CN111771070A

CN111771070A - An operating device with an axially nested slave cylinder; clutch system and drive unit

Info

Publication number: CN111771070A
Application number: CN201980015647.2A
Authority: CN
Inventors: 西蒙·奥特曼; 菲利普·瓦格纳
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2018-02-27
Filing date: 2019-02-12
Publication date: 2020-10-13
Anticipated expiration: 2039-02-12
Also published as: CN111771070B; DE102018104372B3; WO2019166055A1

Abstract

The invention relates to an actuating device (1) for a clutch system (2) of a motor vehicle, comprising two slave cylinders (3, 4) each designed for actuating a clutch (5, 6), wherein each slave cylinder (3, 4) has a piston (7a, 7b) and a housing component (9a, 9b) which guides the piston (7a, 7b) in the direction of movement thereof and which delimits a fluid chamber (8a, 8b) with the piston (7a, 7b), and a supply component (10), on which supply component (10) the slave cylinders (3, 4) are arranged in such a way that: for each slave cylinder (3, 4), the fluid feed channel (11a, 11b) of the supply member (10) is fluidically connected to the fluid chamber (8a, 8b), wherein the housing members (9a, 9b) of the two slave cylinders (3, 4) are supported or supported on the supply member (10) directly one above the other in the axial direction of the longitudinal axis (12) of the supply member (10). The invention further relates to a coupling system (2) suitable for a motor vehicle drive train, having the operating device (1) and a drive unit (30).

Description

An operating device with an axially nested slave cylinder; clutch system and drive unit

Technical Field

The invention relates to an actuating device for a clutch system of a motor vehicle (for example a passenger vehicle, truck, bus or other commercial vehicle), comprising two slave cylinders (a first slave cylinder and a second slave cylinder) which are each designed for actuating a clutch, wherein each slave cylinder has a piston and a housing part which guides the piston in the direction of movement of the piston and which delimits a fluid chamber with the piston, and comprising a supply part on which the slave cylinders are arranged in such a way that: for each slave cylinder, the fluid feed channel of the supply member is fluidically connected to the fluid chamber (of the slave cylinder). This results in an operating device with dual slave cylinders. The invention further relates to a coupling system suitable for a motor vehicle drive-train, having two clutches and the operating device. The invention further relates to a drive unit suitable for a motor vehicle drive train having the clutch system.

Background

Such background art is known, for example, from DE 102013216333 a 1. In this respect, a multi-clutch device, in particular a multi-clutch device designed as a dual clutch device, is disclosed. The multi-clutch device has a first friction clutch and a second friction clutch, wherein the two friction clutches are connected or connectable to the engine shaft on the one hand and to the transmission input shaft on the other hand. The two friction clutches can be operated by means of an operating device, wherein both clutch devices have the same operating device and therefore the friction clutches can be operated simultaneously.

However, the known operating device has proven to have the following disadvantages: the design dimensions are usually relatively large and the installation costs in the respective clutch system are high. The slave cylinders, which are usually supplied by means of so-called swivel joints, are mounted by a relatively large number of mounting steps to the supply member, which is ensured by the swivel joint, and are connected to the assembly of the clutch.

Disclosure of Invention

The object of the present invention is therefore to eliminate the disadvantages known from the background art and in particular to provide an actuating device for a clutch system, which can be installed in a simple manner in the clutch system with the least possible installation space requirement.

According to the invention, the object is achieved by the following solution: the housing members of the two slave cylinders are supported or supported on the supply member directly overlapping each other in the axial direction of the longitudinal axis of the supply member.

This results in a particularly compact axial nesting design of the two slave cylinders. While also significantly reducing the number of components. Simple mounting is also ensured thereby.

Further advantageous embodiments are claimed in the dependent claims and are explained in detail below.

It is accordingly also advantageous if the piston of the respective slave cylinder is connected to the actuating bearing in a rotationally fixed manner on the side facing axially away from the fluid chamber, and if the actuating bearing of the first slave cylinder (of the two slave cylinders) and/or the actuating bearing of the second slave cylinder (of the two slave cylinders) is/are designed as an (axial/axial) needle bearing. This further saves axial installation space.

A compact design in the radial direction is also achieved if the housing members of the two slave cylinders directly overlap/support each other in the radial direction of the longitudinal axis of the supply member. The housing members of the two slave cylinders are additionally supported in the radial direction on the supply member.

