FR3074241A1 - WET CLUTCH SYSTEM SUPPLIED WITH FLUID BY A CHANNEL FORMED BETWEEN TWO SLEEVES - Google Patents

Abstract

A clutch mechanism (18) has a disk carrier assembly (22) defining an interior volume (200) and at least a first wet friction (E1) housed in the interior volume (200) of the disk carrier assembly ( 22). A guide bearing (30) guides the disk carrier assembly (22) in rotation about an axis of revolution (100). The guide bearing (30) is mounted on a clutch carrier (72), forming at least one passage channel (86) connecting a fluid inlet (88) opening out of the carrier assembly ( 22) at a fluid outlet (90) located axially away from the fluid inlet (88) and opening into the interior volume (200) of the disk carrier assembly (22) radially between the axis of revolution (100) and the first wet friction (E1), a first fluid path being formed in the interior volume (200) of the disk carrier assembly (22) between the fluid outlet (90) and the first wet friction ( E1) for supplying fluid with the first wet friction (E1). The clutch support (72) has two coaxial sleeves (74, 76) aligned with the axis of revolution (100), consisting of an outer sleeve (74) and an inner sleeve (76) at least partially positioned at the inside the outer sleeve (74).

Description

WET CLUTCH SYSTEM SUPPLIED IN FLUID THROUGH A FORMED CHANNEL BETWEEN TWO SLEEVES

TECHNICAL FIELD OF THE INVENTION The invention relates to the circulation of a fluid, in particular a cooling and or lubrication fluid, in a clutch system, in particular in order to convey the fluid to a wet friction of the clutch system.

STATE OF THE PRIOR ART In document FR 3 049 021 is described a wet double clutch system intended to be installed between a drive shaft and at least one gearbox with two coaxial input shafts. The clutch system includes a clutch mechanism comprising a disc carrier assembly defining an interior volume in which are housed two wet frictions and two force transmission members for applying a force to each of the two wet frictions. A guide bearing guides the disc holder assembly in rotation about an axis of revolution. The clutch system further comprises a clutch actuator situated outside the interior volume of the disc holder assembly, the clutch actuator comprising a fixed casing in which two annular chambers are formed, each closed by an annular piston arranged to move axially parallel to the axis of revolution relative to the housing. Clutch bearings allow the force transmission from the pistons to the force transmission members. The guide bearing is mounted on a tubular extension of the clutch housing which has a clutch support function. To supply wet friction with coolant, the tubular extension of the clutch housing includes an axial bore providing a supply channel connecting a fluid inlet opening outside the disc holder assembly to a fluid outlet produced by a radial bore at the end of the tubular extension of the casing, and opening into the interior volume of the disc holder assembly, radially between the axis of revolution and the first wet friction. A fluid path is formed in the interior volume of the disc assembly between the fluid outlet and the first wet friction.

This architecture offers the advantage of grouping the control functions outside the volume delimited by the rotating disc holder assembly, in a technological brick, namely an annular actuator whose casing remains fixed, which facilitates its energy supply. The supply of wet friction with coolant also passes through channels formed in parts which are not in rotation, which simplifies the supply and prevents the flow from being disturbed by the effects of centrifugation. However, this result is obtained at the cost of increased complexity of the single part which constitutes the actuator housing and the clutch support, in which axial and radial bores must be made to constitute the fluid supply channel. cooling and fluid outlet.

SUMMARY OF THE INVENTION The invention aims to remedy the drawbacks of the state of the art and to propose a simple structure for conveying a fluid, in particular cooling or lubrication, inside a door assembly - wet friction clutch mechanism discs.

To do this, there is proposed, according to a first aspect of the invention, a clutch system intended to be installed between a drive shaft and at least one transmission shaft, the clutch system comprising:

a clutch mechanism comprising a disc holder assembly defining an interior volume and at least one first wet friction housed in the interior volume of the disc holder assembly;

a guide bearing for guiding the disc carrier assembly in rotation about an axis of revolution;

a clutch support, the guide bearing being mounted on the clutch support, the clutch support forming at least one passage channel connecting a fluid inlet opening out of the disc holder assembly to a fluid outlet located axially away from the fluid inlet and opening into the interior volume of the disc holder assembly, radially between the axis of revolution and the first wet friction, a first fluid path being formed in the volume inside the disc holder assembly between the fluid outlet and the first wet friction to supply the first wet friction with fluid.

