Wet clutch structure

Abstract

The invention relates to the technical field of clutch structures, and discloses a wet clutch structure which mainly comprises a piston, a clutch outer drum, a clutch inner drum and a movable part. The clutch outer drum and the driving piece are connected and jointly form a cavity, the piston is movably arranged in the cavity, and the cavity is divided into a first oil cavity and a second oil cavity through the sealing piece. The driving piece is provided with a first oil way, a second oil way and a containing cavity for containing the movable part, and the first oil way and the second oil way communicate with the two oil cavities correspondingly. The movable part can block at least one opening in the first oil way or the second oil way under hydraulic drive, and the pressure of hydraulic oil relative to the piston is adjusted, so that connection of an inner drum and an outer drum of the clutch is controlled, and transmission of power from a driving piece to a driven piece is achieved. According to the structure, the flowing direction of hydraulic oil and the pressure on the piston are adjusted through the movable part, the response speed and operation precision of the clutch are improved, and the clutch is suitable for various application scenes needing efficient power transmission.

Description

Technical Field

[0001] The present application relates to the technical field of clutch structures, and further to a wet clutch structure. Background Art

[0002] At present, hydraulically controlled wet clutches are widely used in various vehicles, construction machinery and mining equipment. This type of clutch achieves power transmission and cutoff through the control of hydraulic oil, and its working principle mainly depends on the hydraulic oil supplied by the oil pump. The oil pump works under the drive of the engine and supplies hydraulic oil to the clutch at a constant flow rate. Due to the constancy of the hydraulic oil flow rate, the movement speed of the piston in the clutch also tends to be constant and cannot be adjusted according to actual working conditions, which limits the performance and reliability of the clutch. Summary of the invention

[0003] In view of the above technical problems, the purpose of the present application is to provide a wet clutch structure that can adjust the piston movement speed and improve the response speed of the clutch.

[0004] In order to achieve the above object, the present application provides a wet clutch structure, comprising:

[0005] piston;

[0006] A clutch outer drum connected to a driving member, wherein the clutch outer drum and the driving member jointly form a cavity, wherein the piston is movably disposed in the cavity, and the driving member is provided with a sealing member, wherein the sealing member abuts against the piston to separate the cavity into a first oil chamber and a second oil chamber;

[0007] The driving member is provided with a first oil circuit and a second oil circuit, the first oil circuit is connected to the first oil chamber, and the second oil circuit is connected to the second oil chamber; the driving member is also provided with a receiving chamber;

[0008] a movable portion, movably disposed in the accommodating cavity, capable of blocking at least one opening in the first oil circuit or the second oil circuit during the hydraulic drive of the movable portion, so as to limit the flow direction of the hydraulic oil, thereby adjusting the pressure of the hydraulic oil relative to the piston;

[0009] A clutch inner drum connected to a driven member, wherein the clutch inner drum and the clutch outer drum are arranged correspondingly and can be engaged under the action of the piston, so that the power of the driving member can be transmitted to the driven member.

[0010] In some embodiments, the sealing member is a sealing ring, and the first oil chamber and the second oil chamber are two concentrically arranged annular oil chambers.

[0011] In some embodiments, the driving member is provided with a hydraulic control oil flow channel for filling and draining hydraulic oil;

[0012] The first oil circuit includes a first oil filling circuit and a first oil discharge circuit, one end of the first oil filling circuit is connected to the hydraulic control oil flow channel, and the other end is connected to the first oil chamber, and one end of the first oil discharge circuit is connected to the first oil chamber, and the other end is connected to the accommodating chamber;

[0013] The second oil circuit includes a second oil filling circuit and a second oil discharge circuit, and the second oil filling circuit and the second oil discharge circuit are both connected to the second oil chamber;

[0014] The first oil filling passage, the first oil discharge passage, the second oil filling passage, and the second oil discharge passage are sequentially arranged on the driving member along the oil inlet direction of the hydraulic oil.

[0015] In some embodiments, the accommodating cavity includes a first accommodating cavity and a second accommodating cavity that are connected to each other, the size of the first accommodating cavity is larger than the size of the second accommodating cavity, and the size of the first accommodating cavity is adapted to the size of the movable part, so that the movable part can move in the first accommodating cavity;

[0016] The second accommodating chamber is in communication with the first oil discharge passage, and the first accommodating chamber is in communication with the second oil filling passage and the second oil discharge passage;

[0017] During the hydraulic oil filling process, the hydraulic oil first flows into the first oil filling passage, the first oil discharge passage and the second accommodating chamber through the hydraulic control oil flow passage to fill the first oil chamber and drive the piston to move. Under the pressure of the hydraulic oil, the movable part moves in the first direction to open the opening of the second oil filling passage and block the opening of the second oil discharge passage, so that the hydraulic oil flows into the second oil chamber through the second oil filling passage, thereby continuously driving the piston to move for the engagement of the clutch outer drum and the clutch inner drum.

