Clutch device having an intermediate lever and a path-based wear adjustment device which acts on said intermediate lever and has a blocking device in the form of a coupling mechanism

Abstract

The invention relates to a clutch device (1) for an agricultural tractor, comprising a friction clutch (5), which has a counter plate (2), a pressure plate (3) which can be axially moved relative to the counter plate (2), and a clutch disc (4) which can be frictionally pressed between the counter plate (2) and the pressure plate (3), and comprising an actuating device (6) for axially moving the pressure plate (3), an actuating lever (7) of the actuating device (6) being pivotably mounted on a bearing device (8) fixed to the housing and being axially movably coupled to the pressure plate (3) indirectly via an actuating device (6) intermediate lever (9) which is pivotally mounted on the actuating lever (7). The radially inner end (10a) of the actuating lever (7) is coupled to an axially movable actuating ring (11), and the radially inner end (12a) of the intermediate lever (9) rests against a bearing surface (13) of an adjustable ramp device (14) while the radially outer end (12b) thereof is axially movably coupled to the pressure plate (3). The ramp device (14) is designed to adjust the actuating lever (7) starting position, which can be changed due to a wear-induced movement of the pressure plate (3) relative to the counter plate (2), and the ramp device (14) has a drive (16) which is controlled on the basis of wear and comprises a biasing device (17), said biasing device being designed to store drive energy for the ramp device (14), and a blocking device (18), said blocking device blocking the biasing device (17) in a blocking state. The blocking device (18) additionally has a coupling mechanism (39).

Description

[0001] Clutch device with an intermediate lever and a path-based wear adjustment device acting on it, with a locking device designed as a coupling gear

[0002] The invention relates to a clutch device for an agricultural tractor, comprising a friction clutch with a counter plate, a pressure plate axially displaceable relative to the counter plate, and a clutch disc pressed between the counter plate and the pressure plate by frictional engagement. Furthermore, the clutch device has an actuating device for axially displacing the pressure plate, wherein an actuating lever of the actuating device is pivotably arranged on a housing-fixed bearing device and is indirectly coupled axially displaceably to the pressure plate via an intermediate lever of the actuating device which is in turn pivotably mounted on the actuating lever.The actuating lever is coupled at its radially inner end to an axially displaceable actuating ring, and the intermediate lever rests at its radially inner end against a bearing surface of an adjustable ramp device, while its radially outer end is axially displaceably coupled to the pressure plate. The ramp device (as part of a wear adjustment device) is designed to readjust the initial position of the actuating lever, which changes as a result of wear-induced displacement of the pressure plate relative to the counter plate.

[0003] Basic coupling devices, also simply referred to as tractor couplings, are already well-known in the prior art. One such tractor coupling is disclosed, for example, in DE 102022 133281 A1. The individual components of tractor couplings are usually designed to be so robust that, despite a certain amount of wear on the friction surfaces, the couplings could be operated throughout their entire service life. However, past developments and the lightweight construction measures implemented in this context, including reductions in installation space, have revealed that tractor couplings are often no longer sufficiently wear-resistant.

[0004] It is therefore an object of the present invention to enable a more efficient clutch actuation of a tractor clutch, which also makes clutches with a compact design usable over a long service life.

[0005] This is solved according to the invention by the ramp device having a wear-dependent controlled drive with a pre-tensioning device designed to store drive energy for the ramp device and a locking device that blocks the pre-tensioning device in a locking state (i.e., keeps the pre-tensioning device in the pre-tensioned state), wherein the locking device further comprises a coupling gear.

[0006] This design of the actuating mechanism allows the tractor clutch to be operated efficiently throughout its entire service life, despite its reduced dimensions. At the same time, it enables low-maintenance operation of the clutch system. This automatically self-adjusting wear-adjusting device ensures that the actuating lever's cup height is automatically adjusted according to the clutch's wear condition, thus remaining largely constant. Even with wear, the cup height initially increases slightly until adjustment occurs. Overall, the clutch system becomes robust and reliable, exhibiting consistent characteristics (such as the engagement threshold of the wear adjustment) throughout its entire service life. Furthermore, the integrated coupling mechanism is subject to minimal wear, ensuring the wear-adjusting device is durable.

