阅读说明：本技术 用于摩擦离合器的压力流体操纵装置 (Pressure fluid actuating device for a friction clutch ) 是由 F·布拉斯 P·施利希特 J·黑特尔 A·赫歇莫 于 2019-07-11 设计创作，主要内容包括：一种用于摩擦离合器的压力流体操纵装置,其包括：第一操纵元件和与第一操纵元件一起限定压力流体腔的第二操纵元件；为了共同地沿着运动轴线的方向运动而与第二操纵元件耦联的旋转分离轴承；在旋转分离轴承和第二操纵元件之间的轴向支撑路径中的补偿组件。其中补偿组件包括：相对于旋转分离轴承轴向支撑的第一补偿元件；相对于第二操纵元件轴向支撑的第二补偿元件,第二补偿元件可相对于第二操纵元件围绕运动轴线旋转,通过补偿元件的相对旋转可改变补偿组件的轴向长度；用于预紧第二补偿元件以相对于第二操纵元件在预紧旋转方向上旋转的预紧装置,通过第二补偿元件的旋转引起补偿组件的轴向长度的增加或减小；用于锁止第二补偿元件以防止旋转运动的锁止装置。(A pressure fluid management device for a friction clutch, comprising: a first actuating element and a second actuating element which together with the first actuating element defines a pressure fluid chamber; a rotary release bearing coupled to the second actuating element for movement jointly in the direction of the movement axis; a compensation assembly in the axial support path between the rotational separator bearing and the second actuating element. Wherein the compensation assembly includes: a first compensation element axially supported relative to the rotational separator bearing; a second compensating member axially supported relative to the second actuating member, the second compensating member being rotatable relative to the second actuating member about the axis of motion, the axial length of the compensating assembly being changeable by relative rotation of the compensating member; a pretensioning device for pretensioning the second compensating element for rotation relative to the second actuating element in a pretensioning rotational direction, the rotation of the second compensating element causing an increase or a decrease in the axial length of the compensating assembly; locking means for locking the second compensating element against rotational movement.)

1. A pressure fluid operator for a friction clutch, said pressure fluid operator comprising:

-a first actuating element (12) and a second actuating element (20) defining a pressure fluid chamber (30) together with the first actuating element (12), wherein the second actuating element (20) is movable relative to the first actuating element (12) in the direction of a movement axis (a) by introducing a pressure fluid into the pressure fluid chamber (30);

-a rotary release bearing (34) coupled to the second actuating element (20) for movement jointly in the direction of the movement axis (a);

-a compensation assembly (38) in an axial support path between the rotational separator bearing (34) and the second manoeuvering member (20),

wherein the compensation assembly (38) comprises:

-a first compensation element (44) axially supported relative to the rotational separator bearing (34), wherein the first compensation element (44) is relatively non-rotatable and axially movable relative to the second operating element (20);

-a second compensation element (48) axially supported with respect to the second actuating element (20), wherein the second compensation element (48) is rotatable with respect to the second actuating element (20) about a movement axis (a), wherein an axial length of the compensation assembly (38) is changeable by rotation of the second compensation element (48) with respect to the first compensation element;

-pretensioning means (60) for pretensioning the second compensation element (48) for rotation relative to the second actuating element (20) in a pretensioning rotational direction, wherein a rotation of the second compensation element (48) in the pretensioning rotational direction causes an increase in the axial length of the compensation assembly (38) and a rotation of the second compensation element (48) in an adjustment rotational direction opposite to the pretensioning rotational direction causes a decrease in the axial length of the compensation assembly (38),

-locking means (70) for locking the second compensation element (48) against rotational movement.

2. A pressure fluid operating device according to claim 1, characterized in that the first operating element (12) is a cylinder and the second operating element (20) is a piston.

3. A pressure fluid operating device according to claim 2, characterized in that the first operating element (12) is an annular cylinder and the second operating element (20) is an annular piston.

4. A pressure fluid manipulation device according to claim 3, wherein the first compensation element (44) and the second compensation element (48) are annularly configured.

