Hydraulic clutch
By introducing a control valve and limiting groove structure into the hydraulic clutch, combined with the restoring force of the elastic member, the efficient and stable disconnection power transmission of the hydraulic clutch at high speed is achieved, and the problem of insufficient elastic restoring force in the prior art is solved.
Patent Information
- Application Number
- CN202422898044.2
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-11-27
- Publication Date
- 2025-08-22
- Estimated Expiration
- 2034-11-27
AI Technical Summary
Existing hydraulic clutches are difficult to quickly and efficiently disconnect power transmission under high power density and high speed, mainly because the elastic recovery force is insufficient to overcome the ineffective discharge of pressure oil caused by centrifugal force.
A hydraulic clutch is designed, including a regulating valve and a limiting groove structure, where the valve ball moves in the limiting groove to control the on and off of the oil passage, and combined with the restorative force of the elastic member to achieve power transmission and disconnection.
The power transmission can be efficiently and stably disconnected in both stationary and rotating states, solving the problem that the hydraulic clutch cannot be disconnected quickly at high speeds in the prior art.
Smart Images
Figure CN223257357U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to the technical field of hydraulic clutches, in particular to a hydraulic clutch. Background Art
[0002] The hydraulic clutch is located in the gearbox and is used to transmit or disconnect power in the transmission system. A hydraulic clutch in the prior art consists of an active part, a piston, a spring, a friction plate structure, and a driven part, with a control oil chamber formed between the active part and the piston. When the hydraulic clutch transmits power, pressurized oil is delivered to the control oil chamber. The pressurized oil pushes the piston to move and squeeze the friction plate structure and the spring, connecting the active part and the driven part to enable power transmission. When the hydraulic clutch disconnects power transmission, the supply of pressurized oil to the control oil chamber stops, and the elastic restoring force of the spring pushes the piston to move and squeeze the pressure oil in the control oil chamber, allowing the pressure oil in the control oil chamber to be discharged, thereby disconnecting power transmission.
[0003] When the driving and driven members are connected, as the power density of the transmission system gradually increases, the speed of the hydraulic clutch will gradually increase, and the centrifugal force of the pressure oil in the control oil chamber will also gradually increase. When the centrifugal force of the pressure oil is greater than the elastic restoring force of the spring, if the power transmission is to be disconnected, the elastic restoring force of the spring will be insufficient to move the piston to squeeze the pressure oil in the control oil chamber out. As a result, the hydraulic clutch cannot quickly and efficiently disconnect the power transmission. The speed of the hydraulic clutch must be reduced to achieve power disconnection, resulting in poor performance. Utility Model Content
[0004] The purpose of the present utility model is to provide a hydraulic clutch to solve the above-mentioned problems existing in the hydraulic clutch in the prior art.
[0005] To achieve this purpose, the present invention adopts the following technical solutions:
[0006] A hydraulic clutch comprises a clutch body, the clutch body comprising an active member, a piston and an elastic member; the piston is axially slidably connected to the active member and forms a control oil chamber between the piston and the active member; the elastic member is axially spaced away from the control oil chamber relative to the piston; one end of the elastic member elastically presses against the piston, and the other end elastically presses against the active member; the hydraulic clutch further comprises a regulating valve, the regulating valve comprising:
[0007] The valve body is fixedly mounted on the active member; the valve body is provided with an oil passage, one end of which is in communication with the outermost radial side of the control oil chamber, and the other end of which is in communication with the outside or the oil tank; an annular limiting groove is concavely formed on the inner peripheral wall of the oil passage;
[0008] The valve ball is movably located in the limiting groove and has a first working state in which the two ends of the oil passage are disconnected, and a second working state in which the two ends of the oil passage are connected.
[0009] As a preferred embodiment of the hydraulic clutch, the valve body includes a first sub-valve body and a second sub-valve body, at least a portion of the second sub-valve body is inserted into the active member and is detachably connected to the active member, and at least a portion of the first sub-valve body is inserted into the second sub-valve body and is detachably connected to the second sub-valve body;
[0010] The oil passage passes through the first sub-valve body and the second sub-valve body, and the limiting groove is provided at the junction of the first sub-valve body and the second sub-valve body.
