Clutch actuating device

Abstract

The present invention relates to a clutch actuating device, which comprises an axially displaceable first piston (1), a transmission member in transmission connection with the clutch, and a wear compensation mechanism that is at least partially located kinematically between the first piston and the transmission member. The wear compensation mechanism includes a first member coupled to the first piston in axial movement and a second member coupled to the transmission member (2) in axial movement. The wear compensation mechanism is configured to be convertible between a locked state and an unlocked state. In the locked state, the first member is radially pressed against the second member so that the first member and the second member are frictionally locked axially relative to each other, thereby enabling the transmission of axial movement between the first piston and the transmission member. In the unlocked state, the second member can move axially relative to the first member to adjust the axial position of the transmission member relative to the first piston in the clutch engaged state according to the wear degree of the clutch.

Description

Technical Field

[0001] The present invention relates to a clutch actuating device. Background Art

[0002] Clutch actuating devices are applied to vehicles for operating a clutch. Generally, the clutch is biased to a fully engaged state, that is, once the external operating force is released, the clutch always returns to its fully engaged state. In practice, wear always inevitably occurs during the use of the clutch, which makes it desirable for the clutch actuating device to compensate for the wear of the clutch according to the degree of wear. Otherwise, the clutch actuating device may cause the clutch to get stuck during engagement and unable to reach the fully engaged state.

[0003] Therefore, it is desirable to provide a compact and easily manufacturable clutch actuating device that can self-adjust to compensate for clutch wear. Summary of the Invention

[0004] The object of the present invention is achieved by providing a clutch actuating device, which includes a housing, a first piston axially displaceable within the housing, a transmission member in transmission connection with the clutch, and a wear compensation mechanism at least partially kinematically located between the first piston and the transmission member. The wear compensation mechanism includes at least one first member coupled to the first piston in axial movement and a second member coupled to the transmission member in axial movement. The wear compensation mechanism is configured to be convertible between a locked state and an unlocked state. In the locked state, the first member is radially pressed against the second member so that the first member and the second member are frictionally locked axially relative to each other to transmit axial movement between the first piston and the transmission member; in the unlocked state, the second member can axially move relative to the first member to adjust the axial position of the transmission member relative to the first piston in the clutch engaged state according to the degree of wear of the clutch.

[0005] According to an optional embodiment, the wear compensation mechanism is converted to the locked state by applying a fluid pressure to the first member, and is converted to the unlocked state by unloading the fluid pressure from the first member.

[0006] According to an optional embodiment, the wear compensation mechanism includes at least one cylinder-piston assembly, the cylinder-piston assembly includes a cylinder body and a second piston sliding at least partially guided within the cylinder body. The first member is configured as the second piston, and the second member is configured as an axially extending sleeve. The cylinder-piston assembly is positioned and oriented such that the second piston slides radially towards or away from the sleeve.

[0007] According to an optional embodiment, the first piston slides within the housing to define a chamber for receiving pressurized fluid, the chamber being located on the side of the first piston opposite the cylinder-piston assembly and being in fluid communication with the cylinder block, in particular by means of a fluid passage through the first piston and in fluid communication with the cylinder block.

[0008] According to an optional embodiment, the cylinder-piston assembly further includes a fluid opening formed in the cylinder block, a sealing head for opening or closing the fluid opening, and a valve core for carrying the sealing head, the valve core being driven to move by the pressurized fluid when pressurized fluid is introduced into the cylinder block so as to open the fluid opening by the sealing head, and returning to the position where the sealing head closes the fluid opening under the biasing force of a biasing member when the pressurized fluid in the cylinder block is drained away.

[0009] According to an optional embodiment, the wear compensation mechanism includes at least two cylinder-piston assemblies which are distributed around the bushing.

[0010] According to an optional embodiment, the valve core and the second piston are arranged in alignment with each other along the cylinder block within the cylinder block, wherein the valve core is at least partially received within the second piston to move guidingly within the second piston, wherein the biasing member is configured as a compression spring, one end of the compression spring acting on the valve core or the cylinder block and the other end acting on the second piston.

[0011] According to an optional embodiment, the second piston includes a piston body and a pressing plate attached to the radially inner end of the piston body, wherein when loaded by fluid pressure, the piston body transfers the fluid load to the pressing plate so that the pressing plate is frictionally locked axially with the bushing.