5. A pressure fluid manipulation device according to any one of the preceding claims, wherein the first compensation element (44) and the second compensation element (48) are supported relative to each other by a ramp structure (50), wherein the ramp structure (50) comprises at least one support ramp (52, 56) on the first compensation element (44) and/or the second compensation element (48) extending in a circumferential direction around the axis of motion.

6. Pressure fluid actuating device according to claim 5, characterized in that the ramp structure (50) comprises a plurality of supporting ramps (52, 56) on the first compensation element (44) and/or on the second compensation element (48) extending in the circumferential direction about the axis of motion, and/or in that the first compensation element (44) and the second compensation element (48) are supported against one another in the region of the ramp structure (50) by means of rolling bodies.

7. A pressure fluid actuating device according to one of the preceding claims, wherein the pretensioning device (60) comprises at least one pretensioning spring (62, 64) acting between the second compensating element (48) and the second actuating element (20).

8. A pressure fluid actuating device according to claim 7, wherein the pretensioning means (60) comprises at least one pressure spring extending substantially in the circumferential direction, or a helical spring.

9. A pressure fluid steering device according to any one of the preceding claims, wherein the locking means (70) comprises at least one pressure fluid locking mechanism (72) which is loadable by fluid pressure in a pressure fluid chamber (30).

10. A pressure fluid actuating device according to claim 9, characterized in that the at least one pressure fluid blocking mechanism (72) is in its blocking position which blocks the second compensating element (48) against rotation when the fluid pressure in the pressure fluid chamber (30) exceeds a limit pressure.

11. Pressure fluid actuating device according to claim 9 or 10, wherein at least one pressure fluid locking mechanism (72) comprises a locking slide (74) which is displaceable by fluid pressure towards the reset force configuration.

12. A pressure fluid actuating device according to claim 11, wherein at least one locking slide (74) is substantially radially displaceable and/or at least one locking slide (74) is substantially axially displaceable.

13. A pressure fluid actuating device according to any one of claims 9 to 12, characterized in that the at least one pressure fluid locking means (72) is in or can be brought into locking interaction with the second compensating element (48) by means of a form-fitting connection, or the at least one locking means (72) is in or can be brought into locking interaction with the second compensating element (48) by means of a frictional connection.

14. A pressure fluid actuating device according to any one of claims 10 to 13, characterised in that, in connection with at least one fluid pressure locking mechanism (72), a locking tooth (78) is provided on the second compensating element (48), and a corresponding locking tooth (82) which is in or can be brought into engagement with the locking tooth (78) for locking the second compensating element (48) against rotation is provided on at least one pressure fluid locking mechanism (72).

15. Pressure fluid actuating device according to one of the preceding claims, wherein the second actuating element (20) is supportable on the first actuating element (12) by means of a pretensioning element (32).

16. Pressure fluid actuating device according to one of the preceding claims, wherein the second actuating element (20) is equipped with a movement stop (68) for limiting the movement of the second actuating element (20) relative to the first actuating element (12) in the direction of a movement axis (A).

17. Clutch system comprising a friction clutch with a force accumulator (94) that can be acted upon by a clutch actuation process by means of a pressure fluid actuation device (10) according to one of the preceding claims.

18. Clutch system according to claim 17, wherein the friction clutch is a pressure clutch and/or the force reservoir (94) is a diaphragm spring.

Technical Field

The present invention relates to a pressure fluid actuating device, such as is used in commercial vehicles, for actuating a friction clutch.

Background

A pressure fluid steering device of this type usually comprises a cylinder which is fixedly positioned relative to the vehicle and a piston which defines a pressure fluid chamber together with the cylinder and is movable in the direction of the axis of movement. The piston can be loaded by a force accumulator which rotates a release bearing, for example a spring tongue of a diaphragm spring, in order to carry out the clutch actuation process in this way.

Disclosure of Invention

The object of the present invention is to provide a pressure fluid actuating device for a friction clutch, which allows a wear-induced change in the installation position of a force accumulator of the friction clutch to be adapted in a simple and reliable manner and method.