If the housing members of the two slave cylinders are fixed to each other, preferably by a press-fit seat/press-fit (acting in the radial direction), the two slave cylinders can be jointly fixed to the supply member in one step during mounting. The two slave cylinders are therefore designed as a common module. Thereby further reducing installation costs.

Alternatively, it is also advantageous if the housing components of the two slave cylinders are fixed/arranged on the supply component in an axially spaced manner from one another. Whereby the case member can be manufactured at low cost. At least one (one-piece) shoulder is preferably molded directly on the supply member (or one shoulder is molded on each housing member in the axial direction between the housing members) with the housing members supported thereon.

It is also advantageous if a first connection region between the first fluid supply channel (of the supply member) and the first slave cylinder housing member is sealed by means of two sealing rings and/or a second connection region between the second fluid supply channel (of the supply member) and the second slave cylinder housing member is sealed by means of two sealing rings. The sealing ring is preferably designed as an O-ring, a-ring or a groove sealing ring, for example.

If the actuating bearing of the first slave cylinder is connected to a connecting element which can be arranged or is arranged on the clutch side (i.e. the axial side of the actuating bearing facing away from the piston), wherein the connecting element projects in the radial direction from the housing component of the first slave cylinder, it is possible to arrange the two slave cylinders more closely to one another in the axial direction.

It is further advantageous in respect of the supply member that it is moulded from a plastics material.

Advantageously, each slave cylinder is designed as a Concentric slave cylinder (CSC/"Concentric slave cylinder").

The invention further relates to a clutch system for a motor vehicle drive-train, comprising at least two clutches and an actuating device according to the invention according to at least one of the above-described embodiments, wherein a first slave cylinder is arranged and designed for actuating the first clutch and a second slave cylinder is arranged and designed for actuating the second clutch.

In the context of a clutch system, it has proven to be further advantageous if the supply member also has a cooling fluid supply channel, wherein the cooling fluid supply channel opens into an interior of the clutch housing, which interior accommodates the first clutch friction element and/or the second clutch friction element, so that, in operation, cooling fluid can be introduced into the interior, radially into the interior of the friction elements, in order to cool the friction elements. The structure of the clutch system is further simplified by the integrated installation of such a cooling system.

It is also advantageous if a clutch bearing designed as a (radial/radial) needle bearing is arranged on the radial outside of the first slave cylinder housing part, which clutch bearing radially supports the clutch pack of the first clutch and/or of the second clutch. The required installation space in the axial direction is significantly reduced by this clutch bearing arrangement.

The invention further relates to a drive unit for a drive train of a motor vehicle, comprising a coupling system according to at least one of the above-described embodiments of the invention and a transmission device, wherein a first transmission input shaft of the transmission device is connected in a rotationally fixed manner to a coupling assembly of a first clutch and a second transmission input shaft of the transmission device is connected in a rotationally fixed manner to a coupling assembly of a second clutch.

In this connection, it has proven to be particularly advantageous if the supply member is supported on the transmission input shaft (i.e. on the outer side of the transmission input shaft) by means of two radial bearings, each of which is preferably designed as a needle bearing. This results in a particularly robust and radially compact drive unit design.

Alternatively, however, it is also advantageous if the two radial bearings can be dispensed with and instead the supply member can be arranged/accommodated/fixed centrally on the transmission housing side. Thereby further reducing the complexity and installation costs of the drive unit.

In other words, the invention thus achieves a radially nested double CSC (two slave cylinders). An operating system (operating device) with an optimized installation space is thus proposed for a three-clutch/hybrid module (clutch system). The actuating devices (slave cylinders) for the first clutch (K1) and the second clutch (K2) are nested axially in series. The fixing and the supply of the two operating devices takes place by means of a supply member arranged radially inside. The K2 casing (second casing member) is axially supported on the K1 casing (first casing member). Axial needle bearings are used for the clutch bearing (operating bearing) in order to save installation space.

Drawings

The invention will be described in detail hereinafter with reference to the drawings, in which different embodiments are shown.