[0012] According to an optional embodiment, the bushing and the pressing plate are engaged with each other by a tooth-groove structure, the teeth and grooves in the tooth-groove structure extending axially along the corresponding one of the bushing and the pressing plate respectively.

[0013] According to an optional embodiment, the first piston has an abutting portion axially abutting against the pressing plate to directly transfer the axial load between the first piston and the pressing plate.

[0014] According to an optional embodiment, the housing includes an inner ring sleeve axially extending from its end wall towards the interior of the housing, and the first piston and the second component are slidably mounted on the inner ring sleeve; or the housing includes an inner ring sleeve and an outer ring sleeve axially extending from its end wall towards the interior of the housing, the outer ring sleeve being located radially outside the inner ring sleeve, the first piston being slidably mounted on the outer ring sleeve, and the second component being slidably mounted on the inner ring sleeve.

[0015] Other advantages and advantageous embodiments of the subject matter of the present invention are apparent from the description, the drawings and the claims. Description of the Drawings

[0016] The further features and advantages of the present invention can be further elaborated by the following detailed description of specific embodiments with reference to the accompanying drawings. The accompanying drawings are as follows:

[0017] Figure 1 A longitudinal sectional view showing a clutch actuating device according to a first embodiment of the present invention;

[0018] Figure 2 A partial transverse sectional view showing a clutch actuating device according to a first embodiment of the present invention;

[0019] Figure 3 A partial longitudinal perspective sectional view showing a clutch actuating device according to a second embodiment of the present invention;

[0020] Figure 4 A longitudinal sectional view showing a clutch actuating device according to a third embodiment of the present invention;

[0021] Figure 5 A partial transverse sectional view showing a clutch actuating device according to a third embodiment of the present invention; and

[0022] Figure 6 A schematic structural view showing a clutch actuating device according to a fourth embodiment of the present invention. Detailed Description of the Specific Embodiment

[0023] In order to make the technical problems, technical solutions and beneficial technical effects to be solved by the present invention more clear and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and multiple exemplary embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention, rather than to limit the protection scope of the present invention. In the accompanying drawings, the same or similar reference numerals refer to the same or equivalent components.

[0024] Figure 1 A longitudinal sectional view showing a clutch actuating device according to a first embodiment of the present invention, Figure 2 A partial transverse sectional view showing a clutch actuating device according to a first embodiment of the present invention. As Figure 1-2 shown, the clutch actuating device 100 includes a housing 4, a first piston 1 axially slidable within the housing 4, a transmission member 2 drivingly connected to a clutch (not shown in the figure), and a wear compensation mechanism 3 at least partially located between the first piston 1 and the transmission member 2 in terms of kinematics.

[0025] The housing 4 is configured as a cylinder with one end open, particularly a cylindrical cylinder, and thus includes a circumferential side wall 41 and an end wall 42 connected to the circumferential side wall 41. The circumferential side wall 41 and the end wall 42 can be integrally formed, for example. A housing aperture 47 for fluid inlet and outlet is provided on the end wall 42. At the position of the housing aperture 47, particularly axially extending from the aperture edge of the housing aperture 47, a bridge pipe 45 is provided on the end wall 42. In particular, the bridge pipe 45 is integrally formed with the housing 4. In addition, an end cap 5 and a dust cover 6 are installed at the open end of the housing 4 opposite to the end wall 42.

[0026] The housing 4 further has an inner ring sleeve 43 axially extending from the center of the end wall 42 towards the interior of the housing. A bush 32, which will be explained in detail below, is slidably installed on the inner ring sleeve 43. In addition, the housing 4 also has an annular outer ring sleeve 44 axially extending from the end wall 42 on the radially outer side of the inner ring sleeve 43. The inner circumferential side of the first piston 1 is slidably supported on the outer ring sleeve 44.

[0027] The first piston 1 includes a piston disc 13 and a flange portion 14 axially extending from the circumferential edge of the piston disc 13. A chamber 7 is defined between the first piston 1 and the housing 4. When the chamber 7 is filled with pressurized fluid, the first piston 1 can be pushed by the pressurized fluid to perform an axial displacement along the inner wall of the housing 4.