According to the invention, this object is achieved by a pressure fluid actuating device for a friction clutch, comprising:

a first actuating element and a second actuating element which together with the first actuating element defines a pressure fluid chamber, wherein the second actuating element is movable relative to the first actuating element in the direction of the movement axis by introducing a pressure fluid into the pressure fluid chamber;

a rotary release bearing coupled to the second actuating element for movement jointly in the direction of the movement axis;

-a compensation assembly in the axial support path between the rotational separator bearing and the second manoeuvering member,

wherein, the compensation assembly includes:

a first compensating element axially supported relative to the rotational separator bearing, wherein the first compensating element is rotationally fixed and axially movable relative to the second actuating element,

a second compensating element axially supported relative to the second actuating element, wherein the second compensating element is rotatable relative to the second actuating element about the axis of movement, wherein the axial length of the compensating assembly is changeable by rotation of the second compensating element relative to the first compensating element,

a pretensioning device for pretensioning the second compensation element for rotation relative to the second actuating element in a pretensioning rotation direction, wherein a rotation of the second compensation element in the pretensioning rotation direction causes an increase in the axial length of the compensation assembly and a rotation of the second compensation element in an adjustment rotation direction opposite to the pretensioning rotation direction causes a decrease in the axial length of the compensation assembly,

locking means for locking the second compensation element against rotational movement.

A pressure fluid actuating device of this type makes it possible to compensate for the increased load on the diaphragm spring which is present as a force accumulator and is used in friction clutches during the service life cycle due to wear. This increased unloading can be compensated for by rotating the second compensating element in the adjustment rotational direction by means of an axial load exerted on the compensating assembly by means of the force store in the engaged state, i.e. when the actuating device is not activated, thereby allowing a reduction of the axial length of the compensating assembly to an extent corresponding to the increased unloading of the force store. During the actuation process, the second compensating element is locked against rotational movement by the locking device, so that in this state no change in length of the compensating assembly occurs.

For a structurally simple design, it is proposed that the first actuating element is a cylinder and the second actuating element is a piston.

In order to provide structural space in the drive train for shafts coupling different drive train regions, it is preferred that the first actuating element is an annular cylinder and the second actuating element is an annular piston.

In accordance with the annular shape of the two actuating elements, the first and second compensating elements can also be of annular design.

In order to achieve a change in the axial length of the compensating assembly in a simple manner by a rotational movement of the two compensating elements relative to one another, it is proposed that the first compensating element and the second compensating element are supported relative to one another by a ramp structure, wherein the ramp structure comprises at least one supporting ramp extending in the circumferential direction about the movement axis on the first compensating element and/or on the second compensating element.

For uniform load distribution, it can be provided that the ramp structure comprises a plurality of supporting ramps extending in the circumferential direction about the axis of motion on the first compensation element and/or on the second compensation element. Furthermore, when the first and second compensation elements are supported by the rolling elements in the region of the ramp structure, frictional effects which could impair the functionality can be minimized.

In order to be able to reliably apply the second compensating element for movement or rotation in the pretensioning direction, the pretensioning device can comprise at least one pretensioning spring acting between the second compensating element and the second actuating element.

In this case, a simple and stable design can be provided, i.e. the prestressing device comprises at least one compression spring extending substantially in the circumferential direction, or the prestressing device comprises a helical spring.

In order to use the pressure fluid provided for the actuation process in order to lock the second compensating element against rotation during the actuation process, it can be provided according to the invention that the locking means comprise at least one pressure fluid locking means which can be acted on by the fluid pressure in the pressure fluid chamber.

The fluid pressure locking means can be designed such that, when the fluid pressure in the pressure fluid chamber exceeds a limit pressure, at least one pressure fluid locking means is in its locking position, in which it locks the second compensating element against rotation. The limit pressure is preferably selected such that the at least one pressure fluid lock is already in its locked position when the fluid pressure is sufficiently high to overcome the pretension provided by the force accumulator and acting in the unloading direction.

In order to ensure that the compensating assembly is released for a compensating movement again after the end of the actuating process, it is proposed that the at least one pressure-fluid locking mechanism comprises a locking slide which can be moved by fluid pressure to the restoring force configuration.

Depending on the available installation space, the at least one locking slide can be displaced substantially radially and/or the at least one locking slide can be displaced substantially axially.

