A high-integration friction clutch oil cylinder structure

Abstract

A high-integration friction clutch oil cylinder structure relates to the field of friction clutch. The existing wet multi-plate friction clutch has the problems of wide and heavy gear box due to long shaft system or easy damage of friction plate under high speed. The present application comprises an input shaft, an end cover, a gear, a piston, a quick release valve core and a return spring; the end cover, the gear and the piston are arranged axially adjacent and coaxially sleeved on the input shaft, the end cover and the piston are respectively located on both sides of the gear, the end cover is rigidly connected with the gear, and the gear is rigidly fixed with the input shaft; the side of the gear close to the piston is provided with an annular space, the piston and the annular space form a working oil cavity, the piston can move axially on the input shaft, the end cover is provided with a quick release oil way and a mounting cavity matched with the quick release valve core, and the return spring is abutted between the piston and the friction plate seat, so as to realize the limited space arrangement of the friction clutch and the quick release under high speed. The present application is applied to the field of friction clutch oil cylinder.

Description

Technical Field

[0001] This invention relates to the field of friction clutches, and more specifically to a highly integrated friction clutch cylinder structure. Background Technology

[0002] A wet multi-plate friction clutch internally contains a working cylinder and friction elements, and externally has a working oil pressure regulating device. Working oil enters the cylinder to drive the piston to axially press against the friction elements, transmitting torque through the friction between the pressed elements. In certain working scenarios, friction clutches in power transmission equipment gearboxes are used to connect two different gear shafts.

[0003] Currently, the existing technical solutions mainly include two types. One type is where the clutch is an independent component with an independent working cylinder, arranged between two gear components. This structure leads to an excessively long shaft system, increasing the width and overall weight of the gearbox.

[0004] Another technical solution involves integrating the gear and clutch, using the space on one side of the gear as a hydraulic cylinder, with working oil supplied directly into the cylinder from the center. Although this structure reduces the axial space to some extent, the clutch disengages slowly at high speeds and is prone to burning of the friction plates under high loads.

[0005] High-speed small and medium-sized power transmission units require small gearbox size and light weight. When high-speed drive equipment disengages under load, it must be quick to do so, otherwise it is easy to damage the friction plates. The existing friction clutch cylinder structure installed in the gearbox is difficult to meet the requirements of space size and quick disengagement in application scenarios. Summary of the Invention

[0006] In order to solve the problems of existing wet multi-plate friction clutches, such as the large and heavy gearbox due to the long shaft system, or the slow disengagement at high speeds which easily damages the friction plates, this invention provides a highly integrated friction clutch cylinder structure.

[0007] The technical solution of this invention is:

[0008] A highly integrated friction clutch cylinder structure includes an input shaft, an end cover, a gear, a piston, a quick-release valve core, and a return spring;

[0009] The end cap, gear, and piston are arranged adjacent to each other along the axial direction and coaxially mounted on the input shaft. The end cap and piston are located on both sides of the gear, the end cap is rigidly connected to the gear, and the gear is rigidly fixed to the input shaft.

[0010] The gear has an annular space on the side near the piston. The piston and the annular space enclose a working oil chamber. The piston can move axially on the input shaft. The end cover has a quick-release oil passage and an installation cavity for the quick-release valve core. The return spring is located between the piston and the friction plate seat, realizing the limited space arrangement of the friction clutch and rapid disengagement at high speed.

[0011] Furthermore, the input shaft has a radially penetrating input shaft working oil passage, and the inner sidewall of the end cover has an annular oil groove. The input shaft working oil passage and the annular oil groove are radially corresponding and connected, forming an initial oil collection channel for the working oil.

[0012] Furthermore, the end cap is provided with a plurality of oil hole groups evenly distributed around the circumference, and each oil hole group includes piston radial oil passage I, piston radial oil passage II, piston axial oil passage I, piston axial oil passage II, piston axial oil passage III and piston drain passage.

[0013] One end of the piston radial oil passage I is connected to the annular oil groove, and the other end is connected to the piston radial oil passage II through the connecting groove on the cover plate. The quick-release valve core is assembled in the piston radial oil passage II and abuts against the spring to form an axially movable oil passage switching structure.

[0014] Furthermore, the gear is provided with gear oil hole groups that are the same number as and correspond to the end cover oil hole groups. Each gear oil hole group includes a gear axial oil passage I, a gear axial oil passage II, and a gear tilting oil passage.