[0028] To ensure the fluid tightness of the chamber 7, a first sealing structure 11 is provided between the first piston 1 and the circumferential side wall 41, and a second sealing structure 12 is provided between the first piston 1 and the outer ring sleeve 44. According to one example, the first and / or second sealing structures 11, 12 are configured as sealing rings.

[0029] The wear compensation mechanism 3 includes at least one first component 31 coupled to the first piston 1 in axial movement and a second component 32 coupled to the transmission component 2 in axial movement. The wear compensation mechanism 3 is configured to be convertible between a locked state and an unlocked state. In the locked state, the first component 31 is radially pressed against the second component 32 so that the first component 31 and the second component 32 are frictionally engaged with each other to transmit axial movement between the first piston 1 and the transmission component 2; in the unlocked state, the second component 32 is axially movable relative to the first component 31 to be able to adjust the axial position of the transmission component 2 relative to the first piston 1 in the clutch engaged state according to the wear degree of the clutch.

[0030] Furthermore, the wear compensation mechanism 3 is converted to the locked state by applying fluid pressure to the first component 31, and the wear compensation mechanism 3 is converted to the unlocked state by unloading the fluid pressure on the first component 31.

[0031] Specifically, the second component 32 is configured as a bushing 32 having a substantially cylindrical shape, particularly a cylindrical shape. The bushing 32 is slidably sleeved on the inner ring sleeve 43 so as to be able to slide along the inner ring sleeve 43 during the operation of the device 100. An annular empty groove 8 is defined between the outer ring sleeve 44 and the inner ring sleeve 43, and the bushing 32 can enter and exit through this empty groove 8. In this way, the bushing 32 has a relatively large axial stroke, so that the wear of the clutch can be compensated within a relatively large range.

[0032] The wear compensation mechanism 3 includes at least one, particularly at least two, for example three cylinder-piston assemblies 30 circumferentially distributed around the bushing 32, as best shown by Figure 5 . These cylinder-piston assemblies 30 can be distributed at equal angular intervals, for example. The cylinder-piston assembly 30 includes a cylinder block 33 and a second piston that slides within the cylinder block 33 and serves as the first component 31 described above. Each cylinder-piston assembly 30 is oriented such that the reciprocating motion of its second piston 31 is performed along the radial direction of the device 100. When pressurized fluid is introduced into the cylinder block 33, the pressurized fluid will exert a force on the second piston 31, so that the second piston 31 is radially and tightly pressed against the outer peripheral surface of the bushing 32, thereby frictionally locking with the bushing 32.

[0033] Exemplarily, after being pre-assembled, the cylinder-piston assembly 30 is fixed to the first piston 1 by bolts 55 (see Figure 2 ).

[0034] In this exemplary embodiment, the second piston 31 includes a piston sleeve 311 that slides while being guided on the inner side wall of the cylinder block 33 and a piston rod 312 that is at least partially located within the piston sleeve 311 and is rigidly connected to the piston sleeve 311 (see Figure 4 ). The fluid (if any) within the cylinder block 33 will radially push the piston sleeve 311 inward and then push the piston rod 312, so that the inner end face 3121 of the piston rod 312 abuts against the bushing 32.

[0035] Exemplarily, in the state where no fluid is loaded, the piston rod 312 at least partially extends out of the cylinder block 33.

[0036] Exemplarily, the piston sleeve 311 is provided with an outer flange 3111 at its radially outer end (see Figure 4 ). This outer flange 3111 is used to bear the second spring 36 on the one hand and serves as the force input surface for the pressurized fluid on the other hand. A working chamber 34 for receiving the pressurized fluid is defined between the cylinder block 33 and the piston sleeve 311 above the outer flange 3111.

[0037] Exemplarily, the inner end face 3121 can be designed to have a shape that mates with the outer peripheral surface of the bush 32. When the bush 32 is cylindrical, the shape of the inner end face 3121 can be an arc surface, and the radius of curvature of this arc surface substantially corresponds to the radius of curvature of the cylinder of the bush 32.