In order to bring about a reliable locking action, it can be provided that the at least one pressure fluid locking means is in or can be brought into a locking interaction with the second compensating element by means of a form fit, or that the at least one locking means is in or can be brought into a locking interaction with the second compensating element by means of a friction fit.

In order to form a positive fit which causes the locking action, it is preferred if, in connection with the at least one fluid pressure locking mechanism, locking teeth can be provided on the second compensating element, and corresponding locking teeth can be provided on the at least one fluid pressure locking mechanism which, for locking the second compensating element against rotation, are in engagement with the locking teeth or can be brought into engagement.

In order to ensure a reliable pretensioning of the second actuating element with respect to the force store of the friction clutch, the second actuating element can be supported on the first actuating element by means of a pretensioning element.

Furthermore, the second actuating element is preferably equipped with a movement stop for limiting the movement of the second actuating element relative to the first actuating element in the direction of the movement axis. In this way, even in the event of failure of the sensor device and actuation of the friction clutch, a limitation of the movement of the two actuating elements relative to one another can be ensured by the generation of a maximum pressure.

The invention further relates to a clutch system comprising a friction clutch having a force accumulator that can be acted upon by a pressure fluid actuating device designed according to the invention for a clutch actuating operation.

The clutch can be a pressure clutch, for example, and the force accumulator can be a diaphragm spring.

Drawings

The present invention is described in detail below with reference to the accompanying drawings. Wherein:

fig. 1 shows a longitudinal section through a pressure fluid actuating device for a friction clutch;

fig. 2 shows a longitudinal section corresponding to that shown in fig. 1, taken in another plane;

FIG. 3 shows a cross-sectional view of the pressure fluid manipulation device taken longitudinally along the line III-III in FIG. 1;

fig. 4 shows an enlarged view of detail IV from fig. 1.

Detailed Description

In the drawing, a pressure fluid actuating device for a friction clutch of a motor vehicle, which is generally also referred to as a release lever (Ausr ü cker), is designated as a whole by reference numeral 10. the pressure fluid actuating device 10, which is designed for generating an actuating force, in particular a release force, comprises a first actuating element 12, which is designed as a ring-shaped cylinder, wherein the first actuating element 12 is designed with a ring-shaped base 14, an inner circumferential wall 16 and an outer circumferential wall 18, and wherein a ring-shaped volume is delimited by the base 14, the inner circumferential wall 16 and the outer circumferential wall 18, wherein a second actuating element 20, which is designed as a ring-shaped piston, is accommodated in the ring-shaped volume in a manner movable in the direction of an actuating axis a. the second actuating element 20 has a base 22, which is arranged opposite the base 14 of the first actuating element 12, wherein the base 22 is coupled by means of a ring-shaped sealing element 24 in a fluid-tight manner relative to the outer circumferential wall 18 of the first actuating element 12, from the base 22, the second actuating element 20 has an inner circumferential wall 26 radially internal, which inner circumferential wall is designed with a sealing element 20, which is arranged in a pressure fluid chamber 30, which is designed as a pressure fluid actuating element 12, which is arranged in a pressure fluid chamber 30, which is arranged in a manner in which is supported by means of the base 14, which is sealed relative to the first actuating element 12, which is arranged in a pressure chamber 14, which is arranged in a pressure fluid actuating element 12, which is arranged in a pressure chamber 30, which is designed by means of a pressure chamber 30, which is arranged in a pressure chamber 30, which is arranged.

The actuating force exerted by the second actuating element 20 on the force accumulator 94 of the friction clutch is transmitted via the rotary release bearing 34. The rotational decoupling bearing comprises a bearing inner ring 36, which is supported relative to the force store 94, a bearing outer ring 40, which is supported relative to the second actuating element 20 via the compensating assembly 38 or is coupled thereto, and a plurality of rolling bodies 42, for example balls, by means of which the bearing inner ring 36 is rotatably supported relative to the bearing outer ring 40.