[0015] The gear axial oil passage I is sealed and connected to the piston axial oil passage I of the end cover, and the gear axial oil passage II is sealed and connected to the piston axial oil passage II of the end cover. One end of the gear tilting oil passage intersects and connects with the gear axial oil passage I and the gear axial oil passage II, and the other end extends to the outer diameter of the working oil chamber and connects with it.

[0016] Furthermore, the radial opening height of the gear axial oil passage I, gear axial oil passage II, and the corresponding piston axial oil passage I and piston axial oil passage II on the end cover is all higher than the outer diameter of the working oil chamber.

[0017] Furthermore, when the quick-release valve core is in the connected / discharge state, the working oil pressure pushes the quick-release valve core to compress the spring, so that the piston radial oil passage II is connected to the piston axial oil passage I, and the piston axial oil passage II is blocked.

[0018] When the quick-release valve core is in the disengaged state, the spring resets and pushes the quick-release valve core to connect the piston radial oil passage II with the piston axial oil passage II and block the piston axial oil passage I.

[0019] Furthermore, the gear is made of alloy steel, and the end cap and piston are made of lightweight aluminum.

[0020] Furthermore, the inner wall of the working oil chamber is provided with a wear-resistant coating, the outer peripheral wall of the piston is provided with a guide ring, and the mating surface between the guide ring and the input shaft adopts a gap sealing structure.

[0021] Furthermore, the piston drain passage is an inclined oil passage, and the inclination angle of the piston drain passage is set to 30°–60°.

[0022] One end of the piston drain passage is connected to the piston axial oil passage II, and the other end passes through the outer peripheral wall of the end cover and faces the oil return chamber of the gearbox.

[0023] Furthermore, the connection surface between the end cover and the gear is provided with a positioning pin and a sealing gasket. The positioning pin ensures the precise alignment of the oil hole assembly, and the sealing gasket is made of oil-resistant rubber material to achieve static sealing between the end cover and the gear.

[0024] Compared with the prior art, the present invention has the following advantages:

[0025] This invention overcomes the difficulty of existing friction clutches in achieving rapid disengagement at high speeds in confined spaces. It provides a friction clutch working cylinder structure highly integrated with gears. Pistons and end caps are arranged on both sides of the gears, and the pistons and end caps are connected by oil passages on the gears. Quick-release oil passages are provided on the end caps and pistons. Working oil is supplied from the end cap side and enters the working oil chamber through the oil passages on the gears to drive the piston, thereby achieving rapid disengagement of the friction clutch at high speeds in confined spaces.

[0026] This invention adopts an integrated structure in which the end cover, gear, and piston are axially adjacent and coaxially fitted. The gear is rigidly fixed to the input shaft, and the end cover is rigidly connected to the gear. It makes full use of the space on both sides of the gear to enclose the working oil chamber, eliminating the need for a separate oil cylinder arrangement, significantly shortening the shaft length, and reducing the width and overall volume of the gearbox. The gear is made of alloy steel to ensure strength, while the end cover and piston are made of lightweight aluminum. While maintaining structural rigidity, the overall weight is significantly reduced, meeting the core requirements of "small size and lightweight" for high-speed small and medium-sized power transmission units.

[0027] The end cap of this invention has a built-in quick-release oil passage and quick-release valve core, which, together with the gear and the axial oil passage on the end cap with a radial height higher than the outer diameter of the working oil chamber, allows the spring to reset and push the valve core to quickly switch the oil passage during disengagement. The oil stored in the working oil chamber is quickly emptied through the inclined oil passage under the dual action of centrifugal force and reset spring, avoiding friction plate burns or damage caused by disengagement delay under high speed and high load conditions, and improving the service life and operational reliability of the clutch.

[0028] When the clutch needs to be engaged, the working oil enters the annular groove on the end cover through the radial oil hole on the input shaft, flows through the annular groove into the radial oil hole on the end cover (piston radial oil passage I), presses the quick release valve core, and the working oil enters the axial hole of the gear (gear axial oil passage I), flows through the axial hole and the inclined oil hole (gear inclined oil passage) into the working oil chamber. The working oil pushes the piston to press the friction element (friction plate assembly) on the friction plate seat, realizing the engagement of the friction clutch;

[0029] When the clutch is disengaged, the working oil stops being supplied to the radial oil hole on the input shaft. The quick-release valve core quickly returns to its original position under the action of the spring, and the oil circuit connection changes. The oil stored in the working oil chamber is quickly discharged through the oil draining passage on the gear and end cover under the action of centrifugal force and piston return spring, thereby realizing the rapid disengagement of the friction clutch. Attached Figure Description

[0030] Figure 1 This is a cross-sectional structural diagram of the working cylinder of the friction clutch;

[0031] Figure 2 This is a cross-sectional view of the friction clutch working cylinder AA.

