Clutch adjusting device

Abstract

Adjusting device (1) for a clutch (15) with an actuation direction (B), comprising - a first ramp ring (2) arranged coaxially about a longitudinal axis (A) for disengaging the clutch (15), wherein the first ramp ring (2) has an adjusting ramp (2.1) and a drive ramp (2.2) in a transverse direction (Q) to the actuation direction (B), - a second ramp ring (5) movable coaxially about the longitudinal axis (A) and in the actuation direction (B) for actuation by a release bearing (16), comprising a first counter ramp (5.1), wherein the first counter ramp (5.1) is formed with a counter contour (5.4) to a contour (2.4) of the adjusting ramp (2.1), wherein the first counter ramp (5.1) is supported with its counter contour (5.4) on the contour (2.4) of the adjusting ramp (2.1), - a sleeve element (7) movable coaxially about the longitudinal axis (A) and in the transverse direction (Q) with a second counter ramp (7.1), wherein the second counter ramp (7.1) can be applied to a contour (2.4) on the drive ramp (2.2) in the direction of actuation (B) with a counter contour (7.4), wherein the drive ramp (2.2) and the second counter ramp (7.1) are designed to slide past each other in the transverse direction (Q) when a contact force is applied in the direction of actuation (B), characterized in that the second ramp ring (5) is movably mounted at least indirectly on the sleeve element (7) in the actuation direction (B) and in the transverse direction (Q), that the sleeve element (7) and the second ramp ring (5) are operatively connected in the transverse direction (Q), and that the contour (2.4) of the first ramp ring (2) and the counter contour (5.4) of the second ramp ring (5) are formed in the form of complementary steps (2.4, 5.4).

Description

[0001] The invention relates to an adjusting device for compensating for wear in a clutch, so that the clutch can always be actuated by an actuating device via the same actuation path. The invention further relates to a clutch with such an adjusting device, in particular a dry friction clutch, by means of which a torque flow can be established or interrupted in the drive train of a motor vehicle.

[0002] Conventional vehicle clutches, such as dry friction clutches without wear compensation, are known from the prior art. If, for example, the friction element on the clutch disc experiences thickness wear over its service life, this typically affects the range of motion of the clutch actuation. In clutches with spring accumulators or disc springs, the range of motion will shift in the opposite direction to the actuation direction, i.e., the release travel, as the friction element wears, to an increasing degree. To counteract this, it is already known from the prior art to arrange an independently adjustable ramp device between the actuating parts of the clutch, e.g., a lever element in the form of a release lever and the release system in the form of a release bearing, in order to compensate for the thickness wear of the friction element.

[0003] The required incline angle of the adjustment ramp components is considered problematic. A relatively steep incline is necessary to achieve the height compensation required for wear adjustment within the available range of motion. However, since the release force must be transmitted via this ramp shape during operation, it should be self-holding, preferably self-locking. Experience has shown, however, that this requirement cannot be reliably met in real-world operation.

[0004] From DE 10 2006 016 666 A1, an adjusting device for a coupling is known which can be read as referring to the preamble of claim 1.

[0005] The present invention is based on the objective of overcoming, at least partially, the disadvantages arising from the prior art.

[0006] The problem is solved according to the invention by an adjusting device with the features of claim 1 and by a coupling according to the invention with the features of claim 10. Dependent claims are directed to advantageous further developments. It should be noted that the features listed individually in the dependent claims can be combined with one another in any technologically meaningful way and define further embodiments of the invention. In addition, the features specified in the claims are further specified and explained in the description, whereby further preferred embodiments of the invention are presented.

[0007] The adjusting device according to the invention for a clutch with one direction of actuation comprises - a first ramp ring arranged coaxially around a longitudinal axis for disengaging the clutch, wherein the first ramp ring has an adjusting ramp and a drive ramp in a transverse direction to the direction of actuation, - a second ramp ring movable coaxially about the longitudinal axis and in the direction of actuation for actuation by a release bearing, comprising a first counter ramp, wherein the first counter ramp is formed with a counter contour to a contour of the adjusting ramp, wherein the first counter ramp with its counter contour is supported on the contour of the adjusting ramp, - a sleeve element movable coaxially about the longitudinal axis and in the transverse direction with a second counter ramp, wherein the second counter ramp can be applied with a counter contour to a contour on the drive ramp in the direction of actuation, wherein the drive ramp and the second counter ramp are designed to slide past each other in the transverse direction when a contact force is applied in the actuation direction. The adjusting device is characterized in that the second ramp ring is movably mounted, at least indirectly, on the sleeve element in the actuation direction, and that the sleeve element and the second ramp ring slide in the transverse direction, preferably via a spring element, are functionally connected and that the contour of the first ramp ring and the counter contour of the second ramp ring are formed in the form of complementary steps.

