High-power automatic hydrodynamic transmission structure

Abstract

The high-power automatic hydrodynamic transmission structure comprises an execution oil way, a hydraulic cushion valve and a clutch, the execution oil way is communicated with the hydraulic cushion valve, the execution oil way is further communicated with the clutch, and the hydraulic cushion valve and the clutch are arranged in parallel; the hydraulic buffer valve comprises a valve body, a buffer cavity is formed in the valve body and communicates with the execution oil way, and a buffer mechanism is arranged at the lower end of the buffer cavity. The clutch comprises a body, a piston, a return spring and a friction plate, an inner cavity is formed in the body, an oil inlet passage penetrates through one end of the bottom of the inner cavity and is communicated with the execution oil way, the return spring is installed at the bottom of the inner cavity, and the friction plate is installed at the upper end of the inner cavity. The upper end part of the piston and the friction plate are oppositely arranged and have a gap; the response efficiency of the clutch can be guaranteed while oil pressure buffering is achieved in the clutch executing process, the hydraulic buffer and the clutch are integrally installed, the oil supply process is reliable, and practicability is high.

Description

Technical Field

[0001] The invention relates to the technical field of clutches, in particular to a high-power automatic hydraulic transmission structure. Background Art

[0002] Automatic hydraulic transmission is generally composed of multiple clutches connected in series. Different gears are obtained according to different clutch combinations. However, when the clutch is engaged, it is necessary to control the oil pressure when the clutch is engaged to obtain a suitable oil pressure gradual increase process, thereby controlling the slip and torque transmission of the clutch. This achieves the purpose of smooth gear shifting and makes the clutch have a longer service life.

[0003] The prior art discloses a comparative document entitled a differential pressure buffer valve, with publication number: CN115750779A. When the piston oil pressure in the clutch is not properly controlled and a shift shock occurs, the structure can have a buffering effect on the oil pressure in the execution oil circuit, so that when a high-power automatic hydraulic transmission shifts in this situation, the shifting process is smooth, avoiding affecting the service life of the transmission system.

[0004] However, since the execution oil circuit in this structure passes directly through the valve body and an oil inlet throttle hole is provided to control the amount of oil in the oil circuit, when shifting gears normally, the piston oil pressure in the clutch passes through the inside of the valve body and the amount of oil is easily restricted, which will also affect the oil pressure entering the clutch, thereby slowing down the reaction speed of the clutch and affecting the response efficiency of the clutch. Summary of the invention

[0005] In order to solve the above technical problems, the present invention provides a high-power automatic hydraulic transmission structure.

[0006] The present invention is achieved through the following technical solutions.

[0007] The invention provides a high-power automatic hydraulic transmission structure, comprising an execution oil circuit, a hydraulic buffer valve and a clutch, wherein the execution oil circuit is connected to the hydraulic buffer valve, the execution oil circuit is also connected to the clutch, and the hydraulic buffer valve and the clutch are arranged in parallel;

[0008] The hydraulic buffer valve comprises a valve body, a buffer cavity is arranged in the valve body, the buffer cavity is communicated with the execution oil circuit, and a buffer mechanism is arranged at the lower end of the buffer cavity for buffering the oil pressure of the execution oil circuit;

[0009] The clutch includes a body, a piston, a return spring and a friction plate. An inner cavity is arranged inside the body. An oil inlet passage passes through one end of the bottom of the inner cavity. The oil inlet passage is connected to the execution oil circuit. The return spring is installed at the bottom of the inner cavity. The friction plate is installed at the upper end of the inner cavity. The piston is movably arranged inside the body. The upper end of the piston is arranged opposite to the friction plate with a gap. The lower end of the piston contacts the return spring. The piston separates the oil inlet passage and the inner cavity.

[0010] Preferably, an oil passage is provided at the top of the valve body, the upper end of the oil passage is communicated with the execution oil circuit, and the lower end of the oil passage is communicated with the buffer cavity.

[0011] Preferably, the buffer mechanism includes a buffer valve core, a follower valve core and a buffer spring. The buffer valve core is slidably arranged at the upper end of the buffer cavity. An accommodating cavity is opened at the upper end of the buffer valve core. A throttling hole is opened at the bottom of the accommodating cavity. The throttling hole passes through the bottom of the buffer valve core and is connected with the buffer cavity. The follower valve core is slidably arranged on the inner side of the buffer cavity. The follower valve core is located at the lower end of the buffer valve core. The lower end of the follower valve core is connected to the buffer spring. The end of the buffer spring away from the follower valve core is connected to the bottom of the buffer cavity.