[0011] As a preferred embodiment of the hydraulic clutch, the oil passage includes a first sub-oil passage provided in the first sub-valve body and a second sub-oil passage provided in the second sub-valve body, and the limiting groove includes a first sub-limiting groove provided in the first sub-valve body and a second sub-limiting groove provided in the second sub-valve body;
[0012] Along the axial direction of the piston, one end of the first sub-oil channel is connected to the control oil chamber, the first sub-limiting groove is located at the other end of the first sub-oil channel, and the second sub-limiting groove is provided at one end of the second sub-oil channel close to the first sub-oil channel.
[0013] As a preferred solution of the above-mentioned hydraulic clutch, the first sub-limiting groove extends in a trapezoidal shape along the axial direction of the piston, the small end of the first sub-limiting groove is connected to the first sub-oil channel, and the maximum inner diameter of the first sub-limiting groove is greater than the diameter of the valve ball.
[0014] As a preferred solution of the above-mentioned hydraulic clutch, the angle between the inner peripheral wall of the second sub-limiting groove and the radial direction of the control oil chamber is an acute angle.
[0015] As a preferred solution of the above-mentioned hydraulic clutch, the diameter of the second sub-oil channel at one end close to the limiting groove is smaller than the diameter of the first sub-oil channel at one end close to the limiting groove.
[0016] As a preferred solution of the above-mentioned hydraulic clutch, along the axial direction of the piston, the cross-sectional area of the limiting groove gradually decreases from the middle to both ends, and the maximum diameter of the limiting groove is greater than the diameter of the valve ball.
[0017] As a preferred solution of the above hydraulic clutch, the first sub-valve body is threadedly connected to the inner peripheral wall of the second sub-valve body; and / or,
[0018] The active component is threadedly connected to the outer peripheral wall of the second sub-valve body.
[0019] As a preferred solution of the above hydraulic clutch, the regulating valve further includes a first sealing member, the first sealing member being used to seal the connection between the first sub-valve body and the second sub-valve body; and / or,
[0020] The regulating valve further includes a second sealing member, which is used to seal the connection between the second sub-valve body and the active member.
[0021] As a preferred solution of the above hydraulic clutch, the oil passage is distributed at a right angle to the control oil chamber; or, the oil passage is distributed at an obtuse angle to the control oil chamber.
[0022] Beneficial effects of the utility model:
[0023] The utility model provides a hydraulic clutch, which includes a clutch body and a regulating valve. The clutch body includes an active part, a piston and an elastic part. The piston is axially slidably connected to the active part and forms a control oil chamber between the piston and the active part. The elastic part is axially away from the control oil chamber relative to the piston. One end of the elastic part is elastically pressed against the piston, and the other end is elastically pressed against the active part. The regulating valve includes a valve body and a valve ball. The valve body is fixedly arranged on the active part; the valve body is provided with an oil channel, one end of the oil channel is connected to the outermost side of the control oil chamber in the radial direction, and the other end is connected to the outside world or the oil tank. The inner circumferential wall of the oil channel is recessed with an annular limit groove. The valve ball is movably located in the limit groove and has a first working state of disconnecting the two ends of the oil channel, and a second working state of connecting the two ends of the oil channel.
[0024] When the hydraulic clutch needs to transmit power, pressurized oil is delivered to the control oil chamber, and the pressurized oil fills the control oil chamber and flows into the oil channel and the limit groove. When the pressurized oil fills the limit groove and the area on the oil channel between the control oil chamber and the valve ball, the pressurized oil in the oil channel and the limit groove causes the valve ball to seal the end of the limit groove away from the control oil chamber, thereby disconnecting the two ends of the oil channel. Continue to deliver pressurized oil to the control oil chamber, and the pressurized oil pushes the piston to move axially and squeeze the elastic part.
[0025] When the hydraulic clutch needs to disconnect power transmission, the supply of pressurized oil to the control oil chamber is stopped and the pressurized oil in the control oil chamber is drained. During this process, if the hydraulic clutch is in a stationary state, all the pressurized oil in the control oil chamber can be directly and smoothly drained from the control oil chamber to disconnect power transmission.