[0007] Further advantageous embodiments are claimed in the dependent claims and explained in more detail below. Accordingly, it is also advantageous if the ramp device has a ramp ring that defines the support surface and is driven by the pre-tensioning device. This allows the ramp device to be designed in the most space-saving way possible.

[0008] The preloading device is preferably designed such that it is brought into its preloaded state by the actuating ring during axial clutch actuation (preferably opening of the friction clutch). This cleverly generates the drive energy required for subsequent readjustment from the axial adjustment that occurs anyway. The design can thus be further simplified.

[0009] In this regard, it is also advantageous if the locking device is designed such that, in the locked state, it acts on the ramp ring / a drive ring that can be coupled to the ramp ring in the opposite direction to a drive force generated by the preloading device in its preloaded state. This allows the locking device and preloading device to be designed simply and compactly. Preferably, the locking device automatically assumes its locked state upon the preloading device reaching its preloaded state once.

[0010] Therefore, it is also advantageous if the linkage mechanism has a toggle lever arrangement. This allows the linkage mechanism to be designed as simply and compactly as possible.

[0011] If the coupling mechanism has an elastic toggle lever, the locking state of the locking device can be activated and deactivated as reliably as possible.

[0012] For ease of manufacture, it is further advantageous in this context if the toggle lever is designed as a mechanical spring, preferably as a curved spring element, in particular a leaf spring or a torsion spring. Furthermore, it is advantageous if the linkage is operatively connected to a drive ring of the drive, which in turn (depending on the state of the wear adjustment device) is rotatable relative to the ramp ring of the ramp device or supported in a twisted position on it.

[0013] If the locking device is designed in such a way that it maintains the locking state of the preloading device up to a certain wear limit of the contacting friction surfaces of the pressure plate, clutch disc and / or counter plate, normal operation can be carried out as efficiently as possible.

[0014] Furthermore, it is advantageous if the locking device is designed such that, upon exceeding a certain wear limit of the contacting friction surfaces of the pressure plate, clutch disc, and / or counter plate, it automatically assumes an unlocked state, thereby releasing a rotation of the ramp ring using the drive force / energy previously stored in the preloading device and thus readjusting the contact surface to the intermediate lever in the direction of the initial position. This ensures a simple final readjustment.

[0015] To ensure the least possible wear on the actuating device, it is advantageous if the radially inner end of the intermediate lever slides against the support surface designed as a ramp rising or falling in the circumferential direction.

[0016] Furthermore, the actuating mechanism is kept as simple as possible if the axial position of the radially inner end of the actuating lever is directly influenced by the position of the intermediate lever. This ensures that any wear-related adjustment / readjustment of the intermediate lever also directly results in a readjustment of the position of the side of the actuating lever contacting the actuating ring (the radially inner end). It is also advantageous if the ramp ring has a multitude of preload teeth on a circumferential area into which a clamping element of the preloading device can be engaged. This allows the components of the preloading device and the clamping device to be arranged next to each other in the most efficient and space-saving way possible.

[0017] If the friction clutch is designed as a normally closed clutch, the actuating device, including its wear adjustment, can be implemented as simply as possible.

[0018] Furthermore, it is advantageous to have two friction clutches and to have an actuating device designed for independent actuation of these two friction clutches. This allows for the efficient implementation of a compact dual clutch.

[0019] In other words, the invention proposes that the ramp ring is pre-tensioned circumferentially and prevented from rotating by a locking device designed as a linkage (acting indirectly on the ramp ring). When the height of the actuating levers in the engaged state (preferably for the drive clutch / gear-shifting clutch, which is designed as a normally engaged clutch) rises above a certain point, the locking device is released, causing the circumferentially spring-loaded ramp ring to rotate in the adjustment direction. During this process, the tips / ends of the intermediate levers slide down the ramps of the ramp ring to a lower height, thereby also restoring the lower height of the actuating levers, or more precisely, their actuating tips / ends, to their original (initial) position. This is thus a displacement-based wear adjustment device.The arrangement with a ramp ring for all actuating / intermediate levers ensures that the same adjustment occurs simultaneously for all levers during an adjustment step. This is not necessarily guaranteed with other arrangement variants for adjustment mechanisms. The invention will now be explained in more detail below with reference to figures, in which context different exemplary embodiments are also illustrated.