[0012] Preferably, the buffer valve core consists of an upper end and a lower end, the end face area of ​​the upper end is smaller than the end face area of ​​the lower end, the inner diameter of the upper end of the buffer cavity is longer than the inner diameter of the lower end, and the lower end is slidably fitted with the lower end of the buffer cavity; an annular block is provided on the outer periphery of the middle position of the upper end, and a limit ring is provided in the middle position of the upper end of the buffer cavity, and the annular block is slidably fitted with the limit ring.

[0013] Preferably, a first oil leakage channel is opened at the upper end of the buffer cavity near the lower end, and the first oil leakage channel is connected to the oil tank through a pipeline.

[0014] Preferably, the end surface area of ​​the upper end portion is larger than the port area of ​​the oil passage.

[0015] Preferably, a connecting pipe is provided at the bottom of the buffer cavity, a second oil drain channel is opened at the bottom of the buffer cavity, the connecting pipe is connected to the oil outlet channel, the center of the connecting pipe and the center of the second oil drain channel are concentrically arranged, and the second oil drain channel is directly connected to the oil tank.

[0016] Preferably, a bottom plate is installed at the bottom of the outer side of the valve body.

[0017] Preferably, a sealing gasket is provided between the bottom of the outer side of the valve body and the bottom plate.

[0018] Preferably, a third oil drain channel is provided at the bottom of the inner cavity, and the third oil drain channel is connected with the oil tank through a pipeline.

[0019] The beneficial effects of the present invention are:

[0020] 1. In the process of supplying oil to the clutch through the execution oil circuit, the oil in the execution oil circuit is dispersed into the clutch and the hydraulic buffer valve, and part of the oil pressure is divided into the hydraulic buffer valve, and the oil pressure in the execution oil circuit is reduced. On the one hand, the clutch oil supply pressure is controlled, so that the oil pressure of the oil in the execution oil circuit entering the inner cavity of the clutch body is reduced, and the initial impact force on the piston is reduced, pushing the piston to move in the empty stroke, and the piston moves toward the friction plate, so that the piston is subjected to a relatively stable thrust to complete the piston empty stroke, and the piston conflicts with the spring plate. The clutch receives a response signal, and the additional impact stress in the transmission structure is also reduced. The torque transmitted when the clutch is engaged also has a gradual increase process, so that multiple clutches are engaged smoothly, avoiding abnormal slipping of the clutch, and ensuring smooth shifting of the high-power automatic hydraulic transmission; on the other hand, it also ensures the response efficiency of the clutch. By changing the oil circuit direction of the valve body and the execution oil circuit, the transmission is prevented from being affected by the oil pressure of the execution oil circuit during normal shifting, ensuring the use efficiency of the high-power automatic hydraulic transmission and extending the service life of the high-power automatic hydraulic transmission.

[0021] 2. The hydraulic buffer valve structure is connected in parallel with the clutch through the execution oil circuit, which has the effect of reducing the oil pressure in the execution oil circuit. At the same time, it is also convenient for the integrated installation of the hydraulic buffer and the clutch. The installation is simple, the structure is compact, the oil supply process is reliable, and the practicability is strong.

[0022] 3. Combined with the buffer valve core, follower valve core and buffer spring, the buffer spring is set with an initial compression amount. The initial compression amount of the buffer spring combined with the buffer valve core and follower valve core determines the initial pressure of the clutch oil circuit, ensuring that the pressure can push the clutch piston, so that the clutch piston moves quickly, completes the piston idle stroke, and improves the clutch response speed.