[0018] During the hydraulic oil drainage process, the hydraulic oil in the first oil chamber and the second accommodating chamber flows out through the hydraulic control oil flow channel, and the movable part moves along the second direction to open the opening of the second oil drainage circuit and block the opening of the second oil inlet circuit, so that the hydraulic oil in the second oil chamber is discharged for the disengagement of the clutch outer drum and the clutch inner drum.

[0019] In some embodiments, the movable part is connected to the inner wall of the driving member through a return spring, and in a natural state, the movable part at least blocks the opening of the second oil filling circuit; under the driving action of the hydraulic oil, the movable part can move and individually block the opening of the second oil filling circuit or the opening of the second oil discharge circuit.

[0020] In some embodiments, the first accommodating cavity extends in a direction away from the second accommodating cavity and penetrates the driving member to form a through-hole structure;

[0021] The wet clutch structure is provided with an oil circuit switching valve, the oil circuit switching valve comprises a valve seat and a valve core, the movable part is the valve core, the valve seat is fixed in the first accommodating chamber, and the valve core is connected to the valve seat through the return spring;

[0022] The valve seat is provided with a valve port, and the valve port is communicated with the through hole structure, so that the hydraulic oil can be discharged through the valve port.

[0023] In some embodiments, a reset member is provided on the clutch inner drum or the clutch outer drum, and the reset member is connected to the piston to assist in resetting the piston.

[0024] In some embodiments, the wet clutch structure includes a friction plate assembly, which is correspondingly arranged between the clutch inner drum and the clutch outer drum, and the piston can act on the friction plate assembly through hydraulic pressure to control the engagement and disengagement of the clutch inner drum and the clutch outer drum.

[0025] In some embodiments, a fluid channel is provided on the piston, and two ends of the fluid channel are respectively connected to the second oil chamber and the friction plate assembly, and a quick oil drain valve is provided in the fluid channel to assist the flow of hydraulic oil.

[0026] In some embodiments, the quick oil release valve includes a valve cover and a steel ball, the valve cover and the steel ball are both arranged in the fluid channel, and the end of the valve cover close to the steel ball is set as a conical surface for mating with the spherical surface of the steel ball;

[0027] When the force exerted by the hydraulic oil on the steel ball is less than a preset value, there is a gap between the conical surface of the valve cover and the spherical surface of the steel ball, and the hydraulic oil can flow through the gap. When the force exerted by the hydraulic oil on the steel ball is greater than the preset value, there is no gap between the conical surface of the valve cover and the spherical surface of the steel ball to block the flow of the hydraulic oil.

[0028] Compared with the prior art, the wet clutch structure provided by the present application has the following beneficial effects:

[0029] 1. A wet clutch structure provided in the present application can separate a cavity into a first oil chamber and a second oil chamber by arranging a seal and a movable part on a driving member, and can flexibly adjust the flow rate of the hydraulic oil and the pressure relative to the piston by blocking the first oil circuit or the second oil circuit, so that the clutch can adjust the movement speed of the piston according to different working conditions, thereby improving the response speed and engagement smoothness of the clutch.

[0030] 2. A wet clutch structure provided by the present application, in the initial stage of the oil filling process, the hydraulic oil quickly fills the first oil chamber and directly drives the piston to advance, thereby achieving a rapid starting response, significantly reducing the idle travel time, and improving the working efficiency of the clutch; as the piston continues to advance, the clutch gradually enters a semi-engaged state. During this process, the resistance generated by the friction plate assembly gradually increases, and the hydraulic oil is filled into the second oil chamber through the opening of the second oil filling path, so that the hydraulic oil in the two oil chambers jointly drives the piston, effectively reducing the impact when the clutch is engaged and achieving a smoother transition.

[0031] 3. The wet clutch structure provided by the present application has a quick oil drain valve built into the piston body, which is composed of a steel ball and a valve cover. When the oil pressure in the piston is low or there is a small amount of lubricating oil, the oil can be quickly discharged, which significantly improves the response speed of the clutch under low oil pressure conditions and optimizes the starting and disengagement process of the clutch. When the oil pressure in the piston increases, the steel ball overcomes the centrifugal force under the push of the oil and moves toward the valve cover, and seals with the conical surface of the valve cover, effectively blocking the hydraulic channel, so that the piston can maintain high pressure, which provides a guarantee for the continuous filling of the clutch and stable engagement. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] The preferred implementation scheme will be described below in a clear and understandable manner with reference to the accompanying drawings to further illustrate the above-mentioned characteristics, technical features, advantages and implementation methods of the present application.

[0033] Figure 1 It is a schematic diagram of the structure of a wet clutch in the prior art;

[0034] Figure 2 is a structural schematic diagram of a wet clutch structure in one embodiment of the present application;

[0035] Figure 3 is a schematic diagram of a wet clutch structure in a first state during oil filling in one embodiment of the present application;

[0036] Figure 4 is a schematic diagram of a second state of a wet clutch structure during oil filling in one embodiment of the present application;

[0037] Figure 5It is a structural schematic diagram of a quick oil discharge valve in an oil discharge state in one embodiment of the present application;

[0038] Figure 6 It is a structural schematic diagram of a quick oil discharge valve in a closed state in one embodiment of the present application.