The compensating assembly 38 comprises a first compensating element 44 of annular design, on which the bearing outer ring 40 is supported in the direction of the actuating axis a, to be precise by means of which the entire rotary decoupling bearing 34 can be moved in the direction of the actuating axis a. The first compensating element 44 is held in its radially inner region by a rotationally fixed arrangement, indicated overall by reference numeral 46, so as to be rotationally fixed relative to the second actuating element 20, but so as to be movable in the direction of the actuating axis a. For example, the non-rotatable structure 46 may comprise a plurality of guide projections on the inner wall 26 of the second actuating element 20, which project radially outward and extend in the direction of the actuating axis a, which engage in corresponding guide recesses of the first compensation element 44 and which bring about a linear movement in the direction of the actuating axis a relative to the second actuating element 20.

Furthermore, the compensating assembly 38 comprises a second compensating element 48, which is annular and is supported on the base 14 of the first actuating element 12 in the direction of the actuating axis a, but is substantially rotatable relative to the first actuating element 12 about the actuating axis a.

The first and second compensation elements 44, 48 are supported relative to each other by a ramp structure, generally indicated by reference numeral 50. The ramp structure 50 preferably comprises a plurality of first supporting ramps 52, which follow one another in the circumferential direction and extend in the circumferential direction, on the first compensation element 44 and have first ramp faces 54 which extend in the circumferential direction in each case. On the second actuating element 48, in association with each first supporting ramp 52 of the first compensating element 44, the ramp structure 50 comprises a second supporting ramp 56 having a respective second ramp face 58 extending in the circumferential direction. The two compensating elements 44, 48 bear against one another in the region of the first ramp surface 54 or the second ramp surface 58. It should be noted that the ramp surfaces 54, 58 have a complementary ramp slope in each case, with which they extend in the circumferential direction and in each case extend axially upward.

The second compensating element 48 is equipped with a pretensioning device, indicated overall by reference numeral 60, which pretensions the second compensating element in a pretensioning direction of rotation in order to rotate relative to the second actuating element 20. In the exemplary embodiment shown, the prestressing device 40 comprises, for example, two prestressing springs 62, 64 which are arranged one behind the other in the circumferential direction and are supported in one circumferential end region relative to the second actuating element 20 and in the other circumferential end region relative to the second compensating element 48. The prestressing spring is designed, for example, as a helical compression spring and is supported radially outward with respect to the second actuating element 20 in the region in which it is surrounded radially outward in its base 22 by a sealing element 24. For this purpose, an annular recess 66 is provided in the base 22 of the second actuating element 20, in which annular recess the pretensioning springs 62, 64 on the one hand and the axial end region of the second compensating element 48 on the other hand are accommodated and are supported axially with respect to the base 22 of the second actuating element 20.

The rotation of the second compensating element 48 in the pretensioned rotational direction, which actually occurs during operation of the pressure fluid actuating device 10, results in an increase in the axial length of the compensating arrangement 38, which comprises the two compensating elements 44, 48, and thus in a movement of the pivot release bearing 34 away from the base 22 of the second actuating element 20. For example, in a state in which the pressure fluid actuating device 10 is not integrated into the drive train and therefore does not interact with a force store which exerts a reaction force on the rotary decoupling bearing 34, such a rotation of the second compensating element 48 in the pretensioning direction of rotation can occur, with the result that, when the second actuating element 20 is supported by the pretensioning element 32 relative to the first actuating element 12, a rotation of the second compensating element 48 in the pretensioning direction of rotation can cause an axial displacement of the first compensating element 44 in the direction of the actuating axis away from the base 14 of the first actuating element 12.

In order to prevent excessive axial movements of the first compensating element 44, a stop device 68 is provided, which comprises, for example, a securing ring 69 arranged on the outer circumferential wall 18 of the first actuating element 12, the first compensating element 44 being able to bear against the securing ring 69 in the direction of the actuating axis a, so that a maximum extended position of the first compensating element 44 relative to the first actuating element 12 is defined by the stop device 68.