[0023] 4. The time taken for the buffering process is controlled by designing the diameter length of the upper and lower ends of the buffer valve core, the difference between the upper and lower ends, and the size of the throttling hole, thereby ensuring that the oil pressure buffering is achieved during the clutch execution process while also ensuring the clutch operation speed. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 It is a structural schematic diagram of the initial state of the present invention;

[0025] Figure 2 It is a structural schematic diagram of the buffering process of the present invention;

[0026] In the figure: 1-execution oil circuit; 2-valve body; 3-buffer cavity; 4-buffer mechanism; 41-buffer valve core; 411-upper end; 412-lower end; 413-annular block; 414-limiting ring; 42-follow-up valve core; 43-buffer spring; 44-accommodating chamber; 45-throttling hole; 5-body; 6-piston; 7-return spring; 8-friction plate; 9-inner cavity; 10-oil inlet passage; 11-oil passage; 12-first oil leakage passage; 13-connecting pipe; 14-second oil leakage passage; 15-bottom plate; 16-sealing gasket; 17-third oil leakage passage; 18-oil tank. DETAILED DESCRIPTION

[0027] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0028] It should be noted that all directional indications in the embodiments of the present invention (such as up, down, left, right, front, back, etc.) are only used to explain the relative position relationship, movement status, etc. between the components under a certain specific posture (as shown in the accompanying drawings). If the specific posture changes, the directional indication will also change accordingly.

[0029] In this embodiment, refer to Figure 1 , including an execution oil circuit 1, a hydraulic buffer valve and a clutch. The execution oil circuit 1 is connected to the hydraulic buffer valve, and the execution oil circuit 1 is also connected to the clutch. The hydraulic buffer valve and the clutch are arranged in parallel to realize the pressure division of the oil pressure on the execution oil circuit 1 during the execution of the clutch. At the same time, the oil pressure in the execution oil circuit 1 does not need to pass through the hydraulic buffer valve, which ensures the normal shifting of the clutch. At the same time, the assembly of the structure is also relatively simple.

[0030] In this embodiment, refer to Figure 1 The hydraulic buffer valve includes a valve body 2, and an oil passage 11 is arranged on the top of the valve body 2. The upper end of the oil passage 11 is connected with the execution oil circuit 1, so that the pipeline of the execution oil circuit 1 is directly installed with the oil passage 11, which is convenient for assembly and disassembly, and can also avoid oil leakage, and also ensure the response efficiency of the clutch, and avoid the transmission being affected by the oil pressure of the execution oil circuit during normal gear shifting, thereby ensuring the use efficiency of the high-power automatic hydraulic transmission;

[0031] A buffer cavity 3 is provided in the valve body 2, and the lower end of the oil passage 11 is directly connected to the buffer cavity 3, so that the buffer cavity 3 is connected to the execution oil circuit 1. A buffer mechanism 4 is provided at the lower end of the buffer cavity 3 for buffering the oil pressure of the execution oil circuit 1, which has a certain pressure dividing effect on the oil pressure entering the clutch.

[0032] In this embodiment, refer to Figure 1 The buffer mechanism 4 specifically includes a buffer valve core 41, a follower valve core 42 and a buffer spring 43. The buffer valve core 41 is slidably arranged at the upper end of the buffer cavity 3. The upper end of the buffer valve core 41 is provided with a receiving cavity 44. The bottom of the receiving cavity 44 is provided with a throttling hole 45. The throttling hole 45 passes through the bottom of the buffer valve core 41 and is connected with the buffer cavity 3. The aperture of the throttling hole 45 is set to R. The size of R controls the response time of the clutch, so as to control the response time of the clutch within an appropriate range and improve the response efficiency of the clutch. The buffer valve core 4 1 is composed of an upper end portion 411 and a lower end portion 412, the end surface area of ​​the upper end portion 411 is smaller than the end surface area of ​​the lower end portion 412, the inner diameter length of the upper end of the buffer cavity 3 is larger than the inner diameter length of the lower end, and the lower end portion 412 is slidably matched with the lower end of the buffer cavity 3; an annular block 413 is provided on the outer periphery of the middle position of the upper end portion 411, and a limiting ring 414 is provided in the middle position of the upper end of the buffer cavity 3. The annular block 413 is slidably matched with the limiting ring 414 to achieve the up-and-down differential effect of the buffer valve core 41, and cooperate with the throttling hole 45 to control the buffer time of the clutch;

[0033] The follower valve core 42 is slidably arranged inside the buffer cavity 3. The follower valve core 42 is located at the lower end of the buffer valve core 41. The lower end of the follower valve core 42 abuts against the buffer spring 43. The end of the buffer spring 43 away from the follower valve core 42 is fixedly connected to the bottom of the buffer cavity 3. The buffer spring 43 is provided with a certain initial compression amount, which is used to control the initial pressure of the oil pressure entering the clutch so as to facilitate the quick response of the clutch.