[0008] It should be noted as a precaution that the numerical terms used here ("first", "second", etc.) primarily serve (only) to distinguish between several similar objects, quantities, or processes, and thus do not necessarily dictate any dependency and / or sequence between these objects, quantities, or processes. Should a dependency and / or sequence be required, this is explicitly stated here, or it will be obvious to a person skilled in the art upon studying the specific configuration described.

[0009] A conventional clutch known from the prior art has two pressure plates, one connected to the input shaft and the other to an output shaft. When the clutch is engaged, these plates are in frictional contact with each other via friction elements. The distance between the pressure plates when the clutch is engaged is determined by the thickness of the friction elements. As the friction elements wear, the distance between the pressure plates decreases when the clutch is engaged. Consequently, a lever element of the clutch, such as a release lever or a disc spring tongue, travels a greater distance between the open and closed positions as the wear increases. If the clutch does not have an adjusting device, this additional travel must also be compensated for by an upstream actuating device, such as a clutch pedal.To prevent the actuating device from having to travel this extended distance and instead always having to travel only an essentially the same distance, an adjusting device according to the invention is arranged between the clutch and the actuating device.

[0010] When the second ramp ring is actuated in the direction of actuation, for example via a clutch pedal, it moves the first ramp ring in the direction of actuation via the first counter-ramp, which rests against the adjusting ramp. This first ramp ring then disengages the clutch on the output side, for example at a release lever or a disc spring tongue. Because the first counter-ramp has a stepped contour on the adjusting ramp, which has a complementary contour in the form of counter-steps, thus creating a self-locking connection between the first counter-ramp and the adjusting ramp, the transmission of such a movement and the associated disengagement force between the first counter-ramp and the adjusting ramp in the direction of actuation is possible without the first counter-ramp slipping off the adjusting ramp and subsequently moving laterally.When the first ramp ring is activated, the drive ramp moves away from the second counter ramp, which is fixed in the direction of activation and therefore immobile.

[0011] When the actuation is terminated, the clutch closes again, for example by means of a spring element, and the first ramp ring is pushed back until the friction elements of the clutch are in contact again. At this point, the drive ramp and the second counter ramp also re-engage. Generally, the drive ramp and the second counter ramp are designed without steps and together form an inclined plane. However, it is also possible for the drive ramp and the second counter ramp to have a contour in the form of steps corresponding to the adjusting ramp and the first counter ramp.

[0012] As soon as wear occurs on the clutch or its friction elements, a force arises between the second counter-ramp and the drive ramp in the direction of actuation. This is because the clutch pushes the first ramp ring back a greater distance than before, while the second counter-ramp remains stationary in the direction of actuation. This force causes the second counter-ramp to slide laterally along the drive ramp, thus generating a lateral force.

[0013] The sliding of the second counter ramp along the drive ramp results in the transfer of the resulting force in the transverse direction to the first counter ramp of the second ramp ring. This is preferably achieved through a rigid connection between the second counter ramp and the first counter ramp, which can be mediated, in particular, by an intermediate element. This variant is structurally simple to manufacture and assemble. Alternatively, it is preferred that this resulting force is stored in a spring element that at least indirectly connects the sleeve element and the second ramp ring. The spring element can, for example, be a tension or compression spring that is subjected to either tensile or compressive force.Once a certain degree of wear is reached and the force stored in the spring element exceeds a threshold, the spring element releases the stored energy, causing the first counter-ramp of the second ramp ring to slide along the adjusting ramp of the first ramp ring. Consequently, the distance between the first and second ramp rings changes approximately the same amount as the distance between the first ramp ring and the sleeve element, namely until further adjustment by the spring element is inhibited by the self-locking mechanism of the stepped adjusting ramp and the stepped first counter-ramp. These steps, in particular, prevent the second ramp ring from rotating backward relative to the first ramp ring.

