Normally closed clutch module

Abstract

The subject of the invention is a normally closed clutch module (1) having a first axis of rotation (X) and comprising:-an output disk carrier (3) rotatable relative to the first axis of rotation (X); at least one friction disk (6), in particular a multi-disk assembly (5); -a piston (20) configured to clamp the friction disc when the clutch module is in the engaged position and to release the friction disc when the clutch module is in the disengaged position; -elastic means (30) configured to exert an elastic restoring force on the piston (20) in order to hold the piston (20) in the engaged position; -a piston actuation system (40) for actuating the piston (20) and axially against the piston (20) on the one hand and against the output disk carrier (3) on the other hand, preferably via a rolling bearing, and configured to bring the piston (20) from the engaged position to the disengaged position against the elastic restoring force of the elastic means (30).

Description

Technical Field

[0001] The field of the invention is clutch modules of the normally closed type, in particular for motor vehicles. Background Art

[0002] A transmission system arranged between a gearbox and an internal combustion engine is known, which transmission system comprises an electric machine and a clutch located on the engine side, which allows the crankshaft of the internal combustion engine to be rotationally coupled to the rotor of the electric machine. Thus, the internal combustion engine can be shut down each time the vehicle stops and restarted using the electric machine. The electric machine can also constitute an electric brake or provide power to the internal combustion engine to help it or prevent it from stalling. The electric machine can also drive the vehicle. When the internal combustion engine is running, the electric machine acts as an alternator. The actuation system has a static state and an active state for controlling the clutch between a position in which the internal combustion engine is coupled (called the "engaged position") and a position in which the internal combustion engine is disengaged (called the "disengaged position"). If the active state of the actuation system corresponds to the engaged position, the clutch is considered to be of the normally open type. If the active state of the actuation system corresponds to the disengaged position, the clutch is considered to be of the normally closed type. Such a transmission assembly is particularly disclosed in patent application EP3532324. In this patent application, the clutch is of the "normally open" type. Summary of the invention

[0003] The invention is particularly directed to further improving torque transmission systems.

[0004] The subject of the invention is therefore a clutch module of the normally closed type having a first axis of rotation and comprising:

[0005] - an output disc carrier rotatable relative to a first axis of rotation;

[0006] - at least one friction disc;

[0007] - a piston configured to clamp the friction disk when the clutch module is in the engaged position and to release the friction disk when the clutch module is in the disengaged position;

[0008] - elastic means configured to exert an elastic restoring force on the piston so as to maintain the piston in the engaged position;

[0009] - A piston actuation system for actuating the piston and resting axially on the one hand against the piston and on the other hand against the output disc carrier, preferably via rolling bearings, and configured to bring the piston from the engaged position to the disengaged position against the elastic restoring force of the elastic means.

[0010] Since the piston actuation system is axially supported against the piston on the one hand and against the output disc carrier on the other hand, the invention makes it possible to create a load path during piston actuation which passes through the actuation system, the piston and the output disc carrier and advantageously not through the housing encapsulating the clutch module.

[0011] The clutch module is self-sufficient or almost self-sufficient in the sense that the load path is inside the clutch module to allow the clutch module to be actuated. In other words, the clutch module is operable, for example for testing / trials, without the need to place the clutch module in its final environment. This is possible because the load path is inside the module (the load path does not need to rely on components outside the clutch module). Another advantage is that the clutch module can be manufactured in a factory and then transported in a practical way and then assembled with other components, such as an input module with a damper. A clutch module of the "normally closed" type also has the following advantages. In order to transmit torque from the internal combustion engine, which represents the main case of vehicle use, there is no need to permanently activate the actuation system, so the invention allows energy savings.

[0012] Preferably, the elastic device is axially supported on the output disc carrier.

[0013] Advantageously, the piston actuation system is axially supported on the output disc carrier by means of rolling bearings. Specifically, the disc carrier rotates at engine speed, while the actuation system is stationary.

[0014] Advantageously, the clutch module is configured to be assembled in a torque transmission system, in particular for a motor vehicle, the torque transmission system also comprising an input module cooperating with the clutch module, the input module being upstream (in the torque transmission direction) of the clutch module.

[0015] According to one aspect of the invention, a clutch module includes a multi-disc assembly positioned between an input disc carrier and an output disc carrier.

[0016] According to an aspect of the present invention, when the clutch module is assembled with the input module, the clutch module is located radially inside the periphery of the elastic member passing through the damper.