[0038] The cylinder block 33 is in fluid communication with the chamber 7. For this purpose, the cylinder block 33 is provided with a first fluid opening 331, and the first piston 1 is provided with a first fluid passage 15 that penetrates the first piston 1 and leads to the chamber 7. Among them, the first fluid opening 331 and the first fluid passage 15 are in fluid communication with each other in an aligned manner. More particularly, the cylinder block 33 defines a fluid passage 334 that extends axially in the direction of the first piston 1 especially at its radially outer end. The fluid passage 334 forms the first fluid opening 331 at its free end, and forms a third fluid opening 333 leading to the working chamber 34 at the other end opposite to the free end. The first fluid passage 15 is formed by a short tube 16 that axially protrudes from the piston disk 13 of the first piston 1. In the assembled state, the fluid passage 334 and the first fluid passage 15 form a straight and continuous passage. Thus, the fluid entering the cylinder block 33 can enter the chamber 7 via this passage.

[0039] In addition, the cylinder block 33 is further provided with a second fluid opening 332. Correspondingly, the first piston 1 is provided with a second fluid passage 17. In the assembled state, the second fluid opening 332 and the second fluid passage 17 are in fluid communication with each other in an aligned manner. Furthermore, the second fluid passage 17 is in fluid communication with the housing port 47 by being inserted by a bridge tube 45 protruding from the housing 4. In this way, the pressurized fluid from an external fluid source (not shown) can enter the cylinder block 33 via the housing port 47, the bridge tube 45, the second fluid passage 17, and the second fluid opening 332.

[0040] Exemplarily, a third sealing structure 48 is provided between the bridge tube 45 and the second fluid passage 17 (see Figure 4 ).

[0041] Furthermore, the cylinder-piston assembly 30 further includes a valve assembly for connecting or disconnecting the fluid communication between the first fluid opening 331 and the second fluid opening 332. The valve assembly is received within the cylinder block 33 and includes a sealing head 351 for opening or closing the third fluid opening 333, a valve core 352 for carrying the sealing head 351, and a second spring 36 for biasing the valve core 352 towards the third fluid opening 333. The radially outer end of the second spring 36 abuts, especially is fixed, on the valve core 352, and the radially inner end abuts, especially is fixed, on the outer flange 3111 of the piston sleeve 311.

[0042] In the assembled and fluid-unloaded state, on the one hand, the second spring 36, which is a compression spring, biases the valve core 352 radially outward so that the sealing head 351 mounted on the valve core 352 seals the third fluid opening 333. On the other hand, it biases the second piston 31 toward the bushing 32 so that the second piston 31 is pressed against the bushing 32 loosely, that is, with a relatively small pushing force. At the same time, an opening gap 39 is left between the radially inner end face of the valve core 352 and the radially outer end face of the piston rod 312 (see Figure 4 ), and a safety gap 38 is left between the outer flange 3111 and the inner end disk 3521 of the valve core 352 (see Figure 4 ). The opening gap 39 ensures that the valve core 352 can perform a radially inward displacement to open the third fluid opening 333, and the safety gap 38 ensures that the second spring 36 is not self-locked between the inner end disk 3521 and the outer end disk 3522 of the valve core 352.

[0043] The distance between the radially outer end face of the piston rod 312 and the radially inner side face of the outer flange 3111 of the piston sleeve 311 is greater than the radial dimension of the inner end disk 3521 of the valve core 352, and the difference between the two is approximately equal to the sum of the opening gap 39 and the safety gap 38.

[0044] Exemplarily, a fourth sealing structure is provided between the inner end disk 3521 of the valve core 352 and the piston sleeve 311 and / or a fifth sealing structure is provided between the piston sleeve 311 and the cylinder block 33 (see Figure 4 ).

[0045] The clutch actuating device 100 further includes a first spring 9 that biases the first piston 1 toward the end wall 42. Specifically, as a pre-compressed spring, one end of the first spring 9 abuts, especially is fixed, on the first piston 1, and the other end abuts, especially is fixed, on the end cover 5. Through the biasing action of the first spring 9, it is ensured that the first piston 1 is always in the initial position abutting against the end wall 42 in the clutch engaged state.

[0046] The end cover 5 is assembled on the bushing 32 in a manner that is axially coupled with the bushing 32. For this purpose, for example, a clamp (not shown in the figure) is used to lock the end cover 5 on the bushing 32. Additionally or alternatively, a first limiting component 10 (such as a limiting ring) can be provided between the radially inner flange 51 of the bushing 32 and the end cover 5 to limit the axial displacement between the bushing 32 and the end cover 5. For this purpose, the bushing 32 and / or the end cover 5 are provided with grooves for receiving the first limiting component 10. Additionally or alternatively, a boss 321 is formed on the bushing 32, and in the assembled state, the radially inner flange 51 of the end cover 5 abuts against the boss 321.