[0034] In this embodiment, refer to Figure 1 A first oil drain channel 12 is provided at the upper end of the buffer cavity 3 near the lower end, and the first oil drain channel 12 is connected to the oil tank 18 through a pipeline; the oil pressure in the execution oil circuit 1 enters the buffer cavity 3, pushing the buffer valve core 41 to move downward, so that the annular block 413 and the limit ring 414 are staggered, so that the upper end of the buffer cavity 3 is connected with the first oil drain channel 12, so that part of the oil flows out through the first oil drain channel 12 and enters the oil tank 18, so that the oil pressure in the execution oil circuit 1 is divided to a certain extent.

[0035] In this embodiment, refer to Figure 1 The end surface area of ​​the upper end portion 411 is larger than the port area of ​​the oil passage 11 , so as to limit the buffer valve core 41 .

[0036] In this embodiment, refer to Figure 1 A connecting pipe 13 is installed at the bottom of the buffer cavity 3, and a second oil drain channel 14 is opened at the bottom of the buffer cavity 3. The connecting pipe 13 is connected to the second oil drain channel 14, and the center of the connecting pipe 13 and the center of the second oil drain channel 14 are concentrically arranged. The second oil drain channel 14 is directly connected to the oil tank 18. The end of the buffer spring 43 away from the follow-up valve core 42 is sleeved on the connecting pipe 13, and a bottom plate 15 is installed at the bottom of the outer side of the valve body 2. The second oil drain channel 14 runs through the bottom plate 15 and is connected to the oil tank 18. The port area of ​​the second oil drain channel 14 at one end of the bottom plate 15 is smaller than the port area of ​​the second oil drain channel 14 at one end of the bottom of the buffer cavity 3. When the oil in the hydraulic buffer valve flows out from the connecting pipe 13 through the second oil drain channel 14, it has a certain throttling effect to avoid excessive oil splashing. A sealing gasket 16 is arranged between the bottom of the outer side of the valve body 2 and the bottom plate 15 to strengthen the sealing effect of the bottom plate 15 and the bottom of the valve body 2 to avoid oil leakage.

[0037] In this embodiment, refer to Figure 1 The clutch includes a body 5, a piston 6, a return spring 7 and a friction plate 8. An inner cavity 9 is arranged inside the body 5. An oil inlet passage 10 is passed through one end of the bottom of the inner cavity 9. The oil inlet passage 10 is connected with the execution oil circuit 1. The return spring 7 is installed at the bottom of the inner cavity 9. The friction plate 8 is installed at the upper end of the inner cavity 9. The piston 6 is movably arranged inside the body 5. The upper end 411 of the piston 6 is arranged opposite to the friction plate 8 and there is a gap. The lower end of the piston 6 contacts with the return spring 7. The piston 6 separates the oil inlet passage 10 and the inner cavity 9.

[0038] The oil pressure in the execution oil circuit 1 enters the clutch, and enters the inner cavity 9 from the oil inlet passage 10, directly pushing the piston 6 to move in the horizontal direction. At this time, the piston 6 starts to move in the idle stroke and moves toward the friction plate 8. The piston 6 moves to the position of the friction plate 8 to realize the clutch response.

[0039] In this embodiment, refer to Figure 1 A third oil drain channel 17 is provided on the side of the bottom of the inner cavity 9 away from the oil inlet passage 10. The third oil drain channel 17 is connected with the oil tank 18 through a pipeline, so that part of the oil entering the inner cavity 9 can be led out from the third oil drain channel 17 to the oil tank 18, thereby avoiding oil leakage inside the clutch.

[0040] In this embodiment, refer to Figure 1The oil tank 18 is directly assembled on the bottom of the valve body 2 and fixed on the bottom plate 15 by bolts, so that the second oil drain channel 14 is directly connected to the oil tank 18, and the first oil drain channel 12 and the third oil drain channel 17 are directly connected to the oil tank 18 through pipelines, so that the oil from the first oil drain channel 12, the second oil drain channel 14 and the third oil drain channel 17 directly enters the oil tank 18, the installation process is simple, the overall structure is highly integrated, and the practicability is strong.