[0014] The axial length in the actuation direction of the first ramp ring and the sleeve element, and the axial length of the first ramp ring and the second ramp ring, always exhibit a nearly identical, fixed difference due to the steps, provided the adjusting ramp and the drive ramp have the same slope. Thus, when the clutch is closed, the second ramp ring always remains in the same position in the actuation direction and does not transmit any increased travel resulting from wear to an actuating device.

[0015] According to a first preferred embodiment, the sleeve element and the second ramp ring are operatively connected in the transverse direction by a pin of the second ramp ring, which is supported in a recess of the sleeve element. The spring element is arranged in the transverse direction within the recess between the pin and the sleeve element. Thus, the spring element is attached at one end to the sleeve element and at the other end to the second ramp ring. The spring element can, for example, be a compression spring arranged between the sleeve element and the second ramp ring, which is compressed with increasing wear before triggering an adjustment. Alternatively, the spring element can also be designed as a tension spring or a shaped spring, such as a bending beam.

[0016] The recess can be formed by a reduction in the wall thickness of the sleeve-shaped element, and can be located on either the inside or outside of the sleeve. Alternatively, a recess can be formed, at least partially, by removing a section of the sleeve element's wall. A combination of a cutout and a reduction in wall thickness is also possible. Multiple recesses are possible, requiring a corresponding number of additional intermediate elements and spring elements.

[0017] In particular, the recess of the sleeve element is designed to provide an interference fit with the pin, allowing the pin to move within the recess both in the direction of actuation and laterally. The pin is an integral part of the second ramp ring, which is directly operatively connected to the sleeve ring. When the friction element of the clutch wears, the pin moves laterally within the recess. In this embodiment, the spring element, located in the recess between the pin and the inner wall of the recess, is designed to absorb the force generated by this lateral movement and to adjust the second ramp ring relative to the first ramp ring.

[0018] According to a second preferred embodiment, the sleeve element and the second ramp ring are operatively connected to each other in the transverse direction by an intermediate element and by the spring element. Particularly preferably, the intermediate element is mounted with a pin in a recess of the sleeve element, and the spring element is supported at one end by the intermediate element and at another end by the second ramp ring. The second embodiment differs from the first embodiment in that the second embodiment is designed with an additional intermediate element. This intermediate element is a component of the adjusting device and serves as a connecting link between the sleeve element, the spring element, and the second ramp ring. Therefore, the second ramp ring is not directly, but indirectly, operatively connected to the sleeve element.The intermediate element has a pin at one end, and the intermediate element is movably mounted in the recess in the sleeve element with the pin in the direction of actuation. In contrast to the first embodiment, however, the recess is dimensioned such that no movement of the pin in the transverse direction is possible. The sleeve element is connected to the spring element at a second end. The spring element can, for example, be a compression spring arranged between the intermediate element and the second ramp ring, which is compressed with increasing wear before triggering an adjustment. Alternatively, the spring element can also be designed as a tension spring.

[0019] Preferably, the adjusting ramp and / or the drive ramp are formed from several ramp elements distributed around the circumference. The counter ramps are then also divided into correspondingly multiple sections. All ramp elements of a ramp are identical. This ensures uniform support of the second ramp ring or the sleeve element on the first ramp ring around the circumference. Particularly preferably, the steps of the adjusting ramp and the steps of the first counter ramp are uniformly distributed across the ramps.

[0020] Preferably, the drive ramp and the adjustment ramp have the same gradient. This ensures that the axial length difference between the first ramp ring and the second ramp ring, on the one hand, and between the first ramp ring and the sleeve element, on the other, does not change significantly, and the second ramp ring is reliably held in a constant position. A small, but negligible, axial length difference arises, however, from the stepwise adjustment of the first counter ramp by the adjustment ramp. Furthermore, any force resulting from wear between the drive ramp and the second counter ramp always leads to the same movement in the transverse direction of the sleeve element and the second ramp ring. Thus, reliable adjustment is ensured in both cases of slight and advanced wear.

[0021] Preferably, a further spring element is arranged between the second ramp ring and a guide element, wherein the further spring element opposes the first spring element. The further spring element, which is arranged in the opposite direction to the adjusting movement, prevents the occurrence of multiple unwanted or uncontrolled adjustments.