[0017] According to one aspect of the invention, the clutch module comprises a transmission ring configured to cooperate in rotation with a rotor shaft of a rotating electrical machine, possibly with a reducer assembly interposed therebetween. The reducer assembly may be configured to allow for multiple gear ratios.

[0018] In particular, a transmission ring connected to the output disc carrier advantageously meshes with a gear connected to the rotor shaft of the rotating electrical machine via the reducer assembly.

[0019] According to one aspect of the invention, the transmission ring faces axially towards the elastic member of the damper.

[0020] “Axially facing” means that the transmission ring and the elastic member of the damper are located on the same geometric cylinder (imaginary curve) centered on the first rotation axis of the clutch module and are offset relative to each other parallel to the first rotation axis.

[0021] According to one aspect of the invention, the transmission ring is toothed.

[0022] According to one aspect of the invention, the drive ring, the multi-disc assembly and the piston actuation system are radially stacked.

[0023] In other words, the drive ring, the multi-plate assembly and the piston actuation system are substantially in the same plane perpendicular to the first rotational axis of the clutch module.

[0024] As a variant, the transmission ring may be axially offset relative to the multi-disc assembly and the piston actuation system while maintaining a larger diameter relative to the multi-disc assembly and the piston actuation system.

[0025] According to one aspect of the invention, the piston cooperates with a rolling bearing mounted on the actuation system, so that the actuation system cooperates with the piston, wherein the piston is free to rotate relative to the actuation system.

[0026] According to one aspect of the invention, the piston comprises at least one actuating finger axially passing through the elastic means.

[0027] According to one aspect of the invention, the elastic means comprises at least one elastic washer, in particular a Belleville spring washer.

[0028] According to another aspect of the invention, the elastic means comprises at least one corrugated washer.

[0029] According to one aspect of the invention, the elastic means comprises a plurality of coil springs connected together directly or indirectly at their ends.

[0030] According to one aspect of the invention, the piston comprises a periphery extending axially so as to press against the friction disk, the periphery axially passing through the elastic means. This makes it possible to improve the radial compactness.

[0031] According to one aspect of the invention, the actuation system bears against the side of the piston which faces the input module.

[0032] According to one aspect of the invention, the actuation system is configured to axially move the piston from the engaged position to the disengaged position.The actuation system may be mechanical, electromechanical, electromagnetic or hydraulic.

[0033] According to one aspect of the invention, the actuation system is a ball rail system.

[0034] As a variant, the drive system is of the hydraulic CSC "Concentric Slave Cylinder" type.

[0035] In particular, the piston actuation system is formed by a hydraulic actuation system known as a concentric slave cylinder or CSC system, which comprises a fixed chamber containing a hydraulic fluid and connected to a fixed part of the actuation system, and a movable part of a piston that moves axially in translation under the action of the pressurized hydraulic fluid and is connected to the clutch module via rolling bearings.

[0036] This hydraulic actuation system is integrated in a similar manner into systems using ball rail systems.

[0037] According to one aspect of the invention, an axial bearing is interposed between the piston actuation system and the output disc carrier, the axial bearing being formed in particular by an axial needle roller thrust bearing or a sliding axial bearing.

[0038] According to one aspect of the invention, the piston comprises an axial portion passing through an axial opening in the elastic means.

[0039] According to one aspect of the invention, the piston further includes an axial portion extending through the axial opening in the output disc carrier.

[0040] According to one aspect of the invention, the clutch module is of the wet clutch type, which is immersed in a transmission fluid such as oil for operation.

[0041] The invention also relates to a torque transmission system, in particular for a motor vehicle, comprising a clutch module as described above and an assembled input module, the input module being located upstream (in the torque transmission direction) of the clutch module.

[0042] According to one aspect of the present invention, the input module includes an input tray positioned facing the output tray.

[0043] According to one aspect of the present invention, an input module includes a damper and an input disc carrier positioned radially and / or axially facing an output disc carrier of a clutch module and connected to an output of the damper.

[0044] In a known manner, the damper is used to filter the torsional vibrations (or non-cycling) of the internal combustion engine, independently of whether the clutch module is in an engaged / disengaged state.

[0045] According to one aspect of the invention, the input and output disc carriers comprise radial areas facing each other and an axial bearing is interposed between these radial areas facing each other, the axial bearing being formed in particular by an axial needle roller thrust bearing or a sliding axial bearing.

