off clutch K0. The oil supply channel 54c is formed by drilling successive axial and radial channels within the assembled oil supply hub 50. The channels open into one another and are arranged to supply fluid under

[0082] The actuating piston 5 of the K0 cut-off clutch is axially mobile, here from rear to front, between a disengaged position and an engaged position, which correspond respectively to the open and closed states of the K0 cut-off clutch. The multi-disc assembly of the K0 cut-off clutch is actuated by a force transmission member 8, the force transmission member 8 being a stamped sheet metal part bearing against the actuating piston 5. The force transmission member 8 receives support from the helical springs 42 of the elastic return element 40.

[0083] In the first embodiment, the oil supply channels 54a, 54b and 54c open onto the outer perimeter of the flange 53 and are closed by the drive cover 80.

[0084] As is known in the operation of a wet clutch, a balancing chamber is associated with each control chamber. The balancing chambers are supplied with coolant. The coolant flows through channels separate from the oil supply channels 54a, 54b, and 54c. These separate channels are also formed in the assembled oil supply hub 50.

[0085] There figure 3 presents an [example of] triple wet clutch 1 similar to the first mode at least in its general operation.

[0086] This [wet triple clutch] differs from the one described in reference to the figures 1 And 2 in that the drive cover 80 includes an electrical connection area 82 linked in rotation with an electrical machine 90 rotating concentrically to the axis of rotation X. The electrical machine is then said to be "in-line".

[0087] The rotor 91 of the electric machine 90 is rotationally fixed to the drive cover 80. In the present case, the electrical connection area 82 and the rotor 91 are axially offset with respect to the first clutch E1 and the second clutch E2 so that the radial compactness of the triple wet clutch is improved.

[0088] This [wet triple clutch] also differs from the one described in reference to the figures 1 And 2 in that an added annular part 60 comprises an inner cylindrical bearing surface 61 for supporting the sealing ring of the actuating piston 25 of the second clutch E2 and an outer cylindrical bearing surface 62 for supporting the sealing ring of the actuating piston 15 of the first clutch E1. The actuating piston 15 is annular and includes added O-rings.

[0089] Advantageously, the free end of the actuating piston 25 of the second clutch E2 bearing on the multi-disc assembly is arranged radially between the first cavity 56 and the second cavity 55. In this way, it is possible to exploit the available internal space within the triple wet clutch and thus reduce the axial footprint.

[0090] Advantageously, the multi-disc assembly of the second clutch E2 is arranged radially between the first cavity 56 and the second cavity 55. In this way, it is possible to exploit the available internal space within the triple wet clutch and thus reduce the axial footprint.

[0091] The added annular piece 60 is fixed to the flange 53 of the central hub 51 by a welding process, for example, laser welding or capacitor discharge welding. The added annular piece 60 partially forms the first annular cavity 56 and the second annular cavity 55.

[0092] The attached annular part 60 has a U-shaped cross-section in a plane passing through the X-axis and can easily be produced by stamping a sheet of steel. Alternatively, the attached annular part 60 could be machined.

[0093] Although the invention has been described in connection with several particular embodiments, it is clearly evident that it is by no means limited to them and that it includes all technical equivalents of the means described as well as their combinations if these fall within the scope of the invention.

[0094] It is clear from the foregoing that the present invention proposes a triple wet clutch in which the clutches are concentric and arranged radially in the same plane. The axial footprint of such a triple wet clutch within a torque transmission chain is reduced. This triple wet clutch includes an assembled oil supply hub in which the network of oil supply channels is simpler to design and requires less manufacturing time.

[0095] The invention is not limited to the means and configurations described and illustrated herein, and also extends to any equivalent means or configuration and to any technical combination operating such means. In particular, the shape of the assembled oil supply hub can be modified without prejudice to the invention, provided that these components ultimately fulfill the same functionalities as those described in this document.

[0096] In claims, any reference sign in parentheses cannot be interpreted as a limitation of claim.

