Clutch assembly
The coupling arrangement with an intermediate lever and rotary-sliding joints addresses the issue of irregular radial displacement in dual clutches, ensuring reliable and simple clutch operation by securely transmitting forces and minimizing radial offset, enhancing vehicle performance.
Patent Information
- Authority / Receiving Office
- WO · WO
- Patent Type
- Applications
- Current Assignee / Owner
- SCHAEFFLER TECHNOLOGIES AG & CO KG
- Filing Date
- 2025-12-03
- Publication Date
- 2026-07-16
AI Technical Summary
Existing clutch arrangements in vehicles, particularly those with dual clutches, suffer from irregularly varying radial displacement of pressure plates due to the arrangement angle of connecting rods, leading to adverse clutch characteristics such as uncomfortable disengagement and disruptive movement.
A coupling arrangement with an intermediate lever and rotary-sliding joints on both sides of the housing, allowing for secure transmission of pulling and pushing forces, and a straight connecting rod with a compression spring to ensure consistent clutch engagement and disengagement, minimizing radial offset and enhancing stability.
The solution provides reliable and simple coupling operation with suitable clutch characteristics, reducing disruptive effects and ensuring smooth clutch engagement and disengagement, even when direction is reversed, thus improving vehicle performance.
Smart Images
Figure DE2025101145_16072026_PF_FP_ABST
Abstract
Description
[0001] Coupling order
[0002] The present disclosure relates to a coupling arrangement, in particular for a vehicle, preferably for a tractor coupling, comprising a housing, a (first) coupling arranged in the housing and an actuating device for actuating the (first) coupling.
[0003] Clutch arrangements are known in which a first clutch or a first partial clutch of a dual clutch is designed as a so-called engine-side (safety) clutch, and a second clutch or a second partial clutch of the dual clutch can also be designed as a so-called transmission-side (safety) clutch. Preferably, the engine-side clutch is arranged closer to an engine than the transmission-side clutch. Preferably, the transmission-side clutch is arranged closer to a transmission than the engine-side clutch. Preferably, the transmission-side clutch is arranged closer to an actuating device for the engine-side and / or transmission-side clutch than the engine-side clutch.
[0004] The engine-side clutch consists of a counter-friction surface, preferably formed by a flywheel on an engine crankshaft, a pressure plate that is axially (within limits) displaceable relative to the counter-friction surface, and a clutch disc arranged between the counter-friction surface and the pressure plate (and clampable between them for torque transmission). To actuate the engine-side clutch, the pressure plate is displaced axially by an actuating device, with the displacement occurring in the direction towards the engine, away from the transmission, or towards a side facing away from the actuating device.
[0005] The transmission-side clutch consists of a counter-friction surface, preferably formed by a housing (or a housing-mounted component), a pressure plate that is axially (within limits) displaceable relative to the counter-friction surface, and a clutch disc arranged between the counter-friction surface and the pressure plate. To actuate the transmission-side clutch, the pressure plate is displaced axially by an actuating device, with the displacement occurring in the direction towards the transmission, away from the engine, or towards a side facing the actuating device.
[0006] Each actuating device typically has an actuating lever and a connecting rod operatively linked to the actuating lever, through which a disengaging movement of a release mechanism is transmitted to the pressure plate. Particularly depending on the so-called arrangement angle of the connecting rod, an irregularly varying radial displacement of the pressure plate during actuation can lead to an adverse height difference of the actuating tips (tip runout). The arrangement angle is specifically the angle formed between a line extending between a pivot bearing of the connecting rod and a connection point for the pressure plate, and the axial direction of the clutch.Due to the uneven height of the actuating domes, the release movement results in an uneven movement of the actuating levers, which has a detrimental effect on the movement of the pressure plate and can lead to disturbing clutch characteristics, for example to uncomfortable disengagement of the friction clutch.
[0007] The purpose of this disclosure is therefore to avoid or at least reduce the disadvantages of the prior art. In particular, it aims to provide a coupling arrangement that enables a particularly reliable and simple coupling operation and, in particular, achieves suitable coupling characteristics.
[0008] The problem addressed in the present disclosure is solved by a coupling arrangement having the features of the independent claim. Advantageous further developments are the subject of the dependent claims.
[0009] Accordingly, the present disclosure relates to a coupling assembly for a vehicle. The coupling assembly includes a housing.