[0047] The flange portion 14 of the first piston 1 is formed with a plurality of finger portions 141, which are circumferentially spaced apart on the flange portion 14. Correspondingly, the radially outward flange 52 of the end cap 5 is provided with a plurality of corresponding recesses 521 for receiving the finger portions 141. That is to say, the first piston 1 and the end cap 5 form an interdigitated fit.

[0048] According to one example, the transmission component 2 mentioned above is configured as a release bearing. The release bearing 2 is drivingly connected to the sleeve 32 by means of the end cap 5, so that the release bearing 2, the end cap 5 and the sleeve 32 are coupled in axial movement. Exemplarily, the release bearing 2 abuts against the end cap 5 with its axial end, and defines a slot 21 for receiving the dust cover 6 with the end cap 5. In addition, exemplarily, a second limiting component 23 (such as a limiting ring) can be provided between the release bearing 2 and the end cap 5 to limit the relative axial displacement between the release bearing 2 and the end cap 5. For this purpose, additional grooves 24, 54 for receiving the second limiting component 23 are formed on the release bearing 2 and / or the end cap 5.

[0049] In one example, the radially outer end of the dust cover 6 is fixed to the housing 4 by means of bolts 61, for example.

[0050] Working Process of Clutch Actuating Device

[0051] 1. Initial State

[0052] In the initial state, the first piston 1 abuts against the end wall 42 of the housing 4 under the action of the first spring 9, while the second piston 31 of the cylinder-piston assembly 30 is pressed against the sleeve 32 with a small pressure under the action of the second spring 36. At the same time, the sleeve 32 is in a static state of force balance. Among them, the sleeve 32 is subject to an axial force to the left input via the release bearing 2 from the clutch side on the one hand, and an axial force to the right input via the end cap 5 from the first spring 9 on the other hand. And there will also be a static friction force between the sleeve 32 and the second piston 31 due to the pressing of the second piston 31 against the sleeve 32. The sleeve 32 is in a state of force balance axially under the action of these three forces.

[0053] 2. Clutch Disengagement Process

[0054] The pressurized fluid enters the working chamber 34 in the cylinder block 33 from the housing port 47 via the bridge pipe 45, the second fluid passage 17, and the second fluid opening 332. Then, the pressurized fluid in the working chamber 34 applies a radially inward thrust to the piston sleeve 311 of the second piston 31 to force the piston rod 312 to tightly press against the outer peripheral surface of the sleeve 32, so that the maximum static friction force between the second piston 31 and the sleeve 32 is large enough.

[0055] The pressurized fluid applies a radially inward thrust to the second piston 2 and also applies a radially inward thrust to the valve element 352, causing the valve element 352 to also shift radially inward until the opening gap 39 is eliminated and the sealing head 351 opens the third fluid opening 333, so that the pressurized fluid in the working chamber 34 can enter the chamber 7 via the third fluid opening 333, the fluid passage 334, the first fluid opening 331, and the first fluid through-hole 15. The working fluid in the chamber 7 can exert an axially rightward thrust on the first piston 2 for separating the clutch.

[0056] Since the second piston 31 and the bushing 32 have been frictionally locked stably enough by the fluid pressure, the first piston 2 can carry the cylinder-piston assembly 30 and further push the bushing 32 to move rightward, thereby further driving the release bearing 2 to extend out to achieve or assist in the separation of the clutch.

[0057] 3. Clutch Engagement Process

[0058] Fluid is discharged or depressurized from the housing port 47. At this time, the pressurized fluid in the chamber 7 will pass through the first fluid through-hole 15, the first fluid opening 331, and the third fluid opening 333, and pass through the unsealed sealing head 351 and then be discharged from the housing port 47 via the second fluid opening 332, the second fluid passage 17, and the bridge pipe 45. When the pressures in the chamber 7 and the working chamber 34 are unloaded, the first piston 1 will retreat to the initial position under the action of the first spring 9 and the clutch reaction thrust, and the sealing head 351 will re-close the third fluid opening 333 under the action of the second spring 36.