Fig. 1 shows a longitudinal section through a drive unit according to a first embodiment of an operating device according to the invention, wherein the structure of the operating device and of a clutch system which interacts with the operating device can be clearly seen,

figure 2a detailed view of the longitudinal cut-away drive unit in the area of the operating device shown in figure 1,

fig. 3 shows a longitudinal section through a drive unit according to a second exemplary embodiment of an actuating device according to the present invention, which differs from the first exemplary embodiment in particular by the arrangement of the restoring springs of the two clutches,

fig. 4 shows a longitudinal section through a drive unit according to the invention of an actuating device according to a third embodiment, in which, in contrast to the first embodiment, two radial bearings for supporting the actuating device supply member on the transmission input shaft are dispensed with,

FIG. 5 is a longitudinal section through a drive unit according to a fourth exemplary embodiment of an operating device according to the invention, wherein, in contrast to the third exemplary embodiment shown in FIG. 4, no spacers are provided on the end face of the supply member, and

fig. 6 shows a detail of a longitudinally sectioned drive unit according to a fifth exemplary embodiment of an operating device according to the present invention.

The drawings are merely schematic in nature and are provided to aid in understanding the present invention. Like elements are provided with like reference numerals. The features of the different embodiments can also be freely combined with each other.

Detailed Description

When viewing the drive unit 30 shown in fig. 1, a first embodiment of the operating device 1 according to the invention can be seen. In this illustration, the operating device 1 has been installed in the drive unit 30 and is in operative connection with the

clutches

5, 6 of the clutch system 2 of the drive unit 30. The operating device 1 is mounted in an interior space 22 of a clutch housing 23 of the clutch system 2. In addition to the clutch system 2, which is designed here as a hybrid module, the drive unit 30 also has a transmission device 26, of which only the

transmission input shafts

27a and 27b are shown for the sake of clarity. In operation, the drive unit 30 is a component of a hybrid vehicle powertrain system (hybrid powertrain system).

As can be seen in detail in fig. 1, the clutch system 2 has a total of three

clutches

5, 6, 33 with regard to the clutch system 2. The three

clutches

5, 6, 33 are also referred to as triple clutches. The first clutch 5 and the second clutch 6 together form a double clutch. The third clutch is embodied in the form of a separating clutch 33.

The input section 34 (also referred to as the coupling/intermediate section) of the clutch system 2 is operatively connected directly or indirectly to an output shaft of the internal combustion engine, which is not shown here to ensure overview. The input part 34 is either directly mounted in a rotationally fixed manner on the output shaft or indirectly/indirectly connected to the output shaft by means of a torsional vibration damping device, for example a dual mass flywheel. The input part 34 is mounted in a pivotable manner on the clutch housing 23 of the clutch system 2. The input portion 34 extends from the axially outer side of the clutch housing 23 into the inner space 22 of the clutch housing 23. In the inner space 22, the input portion 34 carries a first clutch pack 35a constituting the disconnect clutch 33. The input part 34 has in particular a bearing region 36 of the first clutch pack 35 a. A plurality of first friction elements 20 (first clutch pack 35a) are accommodated on the bearing region 36 in a rotatable and axially displaceable manner relative to one another. On the other second clutch partner 35b of the separating clutch 33, a plurality of second friction elements 21 are again provided, which are arranged in an alternating manner in the axial direction with the first friction elements 20. The second friction elements 21 are accommodated on the holder 37 in a manner such that they can be swiveled and axially displaced relative to one another.

The holder 37 at the same time forms a sleeve-like rotor receiving region 38. The rotor receiving region 38 receives a rotor 39 of an electric motor 40 on its radial outer side in a rotationally fixed manner. The electric machine 40 is also typically an integral part of the clutch system 2. The motor 40 is arranged coaxially with the rotary shaft 13. The rotor 39 therefore likewise extends continuously about the axis of rotation 13. The stator of the electric motor 40, which is not shown in detail here to ensure overview, is accommodated in a fixed manner in the clutch housing 23. The rotor 39 is normally rotatably supported relative to the stator (by the bracket 37) and is drivable by the stator.

The two

clutches

5 and 6 act between the carrier 37 and the respective

transmission input shafts

27a, 27b of the transmission device 26. The

friction elements

20, 21 of the first clutch 5 are arranged radially outside (at least partially) the

friction elements

20, 21 of the separator clutch 33. At the same time, the

friction elements

20, 21 of the first clutch 5 are arranged axially offset from the

friction elements

20, 21 of the second clutch 6.