The clutch support comprises two coaxial sleeves aligned with the axis of revolution, consisting of an outer sleeve and an inner sleeve positioned at least partially inside the outer sleeve, the outer sleeve and the inner sleeve being two separate parts, the passage channel being formed between an inner wall of the outer sleeve and an outer wall of the inner sleeve.

By making the passage channel between two separate parts fitted into one another, drilling is avoided. As the two sleeves are fixed, the circulation of the fluid in the passage channel is not disturbed by the rotating parts. The circulation of the fluid between the fluid outlet and the friction is facilitated by centrifugation in the support of the clutch mechanism.

The fluid outlet may include one or more outlet openings distributed over a periphery of the clutch support, if necessary in the same plane perpendicular to the axis of revolution, or in several rows in at least two separate planes perpendicular to the axis of revolution, for optimal distribution of the fluid in the interior volume of the disc holder assembly. Advantageously, the fluid outlet may include a plurality of outlet openings passing through the outer sleeve.

According to one embodiment, the fluid inlet and the fluid outlet are located axially on either side of the guide bearing. If necessary, the fluid outlet is located between a needle bearing of the clutch mechanism, located inside the disc holder assembly and the rolling bearing.

According to one embodiment, the clutch support comprises an interface for fixing to a casing of a propulsion unit, in particular to a gearbox casing. This interface may in particular consist of fixing holes, for inserting fixing elements, for example threaded rods or rivets.

According to one embodiment, the clutch mechanism comprises at least a first force transmission member for applying a force to the first wet friction, the clutch system further comprising an annular clutch control located outside of the internal volume of the disc holder assembly and aligned with the axis of revolution, the clutch control comprising at least a first control housing, a first control output arranged to move axially parallel to the axis of revolution relative to the first control housing and a first rotary stop between the first control output and the first force transmission member, the first control housing being fixed relative to the clutch support. The first control output can be driven in particular electromagnetically, electromechanically (for example by a motor driving a worm) or, preferably, hydraulically, the control output then being a piston closing a variable volume chamber formed in the first control housing. In all cases, the first control housing is fixed, so that the power supply to the actuator is simple.

According to one embodiment, the first control housing is in one piece with one of the two coaxial sleeves, which can be the outer sleeve or the inner sleeve.

Alternatively, the first control housing consists of one or more separate parts of the two coaxial sleeves.

According to one embodiment, the outer sleeve has an intermediate orifice located axially between the fluid inlet and the fluid outlet, the intermediate orifice connecting the fluid passage channel to a volume in which the first is located rotary stop. This ensures the delivery of part of the fluid passing through the passage channel to the first rotary stop.

According to one embodiment, one of the two coaxial sleeves has a centering or hooping surface in contact with a concave cylindrical wall of the first control housing.

According to one embodiment, one of the two coaxial sleeves is formed in one piece with a base extending radially outwards, the first control housing being in direct or indirect axial support against a shoulder of the base. Advantageously, one or more of the following options can be provided:

The base is provided with supply holes for a variable volume chamber of the first control housing, closed by an annular piston forming the first control outlet.

The base has an interface for fixing to a casing of a propulsion unit, in particular to a gearbox casing.

The base has the fluid inlet

The base is formed in one piece with the inner sleeve.

The base is made in one piece with the outer sleeve.

Preferably, the two coaxial sleeves are fixed to each other by a fixing interface. One can in particular provide the fixing interface is constituted by two cylindrical bearing surfaces hooped or glued to each other. Alternatively, provision may be made for the fixing interface to be constituted by a fixing flange formed in one piece with the inner sleeve, coming to bear against a shoulder formed in one piece with the outer sleeve.

According to one embodiment, the passage channel is located between the fluid inlet and the fixing interface. Alternatively, the passage channel can be located between the fluid outlet and the attachment interface.