[0032] Figure 3 This is a schematic diagram of the working oil path in the cylinder cross section when the working oil of the friction clutch is supplied;

[0033] Figure 4 This is a schematic diagram of the working oil path in the cross section of cylinder BB when the working oil of the friction clutch is supplied;

[0034] Figure 5 This is a schematic diagram of the working oil path in the cylinder cross section when the working oil of the friction clutch is leaking;

[0035] Figure 6 This is a schematic diagram of the working oil path in the CC section of the oil cylinder when the working oil of the friction clutch is leaking;

[0036] Figure 7 yes Figure 1 A magnified view of part M in the image;

[0037] Figure 8 yes Figure 2 A magnified view of part H in the image;

[0038] In the diagram: Input shaft 10, input shaft working oil passage 101, end cover 20, annular groove 201, piston radial oil passage I 202, piston axial oil passage III 203, piston axial oil passage II 204, piston axial oil passage I 205, piston drain oil passage 206, piston radial oil passage II 207, quick-release valve core 30, spring 310, cover plate 40, connecting groove 401, gear 50, gear axial oil passage I 501, gear axial oil passage II 502, gear tilting oil passage 503, working oil chamber 504, piston 60, return spring 610, friction plate assembly 70, friction plate seat 80, output gear ring 90. Detailed Implementation

[0039] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments will be clearly and completely described below with reference to the accompanying drawings. The following embodiments are used to illustrate the present invention, but are not intended to limit the scope of the present invention. Specific implementation method one:

[0041] Combination Figure 1 and Figure 2 This embodiment describes a highly integrated friction clutch cylinder structure. Figure 1 , Figure 2 The upper part is the section where the hydraulic cylinder is not supplied with working oil. Figure 1 , Figure 2 The lower part is where the hydraulic cylinder is supplied with working oil.

[0042] Figure 1 The middle end cover 20, gear 50, and piston 60 are arranged axially adjacent to each other and coaxially mounted on the input shaft 10. The end cover 20 and piston 60 are located on both sides of gear 50, and the end cover 20 and gear 50 are rigidly connected by bolts. Gear 50 is rigidly connected to input shaft 10. There is an annular space on the side of gear 50 near piston 60. Piston 60 and gear 50 form a working oil chamber 504. Under the action of working oil, piston 60 can move axially on input shaft 10.

[0043] The input shaft 10 is machined with radial oil holes 101, and the end cover 20 is machined with an annular oil groove 201 and a circumferentially distributed oil hole group. In this embodiment, there are two oil hole groups, but there can also be multiple groups. Each oil hole group includes two radial oil holes, three axial oil holes and one inclined oil hole. The piston radial oil passage I 202 and the piston radial oil passage II 207 are connected through the connecting groove 401 on the cover plate 40. The piston radial oil passage I 202 is connected to the annular groove 201. The piston radial oil passage II 207 is equipped with a quick-release valve core 30 and the oil passage is connected to the piston axial oil passage III 203, the piston axial oil passage II 204, the piston axial oil passage I 205 and the piston drain oil passage 206.

[0044] Figure 1The upper part of the schematic diagram shows the state without oil supply. The quick-release valve core 30 is held in the initial position under the action of the spring 310. The change of the position of the quick-release valve core 30 causes a change in the oil circuit connection, realizing the oil supply and discharge of the working oil chamber 504. The number of oil hole groups on the gear 50 is consistent with the number of oil hole groups on the end cover 20, and a certain correspondence is ensured. Each oil hole group on the gear 50 has 2 axial oil holes and 1 inclined oil hole. The inclined oil hole 503 is connected to the gear axial oil circuit I 501, the gear axial oil circuit II 502, and the outer diameter of the working oil chamber 504. The gear axial oil circuit I 501 of the gear 50 is connected to the piston axial oil circuit I 205 on the end cover 20. The gear axial oil circuit II 502 of the gear 50 is connected to the piston axial oil circuit II 204 on the end cover 20. The gear axial oil circuit II 502 on the gear 50 and the piston axial oil circuit II 204 on the end cover 20 are both higher than the outer diameter of the working oil chamber 504 to facilitate oil discharge when the clutch is disengaged. Specific Implementation Method Two:

[0046] Combination Figure 3 and Figure 4 This embodiment describes a highly integrated friction clutch cylinder structure. During clutch engagement and disengagement, working oil enters the annular groove 201 on the end cover 20 through the input shaft working oil passage 101 on the input shaft 10. It then flows through the annular groove 201 into the piston radial oil passage I 202 on the end cover 20, and through the connecting groove 401 into the piston radial oil passage II 207. The working oil presses against the quick-release valve core 30, changing its position and connecting the piston radial oil passage II 207 with the piston axial oil passage I 205 and the gear axial oil passage I 501. Simultaneously, it blocks the gear axial oil passage II 502 from connecting with the piston radial oil passage II 207. This allows the working oil to enter the working oil chamber 504 through the gear tilting oil passage 503. The working oil pushes the piston 60 to move axially, pressing the friction plate assembly 70 on the friction plate seat 80, thus transmitting torque from the input shaft 10 to the output gear ring 90. Specific implementation method three:

[0048] Combination Figure 5 and Figure 6 This embodiment describes a highly integrated friction clutch cylinder structure. When the clutch is disengaged, the working oil supply to the input shaft working oil passage 101 on the input shaft 10 stops. At this time, the quick-release valve core 30 returns to its initial position under the action of the spring 310, blocking the piston radial oil passage II 207 from the gear axial oil passage I 501, while simultaneously connecting the gear axial oil passage II 502 with the piston radial oil passage II 207. The oil stored in the working oil chamber 504 is quickly discharged through the inclined oil hole 503, gear axial oil passage II 502, piston axial oil passage II 204, and piston drain passage 206 under the action of centrifugal force and the return spring 610, thereby achieving rapid disengagement of the friction clutch.

[0049] To achieve a lightweight design for the friction clutch, gear 50 is made of steel, while end cap 20 and piston 60 are made of lightweight materials such as aluminum. Specific implementation method four:

[0051] Combination Figure 1 — Figure 8 This embodiment describes a highly integrated friction clutch cylinder structure.

[0052] This structure enables the friction clutch to be arranged in a limited space and to disengage quickly at high speeds.

[0053] The working cylinder is mainly composed of end cover 20, gear 50 and piston 60. End cover 20, gear 50 and piston 60 are arranged axially adjacent to each other and coaxially mounted on input shaft 10. End cover 20 and piston 60 are located on both sides of gear 50. Gear 50 has an annular space on the side close to piston 60. Piston 60 and gear 50 form a working oil chamber 504. End cover 20 is provided with a quick-release oil passage.

[0054] The input shaft working oil passage 101 on the input shaft 10 is opened on the side of the end cover 20. The end cover 20, gear 50 and piston 60 are provided with a through working oil passage. When the clutch is engaged or disengaged, the working oil enters from the input shaft working oil passage 101, passes through the working oil passages on the end cover 20, gear 50 and piston 60 and enters the working oil chamber 504. The oil passage is switched by changing the position of the fast release valve core 30 on the oil passage of the end cover 20.

[0055] The input shaft working oil passage 101 is radially supplied with oil. The radial oil supply hole 101 of the input shaft 10 corresponds to the oil collecting ring groove 201 on the end cover 20. The oil collecting ring groove 201 is connected to the radial oil passage (piston radial oil passage I 202) opened on the end cover 20. The radial oil passage on the end cover 20 is connected to the axial working oil passage (piston axial oil passage I 205) on the end cover 20. The axial oil passage on the end cover 20 is connected to the axial oil passage (gear axial oil passage I 501) on the gear 50. The axial oil passage on the gear 50 is connected to the inclined oil passage (gear inclined oil passage 503) on the gear 50. The inclined oil passage on the gear 50 is connected to the working oil chamber 504.

