Multi-stage buffer oil cylinder for liquid-gas separation

Abstract

The invention relates to the technical field of hydraulic cylinders, in particular to a liquid-gas separation multistage buffering oil cylinder which comprises a cylinder barrel and a piston rod, the piston rod is inserted in the cylinder barrel and is hollow, a floating piston is arranged in the piston rod in the axial direction of the cylinder barrel in a sliding mode, and a second gas cavity is formed in the side, away from the bottom of the cylinder barrel, of the floating piston. The piston is connected to the end, inserted into the cylinder barrel, of the piston rod. The one-way valve assembly is slidably arranged at the end, facing the interior of the piston rod, of the piston through a sliding block in the axial direction of the cylinder barrel, a valve port is formed in the one-way valve assembly, and a throttling gap is formed between the one-way valve assembly and the piston. Multi-stage buffering is formed through the one-way valve, the sliding block and the floating piston, when the piston rod is compressed and reset, impact energy is absorbed, the longitudinal impact and vibration problems caused by locomotive traction change or mutual collision between trains during starting, braking and shunting operation in the running process of the train are greatly relieved and dissipated, and the service life of the train is prolonged. Therefore, the stability and the safety of train operation are improved.

Description

Technical Field

[0001] The present application relates to the technical field of hydraulic cylinders, and in particular to a multi-stage buffer cylinder with liquid-gas separation. Background Art

[0002] With the development of heavy-haul railway transportation and the increase in shunting coupling speeds, the longitudinal forces between vehicles have increased dramatically, placing higher demands on the buffer cylinders that act as elastic and damping elements between impact masses. The buffer cylinders are a prominent weak link in China's freight trains.

[0003] The low capacity and poor reliability of existing buffer cylinders have seriously restricted the development of railway transportation towards high speed and heavy load. With the continuous improvement of train speed and quality, the performance of existing buffers is difficult to meet the operational requirements, resulting in a decline in driving quality and a sharp increase in maintenance costs. Therefore, it is urgent to develop new buffers that are suitable for China's high-speed and heavy-load operations.

[0004] Existing technology solutions: Current shock absorbers absorb little impact energy and have a short lifespan. Conventional gas-liquid shock absorbers can only be compressed, absorbing impact energy only under compression. However, during the recovery process, the cylinder releases the recovery energy stored in the internal gas spring during the return stroke after compression. This energy is converted into kinetic energy of the external object, hindering the full dissipation of the external impact kinetic energy. Summary of the Invention

[0005] The technical problem to be solved by the present invention is that in the existing gas-liquid buffer, during the recovery process of the piston rod, the oil cylinder will release the recovery energy stored in the internal gas spring during the return stroke after compression, and convert it into kinetic energy of external objects, which is not conducive to the full dissipation of external impact kinetic energy.

[0006] To this end, the present invention provides a multi-stage buffer cylinder with liquid-gas separation, which can significantly reduce and dissipate the longitudinal impact and vibration problems caused by changes in locomotive traction during train operation or collisions between vehicles during starting, braking and shunting operations, thereby reducing the destructive effects on the vehicle body structure and loaded cargo, and improving the stability and safety of train operation.

[0007] The technical solution adopted by the present invention to solve its technical problem is:

[0008] A multi-stage buffer oil cylinder with liquid-gas separation, comprising:

[0009] cylinder, and

[0010] A piston rod is inserted into the cylinder, the piston rod is hollow, a floating piston is provided in the piston rod and slides along the axial direction of the cylinder, and a side of the floating piston in the piston rod away from the bottom of the cylinder is a second air cavity;

[0011] A piston connected to one end of a piston rod inserted into the cylinder;

[0012] A one-way valve assembly, wherein the one-way valve assembly is arranged at one end of the piston facing the inside of the piston rod by sliding along the axial direction of the cylinder through a slider, the one-way valve assembly is provided with a valve port, and a throttling gap that can be opened and closed is provided between the one-way valve assembly and the piston;

[0013] In which, a first oil chamber is formed between the piston and the bottom of the cylinder, and a second oil chamber is formed between the floating piston, the piston and the one-way valve assembly. The throttling gap can only allow the hydraulic oil to flow from the first oil chamber to the second oil chamber, and the valve port can only allow the hydraulic oil to flow from the second oil chamber to the first oil chamber.