Clutch system according to any one of the preceding claims, characterized in that the bearing comprises an outer ring secured to the disc holder assembly and an inner ring hooped on the clutch support. 11 may in particular be a rolling bearing, preferably an angular contact rolling bearing capable of taking up axial and radial forces.

If necessary, the inner ring can be shrunk directly onto one of the two coaxial sleeves.

According to a particularly advantageous embodiment, the clutch support comprises an intermediate ring disposed between the two coaxial sleeves and the guide bearing, and a blocking member, preferably reversible, interacting with the intermediate ring and with the two coaxial sleeves to lock the intermediate ring in position relative to the two coaxial sleeves. The locking member may in particular be an elastic ring. This arrangement facilitates mounting. The clutch can be configured to preserve an access shaft to the locking member open axially opposite the actuator.

According to one embodiment, the fluid outlet includes at least one lumen passing through the intermediate ring.

According to one embodiment, the intermediate ring comprises an annular raceway for a bearing, preferably a needle bearing, of the clutch mechanism, the guide bearing and the annular raceway being located axially on the side on the other side of the fluid outlet.

According to one embodiment, the clutch support includes a bypass orifice connecting the fluid passage channel to an interior cavity of the interior volume of the disc holder assembly housing at least one internal bearing of the mechanism. clutch. This ensures the delivery of part of the fluid passing through the passage channel to the internal bearing. This internal bearing can in particular be a needle stop.

The architecture is applicable to single or double wet clutches.

According to one embodiment, the clutch mechanism comprises at least a second wet friction housed in the interior volume of the disc holder assembly and at least a second force transmission member for applying a force to the second wet friction, a second fluid path being formed in the interior volume of the disc holder assembly between the fluid outlet and the second wet friction, the second fluid path and the first fluid path having, if necessary, a common portion . In the event that the two fluid paths have a common portion, the fluid outlet may include one or more orifices supplying this common portion. Inside the clutch mechanism, fluid passages are then provided between the first wet friction and the second wet friction.

In the event that the two fluid paths are separated, it is expected that the fluid outlet comprises one or more first orifices for supplying the first fluid path inside the clutch mechanism and one or more second supply ports of the second fluid path inside the clutch mechanism.

According to a preferred embodiment, the clutch control comprises a second control output arranged to move axially parallel to the axis of revolution and a second rotary stop between the second control output and the second transmission member by force. The second control output can be guided by a casing common with the first control output or by a separate casing, the two casings being in this case fixed relative to one another.

BRIEF DESCRIPTION OF THE FIGURES Other characteristics and advantages of the invention will emerge on reading the description which follows, with reference to the appended figures, which illustrate:

Figure 1, an axial section of a clutch system according to a first embodiment of the invention;

Figure 2, an axial section of a clutch system according to a second embodiment of the invention;

Figure 3, an axial section of a clutch system according to a third embodiment of the invention;

Figure 4, an axial section of a clutch system according to a fourth embodiment of the invention;

Figure 5, a detail of a sleeve of the clutch system of Figure 4;

Figure 6, an axial section through a clutch system according to a fifth embodiment of the invention.

For the sake of clarity, identical or similar elements are identified by identical reference signs in all of the figures.

DETAILED DESCRIPTION OF EMBODIMENTS In FIG. 1 is illustrated an exemplary embodiment of a clutch system, in the form of a wet double clutch 10 intended to be installed between a motor shaft 12 and two shafts d coaxial input 14, 16 of a gearbox to form a propulsion unit of a vehicle. The clutch system 10 comprises a wet double clutch mechanism 18 and an annular clutch control 20, the wet double clutch mechanism 18 rotating about an axis of revolution 100 which is also the axis of revolution of the motor shaft and two shafts 14.16.