[0010] The coupling assembly comprises a (first) coupling located within the housing. The coupling can be a single coupling or a (first) partial coupling of a dual coupling. The coupling includes a mating friction surface, a pressure plate that is axially (within limits) displaceable relative to the mating friction surface, and a coupling disc arranged between the mating friction surface and the pressure plate. Axial displacement of the pressure plate can be limited by a stop fixed to the housing.
[0011] The clutch assembly includes an actuating device for actuating the clutch, in particular for axially displacing the pressure plate relative to the mating friction surface. The actuating device includes an actuating lever. The actuating lever is coupled to a disengagement mechanism, in particular an axially displaceable piston of a piston-cylinder unit. In particular, disengagement of the piston displaces a radially inner end of the actuating lever axially towards the clutch. In particular, the actuating lever can be mounted (preferably directly) on the housing via a first pivot joint, such as a bolt or a bushing. In particular, the first pivot joint can be arranged at a radially outer end of the actuating lever.
[0012] The actuating device includes an intermediate lever. The intermediate lever is coupled to the actuating lever. In particular, the intermediate lever can be rotatably mounted (preferably directly) on the actuating lever via a second pivot joint, such as a bolt or a bushing. In particular, an axis of rotation of the second pivot joint can be aligned parallel to the axis of rotation of the first pivot joint. In particular, the second pivot joint can be arranged radially between a radially outer end and a radially inner end of the intermediate lever. For example, the second pivot joint can be arranged radially further inward than the first pivot joint (on the actuating lever). For example, the second pivot joint can be arranged axially at substantially the same level as the first pivot joint and / or axially further away from the coupling than the radially inner end and / or the radially outer end of the intermediate lever.
[0013] The actuating device includes a connecting rod. The connecting rod is coupled to the intermediate lever. In particular, the connecting rod can be mounted on the intermediate lever via a third pivot joint (preferably directly). In particular, the axis of rotation of the third pivot joint can be aligned parallel to the axis of rotation of the first pivot joint and / or the second pivot joint. In particular, the third pivot joint is arranged at the radially outer end of the intermediate lever. In particular, the third pivot joint is arranged at a first end of the connecting rod, preferably one furthest from the pressure plate.
[0014] In particular, the third pivot joint is arranged radially at substantially the same height as the first pivot joint. Specifically, the third pivot joint is arranged radially outside the second pivot joint. In particular, the connecting rod may have an eye bolt or a clevis to form the third pivot joint. For example, the third pivot joint may be arranged axially closer to the coupling than the first and / or the second pivot joint. The connecting rod is coupled to the pressure plate (by means of an axial displacement).
[0015] The clutch assembly includes a return spring. Contrary to the spring action of the return spring, the actuating device, in particular the actuating lever that acts (directly) on the return spring, can be actuated to close the clutch. This means that the clutch is open in the unactuated state and closed in the actuated state.
[0016] In the coupling arrangement, the intermediate lever, in particular a first, and especially the radially inner end of the intermediate lever, is supported on both sides in the axial direction against the housing and guided to be displaceable in the radial direction relative to the housing. This means that a pivot point between the intermediate lever and the housing is designed, in particular, as a (complete) rotary-sliding joint.
[0017] This has the advantage that pulling and pushing forces can be transmitted via the intermediate lever. In contrast to known arrangements that use one-sided contact points with the housing, a force-acting joint is now used on both sides to enable the pulling force on the pressure plate to be exerted by the return springs on the actuating lever. This allows the joint to function securely even when the direction is reversed.
[0018] According to one embodiment, the actuating device can have a compression spring via which an axial force (pushing force) can be transmitted from the connecting rod to the pressure plate. In particular, the compression spring is mounted radially on the connecting rod. Specifically, the compression spring bears axially against (a flange) the connecting rod on one axial side and axially against the pressure plate on the other axial side. In this way, a desired coupling characteristic can be achieved.
[0019] According to a preferred embodiment, the connecting rod can be essentially or nearly straight, in particular without a (significant) bend or with only a slight bend. Preferably, a longitudinal axis of the connecting rod can extend essentially along the axial direction of the clutch. This has the advantage that the pressure plate has no or only a slight radial offset when the clutch is actuated. Accordingly, the clutch engagement can be advantageously reduced. In addition, the (longer) straight length, especially without a bend in the connecting rod, allows for a longer mounting area for the compression spring, so that a smaller-diameter, but longer spring can be used. This can offer additional space-saving advantages.