[0014] Furthermore, an annular groove is provided on the piston, and the slider slides along the axial direction of the piston and slides in cooperation with the groove. A damping hole is provided on the slider, and the damping hole is opposite to the throttling gap. The one-way valve assembly includes a valve cylinder, and the open end of the valve cylinder faces the piston and is provided with a first limiting step. A second limiting step is provided on the connecting ring, and the first limiting step and the second limiting step cooperate with each other.

[0015] Furthermore, a limiting groove is provided on the outer side wall of the slider, a nut is threadedly connected to the notch of the sliding groove, the nut is located in the sliding groove, and the bottom of the limiting groove can abut against the nut to limit the sliding stroke of the slider.

[0016] Furthermore, the abutment between the valve cylinder and the piston is set as an inclined surface, and the end of the inclined surface away from the bottom of the cylinder is inclined away from the axial direction of the cylinder. When the valve cylinder and the piston are separated, a throttling gap is formed between the valve cylinder and the piston. When the valve cylinder and the piston abut, a primary conical surface seal is formed at the abutment between the valve cylinder and the piston.

[0017] Furthermore, sealing rings are provided between the inner side wall, the outer side wall of the slider and the side wall of the sliding groove.

[0018] Furthermore, the floating piston is provided with a socket for inserting the valve cylinder, the floating piston is provided with a first mating surface, and the slider is provided with a second mating surface. The first mating surface and the second mating surface are both set as inclined surfaces, and the ends of the first mating surface and the second mating surface close to the bottom of the cylinder are inclined in a direction away from the axis of the cylinder.

[0019] Furthermore, a buffer column is connected to the bottom of the cylinder, the buffer column is plugged into the through hole on the piston, and the side wall of the buffer column is a conical surface.

[0020] Furthermore, a retaining ring is provided near the cylinder mouth, a positioning step is provided on the piston rod, and a positioning groove for clamping the retaining ring is provided on the inner wall of the cylinder. When the piston rod is fully extended, the inner part of the retaining ring end abuts against the positioning step on the piston rod.

[0021] Furthermore, a steel wire clamping spring is embedded between the outer side wall of the retaining ring and the side wall of the positioning groove, and one end of the steel wire clamping spring is bent toward the retaining ring and inserted on the outer side wall of the retaining ring.

[0022] Furthermore, an anti-loosening gasket is provided between the piston and the end of the piston rod, a groove is provided at the end of the piston or the piston rod, and a protrusion adapted to the groove is provided on the anti-loosening gasket.

[0023] The beneficial effect of the present invention is that the present application forms a multi-stage buffer through a buffer column, a one-way valve, a slider, and a floating piston. When the piston rod is compressed, the conical gap between the buffer column and the piston forms a throttling buffer, and the hydraulic oil is sealed at the first conical surface between the one-way valve, the slider and the one-way valve to achieve buffer compression. When the piston rod is reset, the secondary seal between the steel ball and the valve cylinder in the one-way valve and the buffer column achieve throttling buffering of the hydraulic oil during reset. Furthermore, when the piston rod is compressed, the floating piston in the piston rod compresses the gas in the second air cavity. During reset, the second air cavity pushes the floating piston under high pressure to compress the second oil cavity, thereby achieving the consumption of the stored energy in the second air cavity and promoting the rapid reset of the piston rod, so that the recovery energy stored in the internal air cavity during the return stroke after compression of the piston rod acts on the inside of the oil cylinder, thereby avoiding the release of energy to act on external objects.

[0024] This application can significantly reduce and dissipate the longitudinal impact and vibration problems caused by changes in locomotive traction during train operation or collisions between vehicles during starting, braking and shunting operations, thereby reducing the destructive effects on the vehicle structure and loaded cargo, and improving the stability and safety of train operation. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The present invention will be further described below with reference to the accompanying drawings and examples.

[0026] Figure 1 It is a structural schematic diagram of the multi-stage buffer oil cylinder with liquid and gas separation in the present invention.

[0027] Figure 2 It is a structural schematic diagram of the anti-loosening gasket in the present invention.

[0028] Figure 3 It is a schematic diagram of the installation structure of the retaining ring and the steel wire retaining spring in the present invention.

[0029] Figure 4 It is a structural schematic diagram of the retaining ring in the present invention.

[0030] Figure 5 It is a structural schematic diagram of the steel wire retaining spring in the present invention.

[0031] Figure 6 It is a structural schematic diagram of the positional relationship between the slider and the one-way valve assembly in the present invention.