[0026] When the hydraulic clutch needs to disconnect power transmission, the supply of pressurized oil to the control oil chamber is stopped and the pressurized oil in the control oil chamber is drained. During this process, if the hydraulic clutch is in a rotating state, part of the pressurized oil in the control oil chamber accumulates in the radially outer peripheral area of the control oil chamber due to the action of centrifugal force. At this time, since the pressurized oil in the control oil chamber has been partially drained, the valve ball connects the two ends of the oil channel under the action of centrifugal force, so that the part of the pressurized oil accumulated in the radially outer peripheral area of the control oil chamber can be effectively discharged from the oil channel. The elastic restoring force of the elastic member can drive the piston to move axially to its initial position, so that the hydraulic clutch can effectively and stably disconnect power transmission even in a rotating state.
[0027] Therefore, the hydraulic clutch can efficiently and stably disconnect power transmission in both static and rotating states. BRIEF DESCRIPTION OF THE DRAWINGS
[0028] Figure 1 is a cross-sectional view of a hydraulic clutch provided by a specific embodiment of the present utility model;
[0029] Figure 2 This is an exploded view of a regulating valve provided by a specific embodiment of the present utility model;
[0030] Figure 3 This is a cross-sectional view of the valve ball blocking the end of the limit groove away from the control oil chamber when the hydraulic clutch provided by the specific embodiment of the utility model transmits power;
[0031] Figure 4 This is a cross-sectional view of the valve ball connecting the two ends of the oil passage under the action of its own gravity when the hydraulic clutch provided by the specific embodiment of the utility model disconnects power transmission and the hydraulic clutch is in a stationary state;
[0032] Figure 5 It is a cross-sectional view of the two ends of the oil passage connected by the valve ball under the action of centrifugal force when the hydraulic clutch provided by the specific embodiment of the utility model disconnects power transmission and the hydraulic clutch is in a rotating state.
[0033] In the picture:
[0034] 1. Clutch body; 11. Active member; 111. Limiting surface; 112. Oil inlet and outlet holes; 12. Piston; 13. Elastic member; 14. Control oil chamber; 15. Follower; 16. Friction plate structure; 17. Second seal; 18. Third seal; 19. Fourth seal;
[0035] 2. Regulating valve; 21. Valve body; 211. First sub-valve body; 212. Second sub-valve body; 22. Valve ball; 23. Oil channel; 231. First sub-oil channel; 232. Second sub-oil channel; 24. Limiting groove; 241. First sub-limiting groove; 242. Second sub-limiting groove; 25. First sealing member. DETAILED DESCRIPTION
[0036] The present invention will be further described in detail below with reference to the accompanying drawings and examples. It should be understood that the specific embodiments described herein are intended only to illustrate the present invention and are not intended to limit the present invention. It should also be noted that, for ease of description, the accompanying drawings only illustrate portions relevant to the present invention, not all of its components.
[0037] In the description of this utility model, unless otherwise specified or limited, the terms "connected," "connect," and "fixed" should be understood in a broad sense. For example, they can refer to fixed connection, detachable connection, or integration; mechanical connection or electrical connection; direct connection or indirect connection through an intermediate medium; internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in this utility model based on the specific circumstances.
[0038] In the present invention, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature may include the first and second features being in direct contact, or may include the first and second features being in contact not directly but through another feature between them. Moreover, a first feature being "above," "above," and "above" a second feature may include the first feature being directly above or obliquely above the second feature, or may simply mean that the first feature is higher in level than the second feature. A first feature being "below," "below," and "below" a second feature may include the first feature being directly below or obliquely below the second feature, or may simply mean that the first feature is lower in level than the second feature.
[0039] In the description of this embodiment, the terms "upper," "lower," "right," and other orientations or positional relationships are based on the orientations or positional relationships shown in the accompanying drawings and are intended solely for ease of description and simplified operation. They do not indicate or imply that the devices or components referred to must have a specific orientation, be constructed, or operate in a specific orientation. Therefore, they should not be construed as limitations on the present invention. Furthermore, the terms "first" and "second" are used solely for descriptive purposes and have no special meaning.