[0022] Furthermore, preferably at least one detent device and / or friction device exerts a counterforce against a transverse readjustment movement of the second ramp ring. The detent device is formed, firstly, by concave recesses on the side of the second ramp ring facing away from the first ramp ring. A second component of the detent device engages in this recess and is designed with at least one raised section. This raised section can, for example, be located on a preload spring that applies the preload. A corresponding arrangement between the drive ramp and the second counter-ramp of the sleeve element is also possible. Alternatively, the raised section can be located on an additional component between the second ramp ring and a release bearing. This prevents unintentional or excessive movement of the second ramp ring during a readjustment movement.Several stages can be skipped uncontrollably.

[0023] To counteract the possibility of unintentional readjustment, a friction device can be provided that increases the contact pressure between the additional component and the second ramp ring. When the clutch is not disengaged, no force is transmitted to the additional component via the release bearing. Thus, the friction device ensures that even when the clutch is engaged, sufficient counterforce is exerted by the detent mechanism to prevent uncontrolled readjustment.

[0024] Furthermore, the steps preferably each have a horizontal bearing surface or a bearing surface with an angle opposite to the ramp's angle in the transverse direction. If the steps are designed such that the bearing surface for axial force transmission has an angle of inclination opposite to the main ramp direction, the detent function can be achieved at this point. When the preload, disengagement force, or, for example, a force due to vibration excitation acts, a force or moment is generated that opposes the direction of the adjusting movement. This inclined ramp shape, in combination with the constant force exerted by the preload springs, thus also achieves the desired detent effect without requiring additional components.

[0025] The invention relates in particular to a coupling for selectively connecting or disconnecting an input shaft and at least one output shaft with a previously described adjusting device. The adjusting device and the coupling can be integrated as a single unit and share a common housing. This reduces the number of components, thus minimizing the interaction of component tolerances. Alternatively, the adjusting device is provided as a separate component and arranged on a receptacle of the coupling.

[0026] Preferably, the coupling has several partial couplings for multiple output shafts, with at least one partial coupling having a previously described adjusting device. For example, such a coupling is provided for an agricultural or construction machine, wherein a first output shaft serves to drive the machine and is, for instance, the input shaft of a drive transmission, and a second shaft is a power take-off shaft for a secondary application such as driving a winch or a lifting device. In one embodiment, only the first partial coupling for the first output shaft is designed or equipped with an adjusting device, since this is subject to greater wear due to more frequent use, especially under load.In such an embodiment, in which the adjusting device is designed coaxially to the longitudinal axis in a cylindrical coordinate system, the first ramp ring, the sleeve element and / or the second ramp ring can have recesses distributed around the circumference for the passage of elements of the second partial coupling in order to create a particularly compact coupling.

[0027] The invention and its technical context are explained in more detail below with reference to the figures. It should be noted that the invention is not intended to be limited by the exemplary embodiments shown. In particular, unless explicitly stated otherwise, it is also possible to extract partial aspects of the situations explained in the figures and combine them with other components and findings from the present description and / or figures. It should be noted in particular that the figures, and especially the depicted proportions, are only schematic. The same reference numerals denote the same objects, so that explanations from other figures can be consulted as needed. The figures show: Fig. 1a: a sectional view of an adjusting device according to the invention in a first example in a new state with the device in the engaged position; Fig. 1b: a sectional view of the adjusting device according to the invention as shown in the first example in a new condition with the device in the disengaged position; Fig. 1c: a sectional view of the first example of the adjusting device in a worn state with the adjustment mechanism in the engaged position; Fig. 2a: a schematic representation of a second example of an adjusting device according to the invention in a new state with the device in the engaged position; Fig. 2b: a schematic representation of the second example of the adjusting device according to the invention in a new state with the disengaged position; Fig. 2c: a schematic representation of the non-adjusted adjusting device according to the second example with worn friction element in engaged position; Fig. 2d: a schematic representation of the downstream adjusting device according to the second example with worn friction element; Fig. 3: a schematic representation of the first example of the adjusting device; Fig. 4: a schematic representation of a third example of an adjusting device; Fig. 5a: a perspective view of a first ramp ring in an adjusting device; Fig. 5b: a perspective view of a second ramp ring in the first example of an adjusting device; Fig. 5c: a perspective view of a sleeve element of the first example of the adjusting device; Fig. 6: a perspective view of a coupling; Fig. 7: a schematic representation of the steps of a counter ramp; Fig. 8a a schematic representation of a fourth example of an adjusting device according to the invention in a new state with the device in the engaged position; and Fig. 8b: a schematic representation of the adjusted device according to the fourth example with worn friction element.

