Multi-stage cushion cylinder for liquid-gas separation

Abstract

The application relates to the technical field of hydraulic cylinders, in particular to a multi-stage buffer oil cylinder with liquid-gas separation, which comprises a cylinder barrel and a piston rod, the piston rod is inserted into the cylinder barrel, the piston rod is hollow, a floating piston is arranged in the piston rod and slides along the axial direction of the cylinder barrel, and the side, away from the bottom of the cylinder barrel, of the floating piston is a second air cavity; the piston is connected to one end of the piston rod inserted into the cylinder barrel; a one-way valve assembly is arranged at one end of the piston, facing the inside of the piston rod, along the axial direction of the cylinder barrel through a sliding block, a valve port is arranged on the one-way valve assembly, and a throttling gap is arranged between the one-way valve assembly and the piston. The application is composed of a one-way valve, a sliding block and a floating piston to form multi-stage buffering, so that the impact energy can be absorbed when the piston rod is compressed and reset, the longitudinal impact and vibration problems caused by the mutual collision between vehicles during the operation of the train due to the change of the locomotive traction force or during the starting, braking and shunting operations can be greatly slowed down and dissipated, and the stability and safety of the train operation can be improved.

Description

Technical Field

[0001] This application relates to the field of hydraulic cylinder technology, and in particular to a multi-stage buffer cylinder with liquid-gas separation. Background Technology

[0002] With the development of heavy-haul railway transportation and the increase in coupling speed during shunting operations, the longitudinal forces between vehicles have increased dramatically, placing higher demands on the buffer cylinder, which serves as an elastic and damping element between impact masses. In Chinese railway freight trains, the buffer cylinder is a relatively prominent weak link.

[0003] Existing buffer cylinders suffer from low capacity and poor reliability, severely hindering the development of railway transportation towards high speed and heavy load. The continuous improvement in train speed and quality makes it difficult for existing buffers to meet operational requirements, leading to a decline in ride quality and a sharp increase in maintenance costs. Therefore, developing new buffers adapted to China's high-speed and heavy-load operations is urgently needed.

[0004] Existing technical solutions: Currently used shock absorbers absorb relatively little impact energy and have a short lifespan. Conventional pneumatic-hydraulic shock absorbers can only be compressed, meaning they can only absorb impact energy under compression. However, during the recovery process, the hydraulic cylinder releases the recovery energy stored in the internal gas spring during the return stroke. This energy is converted back into the kinetic energy of the external object, thus hindering the full dissipation of the external impact's kinetic energy. Summary of the Invention

[0005] The technical problem to be solved by the present invention is that in the existing gas-liquid damper, during the piston rod recovery process, the oil cylinder releases the recovery energy stored in the internal gas spring during the compression and return stroke, which is restored as the kinetic energy of the external object, which is not conducive to the full dissipation of the kinetic energy of the external impact.

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

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

[0008] A multi-stage buffer cylinder for liquid-gas separation includes,

[0009] Cylinder, and

[0010] A piston rod is inserted into the cylinder. The piston rod is hollow. A floating piston is slidably disposed inside the piston rod along the cylinder axis. The side of the floating piston inside the piston rod away from the bottom of the cylinder is a second air chamber.

[0011] A piston, which is connected to one end of a piston rod inserted into a cylinder.

[0012] A one-way valve assembly is provided, wherein the one-way valve assembly is slidably disposed at one end of the piston facing the piston rod via a slider along the axial direction of the cylinder, 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] The piston and the bottom of the cylinder form a first oil chamber, and the floating piston and the piston and one-way valve assembly form a second oil chamber. The throttling gap can only allow hydraulic oil to flow from the first oil chamber to the second oil chamber, and the valve port can only allow hydraulic oil to flow from the second oil chamber to the first oil chamber.

[0014] Furthermore, the piston is provided with an annular groove, the slider slides along the piston axis and slides in cooperation with the groove, the slider is provided with a damping hole, the damping hole is opposite to the throttling gap, the one-way valve assembly includes a valve cylinder, the open end of the valve cylinder faces the piston and is provided with a first limiting step, the connecting ring is provided with a second limiting step, 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, and a nut is threadedly connected to the groove opening. The nut is located inside the groove, and the bottom of the limiting groove can abut against the nut to limit the sliding stroke of the slider.