[0046] According to one aspect of the invention, the axial bearing, the rolling bearing mounted on the actuation system and the actuation system are arranged to be axially stacked (ie located on a geometric line parallel to the first rotation axis) and have substantially the same radial distance from the first rotation axis of the clutch module.

[0047] According to one aspect of the invention, the clutch module and the damping module are placed in a housing formed by a casing.

[0048] According to one aspect of the invention, the bottom of the housing contains transmission fluid, and the clutch module is immersed in the transmission fluid.

[0049] According to one aspect of the invention, the clutch module is mounted with the input module via a connection between the input disc carrier and the output web of the damper, in particular using rivets or welding.

[0050] The torque transmission system is particularly used in hybrid vehicles comprising an internal combustion engine and a rotary electric machine, the clutch module being used to couple / decouple the internal combustion engine with respect to a driveline of the vehicle. BRIEF DESCRIPTION OF THE DRAWINGS

[0051] Other characteristics, details and advantages of the invention will become more apparent on reading the following description and studying a number of exemplary embodiments given by way of non-limiting indication with reference to the accompanying drawings, in which:

[0052] Figure 1 is a cross-sectional view of a torque transmission system according to one embodiment of the present invention;

[0053] Figure 2 yes Figure 1 Detailed view of the system;

[0054] Figure 3 is a cross-sectional view of a torque transmitting system according to another embodiment that does not form a part of the present invention. DETAILED DESCRIPTION

[0055] The features, variants and different embodiments of the present invention can be combined with each other in various combinations, as long as they are not mutually incompatible or mutually exclusive. In particular, if this feature selection is sufficient to give technical advantages and / or distinguish the present invention from the prior art, it is possible to envision a variant of the present invention that only includes the selection of the following features, separated from the other features described.

[0056] Figure 1 A cross-section of a torque transmitting system 100 is depicted in accordance with one embodiment of the present invention.

[0057] The torque transmitting system 100 forms part of a driveline of a motor vehicle transmission.

[0058] The transmission system includes an electric motor 200 provided with a stator and a rotor.

[0059] The vehicle may be propelled by an internal combustion engine or an electric motor 200 as desired.

[0060] The torque transmission device 100 comprises a damper 300 having a damper input element 301 which is rotatable about a first axis of rotation X. The damper 300 forms an input module 350 within the meaning of the present invention. In a known manner, the damper 300 serves to filter torsional vibrations (or acyclic) of the internal combustion engine, independently of whether the clutch module 1 is in an engaged / disengaged state.

[0061] The washer-type damper input element 301 is rotatably coupled to the crankshaft of the internal combustion engine in a manner known per se.

[0062] The damper 300 includes a torque output element 310 rotatably coupled to, for example, an input shaft of a gearbox.

[0063] The input element 301 is pivotable about a first rotational axis X relative to the output element 310 .

[0064] The damper 300 includes a plurality of elastic members 304 that resist rotation of the output element 310 relative to the input element 301 .

[0065] In the example discussed, the elastic element 304 is a helical spring.

[0066] On either side of the spring 304 is an input element 301 which can be locally moved closer together between the springs 304 so as to define circumferential bearing areas for cooperating with the springs. These bearing areas make it possible to transmit torque between the input element 301 and the spring 304.

[0067] The input element 301 is extended centrally by an axial extension 307 to cooperate with the output element 310 via a centering needle bearing 308, thereby centering the input element 301 with the housing 70. In the center, the input element 301 is driven by the crankshaft hub 306 via splines.

[0068] The torque output element 310 here is an intermediate element arranged between the elastic member 304 and the clutch module 1 for transmitting torque.

[0069] The clutch module 1 and the input module 350 are placed in a housing 71 formed by a casing 70 .

[0070] The bottom of the housing 70 contains a transmission fluid, which is in particular oil, and the clutch module is immersed in the transmission fluid. Therefore, the clutch module 1 is wet. It operates immersed in a transmission fluid such as oil. In this case, an annular sealing ring 98 is provided to seal the housing 70.

[0071] The housing 70 is formed from two assembled half-shells 72 .

[0072] The intermediate element 310 includes a web 311 having a notch 312 at its radial outer periphery, and the notch 312 is circumferentially interposed between the springs 304 .