[0059] 4. Wear Self-Adjustment Process

[0060] In the case of clutch wear, when the first piston 1 has moved to abut against the end wall 42, the release bearing 2 still needs to move further leftward following the clutch. At this time, the fluid pressures in the chamber 7 and the working chamber 34 have been unloaded, so the second piston 31 only forms a very small pressure on the bushing 32 and thus the maximum static friction force between the second piston 31 and the bushing 32 is small enough that the reaction thrust from the clutch side input by the release bearing 2 can overcome this friction force and push the bushing 32 to continue moving leftward relative to the stationary first and second pistons 1, 31 for a certain distance until a new force balance position is reached.

[0061] Therefore, the clutch actuating device according to the present invention can perform self-adjustment following the wear degree of the clutch each time the clutch is closed.

[0062] Figure 3 A partial longitudinal perspective sectional view showing the clutch actuating device 100' according to the second embodiment of the present invention. In this embodiment, most of the features and details of the clutch actuating device 100' are the same asFigure 1-2 is the same as the clutch actuating device 100 shown, and will not be described herein again. Only the differences of the clutch actuating device 100' from the clutch actuating device 100 will be explained below.

[0063] In this embodiment, the outer ring sleeve 44 is omitted and thus the empty groove 8 is cancelled. The first piston 1 is not assembled on the outer ring sleeve 44 as in the first embodiment, but is assembled on the inner ring sleeve 43. In this way, although the wear-adjustable stroke for the bush 32 is shortened, the effective acting area of the first piston 2 is increased.

[0064] Figure 4 A longitudinal sectional view showing a clutch actuating device 100'' according to a third embodiment of the present invention Figure 5 shows a partial transverse sectional view of a clutch actuating device 100'' according to a third embodiment of the present invention. In this embodiment, most of the features and details of the clutch actuating device 100'' are the same as those of Figure 1-2 the clutch actuating device 100 shown, and will not be described herein again. Only the differences of the clutch actuating device 100'' from the clutch actuating device 100 will be explained below.

[0065] First, like the second embodiment, the outer ring sleeve 44 and the empty groove 8 of the clutch actuating device 100'' are cancelled.

[0066] Additionally, the second piston 31 is provided with a pressure plate 37 at the radially inner end facing the bush 32. The pressure plate 37 can be arranged outside the cylinder block 33 on the radially inner side of the cylinder block 33. When the second piston 31 is loaded with fluid pressure, the second piston 31 presses against the outer peripheral surface of the bush 32 with its pressure plate 37 and thus frictionally locks with the bush 32. Accordingly, the piston rod 312 of the second piston 31 no longer directly contacts the bush 32 as in the first and second embodiments. When the second piston 31 is not loaded with fluid pressure, relative axial displacement can be performed between the pressure plate 37 and the bush 32.

[0067] Furthermore, referring to Figure 5 , the pressure plates 37 assigned to each cylinder-piston assembly 30 extend sectionally in the circumferential direction, and there can be an especially substantially constant angular gap between adjacent pressure plates 37. And, at least one protrusion 371 is integrally formed, for example, on the inner circumferential side of the pressure plate 37 facing the bush 32, and at least one groove 323 for receiving the protrusion 371 is correspondingly formed on the outer circumferential side of the bush 32 facing the pressure plate 37, wherein the protrusion 371 and the groove 323 can form a form-fit. Exemplarily, when observed axially, the protrusion 371 and the groove 323 can be in the form of a V shape or an inverted V shape.

[0068] Additionally or alternatively, a receiving portion 372 is formed on the outer circumferential side of the pressing plate 37 facing the second piston 31, and at least a part of the second piston 31, in particular at least a part of the section of the piston rod 312 extending out of the cylinder block 33, is received in the receiving portion 372.

[0069] Furthermore, the first piston 1 is configured to axially abut against the pressing plate 37, so that the axial load exerted on the first piston 1 by the pressurized fluid is directly transmitted to the pressing plate 37 and then transmitted to the bushing 32 that is frictionally engaged with the pressing plate 37. In one example, the first piston 1 is formed with a protrusion 18 extending from the piston disk 13, and the protrusion 18 axially extends until it abuts against the pressing plate 37. In this way, the load transmission path is changed, so that the output force of the first piston 1 is mainly transmitted through the protrusion 18, thereby preventing the cylinder-piston assembly 30 from bearing heavy loads, and thus improving the transmission and stability of the output force.