The first clutch pack 28a of the first clutch 5 is formed directly from the carrier 37 and the first friction element 20. The first friction elements 20 of the first clutch 5 are accommodated on the radial inside of the carrier 37/rotor receiving region 38 in a rotationally fixed and axially displaceable manner relative to one another. The second clutch arrangement 28b of the first clutch 5 is connected in a rotationally fixed manner to the first transmission input shaft 27 a. The second clutch pack 28b has a (first) friction element carrier 41a, on which a plurality of second friction elements 21 of the first clutch 5 are accommodated in a rotationally fixed and axially displaceable manner relative to one another. The first friction element carrier 41a is mounted in a rotationally fixed manner on the first transmission input shaft 27 a. In the closed position of the first clutch 5, its

friction elements

20 and 21 are normally pressed axially together in the following manner: they are connected to one another in the direction of rotation in a friction-fit manner. In this closed position, the two

clutch packs

28a and 28b are thus pivoted together. In the open position of the first clutch 5, the two

clutch packs

28a and 28b are rotationally decoupled and can therefore rotate freely relative to one another. For actuating the first clutch 5, the actuating device 1 described in more detail below has a first slave cylinder 3.

The second clutch 6 is designed to a maximum extent in accordance with the first clutch 5. The second clutch 6 likewise has a first clutch pack 29a, which additionally has a plurality of first friction elements 20. The first friction elements 20 of the second clutch 6 are likewise accommodated on the radial inside of the carrier 37/rotor receiving region 38 in a rotationally fixed and axially displaceable manner relative to one another. The second clutch arrangement 29b of the second clutch 6 is connected in a rotationally fixed manner to the second transmission input shaft 27 b. The second clutch pack 29b of the second clutch 6 in turn has a plurality of second friction elements 21 and a (second) friction element carrier 41 b. The second friction element carrier 41b is mounted in a rotationally fixed manner on the second transmission input shaft 27 b. In the closed position of the second clutch 6, its

friction elements

clutch packs

29a and 29b are thus pivoted together. In the open position of the second clutch 6, the two

clutch packs

29a and 29b are rotationally decoupled and can therefore rotate freely relative to one another. For actuating the second clutch 6, the actuating device 1 described in more detail below has a second slave cylinder 4.

As can be seen in fig. 1, the first transmission input shaft 27a is arranged radially inside the second transmission input shaft 27 b. The second transmission input shaft 27b is therefore embodied in the form of a hollow shaft.

The operating device 1 according to the invention is designed as a double-slave cylinder/double-slave cylinder unit, as is shown in detail in fig. 2. The operating device 1 has two

slave cylinders

3 and 4 arranged/connected as a module. The

individual slave cylinders

3, 4 are designed as

concentric slave cylinders

3, 4.

The two

slave cylinders

3, 4 have

housing members

9a, 9 b. The

respective housing members

9a and 9b accommodate

pistons

7a and 7b so as to be axially movable, i.e., movable along the rotary shaft 13. The

pistons

7a, 7b together with the

housing members

9a, 9b enclose the

fluid chambers

8a, 8 b. The two

slave cylinders

3, 4 are of substantially identical construction. To operate the respective first or

second clutch

5, 6, a pressure is applied to the

respective fluid chamber

8a, 8b during operation.

It can also be seen that the (first) housing member 9a of the first slave cylinder 3 is moulded in a C-shape, viewed in the longitudinal sectional direction. The first housing member 9a is preferably molded from a metal plate. The first housing member 9a has an axial (first) opening 42a aligned in the direction of the first clutch 5. The first housing member 9a is of an annular structure as a whole. In the first housing member 9a, a first piston 7a, which is designed as an annular piston, is accommodated in a movable manner. In order to seal the first fluid chamber 8a enclosed between the first piston 7a and the second housing member 9a, piston seal rings 43 are used on the radially inner side and the radially outer side of the first piston 7a between the first piston 7a and the housing member 9 a. The piston seal ring 43 is accommodated on the radially inner side of the first piston 7a and the piston seal ring 43 is accommodated on the radially outer side of the first piston 7 a. The first piston 7a is axially accommodated/guided within the first housing member 9a during the entire displacement stroke carried out during operation. The piston sealing ring 43 is designed, for example, as an O-ring, an a-ring or a groove sealing ring.