[0032] Figure 7 It is a structural schematic diagram of the buffer oil cylinder in the present invention in a low-impact state.

[0033] Figure 8 It is a structural schematic diagram of the buffer oil cylinder in the present invention under a high impact state.

[0034] Figure 9 It is a structural schematic diagram of the buffer oil cylinder in the present invention in a restored state.

[0035] In the figure: 1. Cylinder; 2. Piston rod; 3. Piston; 4. Floating piston; 5. Buffer column; 6. Slide groove; 7. Nut; 8. Slider; 9. Connecting ring; 10. Damping hole; 11. Rod sealing ring; 12. Hole sealing ring; 13. One-way valve assembly; 14. Valve barrel; 15. Valve core; 16. Spring; 17. Steel ball; 18. Throttling gap; 19. First mating surface; 20. Second mating surface; 21. Socket; 22. Anti-loosening gasket; 23. Protrusion; 24. First limiting step; 25. Second limiting step; 26. Positioning step; 27. Retaining ring; 28. Wire retaining spring; 29. Positioning groove; 30. Embedded groove; 31. First oil chamber; 32. Second oil chamber; 33. First air chamber; 34. Second air chamber; 35. Inflating valve. DETAILED DESCRIPTION

[0036] The present invention will now be described in further detail with reference to the accompanying drawings, which are simplified schematic diagrams that illustrate the basic structure of the present invention in a schematic manner.

[0037] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "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. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, features defined as "first" or "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise specified, "multiple" means two or more.

[0038] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediate medium; and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0039] Reference Figure 1 A multi-stage buffer cylinder with liquid-gas separation includes a cylinder barrel 1, a piston rod 2, a piston 3, and a floating piston 4.

[0040] The piston rod 2 is inserted in the cylinder 1, and the piston 3 is threadedly connected to one end of the piston rod 2 inserted in the cylinder 1. An anti-loosening gasket 22 is arranged between the piston 3 and the end of the piston rod 2. The piston rod 2 is hollow, and the floating piston 4 is arranged in the piston rod 2 for axial sliding along the cylinder 1. Guide rings and sealing rings are provided between the piston rod 2 and the cylinder 1, between the piston 3 and the cylinder 1, and between the floating piston 4 and the inner wall of the piston rod 2. A buffer column 5 is threadedly connected to the bottom of the cylinder 1, and a through hole is provided on the piston 3 for the buffer column 5 to be inserted. The through hole passes through the piston 3, and the side wall of the buffer column 5 is a conical surface.

[0041] It should be noted that if Figure 2 As shown, a slot is provided at the end of the piston rod 2, and a protrusion 23 adapted to the slot is provided on the anti-loosening gasket 22, so that when the anti-loosening gasket 22 is arranged between the piston rod 2 and the piston 3, the possibility of relative rotation between the anti-loosening gasket 22 and the piston rod 2 can be reduced.

[0042] Further, if Figure 3 As shown, a retaining ring 27 and a wire retaining spring 28 are provided near the mouth of the cylinder 1 to prevent the piston rod 2 from falling out. Specifically, a positioning step 26 is provided on the piston rod 2, and a positioning groove 29 is also provided on the inner wall of the cylinder 1. The retaining ring 27 is clamped in the positioning groove 29 on the cylinder 1. When the piston rod 2 is fully extended, the inner part of the end of the retaining ring 27 abuts against the positioning step 26 on the piston rod 2; Figure 4 、 5 As shown, an embedding groove 30 for embedding a retaining spring is provided on the side wall of the positioning groove 29 and the outer wall of the retaining ring 27. The wire retaining spring 28 is embedded between the outer wall of the retaining ring 27 and the side wall of the positioning groove 29. One end of the wire retaining spring 28 is bent toward the retaining ring 27 and inserted on the outer wall of the retaining ring 27.

[0043] Reference Figure 6An annular slide groove 6 is provided on the piston 3, and the slide groove 6 is coaxially arranged with the piston 3. A slider 8 is provided in the slide groove 6 to slide axially along the piston 3. A hole sealing ring 12 is used to seal the outer wall of the slider 8 and the side wall of the slide groove 6, and a rod sealing ring 11 is used to seal the inner wall of the slider 8 and the side wall of the slide groove 6. A limiting groove is provided on the outer wall of the slider 8, and a nut 7 is threadedly connected to the notch of the slide groove 6. The nut 7 is located in the slide groove 6. When the slider 8 moves in the slide groove 6, the bottom of the limiting groove abuts against the nut 7, thereby preventing the slider 8 from moving out of the slide groove 6.