[0070] In addition, the cylinder block 33 is integrated with the first piston 1, especially integrally formed with the first piston 1. In this case, the first fluid passage 19 for connecting the working chamber 34 of the cylinder block 33 and the chamber 7 is integrally formed with the cylinder block 33 and the first piston 1, rather than being formed by docking the short tube 16 of the first piston 1 and the fluid passage 334 of the cylinder block 33 as in the first and second embodiments. Similarly, the second fluid passage 29 for connecting the working chamber 34 and the bridge pipe 45 is also integrally formed with the cylinder block 33 and the first piston 1, rather than being formed by docking the second fluid passage 17 of the first piston 1 and the second fluid opening 332 of the cylinder block 33 as in the first and second embodiments. In this way, the connecting bolt 55 between the cylinder-piston assembly 30 and the first piston 1 is cancelled, increasing the structural stability.

[0071] Figure 6 The schematic structural diagram of the clutch actuating device 100”’ according to the fourth embodiment of the present invention is shown. The outer border in this figure does not belong to the components of the device 100”’. In this embodiment, most of the features and details of the clutch actuating device 100” are the same as Figure 1-2 the clutch actuating device 100 shown, and will not be elaborated here. Only the differences between the clutch actuating device 100”’ and the clutch actuating device 100 will be explained below.

[0072] In the initial state, the second piston 31 is pressed against the bushing 32 under the pre-pressure of the second spring 36 to at least to some extent limit the radial movement freedom of the second piston 31. And, the radially extending structure of the cylinder block 33, such as the cylinder wall for delimiting the working chamber 34, limits the axial movement freedom of the second piston 31.

[0073] Furthermore, the bridge pipe 45 and the second fluid passage 29 for connecting the bridge pipe 45 to the working chamber 34 (specifically, the second fluid opening 332 of the cylinder block 33 and the second fluid passage 17 of the first piston 1, see Figure 1 and Figure 4 ) are cancelled. Instead, the working chamber 34 inputs or discharges pressurized fluid from the chamber 7 through the first fluid passage 19. Specifically, when it is necessary to disengage the clutch, the pressurized fluid is first introduced into the chamber 7, and then enters the working chamber 34 from the chamber 7 through the first fluid passage 19. Thus, while the first piston 1 is pushed to the right by the pressurized fluid, the second piston 31 is frictionally locked with the bushing 32, so that the axial output force of the chamber 7 is transmitted to the clutch end through the bushing 32. When the clutch is engaged, the fluid in the chamber 7 is discharged outward, and at the same time the fluid in the working chamber 34 is also discharged outward through the chamber 7, so that the first piston 1 and the bushing 32 return to their initial positions under the action of the first spring and the clutch reaction force. At the same time, the fluid pressure in the working chamber 34 is unloaded, so that the maximum static friction force between the second piston 31 and the bushing 32 is very small, so that the bushing 32 can freely continue to retract under the action of the clutch reaction force to compensate for the wear of the clutch.

[0074] Here, it should be noted that the geometric form of the second piston 31 is not limited to Figure 6 the cylindrical block form shown in, but other suitable shapes conceivable by those skilled in the art, such as hollow cylinders, T-shaped cross-sections, and I-shaped cross-sections, are also possible.

[0075] According to an exemplary embodiment of the present invention, the pressurized fluid can be pressurized gas or pressurized liquid.

[0076] The clutch actuating device according to the present invention is applicable to a clutch biased to the fully engaged state, in which clutch, once the external operating force is released, the clutch always returns to its fully engaged state.

[0077] Although some embodiments have been described, these embodiments are merely presented by way of example and are not intended to limit the scope of the present invention. The appended claims and their equivalent forms are intended to cover all modifications, alternatives, and changes falling within the scope and spirit of the present invention.