As shown in fig. 2, the first piston 7a has, for support in the initial position (retracted position), a stop 44, by means of which it rests on a (radially aligned) bottom region 45 of the first housing component 9 a. The stop 44 is formed on the axial side 15 (second axial side 15) of the first piston 7a facing away from the first clutch 5. When pressure is applied to the (first) fluid chamber 8a, the first piston 7a will be moved to its extended position and thus a spacing distance is formed between the stop 44 and the bottom area 45. In order to actuate the first clutch 5/in order to transmit the pressure to be transmitted to the (first) pressure tank 46 of the first clutch 5 when the first piston 7a is moved from its retracted position into its extended position, the first piston 7a is (indirectly) connected to the first pressure tank 46 in a rotationally fixed but rotationally fixed manner by means of the (first) actuating bearing 16 a. A first operating bearing 16a is received/supported on the first axial side 14 (facing away from the second axial side 15) of the first piston 7 a. The first operating bearing 16a is designed as a needle bearing, i.e. as an axial needle bearing.

The first operating bearing 16a is supported on the first pressure tank 46 on the axial side facing away from the first piston 7a by means of a connecting element 19 which extends in the axial direction as well as in the radial direction away from the first operating bearing 16 a. The first pressure tank 46 is then coupled in turn axially movably with the

friction elements

20, 21 of the first clutch 5. As shown, the first connecting element 19 is dimensioned in such a way that: which extends outwardly in the radial direction to such an extent that it exceeds the first housing element 9a in the radial direction. The actuating device 1 can thereby be of a particularly compact axial design.

The second slave cylinder 4 is designed according to the first slave cylinder 3. The second housing component 9b thus likewise accommodates the second piston 7b (annular piston) in a movable manner and encloses the second fluid chamber 8b therewith. The second housing part 9b is likewise designed substantially C-shaped, viewed in the direction of the longitudinal section. As a support means in the initial position shown in fig. 2, the second piston 7b likewise has a stop 44 on the side of the bottom region 45 of the second housing component 9 b. The (second) opening 42b of the second housing member 9b is co-directional with the first opening 42a in the axial direction. The second actuating bearing 16b is likewise designed in the form of an axial needle bearing, which is arranged between the second piston 7b and a further (second) pressure tank 47 (of the second clutch 6). The second operating bearing 16b is supported axially directly on the (second) pressure tank 47 of the second clutch 6.

The

housing members

9a, 9b of the two

slave cylinders

3 and 4 are arranged jointly on the supply member 10 of the operating device 1. The supply member 10 is designed substantially sleeve-shaped. The supply member 10 has a longitudinal axis 12, which in fig. 1 and 2 is arranged coaxially with a rotational axis 13.

According to the invention, the two

housing members

9a and 9b are directly supported to each other in the axial direction. For this purpose, the first housing component 9a has, on the radial inside, a web region 48 which extends in the axial direction. The web region 48 is supported directly by its axial end face (toward the first axial side 14) on the base region 45 of the second piston 7 b. In the base region 45 of the second housing component 9b, a defined abutment 49 is introduced, in which the web region 48 abuts in a planar manner in the axial direction. In addition, the support 49 is also designed in such a way that: it has a (radial) shoulder 50 projecting in the axial direction. The shoulder 50 interacts with the radially outer side of the web region 48 in such a way that: the two

housing parts

9a and 9b are firmly connected to one another in this region by means of a press fit. Thereby achieving radial centering of the

housing members

9a and 9b relative to the axis of rotation 13.

The supply member 10 serves both for radial and axial positioning of the two

slave cylinders

3 and 4/

housing members

9a, 9 b. In addition, the supply member 10 also serves to supply the

fluid chambers

8a and 8b with fluid during operation. For this purpose, a second fluid duct 11b, which is provided in the supply component 10 and into which a first fluid duct 11a, which is fluidically connected to the first fluid chamber 8a, is likewise provided in the supply component 10, is designed separately from the first fluid duct 11a and fluidically connected to the second fluid chamber 8 b. Thus, the

respective slave cylinders

3, 4 can be controlled in accordance with the fluid pressures in the respective

fluid delivery passages

11a, 11 b. In order to seal the connecting

region

17a or 17b between the respective

fluid supply channel

11a, 11b and the

fluid chamber

8a, 8b, a sealing ring 18 is arranged in an axially offset manner. The sealing ring 18 is embodied, for example, in the form of an O-ring, an a-ring or a groove sealing ring.