[0020] According to one embodiment, a first contact surface (of the first end) of the intermediate lever can be supported against the housing when the clutch is closed. This enables power transmission.
[0021] According to one embodiment, a second contact surface (of the first end) of the intermediate lever can rest against the housing when the clutch is opened. This enables power transmission.
[0022] According to a preferred embodiment, the first contact surface of the intermediate lever can be larger than the second contact surface. This means that the pivot point between the intermediate lever and the housing is designed such that, in the direction of clutch actuation (i.e., for closing or transmitting torque to the clutch), a significantly greater force (required for the clamping force) can be generated than in the opposite direction (i.e., for opening or lifting the clutch). This has the advantage that the second contact surface (in contrast to the first contact surface, which is robustly designed) can be made considerably simpler or weaker, thus requiring minimal additional effort. Consequently, the additional effort required to design the (additional) pivot point can be kept to a minimum.
[0023] According to one embodiment, the first contact surface can be formed by a circular arc segment of a first (circular) cylindrical surface. This promotes rolling.
[0024] According to one embodiment, the second contact surface can be formed by a (circular arc) segment of a second (circular) cylindrical surface. This facilitates rolling.
[0025] According to a preferred embodiment, the first cylindrical surface can have a larger radius than the second cylindrical surface. This ensures that the first contact area is sufficiently large and that the second contact area can be implemented easily and without significant modifications to other components.
[0026] According to one embodiment, the intermediate lever can have a base body and a bolt mounted thereon. For example, a longitudinal axis of the bolt can be aligned parallel to an axis of rotation of the second pivot joint.
[0027] According to a preferred embodiment, the first contact surface can be formed on the base body and the second contact surface on the bolt. A mating surface for the bolt in the housing can be produced by machining.
[0028] According to a preferred embodiment, the first contact surface and the second contact surface can be formed on a single-piece section of the intermediate lever. This ensures simple manufacturing.
[0029] According to a preferred embodiment, the actuating device can have a contact element, preferably a single piece, particularly designed as a formed part, for example U-shaped. The contact element can be arranged (preferably directly) between the first contact surface and the housing and / or (preferably directly) between the second contact surface and the housing, in particular bearing against it. This allows the contact point to be optimized.
[0030] According to a preferred embodiment, the contact element between the intermediate lever and the housing can be elastically preloaded. This means that the contact element has a certain elastic preload, so that the joint is backlash-free and good functional properties, such as backlash-free reversal from the actuation direction to the retraction direction, can be achieved.
[0031] According to a preferred embodiment, the actuating device can include a sliding block. Preferably, the intermediate lever can be supported axially on both sides of the housing via the sliding block and guided to be slidably mounted radially relative to the housing. This ensures secure, low-friction guidance.
[0032] According to a preferred embodiment, the first contact surface can be essentially the same size as the second contact surface. This allows the contact surfaces to be manufactured in a particularly simple manner.
[0033] According to a preferred embodiment, the first and second cylindrical surfaces can be formed by (circumferentially) substantially opposite sections of a common cylindrical surface. This means that the first cylindrical surface has substantially the same radius as the second cylindrical surface. This simplifies the manufacturing process.
[0034] According to a preferred embodiment, the clutch can be a motor-side clutch. This means that the pressure plate for closing the clutch is axially displaceable towards a motor, away from a transmission, or away from the actuating device.
[0035] According to a preferred embodiment, the clutch assembly can include a flywheel, wherein the counter-friction surface of the clutch is formed by the flywheel. The flywheel can preferably be formed by or attached to the engine crankshaft.
[0036] According to a preferred embodiment, the coupling arrangement can include a (second) coupling located in the housing. The coupling can be a (second) partial coupling of the double coupling.
[0037] According to a preferred embodiment, the (second) coupling can have a counter-friction surface, preferably formed by the housing or a housing-fixed component, a pressure plate that can be displaced axially (within limits) to the counter-friction surface, and a coupling disc arranged between the counter-friction surface and the pressure plate (and which can be clamped between them for torque transmission).