The clutch mechanism 18 includes a disc holder assembly 22 comprising an input disc holder 24 and an input web 26 for securing the input disc holder 24 to a hub 25 fitted in the motor shaft 12 by a grooved interface. This disc holder assembly 22 defines an interior volume 200 of the clutch mechanism. The input disc holder 24 is here a single piece obtained if necessary by welding several pieces of stamped sheet metal, and has a cylindrical guide surface 28 facing the axis of revolution 100, in which an outer ring is hooped a guide bearing 30, a transverse wall 32 extending radially from the guide surface 28 to an perforated outer skirt 34, and an perforated inner skirt 36 located radially inside the outer skirt 34. The two skirts 34, 36 are located axially on the same side of the transverse wall 32, in axial overlap with one another, in the internal volume 200 of the clutch mechanism.

The outer skirt 34 of the input disc holder is provided with inner grooves. The wet double clutch mechanism 18 further comprises a first outlet web 38, which comprises an openwork skirt 40 provided with external grooves located opposite and at a distance from the internal grooves of the external skirt 34 and a first interface for fixing in rotation 42 to a first input shaft 14 of the gearbox. In the annular volume delimited radially by the outer skirt 34 of the input disc holder 24 and by the first outlet disc 38 is housed a first wet friction constituted by a first multidisc clutch assembly El comprising a first set of discs d 'in engagement with the grooves of the outer skirt 34 of the input disc holder 24 and a first set of outlet discs in engagement with the grooves 40 of the first outlet web 38. The discs of the first set of outlet discs are interspersed with the discs from the first set of input discs. Preferably elastic washers are arranged between the discs and tend to separate them from each other. The first wet friction El thus constitutes in a known manner a first kinematic connection between the inlet disc holder 24 and the first outlet web 38.

The inner skirt 36 is also provided with inner grooves. The wet double clutch mechanism 18 also comprises a second outlet wall 44, which comprises a second outlet grooved skirt 46 located opposite and at a distance from the grooves of the inner skirt 36 and a second interface for fixing in rotation 48 to a second gearbox input shaft 16. In the annular volume delimited radially by the internal skirt 36 of the input disc carrier 24 and by the second output web 44 is housed a second wet friction E2 constituted by a second multidisc clutch assembly comprising a second set of discs d 'engagement with the grooves of the inner skirt 36 of the input disc holder 24, and a second set of outlet discs engaged with the grooves of the skirt 46 of the second outlet veil 44. The discs of the second set output discs are interspersed with the discs of the second set of input discs. Elastic washers are preferably placed between the discs and tend to separate them from each other. The second multidisc clutch assembly E2 thus constitutes, in a known manner, a second kinematic connection between the input disc holder 24 and the second output disc 44.

The transverse wall 32 has first passage openings 50 distributed circumferentially and opening into the volume delimited by the outer skirt 34 and the first outlet web 38 and second passage openings 52 distributed circumferentially and opening into the volume delimited by the inner skirt 36 and the second outlet veil 44.

The clutch control 20 is of annular shape and aligned on the axis of revolution 100 so as to surround the two coaxial shafts 14,16 of the gearbox input, or the hub 25. It s here acts of a hydraulic control which comprises a first control output constituted by a first piston 54, and a first rotary stop 56 bearing against a first force transmission member 58 of the clutch mechanism, which passes through the first openings of passage 50 of the input disc holder 24 to allow a force transmission from the first piston 54 to the first wet friction El. The clutch control 20 further comprises a second control output constituted by a second piston 60, located radially inside the first piston 54, and a second rotary stop 62 bearing against a second force transmission member 64 of the clutch mechanism, which pass through the second openings passage 52 of the input disc holder 24 to allow a force transmission from the second control output 60 to the second wet friction E2.

The clutch control 20 preferably comprises a single fixed casing 66 in which are formed annular chambers 68, 70 in which the two pistons 54, 60 slide.

The clutch system also includes a clutch support 72 for supporting the clutch mechanism 18 and the clutch control 20.

The clutch support 72 is a fixed sub-assembly comprising two coaxial sleeves aligned on the axis of revolution, consisting of an outer sleeve 74 and an inner sleeve 76 positioned inside the outer sleeve 74 The inner sleeve 76 and the outer sleeve 74 are two separate parts. The inner sleeve 76 is a thin piece, made of light metal sheet or plastic, comprising a tubular part 76.1 and a fixing flange 76.2, which abuts against a shoulder formed on the outer sleeve 74, the two sleeves 74, 76 being secured to one another at this fixing interface 77 by gluing, welding or any other means. The opposite end of the inner sleeve 76 is in contact with an inner shoulder 74.1 of the outer sleeve 74.