[0028] The Fig. Figures 1a to 1c each show a sectional view of a first example of an adjusting device 1, the representation being abstracted to the essential functional elements and those describing the invention. The adjusting device 1 has a first ramp ring 2 with a stepped 2.4 adjusting ramp 2.1 and a stepless drive ramp 2.2 in the form of a sensing ramp. The first ramp ring 2 is movably mounted on a guide element 3 in the form of a support disc in an actuation direction B and presses on the output side against a lever element 4, which here is designed as a release lever and is pivotably mounted on a housing (not shown). The support disc is also translationally and rotationally attached to the housing. In the actuation direction B, upstream of the first ramp ring 2, a second ramp ring 5 with a stepped 5.4 first counter ramp 5.1 is arranged.The second ramp ring 5 is movably mounted in the direction of actuation B on a sleeve element 7, which has a second counter ramp 7.1, wherein the second counter ramp 7.1 is designed without steps. The sleeve element 7 is fixed in the direction of actuation B and rotatably mounted about a longitudinal axis A on the support disc 3.

[0029] The steps 5.4 of the first counter ramp 5.1 are designed to be complementary to the steps 2.4 of the adjusting ramp 2.1. In the assembled state, the steps 5.4 of the first counter ramp 5.1 are at least partially in contact with the steps 2.4 of the adjusting ramp 2.1, forming an inclined plane consisting of several steps 2.4, 5.4. This plane is helically oriented, meaning that its slope a runs both in the direction of the longitudinal axis A and partially around the longitudinal axis A in a transverse direction. The second counter ramp 7.1 is in contact with the drive ramp 2.2 and also forms an inclined plane with it, which is likewise helically oriented, with its slope a also running both in the direction of the longitudinal axis A and partially around the longitudinal axis A in a transverse direction.

[0030] The Fig. Figures 1a to 1c illustrate, in particular, an adjusting device 1 according to a first embodiment, once in the engaged and once in the disengaged position in a new condition, and once in the engaged position in a worn condition of the clutch 15. Engaged means that no force is exerted by a release bearing 16 on the second ramp ring 5; thus, in the engaged position, the clutch 15 transmits force, for example, from a flywheel (not shown) of an internal combustion engine to a transmission (not shown). In the disengaged position, this power flow is interrupted.

[0031] The first ramp ring 2, the second ramp ring 5, and the sleeve element 7 are designed as circular disks and sleeves, respectively, arranged coaxially with respect to the longitudinal axis A, with a transverse direction Q corresponding to a circumferential direction around the common longitudinal axis A of the components. The ramps 5.1 and 7.1 extend along a trajectory that follows the circumferential direction with respect to the longitudinal axis A. The sleeve element 7 is fixed to the support disk 3 in the actuation direction B, which here is parallel to the longitudinal axis A, and is provided with a recess 7.2 into which at least one pin 5.3 of the second ramp ring 5 engages. The fit between pin 5.3 and recess 7.2 is a clearance fit, with the spring element 9 arranged on one side with one end on pin 5.3 and with the other end on the inside of the recess 7.2.

[0032] The first ramp ring 2, as in Fig. As shown in 2b, it is actuated by a lever element 4 of the clutch 15, which here is a release lever. As in Fig. As shown in Figure 2c, with progressive wear of the friction element of the clutch 15, the drive ramp 2.2 slides along the second counter ramp 7.1 of the sleeve element 7, thereby compressing the spring element 9, with readjustment occurring as previously described. The distance between the first ramp ring 2 and the second ramp ring 5 decreases, while the second ramp ring 5 remains in the same position in the direction of actuation B when the clutch 15 is closed, i.e., when the lever element 4 is not actuated. The sleeve element 7 and the second ramp ring 5 are clearly offset in the transverse direction Q, here the circumferential direction, compared to the direction shown in Figure 2c. Fig. The situation shown in 2a is deflected.

[0033] The following will be the Fig. 2a to 2d as well as the Fig. 3 and Fig. Section 4 describes the operation of stages 2.4 and 5.4 for the adjusting device 1. Although the figures partly depict different examples, their basic operation is identical. It should be noted that the figures mentioned are functional sketches, not derived from any engineering drawing, and serve only to illustrate the functional relationships of the various components of the adjusting device 1.

[0034] In Fig. Figure 2a shows a schematic representation of a second example of an adjusting device 1 in its new state with the engagement position. Since no wear has yet occurred on the friction elements of the clutch 15, the stepped 2.4 first counter ramp 5.1 of the second ramp ring 5 rests positively on the opposite stepped adjusting ramp 2.1 of the first ramp ring 2 on the highest step 2.4.