[0020] They show:

[0021] Fig. 1 shows a schematic representation of a coupling device according to the invention in a preferred embodiment, in which in particular the structure of an actuating device of the coupling device can be seen and a closed position / a closed state of a friction clutch is implemented.

[0022] Fig. 2 shows a schematic representation of the coupling device similar to Fig. 1, wherein the actuating device in its actuated state has now moved the friction clutch into its open position / open state, wherein at the same time a preloading device of a wear adjustment device is preloaded relative to a ramp ring and a locking device acting against this preloading device already engages a drive ring coupled or connectable to the ramp ring.

[0023] Fig. 3 shows a schematic representation of the coupling device similar to Fig. 1, illustrating that following the state of Fig. 2, after the friction clutch has been closed again, the locking device holds the preloading device in its preloaded state.

[0024] Fig. 4 shows a detailed view of Fig. 1 in the area of ​​the locking device,

[0025] Fig. 5 shows a detailed view of Fig. 2 in the area of ​​the locking device.

[0026] Fig. 6 is a detailed view of Fig. 3 in the area of ​​the locking device, Fig. 7 is a schematic detailed view of the coupling device similar to Fig. 6, wherein the friction clutch now closes after a certain wear of the components of the friction clutch, so that the locking device is released,

[0027] Fig. 8 shows a schematic detail view of the coupling device similar to Fig. 7, wherein, in comparison to Fig. 7, an elastic toggle lever of the coupling mechanism is completely relaxed.

[0028] Fig. 9 shows a schematic detail view of the coupling device similar to Fig. 1 in the state after readjustment of the actuating device upon reactivation of the locking device.

[0029] Fig. 10 shows a perspective view of the coupling device shown in more detail according to Fig. 1.

[0030] Fig. 11 shows two partial views of the coupling device of Fig. 1, wherein the coupling mechanism is shown in detail in the upper partial view and the components complementary to Fig. 1 are shown schematically in the lower partial view.

[0031] Fig. 12 shows a perspective view of the elastic toggle lever of the locking device,

[0032] Fig. 13 shows a perspective view of a locking plate of the locking device,

[0033] Fig. 14 shows a perspective view of a release bolt of the locking device,

[0034] Fig. 15 shows a perspective view of a support bolt of the locking device, and Figs. 16a to 20b show various views of the coupling device in the area of ​​the pre-tensioning device and the locking device in the individual states before and after wear-related readjustment.

[0035] The figures are purely schematic and serve solely to illustrate the invention. The same elements are identified by the same reference symbols.

[0036] Figure 1 schematically illustrates the coupling device 1 according to a preferred embodiment of the invention. The coupling device 1 is designed as a double clutch. Furthermore, the coupling device 1 is used as a tractor clutch, that is, as a clutch in a drive train of an agricultural tractor.

[0037] The coupling device 1 therefore has two friction clutches 5, of which only one friction clutch 5 is shown in Fig. 1 for the sake of clarity. In alternative embodiments, the coupling device 1 can also be implemented as a single clutch and thus contain only one friction clutch 5. The two friction clutches 5 can be actuated independently of each other.

[0038] An actuating device 6, which is also part of the coupling device 1, serves to actuate the friction clutch 5 shown in Fig. 1. For a more detailed description of the design and function of this actuating device 6, reference is made to DE 10 2022 133 281 A1, which is considered incorporated herein for this purpose. The basic design of the actuating device 6 thus corresponds to the actuating device of DE 10 2022 133 281 A1.

[0039] The actuating device 6 therefore serves to actuate the friction clutch 5, that is, to adjust the friction clutch 5 between a closed position and an open position, the closed position representing a normal / start position of the friction clutch 5. The friction clutch 5 is thus implemented as a normally closed friction clutch 5. The actuating device 6 is therefore arranged in its unactuated / inactivated state such that the friction clutch 5 is closed, and in its actuated / activated state such that the friction clutch 5 is open.