[0039] Explanation of the accompanying drawings: piston 1; clutch outer drum 2; clutch inner drum 3; movable part 4; driving member 5; first oil chamber 6; second oil chamber 7; hydraulic control oil flow channel 8; first oil filling circuit 9; first oil discharge circuit 10; second oil filling circuit 11; second oil discharge circuit 12; accommodating chamber 13; first accommodating chamber 130; second accommodating chamber 140; return spring 15; valve seat 16; valve port 160; friction plate assembly 17; return member 18; fluid channel 19; quick oil drain valve 20; valve cover 201; steel ball 202; end plate 21; sealing member 22. DETAILED DESCRIPTION

[0040] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the specific implementation methods of the present application will be described below with reference to the accompanying drawings. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings and other implementation methods can be obtained based on these drawings without creative work.

[0041] In order to simplify the drawings, only the parts related to the application are schematically shown in each figure, and they do not represent the actual structure of the product. In addition, in order to simplify the drawings and facilitate understanding, in some figures, only one of the parts with the same structure or function is schematically drawn or marked. In this article, "one" not only means "only one", but also means "more than one".

[0042] It should be further understood that the term “and / or” used in the specification and appended claims refers to any combination and all possible combinations of one or more of the associated listed items, and includes these combinations.

[0043] In this document, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0044] In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application.

[0045] In addition, in the description of the present application, the terms "first", "second", etc. are only used to distinguish the description and cannot be understood as indicating or implying relative importance. It should be noted that the flow direction of the oil (hydraulic oil) is indicated by arrows in the drawings of the present application.

[0046] In modern industry, hydraulically controlled wet clutches are widely used in vehicles, construction machinery, mining equipment and other fields because they can transmit large torques. The operation of these clutches depends on the hydraulic oil provided by the oil pump, which works under the drive of the engine and provides hydraulic oil to the clutch at a constant flow rate. Due to the constancy of the hydraulic oil flow rate, the movement speed of the piston 1 in the clutch also tends to be constant and cannot be adjusted according to actual working conditions.

[0047] like Figure 1 As shown in the figure, the hydraulic oil flows into the oil chamber through only one flow channel to press down the piston a. This constant pressure supply method limits the performance of the wet clutch. During the clutch engagement process, due to the non-adjustability of the hydraulic oil pressure, the movement speed of the piston a cannot adapt to the different engagement stages. This leads to insufficient response speed of the clutch in situations where a quick response is required, such as quick start or shifting, which prolongs the engagement time and affects the overall work efficiency. On the contrary, in the engagement stage that requires a smooth transition, due to the excessive movement speed of the piston a, a large impact will be generated when the clutch is engaged. This impact not only reduces driving comfort, but may also damage the various components of the clutch and shorten its service life.

[0048] Therefore, when the wet clutch in the prior art faces different working conditions, due to the fixed hydraulic oil pressure, it is impossible to achieve accurate control of the movement speed of the piston a, which limits the performance and reliability of the clutch. In order to solve these problems, it is necessary to improve the existing wet clutch structure.

[0049] In one embodiment, the reference specification Figure 2The wet clutch structure provided in the present application can adjust the piston movement speed, improve the response speed and engagement smoothness of the clutch, and thus improve the overall performance and durability.

[0050] Reference Manual Attached Figure 2 The present application provides a wet clutch structure, which mainly includes a piston 1, a clutch outer drum 2, a clutch inner drum 3 and a movable part 4. The clutch outer drum 2 is connected to a driving member 5 to form a cavity, and the piston 1 is movably arranged in the cavity. A sealing member 22 is arranged on the driving member 5, and the sealing member 22 abuts against the piston 1 to separate the cavity into a first oil chamber 6 and a second oil chamber 7.

[0051] The driving member 5 is also provided with a receiving chamber 13, a first oil circuit and a second oil circuit, the first oil circuit is connected to the first oil chamber 6, and the second oil circuit is connected to the second oil chamber 7. The movable part 4 is movably arranged in the receiving chamber 13, and can block at least one opening in the first oil circuit or the second oil circuit under hydraulic drive, thereby limiting the flow direction of the hydraulic oil and adjusting the pressure of the hydraulic oil relative to the piston 1. The clutch inner drum 3 is connected to the driven member, and is arranged corresponding to the clutch outer drum 2, and can be engaged under the action of the piston 1, so that the power of the driving member 5 is transmitted to the driven member.

[0052] In this embodiment, by blocking the oil circuit by the movable part 4, the present invention can accurately control the pressure of the hydraulic oil on the piston 1, provide more precise clutch engagement control, reduce engagement shock, and improve driving comfort. Specifically, in situations where a quick response is required, such as quick start or shifting, the present invention can quickly change the oil circuit state by adjusting the position of the movable part 4, achieve rapid movement of the piston 1, and thus speed up the clutch engagement speed.