[0038] According to a preferred embodiment, the (second) clutch can be a transmission-side clutch. This means that the pressure plate for closing the clutch is axially displaceable in the direction away from the engine, towards the transmission, or towards the actuating device.
[0039] According to a preferred embodiment, the clutch assembly can include a (second) actuating device for actuating the (second) clutch, in particular for axially displacing the pressure plate relative to the mating friction surface. The actuating device has a (second) actuating lever. The actuating lever is coupled to a (second) release mechanism, in particular an axially displaceable piston of a piston-cylinder unit. The actuating device has a connecting rod. The connecting rod is coupled to the actuating lever and the pressure plate. The clutch assembly has a return spring. Contrary to the spring action of the return spring, the actuating device, in particular the actuating lever acting (directly) on the return spring, can be actuated to engage the clutch. This means that the (second) actuating device is designed without the intermediate lever.Alternatively, the (second) actuating device could also be designed analogously to the actuating device of the (first) clutch with the intermediate lever. In other words, the present disclosure addresses the problem that, in known arrangements of engine-side (safety) clutches, the actuating mechanism is designed in such a way that an adverse height difference of the actuating tips (tip hit) can occur with an irregularly changing radial displacement of the pressure plate. This is because, due to the required gear ratio, a considerable inclination (angle) of the coupling elements is necessary. Particularly in powershuttle clutches, both partial clutches are used as starting clutches (forward / reverse travel). To ensure a smooth change of direction, a reliable, consistent characteristic for both partial clutches is advantageous.In this context, an irregularly varying height difference of the actuating surfaces (surge) can be considered particularly disadvantageous. Even in dual clutches with only one engine-side (safety) clutch as a partial clutch (e.g., for a power take-off), the potentially irregularly varying height difference of the actuating surfaces (surge) can be seen as a comfort disadvantage. While this surge problem can be avoided by installing an intermediate lever (between the actuating lever and the connecting rod), this is unsuitable for a lifting motion (opening / disengaging) in known configurations, as a force-transmitting path from the actuating lever via the connecting rod to the pressure plate would have to be possible in both directions of movement, which has not been the case so far.Thus, advantageous clutch characteristics should be achieved for an engine-side safety clutch (compressed clutch, as a single clutch, as part of a dual clutch, or specifically as a partial clutch in a powershuttle clutch), in particular avoiding irregularly changing clutch engagement. Especially in a powershuttle clutch, the clutch characteristics of both partial clutches should be advantageously comparable to enable comfortable execution of a desired change of direction.
[0040] As a solution, it is proposed to equip each actuating lever with an intermediate lever. The connecting rods (coupling elements / pressure levers (possibly combined with spring elements)) for actuating the pressure plate are then driven by these intermediate levers. This results in the connecting rods having a small angle of inclination, so that no disruptive effects occur due to irregularly varying hilltop impact. This allows both pulling and pushing forces to be transmitted via the coupling elements. In order to achieve the pulling effect on the pressure plate via the return springs on the actuating levers, the joints of the intermediate levers to the housing are designed as force-acting joints on both sides, e.g., as complete rotary-sliding joints. This allows these joints to act in a force-locking or positive-locking manner even when the direction is reversed.In the direction of clutch actuation (closing / torque transmission), a significantly greater force acts than in the opposite direction (opening / lifting), which is taken into account in the design of the pivot point between the intermediate lever and the housing. The contact side for actuation to close can be designed in the known, conventional, robust manner (e.g., also with a support element). For the opposite side, for the lift-off safety mechanism, this pivot point can be designed much simpler or with less resistance. The connections of the coupling elements to the respective intermediate levers and the connections of the intermediate levers to the respective actuating levers can be implemented using swivel joints (bolts / bushings). Depending on the design of the intermediate lever, the coupling elements can be designed as eyebolts or as push levers with a clevis head (enclosing the intermediate lever). The return springs can act on the respective actuating levers (lifting direction, clutch opening).The coupling elements can be equipped with a stop (and optionally a disc for improved spring mounting) and may be connected via individual springs (e.g.
[0041] Compression springs exert a clamping force on the pressure plate in the actuation direction. For the opposite direction (retraction direction), adjusting nuts can be used to allow initial adjustment of the actuating device during clutch assembly and to ensure a retraction movement during operation.