[0016] Furthermore, the contact point between the valve cylinder and the piston is configured as an inclined surface, with one end of the inclined surface away from the bottom of the cylinder inclined away from the cylinder axis. 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 are in contact, a first-stage conical seal is formed at the contact point between the valve cylinder and the piston.

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

[0018] Furthermore, the floating piston is provided with an insertion hole 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. Both the first mating surface and the second mating surface are set as inclined surfaces, and the ends of the first mating surface and the second mating surface near the bottom of the cylinder are inclined in a direction away from the cylinder axis.

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

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

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

[0022] Furthermore, an anti-loosening washer is provided between the piston and the piston rod end, and a groove is provided at the end of the piston or piston rod. The anti-loosening washer is provided with a protrusion that matches the groove.

[0023] The beneficial effects of this invention are that it constructs a multi-stage buffer system using 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. The hydraulic oil achieves buffered compression through a first-stage conical seal between the one-way valve, the slider, and the one-way valve. When the piston rod returns to its original position, the second-stage seal between the steel ball in the one-way valve and the valve cylinder, along with the buffer column, achieves throttling buffering of the hydraulic oil during the return process. Furthermore, when the piston rod is compressed, the floating piston inside the piston rod compresses the gas in the second air chamber. During the return process, the second air chamber pushes the floating piston under high pressure, compressing the second oil chamber, thereby consuming the energy stored in the second air chamber and promoting the rapid return of the piston rod. This allows the recovery energy stored in the internal air chamber to act on the inside of the cylinder during the piston rod's return stroke after compression, preventing energy release from acting on external objects.

[0024] This application can significantly reduce and dissipate longitudinal impacts and vibrations caused by changes in locomotive traction or collisions between vehicles during starting, braking, and shunting operations, thereby reducing the damaging effects on the car body structure and loaded cargo, and improving the stability and safety of train operation. Attached Figure Description

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

[0026] Figure 1 This is a schematic diagram of the structure of the multi-stage buffer cylinder for liquid-gas separation in this invention.

[0027] Figure 2 This is a schematic diagram of the anti-loosening gasket in this invention.

[0028] Figure 3 This is a schematic diagram of the installation structure of the retaining ring and the wire snap ring in this invention.

[0029] Figure 4 This is a schematic diagram of the retaining ring in this invention.

[0030] Figure 5 This is a schematic diagram of the steel wire snap ring in this invention.

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

[0032] Figure 7 This is a schematic diagram of the buffer cylinder in the low-impact state in this invention.

[0033] Figure 8 This is a schematic diagram of the buffer cylinder in the present invention under high impact conditions.

[0034] Figure 9 This is a schematic diagram of the buffer cylinder in the restored state in this invention.

[0035] In the diagram: 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 cylinder; 15. Valve core; 16. Spring; 17. Steel ball; 18. Throttling gap; 19. First mating surface; 20. Second mating surface; 21. Insertion hole; 22. Anti-loosening gasket; 23. Protrusion; 24. First limiting step; 25. Second limiting step; 26. Positioning step; 27. Retaining ring; 28. Steel wire snap ring; 29. ​​Positioning groove; 30. Embedded groove; 31. First oil chamber; 32. Second oil chamber; 33. First air chamber; 34. Second air chamber; 35. Inflation valve. Detailed Implementation

[0036] The present invention will now be described in further detail with reference to the accompanying drawings. These drawings are simplified schematic diagrams, illustrating only the basic structure of the invention, and therefore only show the components relevant to the invention.

[0037] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential," etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, features defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0038] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

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

[0040] Piston rod 2 is inserted into cylinder 1. Piston 3 is threadedly connected to one end of piston rod 2 inserted into cylinder 1. Anti-loosening gasket 22 is provided between piston 3 and the end of piston rod 2. Piston rod 2 is hollow. Floating piston 4 is slidably disposed in piston rod 2 along cylinder 1. Guide rings and sealing rings are provided between piston rod 2 and cylinder 1, between piston 3 and cylinder 1, and between floating piston 4 and the inner wall of piston rod 2. Buffer column 5 is threadedly connected to the bottom of cylinder 1. Piston 3 is provided with a through hole for buffer column 5 to be inserted. The through hole penetrates piston 3. The side wall of buffer column 5 is conical.