[0040] like Figure 1-5As shown, the utility model provides a hydraulic clutch, which includes a clutch body 1 and a regulating valve 2. The clutch body 1 includes an active part 11, a piston 12 and an elastic part 13. The piston 12 is axially slidably connected to the active part 11 and forms a control oil chamber 14 between the piston 12 and the active part 11. The elastic part 13 is axially away from the control oil chamber 14 relative to the piston 12. One end of the elastic part 13 is elastically pressed against the piston 12, and the other end is elastically pressed against the active part 11. The regulating valve 2 includes a valve body 21 and a valve ball 22. The valve body 21 is fixedly arranged on the active part 11; the valve body 21 is provided with an oil channel 23, one end of the oil channel 23 is connected to the outermost side of the control oil chamber 14 in the radial direction, and the other end is connected to the outside or the oil tank. The inner peripheral wall of the oil channel 23 is recessed with an annular limit groove 24. The valve ball 22 is movably located in the limit groove 24 and has a first working state in which the two ends of the oil channel 23 are disconnected, and a second working state in which the two ends of the oil channel 23 are connected.
[0041] like Figure 1 and Figure 3 As shown, when the hydraulic clutch needs to transmit power, pressurized oil is delivered to the control oil chamber 14, the pressurized oil fills the control oil chamber 14 and flows into the oil passage 23 and the limit groove 24. When the pressurized oil fills the limit groove 24 and the area on the oil passage 23 between the control oil chamber 14 and the valve ball 22, the pressurized oil in the oil passage 23 and the limit groove 24 causes the valve ball 22 to block the end of the limit groove 24 away from the control oil chamber 14, thereby disconnecting the two ends of the oil passage 23; the pressurized oil continues to be delivered to the control oil chamber 14, and the pressurized oil pushes the piston 12 to move axially and squeeze the elastic member 13.
[0042] like Figure 1 and Figure 4 As shown, when the hydraulic clutch needs to disconnect power transmission, the supply of pressurized oil to the control oil chamber 14 is stopped and the pressurized oil in the control oil chamber 14 is drained. During this process, if the hydraulic clutch is in a static state, all the pressurized oil in the control oil chamber 14 can be directly and smoothly drained from the control oil chamber 14 to disconnect power transmission. Because all the pressurized oil in the control oil chamber 14 can be directly and smoothly drained from the control oil chamber 14, during this process, the valve ball 22 communicates with both ends of the oil passage 23 under the action of its own weight.
[0043] like Figure 1 and Figure 5As shown, when the hydraulic clutch needs to disconnect power transmission, the supply of pressurized oil to the control oil chamber 14 is stopped and the pressurized oil in the control oil chamber 14 is drained. During this process, if the hydraulic clutch is in a rotating state, part of the pressurized oil in the control oil chamber 14 accumulates in the radially outer peripheral area of the control oil chamber 14 due to the action of centrifugal force. At this time, since the pressurized oil in the control oil chamber 14 has been partially drained, the valve ball 22 is connected to the two ends of the oil passage 23 under the action of centrifugal force, so that the part of the pressurized oil accumulated in the radially outer peripheral area of the control oil chamber 14 can be effectively discharged from the oil passage 23. The elastic restoring force of the elastic member 13 can drive the piston 12 to move axially to the initial position, thereby achieving efficient and stable disconnection of power transmission even when the hydraulic clutch is in a rotating state.
[0044] Therefore, the hydraulic clutch can efficiently and stably disconnect power transmission in both static and rotating states.
[0045] In this embodiment, the axial direction of the piston 12 and the axial direction of the control oil chamber 14 are both Figure 1 In the left and right directions, the radial direction of the piston 12 and the radial direction of the control oil chamber 14 are both Figure 1 The up and down directions in .
[0046] In this embodiment, if Figure 1 As shown in the exemplary embodiment, when the piston 12 abuts against the limiting surface 111 of the active member 11 , the piston 12 is located at the initial position. The limiting surface 111 is the inner circumferential wall of the control oil chamber 14 that is axially away from the elastic member 13 .
[0047] It is understandable that if Figure 1 As shown, the axial direction of the active member 11, the axial direction of the piston 12, the axial direction of the elastic member 13, and the axial direction of the control oil chamber 14 are all parallel. The central axis of the active member 11, the rotation centerline of the active member 11, the central axis of the piston 12, the rotation centerline of the piston 12, the central axis of the elastic member 13, the rotation centerline of the elastic member 13, and the central axis of the control oil chamber 14 are all collinear.