Claims

1. A clutch actuating device (100, 100', 100", 100'"), comprising a housing (4), a first piston (1) axially displaceable in the housing (4), a transmission component (2) transmission-connected to the clutch, and a wear compensation mechanism (3) transmission-at least partially located between the first piston (1) and the transmission component (2), the wear compensation mechanism comprising at least one first component coupled to the first piston (1) in axial movement and a second component coupled to the transmission component (2) in axial movement, the wear compensation mechanism being configured to be switchable between a locked state and an unlocked state, in which, in the locked state, the first component is radially pressed against the second component so that the first component and the second component are frictionally locked relative to each other in the axial direction, thereby transmitting axial movement between the first piston (1) and the transmission component (2); in the unlocked state, the second component is axially movable relative to the first component so as to adjust the axial position of the transmission component (2) relative to the first piston (1) in the clutch engaged state according to the degree of wear of the clutch, in, The wear compensation mechanism (3) is switched to a locked state by applying fluid pressure to the first component, and is switched to an unlocked state by unloading the fluid pressure on the first component; and The wear compensation mechanism (3) includes at least one cylinder-piston assembly (30), the cylinder-piston assembly including a cylinder body (33) and a second piston (31) that can slide in a guided manner in the cylinder body (33), the first component is configured as the second piston (31), the second component is configured as an axially extending sleeve (32), and the cylinder-piston assembly (30) is positioned and oriented so that the second piston (31) slides radially toward or away from the sleeve (32).

2. The clutch actuating device (100, 100', 100", 100'") according to claim 1, characterized in that The first piston (1) slides in the housing (4) to define a chamber (7) for receiving pressurized fluid, the chamber (7) being located on the side of the first piston (1) opposite to the cylinder-piston assembly (30) and being in fluid communication with the cylinder body (33).

3. The clutch actuating device (100, 100', 100", 100'") according to claim 1 or 2, characterized in that The cylinder-piston assembly (30) further comprises a fluid opening (331, 333) provided on the cylinder body (33), a sealing head (351) for opening or closing the fluid opening, and a valve core (352) for carrying the sealing head (351), wherein the valve core can be driven to move by the pressurized fluid when the pressurized fluid is introduced into the cylinder body (33), so that the sealing head (351) opens the fluid opening, and returns to the following position under the biasing force of the biasing member (36) when the pressurized fluid in the cylinder body is exhausted: at this position, the sealing head (351) closes the fluid opening; and / or The wear compensation mechanism (3) comprises at least two cylinder-piston assemblies (30), which are distributed around the shaft sleeve (32).

4. The clutch actuating device (100, 100', 100", 100'") according to claim 3, characterized in that The valve core (352) and the second piston (31) are arranged in alignment with each other along the cylinder body (33), wherein the valve core (352) is at least partially received in the second piston (31) to move guided in the second piston (31), wherein the biasing member is configured as a compression spring, one end of the compression spring acts on the valve core (352) and the other end acts on the second piston (31).

5. The clutch actuating device (100, 100', 100", 100'") according to any one of claims 1 to 2 and 4, characterized in that: The second piston (31) includes a piston body (311, 312) and a pressure plate (37) attached to the radial inner end of the piston body, wherein when loaded by fluid pressure, the piston body transmits the fluid pressure load to the pressure plate (37) so that the pressure plate (37) and the sleeve (32) are frictionally locked in the axial direction.

6. The clutch actuating device (100, 100', 100", 100'") according to claim 5, characterized in that The shaft sleeve (32) and the pressure plate (37) are engaged with each other through a tooth-groove structure, wherein the tooth portion (371) and the groove portion (323) of the tooth-groove structure extend axially on a corresponding one of the shaft sleeve (32) and the pressure plate (37).

7. The clutch actuating device (100, 100', 100", 100'") according to claim 5, characterized in that The first piston (1) has an abutment portion (18) axially abutting against the pressure plate (37) for directly transmitting an axial load between the first piston (1) and the pressure plate (37).

8. The clutch actuating device (100, 100', 100", 100'") according to any one of claims 1 to 2, 4, 6 to 7, characterized in that The housing (4) comprises an inner ring sleeve (43) extending axially from its end wall (42) toward the interior of the housing, and the first piston (1) and the second component are slidably mounted on the inner ring sleeve (43); or The housing (4) includes an inner ring sleeve (43) and an outer ring sleeve (44) extending axially from its end wall (42) toward the interior of the housing, wherein the outer ring sleeve is located radially outside the inner ring sleeve, the first piston (1) is slidably mounted on the outer ring sleeve (44), and the second component is slidably mounted on the inner ring sleeve (43).

9. The clutch actuating device (100, 100', 100", 100'") according to claim 2, characterized in that The chamber (7) is located on the opposite side of the first piston (1) from the cylinder-piston assembly (30) and is in fluid communication with the cylinder (33) via fluid passages (15, 19) passing through the first piston (1).

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