[0041] The working process of this embodiment: Figure 2 When the execution oil circuit 1 supplies oil to the clutch, part of the pressure oil is diverted into the valve body 2, initially pushing the buffer valve core 41 to move a certain distance toward the bottom of the buffer cavity 3, so that the annular block 413 and the limit ring 414 are staggered, so that the upper end of the buffer cavity 3 is connected with the first oil leakage channel 12, and part of the pressure oil enters the oil tank 18 from the first oil leakage channel 12, so that the oil pressure in the execution oil circuit 1 is reduced;

[0042] A closed cavity is formed between the buffer valve core 41 and the follower valve core 42, and the closed cavity is represented by Q. As the pressure oil in the valve body 2 gradually increases, the pressure oil enters the accommodating cavity 44 and flows out from the throttling hole 45 into the closed cavity. At this time, since the buffer spring 43 has an initial compression amount, when working, on the one hand, the pressure oil will generate an initial oil pressure on the execution oil circuit 1, and the oil pressure quickly pushes the clutch internal piston 6 to move. On the other hand, the pressure oil enters the closed cavity to push the follower valve core 42 to move downward, and the buffer spring 43 is further compressed.

[0043] As the pressure oil in the closed cavity gradually increases, the compression amount of the buffer spring 43 continues to increase, and the pressure of the pressure oil in the closed cavity continues to increase until a dynamic balance is formed in the buffer cavity 3 and the execution oil circuit 1. At this time, the oil pressure at the upper end 411 of the buffer valve core 41 is greater than the oil pressure at the lower end 412, and the end surface area of ​​the upper end 411 is smaller than the end surface area of ​​the lower end 412. The buffer valve core 41 automatically adjusts the flow rate at the throttling hole 45, so that the upper end 411 and the lower end 412 of the buffer valve core 41 are in a dynamic force balance state, and the oil pressure at the upper end of the buffer valve core 41 is equal to the sum of the oil pressure in the closed cavity and the pressure difference of the oil flowing through the throttling hole 45;

[0044] As the follow-up valve core 42 moves downward, the compression amount of the buffer spring 43 increases, and the oil pressure inside the closed chamber gradually increases. The oil pressure is adjusted by the buffer valve core 41 and transmitted to the clutch through the execution oil circuit 1, so that the initial impact force on the piston 6 is reduced, so that the oil supply pressure of the clutch gradually increases synchronously, pushing the piston 6 to move in the empty stroke. The piston 6 moves toward the friction plate 8, so that the piston 6 is subjected to a relatively stable thrust to complete the piston 6 empty stroke. The piston 6 conflicts with the friction plate 8, and the clutch receives a response signal, and the additional impact stress in the transmission structure is also reduced. The transmission torque generated by the clutch is also gradually increased, so that the clutch is smoothly engaged, avoiding abnormal slippage of the clutch, and ensuring smooth shifting of the high-power automatic hydraulic transmission;

[0045] The clutch execution process is finished, and the execution oil circuit 1 is no longer supplied with oil. The follower valve core 42 moves downward and contacts the connecting pipe 13, and the oil pressure in the closed chamber rises rapidly until no liquid flows in the throttling hole 45. At this time, the buffer valve core 41 moves upward, and the annular block 413 contacts the limit ring 414, closing the first oil drain channel 12, and the buffer process is finished.

[0046] When the high-power automatic hydraulic transmission is shifted into other gears, the clutch connects the third oil drain channel 17, the oil in the execution oil circuit 1 is drained, the buffer spring 43 pushes the follower valve core 42 to move upward, and the oil pressure in the closed cavity is squeezed out through the throttling hole 45 and discharged into the buffer cavity 3, and the overall structure returns to the initial state.

[0047] The above are only preferred embodiments of the present invention, and are not intended to limit the patent scope of the present invention. All equivalent structural changes made using the contents of the present invention's specification and drawings, or directly / indirectly applied in other related technical fields, are included in the patent protection scope of the present invention.