[0042] In particular, the pivot point of the intermediate lever at its radially inner end relative to the housing is specially designed. To ensure proper function, especially with regard to kinematic positive movement, a rotary-sliding joint is used for actuation. A pre-assembled lever assembly can be inserted into the housing, for example, before the housing bearing of the actuating lever is mounted. In a first embodiment, a contact area on the intermediate lever has the same radius for both force directions. In a second embodiment, the joint is designed as a rotary-sliding joint with a sliding block. In a third embodiment, the joint has a large radius on the contact side for the higher actuating forces and a mounted bolt with a smaller radius for the retraction contact side.This means that a simple bolt, easily mounted in the intermediate lever, is used as the pivot point, and a mating surface can be formed in the housing, particularly by machining. In a fourth embodiment, the pivot is designed with a large radius on the contact side for the higher actuating forces and a smaller radius for the retraction contact side, with a single, possibly one-piece, contact element being used for both contact sides. This contact element can, for example, be formed as a single piece such that a mating surface is provided for each retraction direction. Advantageously, this element can have a certain elastic preload, so that the pivot point is backlash-free and good functional properties (backlash-free reversal from actuation direction to retraction direction) can be achieved.The intermediate lever can be formed in one piece with a large radius on the contact side for the higher actuation forces and with a smaller radius for the lifting contact side.
[0043] This also offers the advantage that a bend in the connecting rod can be eliminated, making the connecting rod significantly more stable and resistant to kinking. The elimination of the bending point also benefits the spring element, which is used to provide smooth clutch actuation (metered torque build-up) and / or to respond to clutch wear. The axial length for the spring element is considerably increased, allowing for improved dimensions, such as better clutch parameters (e.g., lower actuation force), or a smaller spring diameter. This, in turn, allows for a larger outer diameter of the clutch disc or provides more installation space for the housing, thus increasing its stability.
[0044] The present disclosure is explained below with the aid of figures. Figures 1 to 4 show schematic longitudinal views of various embodiments of a coupling arrangement according to the present disclosure.
[0045] Fig. 5 shows a schematic functional representation of the coupling arrangement,
[0046] Fig. 6 shows a longitudinal view of the coupling arrangement,
[0047] Fig. 7 shows a perspective view of the coupling arrangement,
[0048] Fig. 8 shows a perspective view of a sub-assembly of the coupling assembly,
[0049] Fig. 9 shows a schematic longitudinal representation of the coupling arrangement.
[0050] The present disclosure is described below with reference to the figures. The features of the different embodiments can be combined arbitrarily.
[0051] Figures 1 to 9 show a coupling arrangement 1. The coupling arrangement 1 is particularly suitable for use in a vehicle, preferably for use in a tractor coupling.
[0052] The coupling assembly 1 has a housing 2. The housing 2 can be stationary.
[0053] The coupling assembly 1 has a (first) coupling 3. The coupling 3 is arranged in the housing 2. The coupling 3 can be a single coupling or a (first) partial coupling of a double coupling.
[0054] The clutch 3 has a counter-friction surface 4 (see Fig. 9). The clutch 3 has a pressure plate 5 that is axially displaceable relative to the counter-friction surface 4. The clutch 3 has a clutch disc arranged between the counter-friction surface 4 and the pressure plate 5 (see Fig. 9). Preferably, the clutch 3 can be an engine-side clutch. This means that the pressure plate 5 is axially displaceable for closing the clutch 3 towards an engine or away from a transmission.
[0055] The clutch assembly 1 has an actuating device 6 for actuating the clutch 3. The actuating device 6 serves in particular to axially displace the pressure plate 5 relative to the counter-friction surface 4. The actuating device 6 can in particular be coupled to a release mechanism 7. The actuating device 6 has an actuating lever 8, an intermediate lever 9, and a connecting rod 10. In particular, the actuating lever 8 is arranged in the power transmission cable (directly) between the release mechanism 7 and the intermediate lever 9. In particular, the intermediate lever 9 is arranged in the power transmission cable (directly) between the actuating lever 8 and the connecting rod 10. In particular, the connecting rod 10 is arranged in the power transmission cable (directly or via an interposed spring element) between the intermediate lever 9 and the pressure plate 5.