As also shown in fig. 1, a third fluid delivery channel 11c is introduced in the supply member 10, which serves to deliver/be used as a cooling fluid delivery channel into the interior space 22. The supply member 10 is therefore also used to convey cooling fluid when the drive unit 30 is operating, in order to cool the

respective friction elements

20, 21 of the

clutches

5, 6, 33. The third fluid supply channel 11c opens directly into the interior 22 of the clutch system 2. The supply member 10 is fixed in a manner spaced from the second friction element holder 41b in the axial direction by a spacer 51. The partitions 51 are grooved at a plurality of positions in the circumferential direction so that the cooling fluid can be circulated accordingly.

As can also be clearly seen in fig. 1, the supply member 10 is supported by its radial inner side directly on the radial outer side of the second transmission input shaft 27b by means of two

radial bearings

32a, 32b arranged offset from one another in the axial direction.

In addition, the holder 37 has a disk region 52 which extends radially inward from the rotor receiving region 38 in the radial direction. A disk region 52, which is also referred to as a clutch cover, is supported on the radial outer side 24 of the housing member 9a via a clutch bearing 25. The clutch bearing 25 is designed as a radial needle bearing. Thus, the first and

second clutches

5, 6 are radially supported during operation at least partially by the clutch bearings 25. It can also be seen that the connecting element 19 extends outwards in the radial direction to such an extent that it overlaps/exceeds/covers the clutch bearing 25 from the axial side. A particularly compact design is thereby achieved.

With reference to fig. 3 to 6, further embodiments of the drive unit 30 and of the operating device 1 according to the invention can be seen. It should be noted that, for the sake of brevity, only the differences between the following embodiments and the first embodiment are described, since their structural principles and functions conform to the first embodiment.

As can be seen in fig. 3, the

respective return springs

31a, 31b of the two

clutches

5, 6 can also be arranged in different positions. In the first exemplary embodiment, the first return spring 31a, which exerts a return action on the first pressure tank 46, is arranged on the side of the second clutch 6

friction elements

20, 21 which faces axially away from the first clutch 5

friction elements

20, 21, while the first return spring 31a is arranged axially between the first clutch 5

friction elements

20, 21 and the second clutch 6

friction elements

20, 21. As in the first exemplary embodiment, the second return spring 31b, which exerts a return action on the second pressure tank 47, is arranged on the side of the

friction elements

20, 21 of the second clutch 6 facing axially away from the

friction elements

20, 21 of the first clutch 5, but in the axially facing region the second pressure tank 47 and the first clutch pack 29a are now in contact with one another.

As can be seen in connection with fig. 4, the use of

radial bearings

32a, 32b can in principle also be dispensed with. In the third exemplary embodiment, the supply member 10 is accommodated directly centrally on a transmission housing, not shown in detail here, of the transmission device 26 to ensure overview. The supply member 10 can in particular be of compact design in the axial direction. Here, a preferred material of the supply member 10 is a plastic material. The supply member 10 in turn forms a preassembled module together with the

slave cylinders

3, 4.

It can also be seen in fig. 5 that, in principle, the webs 51 can be dispensed with in order to allow, in operation, an unobstructed flow of cooling fluid from the radially inner side to the radially outer side in the interior space 22.

In fig. 6, the two

housing members

9a, 9b are not directly/indirectly supported to each other in the axial direction of the longitudinal shaft 12, but are supported on the supply member 10. Thereby, the two

housing members

9a, 9b are indirectly supported (by the supply member 10) with respect to each other in the axial direction. Thus, the two

housing members

9a, 9b are spaced from each other in the axial direction. In the radial direction of the longitudinal axis 12 they are no longer directly/indirectly supported but on the supply member 10.

In other words, the invention implements an axially nested clutch lever combination (first and second slave cylinders 3, 4). Thereby a module/a separate unit is realized. For this purpose, a distribution member (supply member 10) is introduced in the axial nesting arrangement, which is responsible for supplying the assembly (operating device 1) with fluid. It is modeled as a supply assembly 1 of swivel joints for creating a synergistic effect. In addition, a bearing design variant for the double/

triple clutch

5, 6, 33 is also implemented according to the advantageous design of the clutch lever.

In the case of a three-clutch (clutch system 2) comprising a rotor 39 with a bearing arrangement on the hybrid module side and a clutch pack K0 (

friction elements

20, 21 of the separator clutch 33), K1 (

friction elements

20, 21 of the first clutch 5) and K2 (

friction elements

20, 21 of the second clutch 6), it is proposed that the transmission side is supported on the

clutch lever members

3, 4 by means of needle bearings 25. The

clutch lever members

3 and 4 are constituted by an operating device K1 (first slave cylinder 3) and an operating device K2 (second slave cylinder 4), which are fitted in series with each other. The fixing and feeding of the

handling devices

3, 4 takes place by means of a feeding member 10 arranged radially inside. The supply member may be pressed into the transmission bell or supported on the shaft K2 (second transmission input shaft 27 b).