[0035] According to the Fig. In sections 2a to 2d, the second ramp ring 5 is not directly and rotationally fixed to the sleeve element 7 by means of the pins 5.3 in the recess 7.2 of the sleeve element 7. An intermediate element 8 is formed between the sleeve element 7 and the second ramp ring 5. This intermediate element 8 is rotationally fixed to the sleeve element 7 by means of a pin 8.1 in the recess 7.2 of the sleeve element 7 and is also supported against the second ramp ring 5 by means of a spring element 9. Furthermore, the drive ramp 2.2 of the first ramp ring 2, which is designed as a plane, rests against the second counter ramp 7.1 of the sleeve element 7.

[0036] If wear and thus abrasion of the friction element of the clutch 15 has occurred, the drive ramp 2.2 slides along the second counter ramp 7.1, compressing the spring element 9. According to Fig. 2d, the potential energy stored in the spring element 9 is released after reaching a certain degree of compression, causing the first ramp ring 2 to rotate about the longitudinal axis A relative to the second ramp ring 5 and the intermediate element 8, thus moving the stepped 5.4 first counter ramp 5.1 downwards along the steps 2.4 of the adjusting ramp 2.1 of the first ramp ring 2. After the movement in the transverse direction Q and when viewed horizontally, the Fig. 2 locks the stepped 5.4 first counter ramp 5.1 at a lower level again to the stepped 2.4 adjusting ramp 2.1 of the first ramp ring 2.

[0037] If the friction element of the clutch 15 is unworn, no compression of the spring element 9 has occurred between the pin 5.3 / 8.1 and the inside of the recess 7.2 of the sleeve element 7. Consequently, no displacement has occurred between the second counter ramp 7.1 and the drive ramp 2.2, so no lateral force acts on the second ramp ring 5 that would cause it to rotate. To prevent unintentional adjustment in the lateral direction Q, a detent device 10 is additionally provided, which applies the necessary counterforce against lateral forces to the second ramp ring 5. The detent device 10 is formed, firstly, by concave recesses 10.2 on the side of the second ramp ring 5 facing away from the first ramp ring 2. A second component of the detent device 10 engages in these recesses and is designed with a raised section 10.1. The raised section 10.1 for example, on a preload spring exerting the preload, which is not shown. The recesses 10.2 are spaced such that this corresponds to the length of a bearing surface 13 of a step 2.4.

[0038] In Fig. Figure 3 is the first example of the adjusting device 1, schematically depicted in functional terms. In this example, the second ramp ring 5 is directly, i.e., without an intermediate element 8, locked in the recess 7.2 by a pin 8.1. As already explained, and in contrast to the second example, the fit between the pin 5.3, which in this embodiment is a component of the second ramp ring 5, and the recess 7.2 is a clearance fit. On one side, the spring element 9 is arranged with one end on the pin 5.3 and with the other end on the inside of the recess 7.2. If, as the friction element of the clutch 15 wears, the drive ramp 2.2 slips along the second counter ramp 7.1 of the sleeve element 7, the spring element 9 is also compressed, thus performing an adjustment.

[0039] According to a third example of the adjusting device 1, shown in Fig. 4, a further spring element 11 is arranged with one end on the first counter ramp 5.1 of the second ramp ring 5 and with its other end on the support disc 3. By means of the further spring element 11, which is compressed with increasing wear of the friction element and thus exerts an increasing counterforce against the spring element 9, uncontrolled readjustment can be improved or avoided. Also according to Fig. 4. A modified locking device 10 is provided, wherein a plurality of convex protrusions 10.1 are formed on an additional component 10.3 between the second ramp ring 5 and a release bearing 16, which engage in corresponding concave recesses 10.2 on the second ramp ring 5. The friction device 12 is specifically designed to increase the contact pressure between the additional component 10.3 and the second ramp ring 5.

[0040] The third example is a variation of the first example. However, it is also possible to incorporate the additional features of the third example based on the second embodiment. Furthermore, it is also possible to combine only certain features of the examples.