[0053] Optionally, the present invention may further include a pressure feedback mechanism for monitoring the pressure of the hydraulic oil and automatically adjusting the position of the movable part 4 according to the pressure change to achieve more intelligent clutch control.

[0054] It should also be noted that in one case of this embodiment, when oil filling is required, the movable part 4 can keep the opening of the first oil circuit unobstructed, allowing the hydraulic oil to flow into the first oil chamber 6, driving the main body of the piston 1 to move, and realizing the engagement of the clutch. In this process, the movable part 4 blocks the opening of the second oil circuit; when oil discharge is required, the movable part 4 blocks the opening of the first oil circuit to prevent the hydraulic oil from continuing to flow into the first oil chamber 6, and at the same time opens the opening of the second oil circuit, so that the hydraulic oil in the first oil chamber 6 is discharged through the second oil circuit, realizing the return of the main body of the piston 1, thereby disengaging the clutch. The opposite is also feasible, which will not be repeated here.

[0055] In addition, the first oil circuit and the second oil circuit may include multiple branches, which may be specifically used for filling or draining oil. For example, the first oil circuit may include multiple filling branches for supplying hydraulic oil to the first oil chamber 6 at different stages, and the second oil circuit may include multiple draining branches for draining the hydraulic oil in the second oil chamber 7 at different stages. By adjusting the opening and blocking of different branches, the movement speed of the piston 1 can be accurately controlled, and the performance of the clutch can be optimized.

[0056] It can be understood that the movement mode of the movable part 4 is not limited in the present embodiment, and a simple mechanical structure and an automatic control system can be adopted. For example, its movement can be realized through a gear transmission mechanism. By designing a series of gears, the movable part 4 can be moved under a specific gear ratio to control the opening and closing of the oil circuit. The structure is simpler and less prone to errors. Alternatively, the movement of the movable part 4 can be automatically controlled by the control end, and the operator can drive the movable part 4 to move according to the actual situation, thereby realizing precise control of the oil circuit and improving the degree of automation of the device.

[0057] Based on the above content, further, the seal 22 is a sealing ring, and the first oil chamber 6 and the second oil chamber 7 are two concentrically arranged annular oil chambers. The sealing ring ensures the sealing between the first oil chamber 6 and the second oil chamber 7 to prevent abnormal leakage of hydraulic oil between the two oil chambers, while preventing external contaminants from entering the oil chamber.

[0058] In this embodiment, the first oil chamber 6 and the second oil chamber 7 are concentrically arranged. In other words, the two oil chambers share the same central axis, which effectively reduces the radial dimension of the clutch, making the clutch structure more compact and easy to integrate into space-constrained applications.

[0059] In a specific embodiment, the sealing ring may be made of a high-pressure-resistant and wear-resistant rubber material or a synthetic material to ensure long-term stability under high-pressure and high-temperature environments.

[0060] In one embodiment, based on the above embodiment, Figure 2 and Figure 3 As shown, the driving member 5 is provided with a hydraulic control oil flow channel 8. Generally, the hydraulic control oil flow channel 8 is directly connected to a hydraulic pump or other pressure source, and delivers hydraulic oil to key components of the clutch; in addition, the hydraulic control oil flow channel 8 is also used for the discharge of oil to facilitate the recycling or release of the oil. It should be noted that one or more hydraulic control oil flow channels 8 can be integrated in the driving member 5 of the clutch, and these oil flow channels can be straight-through or branched to meet different oil flow requirements. In some applications, the oil flow channel can be designed with a regulating valve to adjust the oil flow under different working conditions.

[0061] In the above embodiment, the first oil circuit includes a first oil filling circuit 9 and a first oil discharge circuit 10. One end of the first oil filling circuit 9 is connected to the hydraulic control oil flow channel 8 to receive hydraulic oil from the pressure source; the other end is connected to the first oil chamber 6 to deliver hydraulic oil to the oil chamber to push the piston 1 and control the engagement of the clutch. One end of the first oil discharge circuit 10 is connected to the first oil chamber 6, and the other end is connected to the accommodating chamber 13 to introduce the hydraulic oil in the oil chamber into the accommodating chamber 13, reduce the pressure of the hydraulic oil on the piston 1, and realize the separation of the clutch.

[0062] In contrast, the second oil circuit includes a second oil filling circuit 11 and a second oil drain circuit 12, both of which are connected to the second oil chamber 7. The second oil filling circuit 11 allows the hydraulic oil to flow from the accommodating chamber 13 of the driving member 5 into the second oil chamber 7. This process is a key step in achieving clutch engagement, because the inflow of hydraulic oil increases the pressure in the second oil chamber 7, pushing the piston 1 to move, thereby engaging the clutch inner drum 3 with the clutch outer drum 2. The second oil drain circuit 12 is responsible for discharging the oil in the second oil chamber 7 to achieve clutch disengagement.