[0044] The slider 8 is integrally connected with a connecting ring 9, the outer side wall of the connecting ring 9 is spaced apart from the inner side wall of the nut 7, a damping hole 10 is provided on the connecting ring 9, and the damping hole 10 is arranged radially along the connecting ring 9. The connecting ring 9 is provided with a one-way valve assembly 13, which includes a valve cylinder 14. The open end of the valve cylinder 14 faces the piston 3 and is provided with a first limiting step 24. A second limiting step 25 is provided on the connecting ring 9. The first limiting step 24 and the second limiting step 25 cooperate with each other so that when the slider 8 moves, the valve cylinder 1 4 can move with the slider 8. It should be noted that the valve cylinder 14 abuts against the end of the piston 3 near the inner ring. The abutment between the valve cylinder 14 and the piston 3 is set as an inclined surface. The end of the inclined surface away from the bottom of the cylinder 1 is inclined away from the axial direction of the cylinder 1. When the valve cylinder 14 and the piston 3 are separated, a throttling gap 18 is formed between the valve cylinder 14 and the piston 3. When the valve cylinder 14 and the piston 3 abut, a primary conical surface seal is formed at the abutment between the valve cylinder 14 and the piston 3. The damping hole 10 is positioned opposite to the open end of the valve cylinder 14.

[0045] A valve port is provided at one end of the valve cylinder 14 away from the piston 3. A valve core 15 and a steel ball 17 are connected to the valve cylinder 14 via a spring 16. When the spring 16 is in a natural state, the steel ball 17 presses against the valve port to form a secondary seal.

[0046] The floating piston 4 is disposed within the piston rod 2, on the side of the one-way valve assembly 13 away from the piston 3. The floating piston 4 is provided with a socket 21 for inserting the valve barrel 14. Furthermore, the floating piston 4 is provided with a first mating surface 19, and the connecting ring 9 is provided with a second mating surface 20. The first mating surface 19 and the second mating surface 20 are parallel to each other. When the valve barrel 14 is inserted into the socket 21, the first mating surface 19 and the second mating surface 20 abut against each other. Both the first mating surface 19 and the second mating surface 20 are configured as inclined surfaces, with the ends of the first mating surface 19 and the second mating surface near the bottom of the cylinder 1 tilted away from the axis of the cylinder 1.

[0047] The end of the piston rod 2, away from the bottom of the cylinder 1, forms the top of the piston rod 2. A charging valve 35 is installed at the top of the piston rod 2. A first oil chamber 31 is formed between the piston 3 and the bottom of the cylinder 1. A second oil chamber 32 is formed between the slider 8, valve cylinder 14, and floating piston 4. A first air chamber 33 is formed within the chute 6 between the slider 8 and the piston 3. A second air chamber 34 is formed between the floating piston 4 and the top of the piston rod 2.

[0048] The implementation principles of this application are:

[0049] The initial state is Figure 1 As shown, at this point, piston rod 2 is fully extended. First air chamber 33 is not pre-charged with any gas, but rather with the air it contains during assembly. Nitrogen is pre-charged to a predetermined pressure in second air chamber 34 via charging valve 35. The inclined surface on piston 3 cooperates with the inclined surface of valve cylinder 14 to achieve a primary conical seal, isolating first oil chamber 31 from second oil chamber 32. Similarly, spring 16 of the one-way valve assembly presses against the steel ball, preventing oil from first oil chamber 31 from entering second oil chamber 32, thus achieving a secondary conical seal.

[0050] Low impact state such as Figure 7 As shown, under low impact, piston rod 2 is compressed minimally, increasing pressure in first oil chamber 31 and closing check valve assembly 13. Steel ball 17 presses against the valve port. Under the action of hydraulic oil, the oil in first oil chamber 31 pushes the valve to the right, and valve cylinder 14 drives slider 8 to the right. At this point, a gap is opened in the primary conical seal, allowing oil from first oil chamber 31 to flow through the gap between valve cylinder 14 and piston 3, and into the secondary oil chamber 32 through the orifice. The increased oil content in secondary oil chamber 32 pushes floating piston 4 to the right, and the secondary air chamber 34 cooperates to evacuate the air. When the impact force is low, the gap throttling dissipates the impact energy, achieving primary cushioning.