The supply member 10 has three fluid delivery areas, similar to swivel joints. In this case, fluid can be supplied to the actuating devices K13 and K24 and to the

clutches

5, 6, 33. The seal (seal ring 18), shown as a black quadrilateral, may be, for example, an O-ring. In the front region, there are fluid-conveying regions for K1 (first connection region 17a) and K2 (second connection region 17b) for the respective operating systems (3 and 4), for which purpose a drilling/fluid-guiding region is provided through the component. Here, the seal is likewise provided by a radially sealing O-ring (sealing ring 18). In a possible variant (not shown in the figures), the operating device K13 may also be supplied axially with operating fluid. The sealing can be effected here, for example, by means of an axial O-ring. The supply member 10 can also function as a stopper for each system. The operating devices K1 and K23, 4 are thus supported by their

respective housing members

9a, 9 b.

The system K1(3 and 4) is composed primarily of a simple rotationally

symmetrical housing component

9a, 9b and a

piston

7a, 7b guided therein, which has a seal (piston seal 43). The inner surfaces of the

housings

9a, 9b are used as sealing surfaces. The

pistons

7a, 7b each represent an axial stop 44, by means of which the

clutch system

5, 6 can support its preload. The preload is transferred from the rotating member to the stationary member through the operating

bearings

16a, 16 b. In the case of K1, an intermediate washer (connecting element 19) is also present, which establishes a connection between clutch K15 (via pressure tank 46) and CSC K13. Ideally, the component can only have the following dimensions: the diameter is smaller than the radial needle bearing 25. It serves to support the

clutches

5, 6 on the transmission side. At the stated dimensional ratios, the

CSCs

3, 4 can be completely assembled together and then loaded into the

clutches

5, 6. This is advantageous for both the installation of the

CSC

3, 4/operating device 1 and for customer-wise installation and engagement options. The fluid supply of the pressure chamber K2 (the second housing component 9b with the second fluid chamber 8b) takes place via the feed element (the second connecting region 17 b). It can be fastened to the pressure chamber K1 (the first housing component 9a with the first fluid chamber 8 a) by means of, for example, a press-fit connection. As shown, the

seals

43, 18 may be implemented by a-or O-rings or groove seals.

The clutch bearing 25 together with the central bearing of the clutch 2 achieves a bearing base which is as wide as possible, so that optimum conditions are achieved for the rotor 39 and the electric motor 40. The bearing 25 is ideally connected to the CSC housing (first housing member 9 a). In this way, when the clutch (clutch system 2) is connected to the CSC 1, it can find its position in the clutch cover (disk region 52) and perform its function. The

members

25, 16a and 16b are ideally needle bearings.

The schematic also shows the position of the return springs 31a, 31b of the

clutches

5, 6. It is also possible to arrange the return spring for K1 (first return spring 31a) between the clutch pack (

friction elements

20, 21 of the first clutch 5 and

friction elements

20, 21 of the second clutch 6). As a variant, it is also conceivable to modify the bearing structure of the K2 shaft (second transmission input shaft 27 b). When the shaft K227 b is further supported in the transmission 26, the

bearings

32a, 32b can thereby be eliminated. This allows the component 10 to be made of plastic.

Description of the reference numerals

1 operating device 2 clutching system 3 first slave cylinder 4 second slave cylinder 5 first clutch 6 second clutch 7a first piston 7b second piston 8a first fluid chamber 8b second fluid chamber 9a first housing member 9b second housing member 10 supply member 11a first fluid delivery passage 11b second fluid delivery passage 11c third fluid delivery passage 12 longitudinal shaft 13 first axial side 15 second axial side 16a first operating bearing 16b second operating bearing 17a first connection region 17b second connection region 18 sealing ring 19 connecting element 20 first friction element 21 second friction element 22 internal space 23 clutch housing 24 first housing member external side 25 clutch bearing 26 variator device 27a first variator input shaft 27b second variator input shaft 28a first clutch assembly 28b first clutch of the first clutch Second clutch pack 29a second clutch pack 29b of the second clutch pack 30 drive unit 31a first return spring 31b second return spring 32a first radial bearing 32b second radial bearing 33 a first clutch pack 35b of the disconnect clutch first clutch pack 34 input section 35a second clutch pack 35b of the disconnect clutch support region 37 support 38 rotor receiving region 39 rotor 40 motor 41a first friction element support 41b second friction element support 42a first opening 42b second opening 43 piston seal 44 stop block 45 bottom region 46 first pressure pot 47 second pressure pot 48 web region 49 seat 50 shoulder 51 diaphragm 52 disk region.