[0040] The actuating device 6 has a known design and includes an actuating lever 7, the radially inner / first end 10a of which is axially displaceable by a corresponding actuating bearing, here with an actuating ring 11 interposed. Furthermore, the actuating lever 7 is mounted at its radially outer / second end 10b in a housing-fixed bearing device 8 (pivotably). The actuating device 6 has several (approximately three) actuating levers 7, which are intended for actuating the friction clutch 5.

[0041] Radially between the first end 10a and the second end 10b, each actuating lever 7 is coupled in a displacement-resistant manner to an intermediate lever 9, preferably also via a bearing device 8 / pivot bearing.

[0042] The intermediate lever 9 rests with its radially outer / second end 12b directly against a coupling element 23 which is connected to a pressure plate 3 of the friction clutch 5 in a displacement-resistant manner. With its radially inner / first end 12a, the intermediate lever 9 rests against a support area, preferably further supported by the housing, in the form of a bearing surface 13 of a ramp ring 15. The ramp ring 15 and the previously mentioned actuating ring 11 are part of a wear adjustment device 24, which will be explained in more detail below.

[0043] The wear adjustment device 24 serves to adjust / recalibrate the contact surface 13 and thus indirectly also to adjust the area of ​​the actuating lever 7 in contact with the actuating ring 11 and thus the actuating bearing in the event of wear occurring during operation of the friction surfaces 19 of the pressure plate 3 and the (usually housing-fixed) counter plate 2, and in particular the clutch disc 4 arranged between them. The wear adjustment device 24 thus serves to adjust / axially adjust a contact area between the intermediate lever 9 and the contact surface 13 / the ramp ring 15 ( / a housing-fixed support point of the intermediate lever 9) at a specific wear path / a specific wear limit.

[0044] The ramp ring 15 of the wear adjustment device 24, which forms a ramp device 14, can also be seen in Fig. 10. The ramp ring 15 has a support surface 13 designed as a ramp for each intermediate lever 9 and thus for each contact area with an intermediate lever 9.

[0045] The ramps slope downwards in the circumferential direction with respect to the initial position shown in Fig. 1 (maximum height of the support surface 13). This is shown in a highly simplified manner in Fig. 1.

[0046] The ramp ring 15 is rotatably mounted on the housing 20, which can be seen, for example, in Fig. 10. The ramp ring 15 can be driven by a preloading device 17. The preloading device 17 is thus part of a drive 16 for driving / rotating the ramp ring 15.

[0047] The preloading device 17 has at least one preload spring 25, which serves to temporarily store a preload force, as can be seen below with reference to Figures 1 to 9. Furthermore, the preloading device 17 has a drive ring 21, which in turn can be directly driven by the actuating ring 11. When the drive ring 21 rotates, it directly preloads the preload spring 25.

[0048] The (overall annular / disc-shaped) actuating ring 11 has a contact surface / contact line / contact chamfer 26 that extends axially in the direction towards the drive ring 21. This contact chamfer 26 is formed, for example, by a conical bolt 22 and causes the drive ring 21 to rotate in a specific direction when the actuating ring 11 is adjusted / displaced axially (when the friction clutch 5 is actuated). The drive ring 21 and the at least one preload spring 25 are matched to each other and, in turn, to the contact chamfer 26 of the actuating ring 11, such that axial adjustment of the actuating ring 11 during actuation of the friction clutch 5 preloads the drive ring 21 and the preload spring 25.

[0049] In the ultimately achieved pre-tensioned state of the pre-tensioning device 17, a locking device 18 blocks the pre-tensioning device 17 / the pre-tensioning spring 25 and thus stores the drive energy required for the subsequent wear adjustment by indirectly supporting the pre-tensioning spring 25.