The outer sleeve 74 is formed, in this embodiment, by a more massive piece, which further comprises, at a proximal end of the outer sleeve 74, a base 78 projecting radially outwardly relative to the outer sleeve 74. The sleeve 74 proper forms in its proximal part a cylindrical centering surface 74.2 for an adjusted or shrunk fitting of the casing 66 of the clutch control 20. The casing 66 comes to bear axially against a shoulder 78.1 of the base 78. The base 78 includes, where appropriate, channels for supplying pressure to the chambers 68, 70 of the hydraulic control 20. The base 78 further comprises an interface for fixing 78.2 to a casing 80 of the gearbox . The attachment interface 78.2 can take various forms, and in particular that of a toothing fitted into a toothing formed in the casing 80 of the gearbox.

The clutch support 72, in this embodiment and preferably, also comprises an intermediate ring 82 fitted on a bearing 74.3, preferably cylindrical, turned radially outward and formed at the distal end of the outer sleeve 74. The intermediate ring 82 is preferably locked in position by a stop shoulder 74.4 of the outer sleeve 74 and an elastic ring 84 engaged in and a retaining groove 74.5 of the outer sleeve 74. The intermediate ring 82 can be keyed or hooped on the bearing 74.3 formed on the outer sleeve 74, to ensure a connection in rotation. The intermediate ring 82 has a cylindrical seat 82.1 turned radially outwards on which the fixed inner ring of the guide bearing 30 is hooped. Preferably, the intermediate ring 82 also forms a raceway 82.2 for an internal bearing 83 of the mechanism clutch, here an annular plane raceway for a needle guide bearing of one of the output sails. The shoulder 74.4 is optional, insofar as the axial forces on the intermediate ring 82 in the operating conditions are always unidirectional, from right to left in the figures.

We can thus assemble blind a sub-assembly consisting of the clutch mechanism 18, the guide bearing 30 and the intermediate ring 82 on a sub-assembly consisting of the two sleeves 74, 76 and the control clutch 20, by simple axial fitting. Preferably, the various elements of the clutch mechanism 18 are shaped so as to preserve, in a particular angular position, a well 300 of access through the clutch mechanism 18 to the elastic ring 84, which allows to consider a non-destructive disassembly.

Remarkably, a passage channel 86 is formed between an inner wall 74.6 of the outer sleeve 74 and an outer wall 76.3 of the inner sleeve 76. This channel 86 may for example be constituted by one or more grooves extending parallel to the axis of revolution, formed in the thickness of the outer sleeve or in the thickness of the inner sleeve, for example six grooves parallel to the axis of revolution 100 and arranged at 60 ° from each other. Advantageously, the grooves are connected to each other by an annular groove, which makes it possible to supply them all by a fluid inlet 80 with a single opening. The passage channel 86 connects a fluid inlet 88 constituted by a conduit formed in the base 78 and opening out of the disc holder assembly 22, to a fluid outlet 90 located axially at a distance from the inlet of fluid 88 and opening into the internal volume 200 of the disc holder assembly 22, radially between the axis of revolution 100 and the wet friction El, E2.

The fluid outlet 90 comprises one or more oblique slots 90.1 formed in the body of the outer sleeve 74 and one or more slots 90.2 of general radial direction formed in the intermediate ring 82.

By supplying cooling fluid to the fluid inlet 88 from a cooling pump, coolant is supplied, in practice a liquid which can also have a lubrication function, through the fluid passage 86, up to at the fluid outlet 90. In contact with the rotating walls of the clutch mechanism 18, the fluid is centrifuged and sprayed in the direction of the wet friction El and E2. A fluid path is formed in the internal volume of the disc holder assembly between the fluid outlet 90 and the second wet friction E2 and between the second wet friction E2 and the first wet friction El, passing through radial slots provided at this effect in the perforated skirts 46, 58 of the outlet webs 38, 44 and the perforated skirt 36 of the input disc holder. The cooling fluid emerges from the internal volume 200 of the clutch mechanism 18 through the perforated skirt 34 of the input disc carrier 32 and is collected in the fixed casing of the clutch system, which is here an extension of the gearbox casing. speed 80.