[0063] At the same time, please refer to the instructions attached Figure 3 The first oil filling circuit 9, the first oil discharge circuit 10, the second oil filling circuit 11, and the second oil discharge circuit 12 are sequentially arranged on the driving member 5 along the oil inlet direction of the hydraulic oil. It can be understood that the flow of the hydraulic oil starts from the first oil filling circuit 9, which directly connects the hydraulic control oil flow channel 8 and the first oil chamber 6 to provide the necessary hydraulic oil for the clutch engagement stage. The hydraulic oil flows from the first oil chamber 6 into the accommodating chamber 13 through the first oil discharge circuit 10, driving the movable part 4 to open the opening of the second oil filling circuit 11; then, the second oil filling circuit 11 introduces the oil from the accommodating chamber 13 into the second oil chamber 7, further pushing the piston 1 and enhancing the clutch engagement force; during the clutch separation process, the oil in the second oil chamber 7 can be discharged through the second oil discharge circuit 12.

[0064] This sequentially arranged oil circuit design ensures the continuity and directionality of the hydraulic oil flow, reduces the chaos and turbulence of the oil flow, and thus improves the efficiency of the oil flow; in addition, the sequentially arranged oil circuits reduce interference between the oil circuits and improve the stability and durability of the system.

[0065] In one embodiment, based on the above content, the accommodating chamber 13 on the driving member 5 further includes a first accommodating chamber 130 and a second accommodating chamber 140 that are connected to each other, the size of the first accommodating chamber 130 is larger than the size of the second accommodating chamber 140, and the size of the first accommodating chamber 130 is adapted to the size of the movable part 4, so that the movable part 4 can move in the first accommodating chamber 130, wherein the second accommodating chamber 140 is connected to the first oil discharge circuit 10, and the first accommodating chamber 130 is respectively connected to the second oil filling circuit 11 and the second oil discharge circuit 12.

[0066] It is worth mentioning that in the design of this embodiment, the size of the second accommodating chamber 140 is designed to be smaller, and is connected to the first row of oil circuits 10 to form a smaller oil chamber. In the initial stage of oil filling, the hydraulic oil quickly accumulates pressure in the smaller oil chamber, thereby effectively improving the starting response time of the clutch. The design of this small-sized oil chamber helps to quickly build up oil pressure, providing a power basis for the rapid engagement of the clutch.

[0067] In contrast, the first accommodating chamber 130 is relatively large in size and is connected to the second oil filling path 11 and the second oil discharge path 12, forming a large oil chamber. This design helps to smooth the operation of the piston 1 during the clutch operation and reduce the impact and vibration caused by sudden changes in oil pressure. The large-sized oil chamber can store more hydraulic oil, thereby buffering pressure fluctuations to a certain extent and ensuring that the clutch transmits power smoothly and evenly.

[0068] Based on the above content, please refer to the attached Figure 3 and Figure 4 It can be seen that in the oil filling process of the wet clutch structure in this embodiment, the hydraulic oil first flows into the first oil filling path 9, the first oil discharge path 10 and the second accommodating chamber 140 through the hydraulic control oil flow channel 8, with the purpose of filling the first oil chamber 6 to drive the piston 1 to move. This design allows the hydraulic oil to accumulate quickly in the first oil chamber 6, thereby quickly building up oil pressure and pushing the piston 1 to achieve the initial engagement of the clutch outer drum 2 and the clutch inner drum 3. As the hydraulic oil pressure increases, the movable part 4 moves along the first direction, opens the opening of the second oil filling path 11 and blocks the opening of the second oil discharge path 12. This action enables the hydraulic oil to flow into the second oil chamber 7 through the second oil filling path 11, further pushing the piston 1, and achieving the complete engagement of the clutch outer drum 2 and the clutch inner drum 3.

[0069] During the hydraulic oil drainage process, the hydraulic oil in the first oil chamber 6 and the second accommodating chamber 140 flows out through the hydraulic control oil flow channel 8. At the same time, the movable part 4 moves along the second direction to open the opening of the second oil drainage path 12 and block the opening of the second oil filling path 11. The hydraulic oil in the second oil chamber 7 is discharged, reducing the pressure of the piston 1, thereby achieving the disengagement of the clutch outer drum 2 and the inner drum.

[0070] It should be noted that the instructions can be found in the attached Figure 4 The first direction in the above content is the direction from the second accommodating cavity 140 to the first accommodating cavity 130 , and the second direction is the direction from the first accommodating cavity 130 to the second accommodating cavity 140 .