[0050] The locking device 18 has a linkage 39 or is preferably designed directly as such a linkage 39. The linkage 39 is further designed as a toggle lever arrangement 40. The locking device 18 therefore has a toggle lever 41 which is coupled to the drive ring 21 at its first end region by forming a first pivot point 42, namely in particular in the circumferential direction / direction of rotation.

[0051] The toggle lever 41 is pivotally connected to a locking plate 45 at a second pivot point 43 (at its second end region), which locking plate 45 constitutes a lifting element. It is particularly evident in Figure 12 that the toggle lever 41 is designed as an elastic spring and is therefore elastically compressible. In the present embodiment, the toggle lever 41 is designed as a curved / partially arcuate or even ring-shaped sheet / leaf spring.

[0052] The locking plate 45 is supported / mounted at its end opposite the second pivot point 43 (third pivot point 44) in a housing-fixed manner. In particular, the locking plate 45 is pivotably mounted on the support bolt 46 shown separately in Fig. 15. The locking lever is coupled to a release bolt 31 between the first pivot point 42 and the second pivot point 43 in the area of ​​a window 47 / through hole. As explained in more detail below, the release bolt 31 serves to unlock the locking device 18. The release bolt 31 is preferably directly and immovably connected to the actuating ring 11.

[0053] As can be seen in Figures 7 to 9, when a certain wear limit is reached of the friction surfaces 19 of the counter plate 2, pressure plate 3, and clutch disc 4, the actuating ring 11 is displaced by the changing lever height of the intermediate lever 9 and the actuating lever 7 by the actuating bearing (not shown for clarity) to such an extent that the locking device 18 automatically releases from its locked position and thus immediately releases the preloading device 17. It should be noted that the actuating ring 11, which is displaced by the actuating bearing when the clutch is disengaged / actuated, is conversely driven by the actuating levers 7 when the clutch is engaged / closed and, in its worn state, reaches an axial height to trigger the adjustment. The actuating bearing may, under certain circumstances, already lift off the actuating ring 11 in the axial direction; thus, it does not actuate in this case.

[0054] The preloading device 17 thus transfers the drive energy previously stored in the preload spring 25 directly to the drive ring 21, which in turn rotates the ramp ring 15 via a corresponding detent mechanism 27. This gradually relaxes the preload spring 25, although it does not reach a fully relaxed state. Simultaneously, the ramp ring 15 rotates relative to the intermediate lever 9, and the radially inner end 12a of the intermediate lever 9 slides along the ramped support surface 13. The force of the preload spring 25 is therefore sufficient to complete the adjustment step. The preload spring 25 thus still retains a certain amount of preload. The extent of the adjustment step is limited by a stop 49, for example, for the drive ring 21.This ultimately returns the contact area between intermediate lever 9 and actuating lever 7 axially to its initial position. Figures 10 to 20b then show several details of the preferred embodiments of the individual components.

[0055] In other words, according to the invention, in order to minimize the adverse effects (wear, hysteresis, etc.) of frictional movements on an adjusting lock (locking device 18), a linkage 39, such as a toggle lever arrangement 40, is to be used as the adjusting lock. Specifically, this assembly should contain at least one elastic element (toggle lever, e.g., a spring) to compensate for tolerances of the kinematic arrangement and to achieve advantageous functional properties (functional reliability, e.g., against unintentional readjustment).

[0056] Figures 4 to 6 show a schematic of an adjusting lock with a toggle lever 41, illustrating the sequence during clutch actuation. A first stage of an adjusting step (spring accumulator tensioning + locking mechanism activation) is visible: The clutch is initially (in Figure 4) unactuated (closed), the spring accumulator is relaxed, and the adjusting lock is open (toggle lever free). The spring element (elastic coupling element; toggle lever 41) is largely relaxed. When the clutch is actuated (opened), the drive ring 21 is forced to move in the opposite direction to the adjusting movement, and the spring accumulator (preload spring 25) is tensioned (Figure 5). Simultaneously, an element / part of the actuating ring / actuating element 11 (e.g., by release bolt 31) activates / closes the adjusting lock. For this purpose, the coupling mechanism (toggle lever) is moved into a corresponding locking position. The elastic coupling element is also tensioned in this process.In the locked position, a force is reliably applied to secure the activated locked position. The preload force of the spring accumulator acts on the locking device 18 in such a way that it remains self-holding in the locked position (Fig. 6). When the clutch is subsequently closed, the drive ring 21 will thus remain in the tensioned position. Therefore, when the clutch is closed again according to Fig. 6, the activated position will be maintained by the preload of the spring accumulator and the tension of the elastic coupling element. Crucially, the loaded elastic coupling element now opposes the drive force of the drive ring 21 and stops it in the tensioned position, thus initially preventing any readjustment without wear. The force component of the activated lock opposing the readjustment movement should be at least equal to or greater than the preload of the spring accumulator.However, to prevent an unwanted reverse rotation of the drive ring 21, it can be equipped with a travel stop.