[0073] These recesses 312 define a circumferential bearing area for transmitting torque between the spring 304 and the output element 310 .

[0074] The clutch module 1 comprises an output disc carrier 3 which is rotationally fixed to an output hub 302 .

[0075] The input module 350 comprises an input disc carrier 2 positioned radially facing the output disc carrier 3 of the clutch module 1 .

[0076] The input disc carrier 2 is fixed to the intermediate member 310 so as to rotate therewith.

[0077] Therefore, the input module 350 includes the damper 300 and the input disc carrier 2 which is placed facing the output disc carrier 3 of the clutch module 1 and connected to the output of the damper 300 .

[0078] When assembled with the input module 350 , the clutch module 1 is located radially inside the perimeter PO of the spring 304 passing through the damper 300 .

[0079] The clutch module 1 includes a toothed transmission ring 80 configured to cooperate with a rotor shaft 210 of a rotary electric machine 200 having a second rotation axis XM, with a reducer assembly 220 interposed therebetween. The rotor shaft 210 is rotationally guided relative to the housing 70 by a ball bearing 81 .

[0080] The speed reducer assembly 220 may be configured to allow for multiple gear ratios.

[0081] The transmission ring 80 is welded to the output disc carrier 3, for example.

[0082] The second rotational axis XM of the electric motor 200 is radially offset relative to the first rotational axis X of the clutch module 1 , these axes being parallel to each other.

[0083] The transmission ring 80 axially faces the elastic element 304 of the damper 300 .

[0084] “Axially facing” means that the transmission ring 80 and the elastic member 304 of the damper are located on the same geometric cylinder (imaginary curve) centered on the first rotation axis X of the clutch module 1 and are offset relative to each other parallel to the first rotation axis X.

[0085] The clutch module 1 also includes a multi-disc assembly 5 including a plurality of friction discs 6 rotationally fixed to the input disc carrier 2 , a plurality of plates 7 rotationally fixed to the output disc carrier 3 disposed on either side of each friction disc 6 , and friction linings arranged between the plates 7 and the friction discs 6 .

[0086] The friction lining can be fixed, in particular glued or riveted, to the friction disk 6. Two friction linings can be fixed axially on either side of the friction disk.

[0087] In another embodiment, not shown, a single friction lining may be fixed to a single axial side of the friction disk.

[0088] In another embodiment not shown, a single friction lining can be axially fixed to a single axial side of the friction disk, while another friction lining can be fixed to a single axial side of the plate.

[0089] The clutch module 1 can adopt a disengaged position and an engaged position in which the plates 7 and the friction discs 6 clamp the friction linings in order to transmit torque between the input disc carrier 2 and the output disc carrier 3 .

[0090] Of course, many other arrangements of friction discs 6 and plates 7 are conceivable.

[0091] The output disc carrier 3 carries an axially fixed reaction element 11 against which the multi-disc assembly 5 is clamped in an engaged position. The reaction element 11 takes the form of a continuous annular ring around the first axis X of rotation.

[0092] The plate 7 and the friction disc 6 are located radially between the cylindrical skirt 12 of the output disc carrier 3 and the cylindrical skirt 14 of the input disc carrier 2 .

[0093] The clutch module 1 may include 2 to 7 friction plates, for example 4 friction plates.

[0094] The clutch module 1 further comprises a piston 20 configured to clamp the multi-disc assembly 5 when the clutch module 1 is in the engaged position and to release the multi-disc assembly 5 when the clutch module 1 is in the disengaged position. The piston 20 presses on a disc support plate 29 which can clamp the multi-disc assembly 5. The disc support plate 29 is rotationally connected to the output disc carrier 3 with the possibility of axial movement.

[0095] The clutch module 1 further comprises elastic means 30 configured to exert an elastic restoring force on the piston 20 so as to maintain the piston 20 in the engaged position. This clutch module 1 is of the type known as the normally closed type.

[0096] The clutch module 1 further comprises a piston actuation system 40 for actuating the piston 20 and axially supported against the piston 20 on the one hand and against the output disc carrier 3 on the other hand and configured to overcome the elastic restoring force of the elastic means 30 to bring the piston 20 from the engaged position to the disengaged position.

[0097] The transmission ring 80, the multi-disc assembly 5 and the piston actuation system 40 are radially stacked.

[0098] In other words, the transmission ring 80 , the multi-disc assembly 5 and the piston actuation system 40 are substantially in the same plane perpendicular to the first axis of rotation X of the clutch module 1 .