[0056] The coupling assembly 1 has a return spring 11. Contrary to the spring action of the return spring 11, the actuating device 6, in particular the actuating lever 8, can be actuated to close the coupling 3. For this purpose, the actuating lever 8 can, in particular, act (directly) on the return spring 11. This means that the coupling 3 is open in an unactuated state and closed in an actuated state.
[0057] According to the present disclosure, the intermediate lever 9 is supported on both sides in the axial direction against the housing 2 and guided to be displaceable in the radial direction relative to the housing 2. This means that a pivot point between the intermediate lever 9 and the housing 2 is designed, in particular, as a (complete) rotary-sliding joint.
[0058] Preferably, a first contact surface (of the first / radially inner end) of the intermediate lever 9 can bear against the housing 2 when the clutch 3 closes. Preferably, a second contact surface (of the first / radially inner end) of the intermediate lever can bear against the housing 2 when the clutch 3 opens. Preferably, the first contact surface can be formed by a (circular arc) segment of a first (circular) cylindrical surface. Preferably, the second contact surface can be formed by a (circular arc) segment of a second (circular) cylindrical surface.
[0059] The actuating lever 8 has a radially inner end and a radially outer end. In particular, the actuating lever 8 is coupled to the release mechanism 7. The release mechanism 7 is, for example, a piston-cylinder unit in which a piston is arranged to be axially displaceable within a (ring) cylinder.
[0060] In particular, the radially inner end of the actuating lever 8 is displaced axially towards the clutch 3 by the piston being disengaged.
[0061] The actuating lever 8 is mounted on the housing 2 via a first pivot joint 12 (preferably directly). In particular, the first pivot joint 12 can be arranged at the radially outer end of the actuating lever 8. The first pivot joint 12 can, for example, be formed by a bolt or a bushing.
[0062] The intermediate lever 9 has a radially inner end and a radially outer end. In particular, the intermediate lever 9 can be substantially C-shaped, with one opening of the C-shape facing the coupling 3. The actuating lever 9 is mounted on the actuating lever 8 via a second pivot joint 13 (preferably directly). In particular, the second pivot joint 13 can be arranged between the radially outer end and the radially inner end of the actuating lever 8. The second pivot joint 13 can, for example, be formed by a bolt or a bushing. An axis of rotation of the second pivot joint 13 can preferably be aligned parallel to the axis of rotation of the first pivot joint 12. The second pivot joint 13 can be arranged radially further inward than the first pivot joint 12 and / or axially at substantially the same level as the first pivot joint 12.The intermediate lever 9 can be axially supported on both sides of the housing 2, particularly in the area of the radially inner end.
[0063] The connecting rod 10 has a first end (farther from the pressure plate) and a second end (closer to the pressure plate). The connecting rod 10 is mounted (preferably directly) on the intermediate lever 9 via a third pivot joint 14. The third pivot joint 14 can be located, in particular, at the first end of the connecting rod 10 and / or the radially outer end of the intermediate lever 9. An axis of rotation of the third pivot joint 14 can be aligned parallel to the axis of rotation of the first pivot joint 12 and / or the second pivot joint 13. The third pivot joint 14 is located radially at essentially the same height as the first pivot joint 12 and / or further outboard than the second pivot joint 13. The third pivot joint 14 is located axially closer to the coupling 3 than the first pivot joint 12 and / or the second pivot joint 13. The connecting rod 10 may, especially at the first end, have an eye bolt or a clevis.
[0064] Preferably, the connecting rod 10 can be essentially or almost straight, in particular without a bend. Preferably, a longitudinal axis of the connecting rod 10 can extend essentially along the axial direction of the coupling 3, i.e., parallel to an axis of rotation of the coupling 3.
[0065] Preferably, the coupling arrangement 1 can have a housing-fixed stop 15. The stop 15 can limit axial displacement of the pressure plate, particularly towards the actuating device 6.
[0066] Preferably, the coupling arrangement 1 can have an adjusting nut 16. The axial position of the pressure plate 5 relative to the connecting rod 10 can be adjusted via the adjusting nut 16.
[0067] Preferably, the coupling assembly 1, in particular the actuating device 6, can have a compression spring 17. An axial force (pushing force) can be transmitted from the connecting rod 10 to the pressure plate 5 via the compression spring 17. This means that the compression spring 17 is arranged (directly) in the force transmission path between the connecting rod and the pressure plate 5. The compression spring 17 is preferably mounted radially on the connecting rod 10.