[0056] The number of oil hole groups on gear 50 is the same as that on end cover 20, and a certain correspondence is ensured. Each oil hole group on gear 50 has two axial oil holes (gear axial oil passage I 501, gear axial oil passage II 502) and an inclined oil hole (gear inclined oil passage 503). The inclined oil hole and the axial oil hole are connected to the outer diameter of the working oil chamber 504. The axial oil holes of gear 50 are respectively connected to the axial oil holes on end cover 20. The radial direction of the axial holes on gear 50 and the axial holes on end cover 20 is higher than the outer diameter of the working oil chamber 504. Specific implementation method five:

[0058] Combination Figure 1 — Figure 8 This embodiment describes a highly integrated friction clutch cylinder structure.

[0059] The end cover 20, gear 50, and piston 60 are arranged axially adjacent to each other and coaxially mounted on the input shaft 10. The end cover 20 and piston 60 are located on both sides of gear 50, and the end cover 20 and gear 50 are rigidly connected by bolts. Gear 50 is rigidly connected to input shaft 10. There is an annular space on the side of gear 50 near piston 60. Piston 60 and gear 50 form a working oil chamber 504. Under the action of working oil, piston 60 can move axially on input shaft 10. The input shaft 10 is machined with radial oil holes 101, and the end cover 20 is machined with an annular oil groove 201 and a group of oil holes evenly distributed around the circumference. Each group of oil holes includes two radial oil holes (piston radial oil passage I 202, piston radial oil passage II 207), three axial oil holes (piston axial oil passage I 205, piston axial oil passage II 204, piston axial oil passage III 203) and one inclined drain hole (piston drain passage 206). The two radial oil holes are connected by a groove (connecting groove 401) on the pressure cover 40. One radial oil hole (piston radial oil passage I 202) is connected to the annular groove 201, and the other radial oil passage (piston radial oil passage II 207) is equipped with a quick-release valve core 30 and connected to the three axial oil holes and the one inclined drain hole. By changing the position of the quick-release valve core 30, the oil passage connection relationship is changed, thereby realizing the oil supply and oil discharge of the working oil chamber 504.

[0060] The number of oil hole groups on gear 50 is the same as that on end cover 20, and a certain correspondence is ensured. Each oil hole group on gear 50 has two axial oil holes (gear axial oil passage I 501, gear axial oil passage II 502) and an inclined oil hole (gear inclined oil passage 503). The inclined oil hole and the axial oil hole are connected to the outer diameter of the working oil chamber 504. The axial oil holes of gear 50 are respectively connected to the axial oil holes on end cover 20. The radial direction of the axial holes on gear 50 and the axial holes on end cover 20 is higher than the outer diameter of the working oil chamber 504.

[0061] When the clutch needs to be engaged, the working oil enters the annular groove 201 on the end cover 20 through the radial oil hole 101 on the input shaft 10, flows through the annular groove 201 and enters the radial oil hole (piston radial oil passage I 202) on the end cover 20, presses the quick release valve core 30, and the working oil enters the axial hole (gear axial oil passage I 501) of the gear 50, flows through the axial hole and the inclined oil hole (gear inclined oil passage 503) and enters the working oil chamber 504. The working oil pushes the piston 60 to press the friction element (friction plate group 70) on the friction plate seat 80, realizing the engagement of the friction clutch;

[0062] When the clutch needs to be disengaged, the working oil stops being supplied to the radial oil hole 101 on the input shaft 10, and the position of the quick release valve core 30 is quickly restored under the action of the spring 310. The oil circuit connection changes, and the oil stored in the working oil chamber 504 is quickly emptied through the oil draining passage on the gear 50 and the end cover 20 under the action of centrifugal force and piston return spring 610, so as to realize the rapid disengagement of the friction clutch.

[0063] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention in any way. Although the present invention has been disclosed above with reference to preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art can make some modifications or alterations to the above-disclosed technical content to create equivalent embodiments without departing from the scope of the present invention. Any simple modifications, equivalent substitutions, and improvements made to the above embodiments without departing from the scope of the present invention, based on the technical essence of the present invention and within the spirit and principles of the present invention, shall still fall within the protection scope of the present invention.