The clutch system of Figure 2 differs from the previous only by the addition of an intermediate orifice 92 located axially between the fluid inlet 88 and the fluid outlet 90, the intermediate orifice connecting the channel passage of fluid 86 to a volume in which the rotary stops 56, 62 are located.

The clutch system of Figure 3 differs from the embodiment of Figure 1 only by the addition, at the fluid outlet 90, of a bypass port 94 of axial orientation to connect the fluid passage channel 86 to an interior cavity of the disc holder assembly housing the needle guide stops of the outlet webs 38, 44.

The clutch system of Figure 4 differs from the previous embodiments in that the base 78 is formed in one piece with the inner sleeve 76, as illustrated in Figure 5, which simplifies the fluid inlet 88. The attachment interface 77 between the inner sleeve 76 and the outer sleeve 74 is positioned at the distal end of the two sleeves 74, 76, the fluid outlet 90 being positioned between the fluid inlet 88 and the fixing interface 77. The fixing between the two sleeves 74, 76 can be carried out by shrinking, gluing, or any other means ensuring sufficient tightness.

The fluid passage channel 86 is formed by a plurality of grooves 76.4 extending parallel to the axis of revolution 100. The grooves are formed for example by machining the outer wall 76.3 of the inner sleeve 76. The grooves 76.4 are distributed circumferentially around the axis of revolution 100. The fluid inlet 88 is produced by holes 78.3 through the base 78 in the axis of each of the grooves 76.3. The base 78 is also provided with bores constituting the fixing interface 78.2 for fixing the clutch support 72 to a gearbox housing by means of screws. Finally, the base 78 is also provided with orifices 78.4, 78.5 opening into channels 68.1, 70.1 formed in the housing 66 of the clutch control for supplying the chambers 68, 70 with high pressure fluid.

The clutch system of Figure 6 differs from the previous embodiment in that the outer sleeve 74 is in one piece with the housing 66 of the clutch control 20.

Naturally, the examples shown in the figures and discussed above are given only by way of illustration and not by way of limitation. It is explicitly provided that the various embodiments illustrated can be combined with one another to propose others.

If necessary, the base 78 can be omitted.

11 is possible to provide two separate control housings for the actuation of the first control output 54 and the second control output 60.

The intermediate ring 82 can also be omitted, the inner ring of the guide bearing 30 then being shrunk directly onto one of the sleeves 74, 76, preferably the outer sleeve 74. Other variants are possible by providing that the inner sleeve 76 is projecting at the distal end of the outer sleeve 74, to constitute the cylindrical bearing surface for supporting the intermediate ring 82, or for shrinking the inner ring of the guide bearing 30.

The invention is also applicable to a wet double clutch mechanism in which the two frictions El, E2 do not overlap axially, 5 in which case it may be necessary to provide a fluid outlet for each friction.

The invention is also applicable to a simple wet clutch mechanism.

It is pointed out that all the characteristics, as they emerge for a person skilled in the art from the present description, the drawings and the attached claims, even if in practice they have only been described in relation with other specified characteristics, both individually and in any combination, may be combined with other characteristics or groups of characteristics disclosed herein, provided that this has not been expressly excluded or that technical circumstances render such impossible or meaningless combinations.

Claims (14)