[0068] In particular, the compression spring 17 rests axially on one axial side against (a flange) the connecting rod 10 and axially against the pressure plate 5 on the other axial side. Figures 1 to 4 show different embodiments of the coupling arrangement 1, in particular of the intermediate lever 9 and a contact point of the intermediate lever 9 to the housing 2.
[0069] Preferably, the first contact surface and the second contact surface can be formed on a single-piece section of the intermediate lever 9 (see Figs. 1 and 3).
[0070] Preferably, the first contact area can be essentially the same size as the second contact area (see Figs. 1 and 2).
[0071] In particular, the first cylindrical surface and the second cylindrical surface can be formed by (in the circumferential direction) essentially opposite sections of a common cylindrical surface (see Fig. 1). That is, the first cylindrical surface has essentially the same radius as the second cylindrical surface.
[0072] In particular, the actuating device 6 can have a sliding block 18.
[0073] Preferably, the intermediate lever 9 can be supported on both sides in the axial direction on the housing 2 via the sliding block 18 and guided to be displaceable in the radial direction relative to the housing 2 (see Fig. 2).
[0074] Preferably, the first contact area can be larger than the second contact area (see Figs. 3 and 4). In particular, the first cylindrical surface can have a larger radius than the second cylindrical surface.
[0075] In particular, the intermediate lever 9 can have a base body 19 and a bolt 20 mounted thereon (see Fig. 3). A longitudinal axis of the bolt 20 can, for example, be aligned parallel to an axis of rotation of the second pivot joint 13. Preferably, the first contact surface is formed on the base body 19 and the second contact surface is formed on the bolt 20. A mating surface for the bolt 20 in the housing 2 can be produced by machining. In particular, the actuating device 6 can have a contact element 21 (see Fig. 3).
[0076] 4) The contact element 21 can be a single piece. The contact element 21 can be formed as a formed part. In the illustrated embodiment, the contact element 21 is U-shaped. The contact element 21 can be arranged (preferably directly) between the first contact surface and the housing 2 or abut it. The contact element 21 can be arranged (preferably directly) between the second contact surface and the housing 2 or abut it. Preferably, the contact element 21 can be elastically preloaded between the intermediate lever 9 and the housing 2.
[0077] Preferably, the clutch assembly 1 can include a flywheel 22. The counter-friction surface 4 of the clutch 3 can be formed by the flywheel 22. The flywheel 22 can preferably be formed by or attached to an engine crankshaft.
[0078] Fig. 9 shows the coupling arrangement 1, in which the coupling 3 is a first partial coupling of a double coupling. The coupling arrangement 1 has a further coupling 23, which can be a (second) partial coupling of the double coupling. The (second) coupling 23 is arranged in the housing 2.
[0079] The (second) coupling 23 has a counter-friction surface 24, a pressure plate 25 which can be displaced axially (within limits) to the counter-friction surface 24, and a coupling disc 26 arranged between the counter-friction surface 24 and the pressure plate 25 (and which can be clamped between them for torque transmission).
[0080] Preferably, the (second) clutch 23 can be a transmission-side clutch. This means that the pressure plate 25 for closing the clutch 23 can be axially displaced in the direction away from the engine or towards the transmission.
[0081] Preferably, the coupling arrangement 1 can have a (second) actuating device 27 for actuating the (second) clutch 23. The actuating device 25 serves in particular for axially displacing the pressure plate 25 relative to the counter-friction surface 24. The actuating device 27 can in particular be coupled to a release mechanism 28. The actuating device 27 has an actuating lever 29 and a connecting rod 30. In particular, the actuating lever 29 is arranged in the power transmission cable (directly) between the release mechanism 28 and the connecting rod 30. In particular, the connecting rod 30 is arranged in the power transmission cable (directly or via a spring element 31) between the actuating lever 29 and the pressure plate 25.
[0082] Alternatively, the (second) actuating device 27 could also be designed analogously to the actuating device 6 of the (first) clutch 3 with an intermediate lever.
[0083] The coupling assembly 1 has a return spring 32. Contrary to the spring action of the return spring 32, the actuating device 27, in particular the actuating lever 29, can be actuated to close the coupling 23. For this purpose, the actuating lever 29 can, in particular, act (directly) on the return spring 32. This means that the coupling 23 is open in an unactuated state and closed in an actuated state.