[0057] In the type of locking device 18 shown, the contact points are partially designed as pivot joints (joint points 42, 43, 44). Therefore, only minor adverse frictional effects and reduced wear are to be expected under the acting forces.

[0058] Furthermore, it is proposed to insert an elastic element (as the toggle lever 41 itself) in the locking device 18. Preferably, this involves a spring-loaded support of the locking device 18 against the frame / housing 20 in the direction of the locking force. Alternatively, it would be possible to insert an elastic element in another form, for example, as an additional component.

[0059] Figures 1 to 3 show a diagram of the process during clutch actuation, with the tensioning of the spring accumulator and activation of the adjustment lock on the drive ring.

[0060] Figures 6 to 9 then schematically illustrate the sequence of an adjustment step: First, the spring accumulator is tensioned and the adjustment lock on the drive ring 21 is activated (Fig. 6). After a certain amount of wear, the adjustment lock is partially opened by the release bolt 31 (Fig. 7). In Fig. 8, the adjustment lock is then fully opened (by releasing the previously pre-tensioned toggle lever 41). The spring accumulator finally releases, thereby adjusting the mechanism and reducing the lever tip height (Fig. 9). This makes it clear that when the adjustment device (spring accumulator) is tensioned, the adjustment lock does not open if the clutch is closed (unactuated) and there is no wear. If clutch wear occurs, the adjustment lock opens. Once a certain wear limit is exceeded, the adjustment lock opens.Here, the opening movement of the coupling mechanism 39 is itself forced by the force exerted by the pre-tensioned coupling element. The drive ring 21 now faces no opposing force, and an adjustment step can be performed.

[0061] The drive ring 21 acts on the locking device 18 with the preload force of the spring accumulator. Due to the arrangement of the linkage 39, only minimal frictional forces occur during any movement, even partial, of the locking device 18 (opening / closing the clutch with wear below the release limit). This also results in minimal wear on the components. Overall, the clutch system with adjustment is robust and reliable, and maintains consistent properties (such as the response threshold of the wear adjustment) throughout its entire operating life, as the position of the actuating levers 7 (height of the inner actuating cups) is compensated for / kept nearly constant during adjustment.

[0062] In conjunction with Figures 10 to 15, it becomes clear that the linkage 39 of the adjusting lock is formed from the locking plate 45 and, for example, a ring spring (toggle lever 41). The support plate / locking plate 45 is mounted relative to the housing 20 by a support bolt 46.

[0063] The ring spring forms the elastic coupling element in one piece. This design advantageously requires only a few components. A multi-part version of the coupling element / toggle lever 41 with an integrated, separate spring element would also be possible.

[0064] The release bolt 31 is fixed to the actuating ring and engages, for example, in an opening in the locking plate 45. It is provided with two shoulders / contact areas 48a, 48b to activate or release the readjustment lock when the clutch opens or when the closed clutch is worn. Figures 16a to 20b illustrate the sequence of clutch actuations; with tensioning of the spring accumulator on the drive ring 21 when the clutch opens / actuates and an adjustment step of the unactuated / closed clutch when wear exceeds a limit.