[0051] High impact conditions such as Figure 8 As shown: under high impact, the piston rod 2 is greatly compressed, and the pressure in the first oil chamber 31 increases sharply, causing the one-way valve group to close. Under the action of the hydraulic oil, the one-way valve assembly 13 drives the slider 8 to move rightward until it contacts the end face of the nut 7, and the first-level conical surface seal is completely opened. Specially, at this time, the buffer column 5 enters the middle pore of the piston 3. The buffer column 5 has a conical surface. The hydraulic oil flows from the oil chamber 1 through the gap between the buffer column 5 and the piston 3, and then through the first-level conical surface annular gap into the second oil chamber 32. The oil in the second oil chamber 32 increases, pushing the floating piston 4 to move rightward. At this time, the gap between the buffer column 5 and the piston 3, the throttling gap 18, and the damping hole 10 on the slider 8 all generate throttling damping, thereby consuming the impact energy and realizing secondary buffering.

[0052] Recovery status Figure 9As shown: when the impact is over, the compressed second air chamber 34 needs to push the piston rod 2 to extend and return to its original state. At this time, the pressure in the second air chamber 34 is high, pushing the floating piston 4 to move to the left, and the pressure in the second oil chamber 32 increases, pushing the slider 8 and the one-way valve assembly 13 to move to the left. At this time, the first-level conical seal is closed first to achieve sealing, and the steel ball 17 in the valve cylinder 14 is pushed open, and the second-level conical seal is opened. The hydraulic oil flows from the second oil chamber 32, through the valve port of the one-way valve group, and enters the first oil chamber 31, thereby consuming the energy stored in the second air chamber 34 again, achieving three-level buffering, so that the whole process can absorb more energy and make the buffering more stable.

[0053] The present application forms a multi-stage buffer through the buffer column 5, the one-way valve, the slider 8, and the floating piston 43. When the piston rod 2 is compressed, the hydraulic oil is sealed on the first conical surface between the valve cylinder 14 and the slider 8 to achieve buffer compression and consume impact energy. When the piston rod 2 is reset, the secondary seal between the steel ball 17 in the one-way valve and the valve cylinder 14 and the buffer column 5 achieves hydraulic oil throttling buffering during reset. Furthermore, when the piston rod 2 is compressed, the floating piston 4 inside the piston rod 2 compresses the gas in the second air chamber 34. When reset, the second air chamber 34 pushes the floating piston 4 under high pressure, compressing the second oil chamber 32, achieving the consumption of the energy stored in the second air chamber 34 and promoting the rapid reset of the piston rod 2. As a result, when the piston rod 2 returns after compression, the recovery energy stored in the internal air chamber acts on the inside of the oil cylinder, allowing the oil cylinder system to absorb more energy, making the buffering more stable and preventing the release of energy from acting on external objects. This can significantly reduce and dissipate the longitudinal impact and vibration problems caused by changes in locomotive traction during train operation or collisions between vehicles during starting, braking and shunting operations, thereby reducing the destructive effects on the vehicle structure and loaded cargo, and improving the stability and safety of train operation.

[0054] Furthermore, the present application provides sealing rings on the inner and outer sides of the slider 8 to improve the sealing and isolation effect between the second oil chamber 32 and the first air chamber 33, thereby ensuring the normal operation of the slider 8 and the opening and closing of the throttling gap 18 between the slider 8 and the one-way valve assembly 13; a combination structure of a retaining ring 27 and a wire retaining spring 28 is used between the piston rod 2 and the cylinder 1 to prevent the piston rod 2 from falling out. The combination structure is compact and reliable, thereby greatly improving the reliability and service life of the cylinder structure.

[0055] With the above-described preferred embodiments of the present invention as a guide, and with reference to the above description, relevant personnel are fully capable of making various changes and modifications without departing from the technical spirit of this invention. The technical scope of this invention is not limited to the contents of the specification, but must be determined according to the scope of the claims.