Claims

1. A highly integrated friction clutch cylinder structure, characterized in that, It includes an input shaft (10), an end cap (20), a gear (50), a piston (60), a quick-release valve core (30), and a return spring (610). The end cap (20), gear (50), and piston (60) are arranged adjacent to each other along the axial direction and coaxially mounted on the input shaft (10). The end cap (20) and piston (60) are located on both sides of the gear (50), the end cap (20) and gear (50) are rigidly connected, and the gear (50) and input shaft (10) are rigidly fixed. The gear (50) has an annular space on the side near the piston (60). The piston (60) and the annular space enclose the working oil chamber (504). The piston (60) can move axially on the input shaft (10). The end cover (20) has a quick-release oil passage and an installation cavity for the quick-release valve core (30). The reset spring (610) is located between the piston (60) and the friction plate seat (80) to realize the limited space arrangement of the friction clutch and the rapid disengagement at high speed.

2. The highly integrated friction clutch cylinder structure according to claim 1, characterized in that, The input shaft (10) has a radially penetrating input shaft working oil passage (101), and the inner sidewall of the end cover (20) has an annular oil groove (201). The input shaft working oil passage (101) and the annular oil groove (201) are radially corresponding and connected to each other, forming an initial oil collection channel for working oil.

3. The highly integrated friction clutch cylinder structure according to claim 1, characterized in that, The end cap (20) is provided with a plurality of oil hole groups evenly distributed around the circumference, and each oil hole group includes piston radial oil passage I (202), piston radial oil passage II (207), piston axial oil passage I (205), piston axial oil passage II (204), piston axial oil passage III (203) and piston drain passage (206). One end of the piston radial oil passage I (202) is connected to the annular oil groove (201), and the other end is connected to the piston radial oil passage II (207) through the connecting groove (401) on the cover plate (40). The quick release valve core (30) is assembled in the piston radial oil passage II (207) and abuts against the spring (310) to form an axially movable oil passage switching structure.

4. The highly integrated friction clutch cylinder structure according to claim 1, characterized in that, The gear (50) is provided with a number of gear oil hole groups that are the same as and correspond to the number of oil hole groups on the end cover (20). Each gear oil hole group includes a gear axial oil passage I (501), a gear axial oil passage II (502), and a gear tilting oil passage (503). The gear axial oil passage I (501) is sealed and connected to the piston axial oil passage I (205) of the end cover (20), the gear axial oil passage II (502) is sealed and connected to the piston axial oil passage II (204) of the end cover (20), one end of the gear tilting oil passage (503) is connected to the gear axial oil passage I (501) and the gear axial oil passage II (502), and the other end extends to the outer diameter of the working oil chamber (504) and is connected to it.

5. The highly integrated friction clutch cylinder structure according to claim 4, characterized in that, The radial opening height of the gear axial oil passage I (501), gear axial oil passage II (502) and the corresponding piston axial oil passage I (205) and piston axial oil passage II (204) on the end cover (20) is higher than the outer diameter of the working oil chamber (504).

6. The highly integrated friction clutch cylinder structure according to claim 1, characterized in that, When the quick-release valve core (30) is in the connected state, the working oil pressure pushes the quick-release valve core (30) to compress the spring (310), so that the piston radial oil passage II (207) is connected to the piston axial oil passage I (205) and the piston axial oil passage II (204) is blocked. When the quick-release valve core (30) is in the disengaged state, the spring (310) resets and pushes the quick-release valve core (30) to connect the piston radial oil passage II (207) with the piston axial oil passage II (204) and block the piston axial oil passage I (205).

7. The highly integrated friction clutch cylinder structure according to claim 2, characterized in that, The gear (50) is made of alloy steel, and the end cap (20) and piston (60) are made of lightweight aluminum.

8. The highly integrated friction clutch cylinder structure according to claim 1, characterized in that, The inner wall of the working oil chamber (504) is provided with a wear-resistant coating, and the outer peripheral wall of the piston (60) is provided with a guide ring. The mating surface between the guide ring and the input shaft (10) adopts a gap sealing structure.

9. The highly integrated friction clutch cylinder structure according to claim 1, characterized in that, The piston drain passage (206) is an inclined oil passage, and the inclination angle of the piston drain passage (206) is set to 30°-60°. The piston drain passage (206) has one end connected to the piston axial oil passage II (204), and the other end passes through the outer peripheral wall of the end cover (20) and faces the return oil chamber of the gearbox.

10. The highly integrated friction clutch cylinder structure according to claim 1, characterized in that, The connection surface between the end cap (20) and the gear (50) is provided with a positioning pin and a sealing gasket. The positioning pin ensures the precise alignment of the oil hole group, and the sealing gasket is made of oil-resistant rubber material to achieve static sealing between the end cap (20) and the gear (50).

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