[0071] Specifically, the movable part 4 is connected to the inner wall of the driving member 5 through the return spring 15. In the natural state, that is, when there is no external hydraulic oil pressure, the movable part 4 at least blocks the opening of the second oil filling path 11 due to the preset tension of the return spring 15, ensuring that in the initial no-load stage, the small volume oil cavity formed by the first oil cavity 6 and the second accommodating cavity 140 can quickly fill with oil, thereby effectively improving the starting response speed of the clutch. By keeping the opening of the second oil filling path 11 blocked, it can be ensured that the hydraulic oil preferentially flows into the smaller oil cavity, quickly builds up oil pressure, and provides power for the rapid engagement of the clutch.

[0072] When the movable part 4 starts to move, that is, the pressure of the hydraulic oil acts on the movable part 4, overcoming the force of the return spring 15, and pushing the movable part 4 to move in a specific direction. During the oil filling process, the movable part 4 opens the opening of the second oil filling path 11 and blocks the opening of the second oil discharge path 12, and the hydraulic oil flows into the second oil chamber 7, continuing to push the piston 1, and realizing the engagement of the clutch outer drum 2 and the inner drum. During the oil discharge process, the movable part 4 moves under the action of the return spring 15, opens the opening of the second oil discharge path 12 and blocks the opening of the second oil filling path 11, so that the hydraulic oil in the second oil chamber 7 is discharged, and the clutch outer drum 2 and the inner drum are disengaged.

[0073] In one embodiment, the wet clutch structure is provided with an oil circuit switching valve, which includes a valve seat 16 and a valve core. The movable part 4 in the above content is the valve core, and the valve core is connected to the valve seat 16 through a return spring 15. The latter is fixed in the first accommodating chamber 130. The first accommodating chamber 130 extends in a direction away from the second accommodating chamber 140 and penetrates the driving member 5 to form a through-hole structure.

[0074] Among them, Figure 2 As shown, the valve seat 16 of the oil circuit switching valve is provided with a valve port 160, which is connected to the through-hole structure, so that the hydraulic oil can be discharged through the valve port 160 during the oil discharge process. Specifically, in the oil discharge stage, the pressure in the hydraulic control oil flow channel 8 is reduced, causing the oil in the first oil chamber 6 and the second accommodating chamber 140 to flow out through the hydraulic control oil flow channel 8. Under low pressure, the movable part 4 (valve core) moves due to the change in hydraulic oil pressure, opening the second oil discharge circuit 12 and the valve port 160. Due to the high-speed rotation of the clutch, centrifugal force acts on the oil in the second oil chamber 7, causing it to be quickly discharged under the centrifugal force of high-speed rotation, accelerating the discharge speed of the oil and improving the oil discharge efficiency.

[0075] Based on the above content, more specifically, the wet clutch structure also includes a friction plate assembly 17, and the friction plate assembly 17 is correspondingly arranged between the clutch inner drum 3 and the clutch outer drum 2. The piston 1 acts on the friction plate assembly 17 through hydraulic pressure to control the engagement and disengagement of the clutch inner drum 3 and the clutch outer drum 2.

[0076] In one embodiment, further, a reset member 18 is provided on the clutch outer drum 2 or the clutch inner drum 3 , and the reset member 18 is connected to the piston 1 to assist the piston 1 in resetting.

[0077] It can be understood that in this embodiment, mechanical force is used to assist the piston 1 to quickly return to its initial position. In the present invention, the reset member 18 can be a spring, a hydraulic cylinder or other forms of elastic elements, which are installed on the clutch inner drum 3 or the clutch outer drum 2 and are directly connected to the piston 1. When the hydraulic oil pressure decreases or disappears, the elastic force of the reset member 18 acts on the piston 1, pushing it to quickly reset, so that the pressure between the friction plate assembly 17 is quickly released, and the clutch is quickly separated. At the same time, it is ensured that the clutch can quickly and accurately return to the initial state after the separation operation, ready for the next engagement.

[0078] In one embodiment, Figures 2 to 4 As shown, a fluid channel 19 is provided on the piston 1, and the two ends of the channel are respectively connected to the second oil chamber 7 and the friction plate assembly 17, ensuring that the hydraulic oil can flow efficiently between the two, reducing the path length of the oil flow and reducing the pressure loss.

[0079] Importantly, a quick oil drain valve 20 is provided in the fluid channel 19, and the valve is mainly used to assist the flow of hydraulic oil so that the oil in the piston 1 cavity is quickly discharged under the action of centrifugal force, thereby ensuring that the clutch can be quickly and completely separated.

[0080] In the unengaged state, it is understandable that there is a certain gap between the friction plates on the clutch outer drum 2 and the clutch inner drum 3. When the driving member 5 runs at high speed, the hydraulic oil can flow through the gap of the friction plates under the action of centrifugal force to form an oil film, so that the inner and outer friction plates do not bind to each other, reducing resistance, thereby disconnecting the connection between the driving member 5 and the driven member. By pressing the friction plate down by the piston 1, the gap between the inner and outer friction plates disappears, the hydraulic oil cannot flow in the middle, the clutch outer drum 2 and the clutch inner drum 3 are connected as a whole, and the power can be transmitted from the driving member 5 to the driven member.