Claims

1. An actuating device (1) for a clutch system (2) of a motor vehicle, having two slave cylinders (3, 4) each designed for actuating a clutch (5, 6), wherein each slave cylinder (3, 4) has a piston (7a, 7b) and a housing component (9a, 9b) which guides the piston (7a, 7b) in the direction of movement of the piston and which delimits a fluid chamber (8a, 8b) with the piston (7a, 7b), and having a supply component (10), on which supply component (10) the slave cylinders (3, 4) are arranged in such a way that: for each slave cylinder (3, 4), the fluid feed channel (11a, 11b) of the supply member (10) is fluidically connected to the fluid chamber (8a, 8b), characterized in that the housing members (9a, 9b) of the two slave cylinders (3, 4) are supported or supported on the supply member (10) directly one above the other in the axial direction of the longitudinal axis (12) of the supply member (10).

2. Operating device (1) according to claim 1, characterised in that the piston (7a, 7b) of the respective slave cylinder (3, 4) is connected in a movement-proof manner to an operating bearing (16a, 16b) on the side (14) axially facing away from the fluid chamber (8a, 8b), and in that the operating bearing (16a) of the first slave cylinder (3) and/or the operating bearing (16b) of the second slave cylinder (4) is designed as a needle bearing or a ball bearing.

3. Operating device (1) according to claim 1 or 2, characterised in that the housing members (9a, 9b) of the two slave cylinders (3, 4) are supported directly overlapping each other in the radial direction of the longitudinal axis (12) of the supply member (10).

4. Operating device (1) according to any one of claims 1 to 3, characterised in that the housing members (9a, 9b) of the two slave cylinders (3, 4) are fixed to each other.

5. Operating device (1) according to one of claims 1 to 4, characterized in that a first connecting region (17a) between a first fluid feed channel (11a) and the housing member (9a) of the first slave cylinder (3) and/or a second connecting region (17b) between a second fluid feed channel (11b) and the housing member (9b) of the second slave cylinder (4) is sealed by means of two sealing rings (18).

6. Operating device (1) according to one of claims 1 to 5, characterised in that the operating bearing (16a) of the first slave cylinder (3) is connected with a connecting element (19) which can be arranged on the clutch side, wherein the connecting element (19) projects in the radial direction from the housing member (9a) of the first slave cylinder (3).

7. Clutch system (2) suitable for a motor vehicle drive train, comprising at least two clutches (5, 6) and one operating device (1) according to one of claims 1 to 6, wherein the first slave cylinder (3) is arranged and designed for operating the first clutch (5) and the second slave cylinder (4) is arranged and designed for operating the second clutch (6).

8. Clutch system (2) according to claim 7, wherein the supply member (10) further has a cooling fluid supply channel (11c), wherein the cooling fluid supply channel (11c) opens into an inner space (22) of a clutch housing (23) accommodating the first clutch (5) friction element (20, 21) and/or the second clutch (6) friction element (20, 21), such that in operation a cooling fluid can be introduced into the inner space (22), radially inside the friction element (20, 21), in order to cool the friction element (20, 21).

9. Clutch system (2) according to claim 7 or 8, characterized in that a clutch bearing (25) designed as a needle bearing is arranged on a radial outer side (24) of the housing member (9a) of the first slave cylinder (3), which radially supports the clutch pack (28a, 29a) of the first clutch (5) and/or the second clutch (6).

10. A drive unit (30) suitable for a motor vehicle drive train, comprising a clutch system (2) according to one of claims 7 to 9 and a transmission device (26), wherein a first transmission input shaft (27a) of the transmission device (26) is connected in a rotationally fixed manner to a clutch pack (28b) of the first clutch (5) and a second transmission input shaft (27b) of the transmission device (26) is connected in a rotationally fixed manner to a clutch pack (29b) of the second clutch (6).