[0084] Coupling arrangement
[0085] Housing
[0086] coupling
[0087] Counter-friction surface
[0088] pressure plate
[0089] Actuating device release mechanism
[0090] Actuating lever
[0091] intermediate lever
[0092] Stabilizer link
[0093] Return spring
[0094] first pivot joint
[0095] second pivot joint
[0096] third pivot joint
[0097] stop
[0098] Adjusting nut
[0099] Compression spring
[0100] Sliding stone
[0101] basic body
[0102] bolt
[0103] Plant component
[0104] flywheel
[0105] coupling
[0106] Counter-friction surface
[0107] pressure plate
[0108] Clutch disc Actuating device Release mechanism Actuating lever
[0109] Stabilizer link
[0110] spring element
[0111] Return spring
Claims
Patent claims 1. Clutch assembly (1) for a vehicle, comprising a housing (2), a clutch (3) arranged in the housing (2) which has a counter-friction surface (4), a pressure plate (5) axially displaceable relative to the counter-friction surface (4), and a clutch disc arranged between the counter-friction surface (4) and the pressure plate (5), an actuating device (6) for actuating the clutch (3) which has an actuating lever (8) that can be coupled to a release mechanism (7), an intermediate lever (9) coupled to the actuating lever (8), and a connecting rod (10) coupled to the intermediate lever (9) and the pressure plate (5), and a return spring (11) against whose spring action the actuating device (6) can be actuated to close the clutch (3), characterized in that the intermediate lever (9) is supported on both sides in the axial direction on the housing (2) and is guided to be displaceable in the radial direction relative to the housing (2). is.
2. Coupling arrangement (1) according to claim 1, characterized in that the connecting rod (10) is essentially or almost straight.
3. Coupling arrangement (1) according to claim 1 or 2, characterized in that a first contact surface of the intermediate lever (9) is supported on the housing (2) when the coupling (3) is closed and a second contact surface of the intermediate lever (9) is supported on the housing (2) when the coupling is opened, wherein the first contact surface is larger than the second contact surface.
4. Coupling arrangement (1) according to claim 3, characterized in that the first contact surface is formed by a section of a first cylindrical surface and the second contact surface is formed by a section of a second cylindrical surface, wherein the first cylindrical surface has a larger radius than the second cylindrical surface.
5. Coupling arrangement (1 ) according to claim 3 or 4, characterized in that the intermediate lever (9) has a base body (19) and a bolt (20) mounted thereon, wherein the first contact surface is formed on the base body (19) and the second contact surface is formed on the bolt (20).
6. Coupling arrangement (1) according to one of claims 3 to 5, characterized in that the actuating device (6) has a contact part (21) which is arranged between the first contact surface and the housing (2) and / or between the second contact surface and the housing (2), wherein the contact part (21) is elastically pre-tensioned between the intermediate lever (9) and the housing (2).
7. Coupling arrangement (1) according to claim 1 or 2, characterized in that a first contact surface of the intermediate lever (9) is supported on the housing (2) when the coupling (3) is closed, and a second contact surface of the intermediate lever (9) is supported on the housing (2) when the coupling (3) is opened, wherein the first contact surface is substantially the same size as the second contact surface, wherein the first contact surface is formed by a section of a first cylindrical surface and the second contact surface is formed by a section of a second cylindrical surface, wherein the first cylindrical surface and the second cylindrical surface are formed by opposing sections of a common cylindrical surface 8. Coupling arrangement (1) according to one of claims 1 to 7, characterized in that the actuating device (6) has a sliding block (18) by which the intermediate lever (9) is supported on both sides in the axial direction against the housing (2) and is guided to be displaceable in the radial direction relative to the housing (2).
9. Clutch arrangement (1) according to one of claims 1 to 8, characterized in that the clutch (3) is a motor-side clutch and / or that the clutch arrangement (1) has a flywheel (22), wherein the counter-friction surface (4) of the clutch (3) is formed by the flywheel (22).
10. Coupling arrangement (1) according to one of claims 1 to 9, characterized in that the coupling arrangement (1) has a further coupling (23) arranged in the housing (2), wherein the coupling (3) and the further coupling (23) form a double coupling.