If the rotary release bearing 34 is acted upon by a force store 94, for example, a spring tongue of a diaphragm spring of a friction clutch, the second compensating element 48 can be rotated in an adjustment direction opposite to the pretensioning direction of rotation by the ramp action of the ramp structure 50 and the axial load exerted on the first compensating element 44 by the force store, wherein the axial length of the compensating assembly 38 is reduced during this rotation. If in this state the pressure fluid chamber 30 is substantially pressure-free, for example because no actuating force for the friction clutch is generated and the friction clutch is thus transferred into the engaged state or is to be held in the engaged state, the compensating assembly 38 can be moved axially together with the second actuating element 20 in the direction of the actuating axis a under an axial load of the force accumulator 94 until the second actuating element 20 is supported on the base 14 of the first actuating element 12 by means of the pretensioning element 32. In this case, a force equilibrium occurs between the axial force exerted by the force store and the axial force exerted by the prestressing element, specifically the force exerted in the circumferential direction by the prestressing springs 62, 64. For example, it can be provided that the pretensioning springs 62, 64 of the pretensioning device 60 are dimensioned such that, although the pretensioning springs 62, 64 can cause a rotation of the second compensation element 48 in a substantially unloaded state, they are compressed to such an extent when an axial load is applied via the force accumulator 94 until the force accumulator is substantially completely released, specifically has its maximum released position in the friction clutch.

Furthermore, the second compensating element 48 is equipped with a locking device, indicated as a whole with 70. The locking device 70 causes that, when the pressure fluid chamber 30 is filled with pressure fluid for an actuation process, specifically the fluid pressure in the pressure fluid chamber 30 increases, the second compensating element 48 is prevented from rotating relative to the first actuating element 20, and therefore the axial length of the compensating assembly 38 can no longer be changed when the locking device 70 is activated.

In the illustrated embodiment, the locking device 70 comprises three locking means 72 arranged at uniform circumferential distances in the radially inner region of the second actuating element 20. The locking mechanism 72 is configured as a locking slide 74 which is movable substantially radially in the second actuating element 20 or relative to the second actuating element 20. Radially on the outside, the locking mechanism 72 is surrounded in a rotationally fixed manner by a toothed ring 76, which is held on the second compensating element 48 and has locking teeth 78 on its inner circumferential region. In association with the locking teeth 78, each locking slider 74 has a corresponding locking tooth 82 on a slider body 80 that engages the locking teeth 78 as the locking slider 74 moves radially outward.

Associated with each locking slide 74, a slide opening 84 is formed in the second actuating element 20. The slide opening can be provided, for example, in the transition region of the inner wall 26 of the second actuating element 20 to its base 22. In a slider opening 84 of this type, the respective locking slider 74, to be precise its slider body 80, is accommodated in a radially displaceable, but not axially displaceable manner. The slide body 80 can be shaped such that it forms, together with the stepped widening 86, a radially inward movement stop for the respective locking slide 74.

A deformable restoring element 90, which also serves as a sealing element, is fastened to the slide body 80 by means of a fastening bolt 88, which is embodied, for example, as a screw. The reset element 90 is fixed relative to the second actuating element 20 by an annular retaining element 92 inserted into the respective slide opening 84, so that on the one hand a fluid-tight closure in the region of the slide opening 84 is produced and on the other hand a reset force pretensioning the respective locking mechanism 72 or locking slide 74 radially inward, i.e. upward in fig. 4, is produced, which reset force causes the corresponding locking tooth 82 of the locking slide 74 to in principle not engage with the locking tooth 78. The restoring element 90 can be embodied, for example, as a rubber or plastic element having a shape such that, when coupled to the respective locking slider 74 on the one hand and the second actuating element 20 on the other hand, the associated locking slider 74 is prestressed radially inward, i.e., to the state in which the second compensating element 48 is released.

The slider opening 84, which correspondingly accommodates the locking slider 74, is open substantially to the pressure fluid chamber 30 on the inner circumferential region of the second actuating element 20. If a pressure fluid is introduced into the pressure fluid chamber 30 and the fluid pressure therein increases, this pressure also acts on the radially inwardly released surface region of the respective locking slide 74 and thus generates a force which acts radially outwardly on the locking slide 74. Under this force, in the event of a deformation of the respectively associated reset element 90, each locking slider 74 is displaced radially outward in the slider opening 84 accommodating it, so that the corresponding locking tooth 82 of the locking slider engages with the locking tooth 78 on the second compensating element 48 and locks it against rotation relative to the second actuating element 20. The restoring force exerted by the restoring element 90 is preferably selected such that a relatively small increase in fluid pressure in the pressure fluid chamber 30 already causes the locking slide 74 to move radially outward and lock the second compensating element 48 against rotation. The locking pressure required to bring about the locking action of the locking arrangement 70 is less than the pressure required to bring about a rotation of the second compensating element 48 in the adjustment direction of rotation against the biasing action of the biasing springs 62, 64.