[0081] In addition, if Figure 3 As shown, the clutch outer drum 2 is provided with an end plate 21 to limit the movement of the friction plate assembly 17 and ensure its stability and reliability during high speed and high torque transmission. In practical applications, the end plate 21 can be made of high-strength material to withstand the high load generated by the clutch during operation.

[0082] Optionally, the end plate 21 is fixedly connected to the clutch outer drum 2 via a spline. In addition, since the spline connection can achieve high-precision positioning and matching through the matching of convex and concave grooves, the accuracy and stability of the connection can be ensured; the spline connection has a large contact area and can share a large load, so that the connection has a high load-bearing capacity. In a wet clutch, this means that a large torque can be effectively transmitted while maintaining the stability of the structure.

[0083] In one embodiment, Figure 5 and Figure 6 As shown, the quick oil drain valve 20 of the above embodiment includes a valve cover 201 and a steel ball 202. The valve cover 201 and the steel ball 202 are both arranged in the fluid channel 19. The end of the valve cover 201 close to the steel ball 202 is designed as a conical surface, which can be matched with the spherical surface of the steel ball 202.

[0084] Specifically, when the force exerted by the hydraulic oil on the steel ball 202 is less than the preset value, there is a gap between the conical surface of the valve cover 201 and the spherical surface of the steel ball 202, allowing the hydraulic oil to flow through the gap to achieve the oil discharge function. In particular, the steel ball 202 rotates to a certain extent under the push of the oil, and this rotation assists the hydraulic oil to be discharged, thereby improving the oil discharge efficiency. On the contrary, when the force exerted by the hydraulic oil on the steel ball 202 is greater than the preset value, the conical surface of the valve cover 201 and the spherical surface of the steel ball 202 are tightly combined to block the flow of the hydraulic oil. The hydraulic oil exerts a force on the piston 1, pressing down the friction plate assembly 17 to engage the inner and outer friction plates, thereby ensuring that the clutch can be stably engaged and transmit power.

[0085] It should be noted that the preset value in this embodiment is determined comprehensively based on parameters such as oil pressure, size of steel ball 202, design of valve cover 201, etc. In other words, the preset value refers to the critical point at which the force of hydraulic oil on steel ball 202 reaches a certain level, thereby triggering the change of the gap between valve cover 201 and steel ball 202. When oil needs to be discharged, there is a gap between valve cover 201 and steel ball 202. When oil does not need to be discharged or the clutch needs to be engaged, there is no gap between valve cover 201 and steel ball 202, blocking the flow of oil and maintaining the necessary oil pressure.

[0086] In combination with the above embodiments, it can be seen that the wet clutch structure in the present application enters the oil release process when the clutch needs to be switched from the engaged state to the disengaged state. (Refer to the attached Figure 2, where the arrow indicates the flow direction of the oil) The hydraulic control oil flow channel 8 begins to discharge the oil in the first oil chamber 6 and the second accommodating chamber 140, reducing the pressure in the system; as the oil is discharged, the movable part 4 (valve core) begins to move to open the valve port 160 and the opening of the second oil channel 12, and part of the oil in the second oil chamber 7 is discharged through the valve port 160, which is the first step to achieve rapid oil discharge. At the same time, the piston 1 is reset when the hydraulic oil pressure is reduced, and the friction plate assembly 17 is no longer pressed, resulting in a gap between the inner and outer friction plates, creating conditions for the discharge of oil.

[0087] When the oil pressure is not high, the quick drain valve 20 starts to work, and a gap is formed between the valve cover 201 and the steel ball 202, so that another part of the oil in the second oil chamber 7 flows to the friction plate assembly 17 through the quick drain valve 20, achieving synchronous oil drain and accelerating the efficiency and speed of oil drain. At this time, since the driving member 5 is in operation, the oil flows through the gaps between the friction plates under the action of centrifugal force to form an oil film. The friction plates are not combined with each other, so that the clutch is converted to a separation state, reducing mechanical shock and wear.

[0088] It should be noted that the above embodiments can be freely combined as needed. The above are only preferred implementations of the present application. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present application, and these improvements and modifications should also be regarded as the protection scope of the present application.

Claims

1. A wet clutch structure, characterized in that: include: piston; A clutch outer drum connected to a driving member, wherein the clutch outer drum and the driving member jointly form a cavity, wherein the piston is movably disposed in the cavity, and the driving member is provided with a sealing member, wherein the sealing member abuts against the piston to separate the cavity into a first oil chamber and a second oil chamber; The driving member is provided with a first oil circuit and a second oil circuit, the first oil circuit is connected to the first oil chamber, and the second oil circuit is connected to the second oil chamber; the driving member is also provided with a receiving chamber; a movable portion, movably disposed in the accommodating cavity, capable of blocking at least one opening in the first oil circuit or the second oil circuit during the hydraulic drive of the movable portion, so as to limit the flow direction of the hydraulic oil, thereby adjusting the pressure of the hydraulic oil relative to the piston; A clutch inner drum connected to a driven member, wherein the clutch inner drum and the clutch outer drum are arranged correspondingly and can be engaged under the action of the piston, so that the power of the driving member can be transmitted to the driven member.