[0048] Specifically, if Figure 1 As shown, the active member 11 is provided with oil inlet and outlet holes 112, which communicate with the control oil chamber 14. The oil inlet and outlet holes 112 are located radially inward of the control oil chamber 14. This allows pressurized oil to be delivered to the control oil chamber 14 and for the pressurized oil in the control oil chamber 14 to escape. Furthermore, the oil inlet and outlet holes 112 are also connected to the oil tank.
[0049] Specifically, if Figure 1As shown, the clutch body 1 further includes a driven member 15 and a friction plate structure 16. The friction plate structure 16 is disposed between the driving member 11 and the driven member 15. The piston 12 can axially compress the friction plate structure 16 and the elastic member 13. The elastic restoring force of the elastic member 13 can drive the piston 12 away from the friction plate structure 16. This allows the driving member 11 and the driven member 15 to be connected to each other for power transmission, and can also be disconnected to terminate power transmission. The specific structure of the clutch body 1 is conventional and will not be described in detail here.
[0050] Specifically, in this embodiment, Figure 1 As shown, the elastic member 13 is a spring.
[0051] Preferably, if Figure 1 As shown, the oil passage 23 is arranged at a right angle to the control oil chamber 14. Compared to an obtuse angle, when the hydraulic clutch needs to transmit power, the pressurized oil fills the limit groove 24 and the area of the oil passage 23 between the control oil chamber 14 and the valve ball 22 with ease, resulting in higher efficiency. When the hydraulic clutch needs to disconnect power transmission and is in a rotating state, oil draining through the oil passage 23 is easier and more efficient. As an alternative, the oil passage 23 can be arranged at an obtuse angle to the control oil chamber 14.
[0052] Preferably, if Figure 2-5 As shown, the valve body 21 includes a first sub-valve body 211 and a second sub-valve body 212. At least a portion of the second sub-valve body 212 is inserted into the active component 11 and is detachably connected thereto. At least a portion of the first sub-valve body 211 is inserted into the second sub-valve body 212 and is detachably connected thereto. An oil passage 23 extends through the first and second sub-valve bodies 211, 212, and a retaining groove 24 is provided at the junction of the first and second sub-valve bodies 211, 212. This facilitates assembly and disassembly of the regulating valve 2 and allows the valve ball 22 to be confined within the retaining groove 24.
[0053] Specifically, if Figure 2-5 As shown, the oil passage 23 includes a first sub-oil passage 231 provided in the first sub-valve body 211 and a second sub-oil passage 232 provided in the second sub-valve body 212. The limiting groove 24 includes a first sub-limiting groove 241 provided in the first sub-valve body 211 and a second sub-limiting groove 242 provided in the second sub-valve body 212. Along the axial direction of the piston 12, one end of the first sub-oil passage 231 communicates with the control oil chamber 14. The first sub-limiting groove 241 is located at the other end of the first sub-oil passage 231, and the second sub-limiting groove 242 is located at the end of the second sub-oil passage 232 closer to the first sub-oil passage 231. This facilitates assembly and disassembly of the regulating valve 2 and confines the valve ball 22 within the limiting groove 24.
[0054] It is understandable that if Figure 2-5As shown, the diameter of the valve ball 22 is larger than the diameter of the first sub-oil passage 231 . The diameter of the valve ball 22 is larger than the diameter of the second sub-oil passage 232 .
[0055] Alternatively, as Figure 2-5 As shown, the first sub-limiting groove 241 extends in a trapezoidal shape along the axial direction of the piston 12. The small end of the first sub-limiting groove 241 is connected to the first sub-oil passage 231, and the maximum inner diameter of the first sub-limiting groove 241 is larger than the diameter of the valve ball 22. This allows the valve ball 22 to be movable within the limit groove 24, with a first operating state in which the two ends of the oil passage 23 are disconnected, and a second operating state in which the two ends of the oil passage 23 are connected.