Claims

1. An assembled oil supply hub (50) for a triple wet clutch comprising a central hub (51) with axis of rotation (X), said central hub (51) comprising: a cylindrical portion (52), a flange (53) extending radially from the cylindrical portion (52), a first annular cavity (56) positioned on the same side as the flange and arranged to receive an actuating piston (15) for the actuation of a first clutch (E1), a second annular cavity (55) positioned on the same side of the flange as the first annular cavity (56) and arranged to receive an actuating piston (25) for the actuation of a second clutch (E2), a third annular cavity (57) arranged radially beyond the other two annular cavities (55, 56) and designed to receive an actuating piston (5) for actuation of an additional torque disconnect clutch (K0), and at least one oil supply channel (54a, 54b, 54c) formed in the central hub (51) passing through the cylindrical portion (52) and / or the flange (53), and opening into one of the annular cavities (55, 56, 57), the said assembled oil supply hub (50) comprising an attached annular component (10, 41, 60) attached to the flange of the central hub, said attached annular component partially forming the first annular cavity (56) and / or the second annular cavity (55), characterized in that the attached annular component (10) is an input disk carrier of the first clutch (E1) and / or of the second clutch (E2), the free end of the attached annular component (10) being splined and the other end being fixed to the flange (53).

2. The assembled oil supply hub (50) as claimed in claim 1, characterized in that it comprises a drive cover (80) designed to be rotationally driven by an electric machine, the drive cover (80) partly forming the third annular cavity (57).

3. The assembled oil supply hub (50) as claimed in claim 2, characterized in that the drive cover (80) is attached to the outer perimeter of the flange (53) of the central hub (51).

4. The assembled oil supply hub (50) as claimed in one of claims 1 to 3, characterized in that the cylindrical portion (52) comprises an external cylindrical bearing surface partly forming the second annular cavity (55) of the second clutch (E2).

5. The assembled oil supply hub (50) as claimed in one of claims 1 to 4, characterized in that the attached annular component (10, 41, 60) is fixed by welding to the flange of the central hub, for example using laser welding, the welded seam being positioned radially above and / or below the outlet orifice of the oil supply channel (54a, 54b, 54c) opening into the annular cavity (55, 56, 57).

6. The assembled oil supply hub (50) as claimed in one of claims 1 to 5, characterized in that the annular cavities (55, 56, 57) of the torque disconnect clutch (K0), of the first clutch (E1) and of the second clutch (E2) succeed one another radially in decreasing distance from the axis (X).

7. The assembled oil supply hub (50) as claimed in one of claims 1 to 6, characterized in that the attached annular component (10) comprises at least one interior and / or exterior cylindrical bearing surface against which a seal of actuating piston (5, 15, 25) can bear.

8. A triple wet clutch (1) for a torque-transmission system comprising: a torque disconnect clutch (K0) of the multidisk type, operated in such a way as to selectively couple a driving shaft to an electric machine, a first clutch (E1) and a second clutch (E2) that are respectively of the multidisk type and are operated in such a way as to selectively couple the electric machine and / or the driving shaft to a first driven shaft and to a second driven shaft, the first and second clutches (E1, E2) being positioned radially one above the other, characterized in that the triple wet clutch (1) comprises an assembled oil supply hub (50) as claimed in any one of the preceding claims, said assembled oil supply hub (50) supplying oil to the control chambers of the torque disconnect clutch (K0), of the first clutch (E1) and of the second clutch (E2).

9. The triple wet clutch (1) as claimed in claims 8, characterized in that the multidisk assembly of the first clutch (E1) is actuated by a first force-transmission member (16), the first force-transmission member (16) being a component made of pressed sheet metal bearing against the actuating piston (15) for actuation of the first clutch (E1).

10. The triple wet clutch (1) as claimed in claim 8 or 9, characterized in that the free end of the actuating piston (25) for actuation of the second clutch (E2) bearing against the multidisk assembly is positioned radially between the first cavity (56) and the second cavity (55) of the assembled oil supply hub (50).