[0041] It should be noted that, as Figure 2 As shown, the end of the piston rod 2 is provided with a groove, and the anti-loosening washer 22 is provided with a protrusion 23 that matches the groove. Thus, when the anti-loosening washer 22 is placed between the piston rod 2 and the piston 3, it can reduce the possibility of relative rotation between the anti-loosening washer 22 and the piston rod 2.

[0042] Furthermore, such as Figure 3 As shown, a retaining ring 27 and a wire retaining spring 28 are provided near the cylinder opening inside the cylinder 1 to prevent the piston rod 2 from dislodging. 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 engaged 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, the side wall of the positioning groove 29 and the outer side wall of the retaining ring 27 are both provided with a groove 30 for embedding a retaining spring. The wire retaining spring 28 is embedded between the outer side 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 into the outer side wall of the retaining ring 27.

[0043] Reference Figure 6The piston 3 is provided with an annular groove 6, which is coaxial with the piston 3. A slider 8 is slidably arranged in the groove 6 along the axial direction of the piston 3. The outer wall of the slider 8 is sealed with the side wall of the groove 6 by a hole sealing ring 12, and the inner wall of the slider 8 is sealed with the side wall of the groove 6 by a rod sealing ring 11. A limit groove is provided on the outer wall of the slider 8. A nut 7 is threadedly connected to the groove opening of the groove 6. The nut 7 is located in the groove 6. When the slider 8 moves in the groove 6, the bottom of the limit groove abuts against the nut 7, thereby preventing the slider 8 from moving out of the groove 6.

[0044] A connecting ring 9 is integrally connected to the slider 8. The outer wall of the connecting ring 9 is spaced apart from the inner wall of the nut 7. A damping hole 10 is provided on the connecting ring 9, which is radially arranged along the connecting ring 9. A one-way valve assembly 13 is provided on the connecting ring 9. The one-way valve assembly 13 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 14... 4 can move together 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 axially inclined away from 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 against each other, a first-stage conical seal is formed at the abutment between the valve cylinder 14 and the piston 3. The damping hole 10 is opposite to the opening end of the valve cylinder 14.

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

[0046] A floating piston 4 is disposed inside the piston rod 2 and located on the side of the one-way valve assembly 13 away from the piston 3. The floating piston 4 is provided with an insertion hole 21 for the valve cylinder 14 to be inserted. Further, 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 cylinder 14 is inserted into the insertion hole 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 set as inclined surfaces. The ends of the first mating surface 19 and the second mating surface near the bottom of the cylinder 1 are inclined in a direction away from the axis of the cylinder 1.

[0047] The end of the piston rod 2 furthest from the bottom of the cylinder 1 is the top of the piston rod 2, and an air filling valve 35 is provided on the top of the piston rod 2. The piston 3 and the bottom of the cylinder 1 form a first oil chamber 31, and the slider 8, valve cylinder 14, and floating piston 4 form a second oil chamber 32; the slider 8 and piston 3 in the slide groove 6 form a first air chamber 33, and the floating piston 4 and the top of the piston rod 2 form a second air chamber 34.

[0048] The implementation principle of this application is as follows:

[0049] Initial state as Figure 1 As shown: At this time, piston rod 2 is fully extended. The first gas chamber 33 is not pre-filled with any gas; it contains the air used during assembly. Nitrogen gas at a certain pressure is pre-filled into the second gas chamber 34 through the inflation valve 35. The inclined surface on piston 3 cooperates with the inclined surface of valve cylinder 14 to achieve a first-stage conical seal, thus isolating the first oil chamber 31 and the second oil chamber 32. Similarly, the spring 16 of the one-way valve assembly presses against the steel ball to prevent the oil in the first oil chamber 31 from entering the second oil chamber 32, thus achieving a second-stage conical seal.

[0050] Low impact conditions such as Figure 7 As shown: Under low impact, the piston rod 2 compresses little, increasing the pressure in the first oil chamber 31. This causes the one-way valve assembly 13 to close, and the steel ball 17 presses against the valve port. Under the action of hydraulic oil, the oil in the first oil chamber 31 pushes the valve to the right, and the valve cylinder 14 drives the slider 8 to move to the right. At this time, the first-stage conical seal is opened by a gap, and the oil enters the second oil chamber 32 from the first oil chamber 31 through the gap between the valve cylinder 14 and the piston 3 and the throttling orifice. The oil in the second oil chamber 32 increases, pushing the floating piston 4 to the right. At this time, the second air chamber 34 cooperates to perform vacuuming. When the impact force is small, the impact energy is consumed by throttling through the gap, achieving first-stage buffering.