[0056] Preferably, if Figure 2 As shown, the angle α between the inner circumferential wall of the second sub-limiting groove 242 and the radial direction of the control oil chamber 14 is acute. This increases the contact area between the valve ball 22 and the inner circumferential wall of the second sub-limiting groove 242 when subjected to the force of the pressurized oil, thereby effectively improving the valve ball 22's ability to seal the end of the limit groove 24 away from the control oil chamber 14.
[0057] As an alternative, the cross-sectional area of the retaining groove 24 decreases gradually from the center toward the ends along the axial direction of the piston 12, with the maximum diameter of the retaining groove 24 being larger than the diameter of the valve ball 22. That is, the cross-sectional shape of the retaining groove 24 along the axial direction of the piston 12 is arcuate. This also allows the valve ball 22 to be movable within the retaining groove 24, with a first operating state that disconnects the two ends of the oil passage 23, and a second operating state that connects the two ends of the oil passage 23.
[0058] Alternatively, as Figure 2-5 As shown, the diameter of the second sub-oil passage 232 near the limiting groove 24 is smaller than the diameter of the first sub-oil passage 231 near the limiting groove 24. This can further improve the reliability of the valve ball 22 blocking the end of the limiting groove 24 away from the control oil chamber 14.
[0059] As an alternative, the diameter of the second sub-oil channel 232 at the end near the limiting groove 24 may be equal to the diameter of the first sub-oil channel 231 at the end near the limiting groove 24. As another alternative, the diameter of the second sub-oil channel 232 at the end near the limiting groove 24 may be greater than the diameter of the first sub-oil channel 231 at the end near the limiting groove 24.
[0060] Optionally, the first sub-valve body 211 is threadedly connected to the inner peripheral wall of the second sub-valve body 212. And / or, the active member 11 is threadedly connected to the outer peripheral wall of the second sub-valve body 212. In this embodiment, Figure 2-5 As shown, the first sub-valve body 211 is preferably threadedly connected to the inner peripheral wall of the second sub-valve body 212, and the active member 11 is threadedly connected to the outer peripheral wall of the second sub-valve body 212, so as to achieve detachable connection between the first sub-valve body 211 and the active member 11 and the second sub-valve body 212.
[0061] Preferably, if Figure 3-5 As shown, the regulating valve 2 further includes a first sealing member 25 , which is used to seal the connection between the first sub-valve body 211 and the second sub-valve body 212 , so as to prevent the pressurized oil in the oil passage 23 from leaking through the gap between the first sub-valve body 211 and the second sub-valve body 212 .
[0062] Preferably, if Figure 3-5 As shown, the regulating valve 2 further includes a second sealing member 17 for sealing the connection between the second sub-valve body 212 and the active member 11 to prevent the pressure oil in the oil passage 23 from leaking through the gap between the second sub-valve body 212 and the active member 11 .
[0063] Preferably, if Figure 1 As shown, a third sealing member 18 is provided on the outer peripheral wall of the piston 12 and / or the inner peripheral wall of the active member 11. The third sealing member 18 is used to seal the gap between the outer peripheral wall of the piston 12 and the inner peripheral wall of the active member 11 to prevent the pressure oil in the control oil chamber 14 from leaking through the gap between the outer peripheral wall of the piston 12 and the inner peripheral wall of the active member 11.
[0064] Preferably, if Figure 1 As shown, a fourth sealing member 19 is provided on the inner circumferential wall of the piston 12 and / or the inner circumferential wall of the active member 11. The fourth sealing member 19 is used to seal the gap between the inner circumferential wall of the piston 12 and the inner circumferential wall of the active member 11 to prevent the pressure oil in the control oil chamber 14 from leaking through the gap between the inner circumferential wall of the piston 12 and the inner circumferential wall of the active member 11.
[0065] Obviously, the above-described embodiments of the present invention are merely examples for the purpose of clearly illustrating the present invention and are not intended to limit the manner in which the present invention is to be implemented. A person skilled in the art would be able to make various obvious changes, readjustments, and substitutions without departing from the scope of protection of the present invention. It is not necessary and impossible to enumerate all embodiments here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention shall be included within the scope of protection of the claims of the present invention.