[0065] List of reference signs

[0066] Coupling device

[0067] Counter plate

[0068] pressure plate

[0069] clutch disc

[0070] Friction clutch

[0071] Actuating device

[0072] Actuating lever

[0073] Storage device

[0074] intermediate lever a first end of the actuating lever b second end of the actuating lever

[0075] Actuating ring a first end of the intermediate lever b second end of the intermediate lever

[0076] Contact surface

[0077] Ramp device

[0078] Ramp ring

[0079] drive

[0080] Pre-tensioning device

[0081] Locking device

[0082] friction surface

[0083] Housing

[0084] drive ring

[0085] Cone bolt

[0086] Coupling element

[0087] Wear adjustment device

[0088] Preload spring

[0089] Contact angle

[0090] Locking mechanism

[0091] trigger bolt

[0092] Linkage gear

[0093] Knee lever arrangement

[0094] Knee lever, first joint point, second joint point, third joint point

[0095] Locking plate

[0096] Support bolts

[0097] Window a first contact area b second contact area 49 stop

Claims

Patent claims 1. Coupling device (1) for an agricultural tractor, comprising a counter plate (2), a pressure plate (3) axially displaceable relative to the counter plate (2), and a clutch disc (4) frictionally pressed between the counter plate (2) and the pressure plate (3), an actuating device (6) for axially displacing the pressure plate (3), wherein an actuating lever (7) of the actuating device (6) is pivotably arranged on a housing-fixed bearing device (8) and is indirectly axially displaceably coupled to the pressure plate (3) via an intermediate lever (9) of the actuating device (6) pivotably mounted on the actuating lever (7).wherein the actuating lever (7) is coupled at its radially inner end (10a) to an axially displaceable actuating ring (11) and the intermediate lever (9) bears at its radially inner end (12a) against a support surface (13) of an adjustable ramp device (14), while its radially outer end (12b) is axially displaceably coupled to the pressure plate (3), wherein the ramp device (14) is designed to readjust an initial position of the actuating lever (7) which may change as a result of wear-related displacement of the pressure plate (3) relative to the counter plate (2), characterized in that the ramp device (14) has a wear-dependent controlled drive (16) with a preloading device (17) designed to store drive energy for the ramp device (14) and a locking device (18) that blocks the preloading device (17) in a locking state,wherein the locking device (18) has a coupling mechanism (39).

2. Coupling device (1 ) according to claim 1 , characterized in that the coupling mechanism (39) has a toggle lever arrangement (40).

3. Coupling device (1 ) according to claim 1 or 2, characterized in that the coupling mechanism (39) has an elastic toggle lever (41 ).

4. Coupling device (1 ) according to claim 3, characterized in that the toggle lever (41 ) is designed as a mechanical spring.

5. Coupling device (1 ) according to one of claims 1 to 4, characterized in that the coupling gear (39) is operatively connected to a drive ring (21 ) of the drive (16), which drive ring (21 ) in turn is rotatable relative to a ramp ring (15) of the ramp device (14).

6. Coupling device (1 ) according to claim 3 or 4, characterized in that the locking device (18) is designed such that it maintains the locking state of the preloading device (17) up to a certain wear limit of the friction surfaces (19) in contact of the pressure plate (3), clutch disc (4) and / or counter plate (2).

7. Coupling device (1 ) according to claims 3 to 5, characterized in that the locking device (18) is designed such that, when a certain wear limit of the contacting friction surfaces (19) of the pressure plate (3), clutch disc (4) and / or counter plate (2) is exceeded, it automatically assumes an unlocked state, releasing a rotation of the ramp ring (15) by means of the drive force previously stored in the preloading device (17) and thus adjusting the contact surface (13) to the intermediate lever (9) in the direction of the initial position.

8. Coupling device (1 ) according to one of claims 1 to 6, characterized in that the radially inner end (12a) of the intermediate lever (9) slides against the support surface (13) designed as a ramp rising or falling in the circumferential direction.

9. Coupling device (1 ) according to one of claims 1 to 7, characterized in that an axial position of the radially inner end (10a) of the actuating lever (7) is directly influenced by the position of the intermediate lever (9).

10. Coupling device (1 ) according to one of claims 1 to 8, characterized in that the friction coupling (5) is designed as a normally closed coupling.

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