[0099] The input disc carrier 2 and the output disc carrier 3 work towards the first axis of rotation X and respectively comprise radial areas 16 and 15 facing each other and between which an axial bearing 37 formed by an axial needle roller thrust bearing or a sliding axial bearing is interposed.

[0100] A further axial bearing 38 formed by an axial needle roller thrust bearing or a plain axial bearing is interposed between the piston actuation system 40 and the radial region 15 of the output disc carrier 3 .

[0101] The piston 20 cooperates with a rolling bearing 39 mounted on the actuation system 40 , resulting in the actuation system 40 cooperating with the piston 20 , wherein the piston 20 is free to rotate about the first axis of rotation X relative to the actuation system 40 .

[0102] The axial bearings 37 and 38 , the rolling bearing 39 mounted on the actuation system 40 and the actuation system 40 are arranged axially stacked, ie on a geometric line XE parallel to the first rotation axis X and at substantially the same radial distance from the first rotation axis X of the clutch module 1 .

[0103] The elastic device 30 comprises a Belleville-type elastic washer 36 on a circlip 49. The circlip 49 is attached between the end lugs 23 of the piston 20. Furthermore, the elastic device 30 is axially supported on the output disc carrier 3.

[0104] Alternatively, the elastic means 30 may comprise at least one corrugated washer.

[0105] In an alternative not shown, the elastic means comprises a plurality of helical springs connected together at their ends. This is known as a "spring pack". In all cases, the piston 20 may comprise fingers passing through the springs in order to clamp the multi-disc assembly.

[0106] The actuation system 40 bears against the side 27 of the piston 20 which faces the input module 350 .

[0107] The clutch module 1 is mounted with the input module 350 via a connection, in particular using rivets, between the input disc carrier 2 and the output web 311 of the damper. Welding may be used instead of rivets.

[0108] The actuation system 40 is configured to axially move the piston 20 from the engaged position to the disengaged position. The actuation system 40 may be of the mechanical, electromechanical, electromagnetic or hydraulic type.

[0109] exist Figure 1 and 2 In the example of FIG. 4 , the actuation system 40 is formed by a ball guide system 42 including a first guide rail 43 and a second guide rail 44 .

[0110] The annular space 45 between the first guide rail 43 and the second guide rail 44 accommodates balls (not shown).

[0111] The first guide 43 takes the form of a ring which bears against the axial bearing 38. This first guide 43 is connected in rotation to an actuating lever 47, for example via a spline or via a weld 48. This actuating lever 47 is formed by a wheel which is toothed on the inside in order to mesh with the second guide 44 and on the outside in order to mesh directly or indirectly with a pinion extending from the actuating motor in the case of a ball guide system.

[0112] As described below, in the case where the ball rail system 42 is replaced by a fork-type actuation system, the actuation lever 47 is formed by an outer toothed wheel so as to engage directly or indirectly with the lever of the fork.

[0113] The second guide 44 takes the form of a toothed ring carrying the rolling bearing 39 .

[0114] The guide rails 43 and 44 are of suitable shape so that they allow the piston 20 to move axially when rotated relative to each other by an electric motor (not shown). The electric motor is connected to an actuating rod 47.

[0115] In a variant not shown, the piston actuation system is formed by a hydraulic actuation system known as a concentric slave cylinder or CSC system, which comprises a fixed chamber containing a hydraulic fluid and connected to a fixed part of the actuation system, and a movable part of the piston 20 which moves axially in translation under the action of the pressurized hydraulic fluid and is connected to the clutch module 1 via a rolling bearing 39.

[0116] This hydraulic actuation system is integrated in a similar manner into systems using ball rail systems.

[0117] In summary, the torque transmission system 100 performing clutch and damper functions is intended for a hybrid vehicle comprising an internal combustion engine and a rotary electric machine, the clutch module 1 being intended to couple / disconnect the internal combustion engine with respect to the vehicle's driveline.

[0118] Figure 3 Another exemplary embodiment is shown in which the ball rail system 42 is replaced by a fork-operated actuation system 400 .

[0119] The fork-operated actuation system 400 comprises a fork 401 configured to be driven axially (parallel to the first axis of rotation X) directly or indirectly by a mechanical drive system connected to the housing 70 and comprising an electric motor (not shown). The fork 401 bears axially at its radially inner end against a circlip 403 fixed to a ring 402 .