The function of the pressure fluid manipulation device 10 is described below.

In this case, it should be assumed that the pressure-fluid actuating device 10, which interacts with the force accumulator 94, which is schematically illustrated in fig. 2 by its radially inner region, is in a state in which no actuating force is to be generated and, correspondingly, the force accumulator 94 is in its most relaxed state in the friction clutch containing it. At this point, the force reservoir 94 exerts a force on the rotational separator bearing 34 in the loosening direction E. Under this force, the pivot release bearing 34 has a position in the direction of the actuating axis a corresponding to the position of the force store 94. Since the first compensating element 44 is coupled to the bearing outer ring 40 of the rotational decoupling bearing 40 by means of one or more coupling elements 96, for example spring-loaded, the first compensating element 44 also has a correspondingly defined axial position in the direction of the actuating axis a. The pressure fluid chamber 30 is substantially pressure-free, which means that the locking device 70 does not lock the second compensating element 48 against rotation, so that the second compensating element can be rotated in the pretensioned rotational direction by the pretensioning springs 62, 64 and in this case exerts an axial force on the second actuating element 20 by the ramp action of the ramp structure 50 and thereby presses the second actuating element against the pretensioning element 32.

If an actuation process is performed to press the friction clutch open, the fluid pressure in the pressure fluid chamber 30 is increased. For this purpose, a pressure fluid system, not shown in the figures, is provided, which has, for example, a generator cylinder or a so-called pressure fluid source. By increasing the fluid pressure in the pressure fluid chamber 30, the locking slide 74 of the locking device 70 is initially loaded radially outward, so that the corresponding locking tooth 82 of the locking slide engages with the locking tooth 78 and fixes the second compensating element 48 against rotation. A further increase in the fluid pressure results in the second actuating element 20, together with the compensating assembly 38 and the rotary release bearing 34, being displaced in the direction of the longitudinal axis a together with the second actuating element and exerting a force directed counter to the loosening direction E on a radially inner end region of the force reservoir 94. At this time, the force accumulator 94, which is embodied as a diaphragm spring, for example, oscillates and thus releases the pressure plate loaded by the force accumulator 94, so that the friction clutch is transferred into the pressed-open state.

For the subsequent joining process, the fluid pressure in the pressure fluid chamber 30 is reduced again, which results in the second actuating element 20 together with the compensating assembly 38 and the rotational release bearing 34 being moved together with the second actuating element in the opposite axial direction along the actuating axis a and the force store 94 being moved with its radially inner region in the loosening direction E. In the event that no wear occurs in the friction clutch, the entire system is again in a state corresponding to the initial state. At the end of the actuation process of the re-engagement of the clutch, the locking device 70 is deactivated again, and the second compensating element 48 is thus substantially released for rotation.

If wear occurs in the friction clutch during repeated engagement or disengagement processes (which is usually indicated by a reduction in the axial thickness of the friction linings of the clutch disk), the result is that, during the transition into the engaged state (due to the reduction in the thickness of the friction linings), the pressure plate is displaced more in the direction of the flywheel or in the direction of the seat surface of the friction clutch than in the state without wear. This in turn causes the force store 94 to relax beyond its installation position corresponding to a state of no wear and, in the maximally relaxed state, the radially inner end region of the force store 94 is displaced axially more in the relaxation direction E than in the unworn or less worn state. As a result, the rotary release bearing 34 and likewise the first compensating element 44 are moved more axially together with the rotary release clutch when the friction clutch is engaged than in the unworn state or the less worn state by further loosening of the force accumulator 94. This in turn results in that, when the fluid pressure in the pressure fluid chamber 30 decreases and the locking device 70 passes into the release state, a rotational movement of the second compensating element 48 in the adjustment rotational direction is caused by the further loosening movement of the force accumulator 94 and thus the axial load exerted on the first compensating element 44 via the ramp structure 50. During the rotational movement of the second compensating element 48, which corresponds to the degree of wear occurring therein, the pretensioning springs 62, 64 are more tensioned and the axial length of the compensating assembly 38 is reduced to the extent that it corresponds to the additional degree of axial movement of the radially inner end region of the force store 94 caused by the wear occurring when shifting into the engaged state.