Claims
1. A hydraulic clutch, comprising a clutch body (1), wherein the clutch body (1) comprises an active member (11), a piston (12) and an elastic member (13); the piston (12) is axially slidably connected to the active member (11) and forms a control oil chamber (14) between the piston (12) and the active member (11); the elastic member (13) is axially away from the control oil chamber (14) relative to the piston (12); one end of the elastic member (13) elastically presses against the piston (12), and the other end elastically presses against the active member (11); and the characteristics are as follows: The hydraulic clutch further comprises a regulating valve (2), wherein the regulating valve (2) comprises: A valve body (21) is fixedly mounted on the active member (11); the valve body (21) is provided with an oil passage (23); one end of the oil passage (23) is in communication with the outermost radial side of the control oil chamber (14), and the other end is in communication with the outside or an oil tank; an annular limiting groove (24) is concavely formed on the inner peripheral wall of the oil passage (23); The valve ball (22) is movably located in the limiting groove (24) and has a first working state of disconnecting the two ends of the oil passage (23) and a second working state of connecting the two ends of the oil passage (23).
2. The hydraulic clutch according to claim 1, characterized in that: The valve body (21) comprises a first sub-valve body (211) and a second sub-valve body (212), at least a portion of the second sub-valve body (212) is inserted into the active component (11) and is detachably connected to the active component (11), and at least a portion of the first sub-valve body (211) is inserted into the second sub-valve body (212) and is detachably connected to the second sub-valve body (212); The oil passage (23) passes through the first sub-valve body (211) and the second sub-valve body (212), and the limiting groove (24) is provided at the junction of the first sub-valve body (211) and the second sub-valve body (212).
3. The hydraulic clutch according to claim 2, characterized in that: The oil passage (23) comprises a first sub-oil passage (231) provided on the first sub-valve body (211) and a second sub-oil passage (232) provided on the second sub-valve body (212); the limiting groove (24) comprises a first sub-limiting groove (241) provided on the first sub-valve body (211) and a second sub-limiting groove (242) provided on the second sub-valve body (212); Along the axial direction of the piston (12), one end of the first sub-oil channel (231) is connected to the control oil chamber (14), the first sub-limiting groove (241) is located at the other end of the first sub-oil channel (231), and the second sub-limiting groove (242) is provided at one end of the second sub-oil channel (232) close to the first sub-oil channel (231).
4. The hydraulic clutch according to claim 3, characterized in that: Along the axial direction of the piston (12), the first sub-limiting groove (241) extends in a trapezoidal shape, the small end of the first sub-limiting groove (241) is connected to the first sub-oil channel (231), and the maximum inner diameter of the first sub-limiting groove (241) is greater than the diameter of the valve ball (22).
5. The hydraulic clutch according to claim 3, characterized in that: The included angle between the inner peripheral wall of the second sub-limiting groove (242) and the radial direction of the control oil chamber (14) is an acute angle.
6. The hydraulic clutch according to claim 3, characterized in that: The diameter of one end of the second sub-oil channel (232) close to the limiting groove (24) is smaller than the diameter of one end of the first sub-oil channel (231) close to the limiting groove (24).
7. The hydraulic clutch according to claim 2, characterized in that: Along the axial direction of the piston (12), the cross-sectional area of the limiting groove (24) gradually decreases from the middle to both ends, and the maximum diameter of the limiting groove (24) is greater than the diameter of the valve ball (22).
8. The hydraulic clutch according to claim 2, characterized in that: The first sub-valve body (211) and the inner peripheral wall of the second sub-valve body (212) are threadedly connected; and / or, The active component (11) is threadedly connected to the outer peripheral wall of the second sub-valve body (212).
9. The hydraulic clutch according to claim 2, characterized in that: The regulating valve (2) further comprises a first sealing member (25), the first sealing member (25) being used to seal the connection between the first sub-valve body (211) and the second sub-valve body (212); and / or, The regulating valve (2) further comprises a second sealing member (17), wherein the second sealing member (17) is used to seal the connection between the second sub-valve body (212) and the active member (11).
10. The hydraulic clutch according to any one of claims 1 to 9, characterized in that: The oil passage (23) and the control oil chamber (14) are distributed at a right angle; or, the oil passage (23) and the control oil chamber (14) are distributed at an obtuse angle.