[0120] The fork 401 axially pulls the ring 402 by bearing axially against the circlip 403 so as to pass from the engaged position to the disengaged position.

[0121] In the disengaged position, an axial gap is created between the ring 402 and a fixed support 406 connected to the housing 70. Thus, as in the above-described exemplary embodiment, the piston 20 can be axially moved between the engaged position and the disengaged position.

Claims

1. A normally closed clutch module (1) having a first rotation axis (X) and comprising: - an output disc carrier (3) rotatable relative to a first axis of rotation (X); - at least one friction disk (6), in particular a multi-disc assembly (5); - a piston (20) configured to clamp the friction disc when the clutch module is in an engaged position and to release the friction disc when the clutch module is in a disengaged position; - elastic means (30) configured to exert an elastic restoring force on the piston (20) so as to maintain the piston (20) in the engaged position; - a piston actuation system (40) for actuating the piston (20) and resting axially on the piston (20) on the one hand and on the output disc carrier (3) on the other hand, preferably via rolling bearings, and configured to bring the piston (20) from the engaged position to the disengaged position against the elastic restoring force of the elastic means (30).

2. The clutch module (1) according to the preceding claim, wherein: The elastic device (30) is axially supported on the output disc bracket (3).

3. A clutch module (1) according to any one of the preceding claims, configured to be assembled in a torque transmission system (100), in particular for a motor vehicle, the torque transmission system further comprising an input module (350) cooperating with the clutch module (1), the input module (350) being located upstream of the clutch module.

4. The clutch module (1) according to the preceding claim, wherein: When assembled with the input module (350), the clutch module (1) is located radially inside the periphery of the elastic member (304) of the damper (300) passing through the input module (350).

5. The clutch module (1) according to any one of the preceding claims, wherein: The clutch module comprises a transmission ring (80) configured to cooperate in rotation with a rotor shaft (210) of a rotating electric machine, a reducer assembly (220) may be inserted between the transmission ring and the rotor shaft of the rotating electric machine, and the transmission ring (80) connected to the output disc bracket (3) is particularly engaged with a gear connected to the rotor shaft (210) of the rotating electric machine via the reducer assembly (220).

6. The clutch module (1) according to the preceding claim, wherein: The transmission ring (80) axially faces the elastic member (304) of the damper.

7. The clutch module (1) according to any one of claims 5 and 6, wherein: The transmission ring (80), the multi-disc assembly (5) and the actuation system (40) for actuating the piston (20) are radially stacked.

8. The clutch module (1) according to any one of the preceding claims, wherein: The piston (20) cooperates with a rolling bearing mounted on the actuation system (40) so that the actuation system (40) cooperates with the piston (20), wherein the piston (20) is free to rotate relative to the actuation system (40) around the first rotation axis (X).

9. The clutch module (1) according to any one of the preceding claims, wherein: The piston (20) comprises at least one actuating finger axially passing through the elastic means (30).

10. The clutch module (1) according to any one of the preceding claims, wherein: The elastic device (30) comprises at least one elastic washer (36), in particular a Belleville spring washer, or a plurality of helical springs connected together at their ends.

11. The clutch module (1) according to any one of the preceding claims, wherein: The actuation system (40) is a ball rail system.

12. A torque transmission system (100), in particular for a motor vehicle, comprising a clutch module according to any of the preceding claims, in particular a wet clutch module, and an input module (350) assembled together, the input module (350) being upstream of the clutch module, the input module and the clutch module being in particular placed in a housing (70), the clutch module (1) being in particular connected to an electric machine.

13. The torque transmission system (100) according to the preceding claim, wherein The input module (350) comprises a damper and an input disc carrier (2), the input disc carrier (2) being positioned axially and / or radially facing the output disc carrier (3) of the clutch module (1) and being connected to the output of the damper (300), and in particular, the actuation system (40) being supported against the side of the piston (20) which faces the input module (350).

14. The torque transmission system (100) according to claim 12 or 13, wherein: The input module comprises an input disc carrier (2) placed facing an output disc carrier (3), and the input disc carrier (2) and the output disc carrier (3) comprise radial areas (15, 16) facing each other, and an axial bearing (37) is interposed between these radial areas facing each other, the axial bearing (37) being particularly formed by an axial thrust needle roller bearing or a sliding axial bearing.

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