In the engaged state of the friction clutch, in which the pressure fluid chamber 30 is substantially pressure-free, the system is held until the next pressure-on operation. The pressure-release process is activated by increasing the fluid pressure in the pressure fluid chamber 30 and activating the locking device 70. If the locking device 70 is active and thus fixes the second compensating element 48 against rotation, the axial displacement of the second actuating element 20 together with the compensating assembly 38 and the rotational release bearing 34 is caused again as the fluid pressure continues to increase, so that the overall axial length of the compensating assembly corresponding to the previous compensation in this state is smaller than before. In this way, it is ensured that, independently of changes in the position of the force accumulator 94 in its maximally relaxed state caused by wear, the pressure fluid actuating device 10 compensates for changes in the position of the force accumulator 94 during the actuation process and is always actuated or activated in the same manner. This also applies to the case in which a change in the installation position of the force store 94 caused by wear does not cause more movement in the loosening direction E, but rather movement in the opposite direction. In this case, a change in the installation position can be compensated for by means of the compensating assembly 38 in that, when the state is transferred into the pressed-open state, the second compensating element 48 is rotated in the pretensioning direction of rotation and, as a result, the axial structural length of the compensating assembly 38 increases to an extent corresponding to the wear occurring.

By means of the stop device 68, not only the maximum axial movement of the first compensating element 44 but also the axial movement of the components comprising the second actuating element 20, the compensating assembly 38 and the rotational decoupling bearing 34 are limited. This is also important if, for example, the sensor device (which, in the case of a controlled or regulated actuation process, can provide positional information about the component) fails, the actuation process is carried out in such a way that, in order to open the friction clutch, the pressure in the pressure fluid chamber 30 is increased to a maximum pressure and thus a maximum movement of the second actuating element 20 is activated. For this movement, the stop device 68 also forms a movement stop, so that it is ensured that the friction clutch can be actuated as before.

It is finally pointed out that it is clear that structural changes may be made in the pressure fluid manipulation device shown in the figures without departing from the principle of the present invention. For example, instead of a prestressing spring which is oriented in the circumferential direction and is in the form of a helical compression spring, the prestressing device can comprise, for example, a helical spring which is supported relative to the second compensating element on the one hand and the second actuating element on the other hand. Instead of a fastening ring fastened to the outer circumferential wall of the first actuating element, the stop means can be provided by crimping the outer circumferential wall of the first actuating element radially inward. The ramp surfaces of the ramp structure can be supported against one another by the rolling bodies in order to reduce friction losses, and for the locking slide, further spring elements, for example helical compression springs or the like, can be used for the restoring action, so that the functions of the restoring action on the one hand and of the sealing action on the other hand can be structurally decoupled from one another.

List of reference numerals

10 pressure fluid operating device

12 first actuating element

14 bottom

16 inner circumferential wall

18 outer circumferential wall

20 second actuating element

22 bottom

24 sealing element

26 inner circumferential wall

28 sealing element

30 pressure fluid chamber

32 pretensioning element

34 rotating separating bearing

36 bearing inner ring

38 compensating assembly

40 bearing outer ring

42 rolling element

44 first compensation element

46 non-rotatable structure

48 second compensating element

50 slope structure

52 support ramp

54 slope surface

56 support ramp

58 ramp surface

60 pretensioning device

62 pre-tightening spring

64 pre-tightening spring

66 gap

68 stop device

69 fixed ring

70 locking device

72 locking mechanism

74 locking slide block

76 toothed ring

78 locking tooth

80 slider body

82 corresponding locking teeth

84 slide block opening

86 widening part

88 fixing bolt

90 reset element

92 holding element

94 force accumulator