[0041] The Fig. Figures 5a to 5c show the individual components of the adjusting device 1, wherein in Fig. 5a shows the first ramp ring 2 according to the first and second examples with the stepped 2.4 adjustment ramp 2.1 and the drive ramp 2.2. It can be seen that the ramps 2.1 and 2.2 are formed from several identical ramp elements 2.6 distributed around the circumference. In this example, the adjustment ramp 2.1 consists of six ramp elements 2.6 and the drive ramp 2.2 of three ramp elements 2.5. Other divisions of the adjustment ramp 2.1 and the drive ramp 2.2 are also possible.

[0042] The first ramp ring 2 also has recesses 2.3 in the circumferential direction, some of which are intended for the passage of components of a partial coupling that is designed together with a partial coupling of the adjusting device 1, and some of which are intended for the passage of lever elements 4 of the partial coupling itself.

[0043] Fig. Figure 5b shows the second ramp ring 5 according to the first embodiment with the first stepped counter ramp 5.1, which here is divided into six sections corresponding to the six ramp elements of the adjusting ramp 2.1. The second ramp ring 5 also has recesses 5.5 for the passage of components of a further partial coupling.

[0044] Fig. Figure 5c shows the sleeve element 7 according to the first embodiment with the second counter ramp 7.1, which is divided into three parts.

[0045] Fig. Figure 6 shows a clutch 15 with an adjusting device 1, wherein the clutch 15 has two sub-clutches 15.1 and 15.2. The adjusting device 1 is associated with the first sub-clutch 15.1, which has three lever elements 4 in the form of release levers that are actuated by the adjusting device 1 as described above. The second sub-clutch 15.2 also has three lever elements 4 in the form of release levers that can engage through the recesses 2.3, 5.5 upon actuation and can be actuated directly without a preceding adjusting device 1. The lever elements 4 of the first sub-clutch 15.1 also engage through recesses 2.3 on the first ramp ring 2.

[0046] Fig. Figure 7 shows a schematic representation of the complementary stages 2.4, 5.4 of the adjusting ramp 2.1 and the first counter-ramp 5.1 according to a first and second design possibility. According to the first design possibility, the contact surfaces 13 of each individual stage 2.4, 5.4 are orthogonal to the direction of actuation B. According to the second design possibility, the stages 2.4, 5.4 are designed such that the contact surfaces 13 for axial force transmission have an inclination angle b opposite to the inclination a of the ramps 2.1, 5.1. Thus, the function of a detent can be realized at this point. When the preload, the disengagement force, or, for example, a force due to vibration excitation acts, a force or a moment is generated that opposes the direction of the adjusting movement.This inclined ramp shape, in combination with the constant force exerted by the preload springs (not shown), thus achieves the desired detent effect without any additional components.

[0047] Fig. 8a and Fig. Figure 8b schematically shows a fourth example of an adjusting device 1. Here, the one in Fig. 8a situation shown in Fig. The situation shown in 2a and the one in Fig. The situation shown in 8b corresponds to the one in Fig. The situation shown in 2d. Refer to the description above. Fig. Reference is made to sections 2a to 2d to avoid repetition; in the following, only the differences between the fourth example and the second example will be discussed.

[0048] In contrast to the second example of an adjusting device 1, the fourth example omits the spring element 9. Instead, the intermediate element 8 is directly connected to the second ramp ring 5, so that a transverse force Q, acting on the intermediate element 8 through the drive ramp 2.2 and the second counter ramp 7.1, is transmitted directly to the second ramp ring 5 and thus, via the first counter ramp 5.1, to the adjusting ramp 2.1, causing movement of the adjusting ramp 2.1 – and thus of the lever element 4 – in the actuation direction B. Fig. Figure 8a shows position 17 of the second ramp ring 5 in the direction of actuation B. The second ramp ring 5 also reaches this position 17 after readjustment (see Figure 8a). Fig. 8b). However, a first position 18 of the lever element 4 differs in the direction of actuation B in the unworn state (cf. Fig. 8a) by means of an adjustment path 20 from a second position 19 of the lever element 4 in the adjusted worn state (cf. Fig. 8b). The adjustment travel 20 corresponds to the step height of steps 2.4 in the direction of actuation B or an integer multiple of this step height. Drive ramp 2.2 and second counter ramp 7.1 are not self-locking. Reference symbol list 1 Adjusting device 2 First ramp ring 2.1 Adjustment ramp 2.2 Drive ramp 2.3 Exclusion 2.4 Contour / Step Adjustment Ramp 2.5 Ramp element 2.6 Ramp element 3 Guide part / support disc 4 lever element 5 second ramp ring 5.1 First counter-ramp 5.3 Cones 5.4 Counter contour / step 5.5 Exclusion 7 Sleeve element 7.1 second counter ramp 7.2 Recess 7.4 Counter contour 8 Intermediate element 8.1 Cones 9 spring element 10 Resting device 10.1 Increase 10.2 Exclusion 10.3 additional component 11 additional spring element 12 Friction device 13 Contact surface 15 Clutch 15.1 first partial coupling 15.2 second partial coupling 16 Release bearings 17 Position of the second ramp ring 18 first position of the lever element 19 second position of the lever element 20 Adjustment path A Longitudinal axis B Direction of action Q transverse direction a slope ramp b Slope of contact surface