1. Clutch system (10) intended to be installed between a drive shaft (12) and at least one transmission shaft (14, 16), the clutch system (10) comprising: a clutch mechanism (18) comprising a disc carrier assembly (22) delimiting an interior volume (200) and at least one first wet friction (El) housed in the interior volume (200) of the disc carrier assembly (22) ; a guide bearing (30) for guiding the disc holder assembly (22) in rotation about an axis of revolution (100); a clutch support (72), the guide bearing (30) being mounted on the clutch support (72), the clutch support (72) forming at least one passage channel (86) connecting an inlet of fluid (88) opening outside the disc holder assembly (22) to a fluid outlet (90) located axially away from the fluid inlet (88) and opening into the interior volume (200) of the disc holder assembly (22), radially between the axis of revolution (100) and the first wet friction (El), a first fluid path being formed in the interior volume (200) of the disc holder assembly (22) between the fluid outlet (90) and the first wet friction (El) to supply fluid to the first wet friction (El), characterized in that the clutch support (72) comprises two coaxial sleeves (74, 76) aligned with the axis of revolution (100), consisting of an outer sleeve (74) and an inner sleeve (76) positioned at the mo ins partially inside the outer sleeve (74), the outer sleeve (74) and the inner sleeve (76) being two separate parts, the passage channel (86) being formed between an inner wall (74.6) of the outer sleeve (74) and an outer wall (76.3) of the inner sleeve (76). 2. Clutch system (10) according to claim 1, characterized in that the fluid inlet (88) and the fluid outlet (90) are located axially on either side of the guide bearing (30) . 3. Clutch system (10) according to any one of the preceding claims, characterized in that the clutch mechanism (18) comprises at least a first force transmission member (58) for applying a force to the first wet friction (El), the clutch system (10) further comprising an annular clutch control (20) located outside the interior volume (200) of the disc holder assembly (22) and aligned with the axis of revolution (100), the clutch control (20) comprising at least a first control housing (66), a first control output (54) arranged to move axially parallel to the axis of revolution (100) by relative to the first control housing (66) and a first rotary stop (56) between the first control output (54) and the first force transmission member (58), the first control housing (66) being fixed relative to to the clutch support (72). 4. Clutch system (10) according to claim 3, characterized in that the first control housing (66) is in one piece with one of the two coaxial sleeves (74, 76). 5. Clutch system (10) according to claim 3, characterized in that the first control housing (66) consists of one or more separate parts of the two coaxial sleeves (74, 76). 6. Clutch system (10) according to any one of claims 3 to 5, characterized in that the outer sleeve (74) has an intermediate orifice (92) located axially between the fluid inlet (88) and the fluid outlet (90), the intermediate orifice (92) connecting the fluid passage channel (86) to a volume in which the first rotary stop (56) is located. 7. Clutch system (10) according to any one of claims 3 to 6, characterized in that one of the two coaxial sleeves (74, 76) is formed in one piece with a base (78) s' extending radially outwards, the first control housing (66) being in direct or indirect axial abutment against a shoulder (78.1) of the base (78). 8. Clutch system (10) according to claim 7, characterized in that the base (78) has the fluid inlet (88). 9. Clutch system (10) according to any one of claims 7 to 8, characterized in that the base (78) is formed in one piece with the inner sleeve (74). 10. Clutch system (10) according to any one of claims 7 to 8, characterized in that the base (78) is formed in one piece with the outer sleeve (76). 11. Clutch system (10) according to any one of claims 1 to 10, characterized in that the two coaxial sleeves (74, 76) are fixed to each other by a fixing interface (77) , the passage channel (86) being located between the fluid inlet (88) and the fixing interface (77). 12. Clutch system (10) according to any one of claims 1 to 10, characterized in that the two coaxial sleeves (74, 76) are fixed to each other by a fixing interface (77) , the passage channel (86) being located between the fluid outlet (90) and the fixing interface (77). 13. Clutch system (10) according to any one of the preceding claims, characterized in that the clutch support (72) comprises an intermediate ring (82) disposed between the two coaxial sleeves (74, 76) and the guide bearing (30), and a locking member (84), preferably reversible, interacting with the intermediate ring (82) and with the two coaxial sleeves (74, 76) to lock the intermediate ring in position relative to the two coaxial sleeves. 14. Clutch system (10) according to any one of the preceding claims, characterized in that the clutch mechanism (18) comprises at least one second wet friction (E2) housed in the interior volume (200) of the the disc holder assembly (22) and at least one second force transmission member (64) for applying a force to the second wet friction (E2), a second fluid path being formed in the interior volume (200) of the disc holder assembly (22) between the fluid outlet (90) and the second wet friction (E2), the second fluid path and the first fluid path possibly having a common portion.