Claims

1. A multi-stage buffer cylinder with liquid-gas separation, characterized in that: include, a cylinder (1), and A piston rod (2), the piston rod (2) being inserted into the cylinder (1), the piston rod (2) being hollow, a floating piston (4) being provided in the piston rod (2) so as to slide axially along the cylinder (1), and a second air cavity (34) being formed on the side of the floating piston (4) in the piston rod (2) away from the bottom of the cylinder (1); A piston (3), the piston (3) being connected to one end of the piston rod (2) inserted into the cylinder (1); a one-way valve assembly (13), the one-way valve assembly (13) being arranged at one end of the piston (3) facing the interior of the piston rod (2) via a slider (8) so as to slide along the axial direction of the cylinder (1), the one-way valve assembly (13) being provided with a valve port, and a throttling gap (18) capable of opening and closing being provided between the one-way valve assembly (13) and the piston (3); A first oil chamber (31) is formed between the piston (3) and the bottom of the cylinder (1), and a second oil chamber (32) is formed between the floating piston (4), the piston (3) and the one-way valve assembly (13). The throttling gap (18) only allows the hydraulic oil to flow from the first oil chamber (31) to the second oil chamber (32), and the valve port only allows the hydraulic oil to flow from the second oil chamber (32) to the first oil chamber (31).

2. The multi-stage buffer cylinder with liquid-gas separation according to claim 1 is characterized in that: The piston (3) is provided with an annular groove (6), the slider (8) slides axially along the piston (3) and slides in cooperation with the groove (6), the slider (8) is provided with a damping hole (10), and the damping hole (10) is opposite to the throttling gap (18), the one-way valve assembly (13) includes a valve cylinder (14), the opening end of the valve cylinder (14) faces the piston (3) and is provided with a first limiting step (24), the slider (8) is provided with a second limiting step (25), and the first limiting step (24) and the second limiting step (25) cooperate with each other.

3. The multi-stage buffer cylinder with liquid-gas separation according to claim 2 is characterized in that: A limiting groove is provided on the outer wall of the slider (8), a nut (7) is threadedly connected to the notch of the slide groove (6), the nut (7) is located in the slide groove (6), and the bottom of the limiting groove can abut against the nut (7) to limit the sliding stroke of the slider (8).

4. The multi-stage buffer cylinder with liquid-gas separation according to claim 2, characterized in that: The abutment between the valve cylinder (14) and the piston (3) is set as an inclined surface, and the end of the inclined surface away from the bottom of the cylinder (1) is set axially away from the cylinder (1) and tilted. When the valve cylinder (14) and the piston (3) are separated, a throttling gap (18) is formed between the valve cylinder (14) and the piston (3). When the valve cylinder (14) and the piston (3) are abutted, a primary conical surface seal is formed at the abutment between the valve cylinder (14) and the piston (3).

5. The multi-stage buffer cylinder with liquid-gas separation according to claim 2, characterized in that: Sealing rings are provided between the inner side wall and the outer side wall of the slider (8) and the side wall of the slide groove (6).

6. The multi-stage buffer cylinder with liquid-gas separation according to claim 1, characterized in that: The floating piston (4) is provided with a socket (21) for inserting the valve cylinder (14), the floating piston (4) is provided with a first mating surface (19), and the slider (8) is provided with a second mating surface (20), the first mating surface (19) and the second mating surface (20) are both configured as inclined surfaces, and the ends of the first mating surface (19) and the second mating surface close to the bottom of the cylinder (1) are inclined in a direction away from the axis of the cylinder (1).

7. The multi-stage buffer cylinder with liquid-gas separation according to claim 1, characterized in that: A buffer column (5) is connected to the bottom of the cylinder (1), the buffer column (5) is plugged into a through hole on the piston (3), and the side wall of the buffer column (5) is a conical surface.

8. The multi-stage buffer cylinder with liquid-gas separation according to claim 1, characterized in that: A retaining ring (27) is provided in the cylinder (1) near the cylinder mouth, a positioning step (26) is provided on the piston rod (2), and a positioning groove (29) for clamping the retaining ring (27) is provided on the inner wall of the cylinder (1). When the piston rod (2) is fully extended, the inner part of the end of the retaining ring (27) abuts against the positioning step (26) on the piston rod (2).

9. The multi-stage buffer cylinder with liquid-gas separation according to claim 8, characterized in that: A steel wire spring (28) is embedded between the outer wall of the retaining ring (27) and the side wall of the positioning groove (29), and one end of the steel wire spring (28) is bent toward the retaining ring (27) and inserted into the outer wall of the retaining ring (27).

10. The multi-stage buffer cylinder with liquid-gas separation according to claim 1, characterized in that: An anti-loosening washer (22) is provided between the piston (3) and the end of the piston rod (2); a slot is provided at the end of the piston (3) or the piston rod (2); and a protrusion (23) adapted to the slot is provided on the anti-loosening washer (22).

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