2. The wet clutch structure according to claim 1, characterized in that: The sealing element is a sealing ring, and the first oil chamber and the second oil chamber are two concentrically arranged annular oil chambers.

3. The wet clutch structure according to claim 1, characterized in that: The driving member is provided with a hydraulic control oil flow channel for filling and draining the hydraulic oil; The first oil circuit includes a first oil filling circuit and a first oil discharge circuit, one end of the first oil filling circuit is connected to the hydraulic control oil flow channel, and the other end is connected to the first oil chamber, and one end of the first oil discharge circuit is connected to the first oil chamber, and the other end is connected to the accommodating chamber; The second oil circuit includes a second oil filling circuit and a second oil discharge circuit, and the second oil filling circuit and the second oil discharge circuit are both connected to the second oil chamber; The first oil filling passage, the first oil discharge passage, the second oil filling passage, and the second oil discharge passage are sequentially arranged on the driving member along the oil inlet direction of the hydraulic oil.

4. The wet clutch structure according to claim 3, characterized in that: The accommodating cavity comprises a first accommodating cavity and a second accommodating cavity which are connected to each other. The size of the first accommodating cavity is larger than that of the second accommodating cavity. The size of the first accommodating cavity is adapted to the size of the movable part, so that the movable part can move in the first accommodating cavity. The second accommodating chamber is in communication with the first oil discharge passage, and the first accommodating chamber is in communication with the second oil filling passage and the second oil discharge passage; During the hydraulic oil filling process, the hydraulic oil first flows into the first oil filling passage, the first oil discharge passage and the second accommodating chamber through the hydraulic control oil flow passage to fill the first oil chamber and drive the piston to move. Under the pressure of the hydraulic oil, the movable part moves in the first direction to open the opening of the second oil filling passage and block the opening of the second oil discharge passage, so that the hydraulic oil flows into the second oil chamber through the second oil filling passage, thereby continuously driving the piston to move for the engagement of the clutch outer drum and the clutch inner drum. During the hydraulic oil drainage process, the hydraulic oil in the first oil chamber and the second accommodating chamber flows out through the hydraulic control oil flow channel, and the movable part moves along the second direction to open the opening of the second oil drainage circuit and block the opening of the second oil inlet circuit, so that the hydraulic oil in the second oil chamber is discharged for the disengagement of the clutch outer drum and the clutch inner drum.

5. The wet clutch structure according to claim 4, characterized in that: The movable part is connected to the inner wall of the driving member through a return spring. In a natural state, the movable part at least blocks the opening of the second oil filling circuit. Under the driving action of the hydraulic oil, the movable part can move and individually block the opening of the second oil filling circuit or the opening of the second oil discharge circuit.

6. The wet clutch structure according to claim 5, characterized in that: The first accommodating cavity extends in a direction away from the second accommodating cavity and penetrates the driving member to form a through-hole structure; The wet clutch structure is provided with an oil circuit switching valve, the oil circuit switching valve comprises a valve seat and a valve core, the movable part is the valve core, the valve seat is fixed in the first accommodating chamber, and the valve core is connected to the valve seat through the return spring; The valve seat is provided with a valve port, and the valve port is communicated with the through hole structure, so that the hydraulic oil can be discharged through the valve port.

7. The wet clutch structure according to claim 1, characterized in that: A reset member is provided on the clutch inner drum or the clutch outer drum, and the reset member is connected to the piston to assist the piston in resetting.

8. The wet clutch structure according to any one of claims 1 to 7, characterized in that: The wet clutch structure includes a friction plate assembly, which is correspondingly arranged between the clutch inner drum and the clutch outer drum. The piston can act on the friction plate assembly through hydraulic pressure to control the engagement and disengagement of the clutch inner drum and the clutch outer drum.

9. The wet clutch structure according to claim 8, characterized in that: A fluid channel is provided on the piston, and two ends of the fluid channel are respectively connected to the second oil chamber and the friction plate assembly. A quick oil drain valve is provided in the fluid channel to assist the flow of hydraulic oil.

10. The wet clutch structure according to claim 9, characterized in that: The quick oil release valve comprises a valve cover and a steel ball, wherein the valve cover and the steel ball are both arranged in the fluid channel, and the end of the valve cover close to the steel ball is arranged as a conical surface for mating with the spherical surface of the steel ball; When the force exerted by the hydraulic oil on the steel ball is less than a preset value, there is a gap between the conical surface of the valve cover and the spherical surface of the steel ball, and the hydraulic oil can flow through the gap. When the force exerted by the hydraulic oil on the steel ball is greater than the preset value, there is no gap between the conical surface of the valve cover and the spherical surface of the steel ball to block the flow of the hydraulic oil.

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