Claims

[1] Adjusting device (1) for a clutch (15) with an actuation direction (B), comprising - a first ramp ring (2) arranged coaxially about a longitudinal axis (A) for disengaging the clutch (15), wherein the first ramp ring (2) has an adjusting ramp (2.1) and a drive ramp (2.2) in a transverse direction (Q) to the actuation direction (B), - a second ramp ring (5) movable coaxially about the longitudinal axis (A) and in the actuation direction (B) for actuation by a release bearing (16), comprising a first counter ramp (5.1), wherein the first counter ramp (5.1) is formed with a counter contour (5.4) to a contour (2.4) of the adjusting ramp (2.1), wherein the first counter ramp (5.1) is supported with its counter contour (5.4) on the contour (2.4) of the adjusting ramp (2.1), - a sleeve element (7) movable coaxially about the longitudinal axis (A) and in the transverse direction (Q) with a second counter ramp (7.1), wherein the second counter ramp (7.1) can be applied to a contour (2.4) on the drive ramp (2.2) in the direction of actuation (B) with a counter contour (7.4), wherein the drive ramp (2.2) and the second counter ramp (7.1) are designed to slide past each other in the transverse direction (Q) when a contact force is applied in the direction of actuation (B), characterized by , that the second ramp ring (5) is movably mounted at least indirectly on the sleeve element (7) in the direction of actuation (B) and in the transverse direction (Q), that the sleeve element (7) and the second ramp ring (5) are operatively connected in the transverse direction (Q), and that the contour (2.4) of the first ramp ring (2) and the counter contour (5.4) of the second ramp ring (5) are formed in the form of complementary steps (2.4, 5.4). [2] Adjusting device (1) according to claim 1, characterized by, that the sleeve element (7) and the second ramp ring (5) are operatively connected in the transverse direction (Q) via a spring element (9). [3] Adjusting device (1) according to one of the preceding claims, wherein the adjusting ramp (2.1) and the drive ramp (2.2) have the same slope (a). [4] Adjusting device (1) according to any one of the preceding claims, characterized by , that the sleeve element (7) and the second ramp ring (5) are operatively connected to each other in the transverse direction (Q) by an intermediate element (8). [5] Adjusting device (1) according to claims 2 and 4, characterized by , that the intermediate element (8) is mounted with a pin (8.1) in a recess (7.2) of the sleeve element (7), wherein the spring element (9) is supported at one end on the intermediate element (8) and at another end on the second ramp ring (5). [6] Adjusting device (1) according to one of claims 2 or 3, characterized by, that the sleeve element (7) and the second ramp ring (5) are operatively connected in the transverse direction (Q) by a pin (5.3) of the second ramp ring (5) which is mounted in a recess (7.2) of the sleeve element (7), wherein in the transverse direction (Q) the spring element (9) is arranged within the recess (7.2) between the pin (5.3) and the sleeve element (7). [7] Adjusting device (1) according to any one of claims 2 to 6, characterized by a further spring element (11) which is arranged between the second ramp ring (5) and a guide part (3) and counteracts the first spring element (9). [8] Adjusting device (1) according to any one of the preceding claims, characterized by , that the steps (2.4, 5.4) each have a horizontal support surface (13) or each have a support surface (13) with an opposite slope (b) to the slope (a) of the ramps (2.1, 5.1) in the transverse direction (Q). [9] Adjusting device (1) according to any one of the preceding claims, characterized by at least one locking device (10) and / or one friction device (12) which exerts a counterforce against a readjusting movement of the second ramp ring (5) in the transverse direction (Q). [10] Coupling (15) for selectively connecting or disconnecting an input shaft and at least one output shaft with an adjusting device (1) according to one of the preceding claims.

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