Claims

1. A high-power automatic hydraulic transmission structure, characterized in that: It comprises an execution oil circuit (1), a hydraulic buffer valve and a clutch, wherein the execution oil circuit (1) is connected to the hydraulic buffer valve, the execution oil circuit (1) is also connected to the clutch, and the hydraulic buffer valve and the clutch are arranged in parallel; The hydraulic buffer valve comprises a valve body (2), a buffer cavity (3) is arranged in the valve body (2), the buffer cavity (3) is communicated with the execution oil circuit (1), and a buffer mechanism (4) is arranged at the lower end of the buffer cavity (3) for buffering the oil pressure of the execution oil circuit (1); The clutch comprises a body (5), a piston (6), a return spring (7) and a friction plate (8); an inner cavity (9) is arranged inside the body (5); an oil inlet passage (10) is passed through one end of the bottom of the inner cavity (9); the oil inlet passage (10) is communicated with the execution oil circuit (1); the return spring (7) is mounted at the bottom of the inner cavity (9); the friction plate (8) is mounted at the upper end of the inner cavity (9); the piston (6) is movably arranged inside the body (5); the upper end of the piston (6) and the friction plate (8) are arranged opposite to each other with a gap; the lower end of the piston (6) contacts the return spring (7); and the piston (6) separates the oil inlet passage (10) and the inner cavity (9).

2. A high-power automatic hydraulic transmission structure as claimed in claim 1, characterized in that: An oil passage (11) is provided at the top of the valve body (2); the upper end of the oil passage (11) is in communication with the execution oil circuit (1), and the lower end of the oil passage (11) is in communication with the buffer cavity (3).

3. A high-power automatic hydraulic transmission structure as claimed in claim 1, characterized in that: The buffer mechanism (4) comprises a buffer valve core (41), a follower valve core (42) and a buffer spring (43); the buffer valve core (41) is slidably arranged at the upper end of the buffer cavity (3); a receiving cavity (44) is provided at the upper end of the buffer valve core (41); a throttling hole (45) is provided at the bottom of the receiving cavity (44); the throttling hole (45) passes through the bottom of the buffer valve core (41) and is connected to the buffer cavity (3); the follower valve core (42) is slidably arranged inside the buffer cavity (3); the follower valve core (42) is located at the lower end of the buffer valve core (41); the lower end of the follower valve core (42) is connected to the buffer spring (43); and the end of the buffer spring (43) away from the follower valve core (42) is connected to the bottom of the buffer cavity (3).

4. A high-power automatic hydraulic transmission structure as claimed in claim 3, characterized in that: The buffer valve core (41) is composed of an upper end portion (411) and a lower end portion (412); the end surface area of ​​the upper end portion (411) is smaller than the end surface area of ​​the lower end portion (412); the inner diameter length of the upper end of the buffer cavity (3) is greater than the inner diameter length of the lower end; the lower end portion (412) is slidably matched with the lower end of the buffer cavity (3); an annular block (413) is provided on the outer periphery of the middle position of the upper end portion (411); a limiting ring (414) is provided in the middle position of the upper end of the buffer cavity (3); the annular block (413) is slidably matched with the limiting ring (414).

5. A high-power automatic hydraulic transmission structure as claimed in claim 1, characterized in that: A first oil leakage passage (12) is provided at the upper end of the buffer cavity (3) near the lower end, and the first oil leakage passage (12) is connected to the oil tank (18) through a pipeline.

6. A high-power automatic hydraulic transmission structure as claimed in claim 4, characterized in that: The end surface area of ​​the upper end portion (411) is larger than the port area of ​​the oil passage (11).

7. A high-power automatic hydraulic transmission structure as claimed in claim 5, characterized in that: A connecting pipe (13) is provided at the bottom of the buffer cavity (3), a second oil drain channel (14) is opened at the bottom of the buffer cavity (3), the connecting pipe (13) is connected to the second oil drain channel (14), the center of the connecting pipe (13) and the center of the second oil drain channel (14) are concentrically arranged, and the second oil drain channel (14) is directly connected to the oil tank (18).

8. A high-power automatic hydraulic transmission structure as claimed in claim 1, characterized in that: A bottom plate (15) is installed at the bottom of the outer side of the valve body (2).

9. A high-power automatic hydraulic transmission structure as claimed in claim 1, characterized in that: A sealing gasket (16) is provided between the bottom of the outer side of the valve body (2) and the bottom plate (15).

10. A high-power automatic hydraulic transmission structure as claimed in claim 5, characterized in that: A third oil drain channel (17) is provided at the bottom of the inner cavity (9), and the third oil drain channel (17) is connected to the oil tank (18) through a pipeline.

Images