[0051] High impact conditions such as Figure 8 As shown: Under high impact, the piston rod 2 compresses greatly, and the pressure in the first oil chamber 31 increases sharply, causing the check valve assembly to close. Under the action of hydraulic oil, the check valve assembly 13 drives the slider 8 to move to the right until it contacts the end face of the nut 7. The first-stage conical seal is fully opened. In particular, at this time, the buffer column 5 enters the middle hole of the piston 3. The buffer column 5 has a conical surface. The hydraulic oil enters the second oil chamber 32 from the oil chamber 1 through the gap between the buffer column 5 and the piston 3, and then through the first-stage conical annular gap. The oil in the second oil chamber 32 increases, pushing the floating piston 4 to move to the right. 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 the second-stage buffering.

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

[0053] This application utilizes a multi-stage buffer system comprised of a buffer column 5, a one-way valve, a slider 8, and a floating piston 43. When the piston rod 2 is compressed, the hydraulic oil achieves buffer compression and consumes impact energy through a primary conical seal between the valve cylinder 14 and the slider 8. When the piston rod 2 resets, the secondary seal between the steel ball 17 in the one-way valve and the valve cylinder 14, along with the buffer column 5, achieves hydraulic oil throttling and 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. During reset, the second air chamber 34 pushes the floating piston 4 under high pressure, compressing the second oil chamber 32. This consumes the energy stored in the second air chamber 34 and promotes the rapid reset of the piston rod 2. Consequently, the recovery energy stored in the internal air chamber during the return stroke of the piston rod 2 after compression acts on the inside of the cylinder, allowing the cylinder system to absorb more energy, making the buffering more stable, and preventing energy release from impacting external objects. This can significantly reduce and dissipate longitudinal impacts and vibrations caused by changes in locomotive traction or collisions between vehicles during starting, braking, and shunting operations, thereby mitigating damage to the car body structure and loaded cargo, and improving the stability and safety of train operation.

[0054] Furthermore, this application provides sealing rings on both 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, ensuring the normal operation of the slider 8 and the opening and closing of the throttling gap 18 between it and the one-way valve assembly 13; a combination structure of retaining ring 27 and wire snap ring 28 is used between the piston rod 2 and the cylinder 1 to prevent the piston rod 2 from coming off. This combination structure is compact and highly reliable, thereby significantly improving the reliability and service life of the cylinder structure.

[0055] Based on the above-described preferred embodiments of the present invention, and through the foregoing description, those skilled in the art can make various changes and modifications without departing from the inventive concept. The technical scope of this invention is not limited to the contents of the specification, but must be determined by the scope of the claims.

Claims

1. A multi-stage buffer cylinder for liquid-gas separation, characterized in that, include, Cylinder (1), and Piston rod (2), the piston rod (2) is inserted into the cylinder (1), the piston rod (2) is hollow, and a floating piston (4) is slidably arranged in the piston rod (2) along the cylinder (1) axis. The side of the floating piston (4) in the piston rod (2) away from the bottom of the cylinder (1) is a second air chamber (34). Piston (3), the piston (3) is connected to one end of piston rod (2) inserted into cylinder (1); A one-way valve assembly (13) is slidably disposed on one end of the piston (3) facing the piston rod (2) along the axial direction of the cylinder (1) via a slider (8). The one-way valve assembly (13) is provided with a valve port. A throttling gap (18) that can be opened and closed is provided between the one-way valve assembly (13) and the piston (3). A damping hole (10) is provided on the slider (8). The damping hole (10) is opposite to the throttling gap (18). The contact point 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 first-stage conical seal is formed at the contact point between the valve cylinder (14) and the piston (3). The piston (3) forms a first oil chamber (31) between the bottom of the cylinder (1), and the floating piston (4) forms a second oil chamber (32) between the piston (3) and the one-way valve assembly (13). The throttling gap (18) can only allow hydraulic oil to flow from the first oil chamber (31) to the second oil chamber (32), and the valve port can only allow hydraulic oil to flow from the second oil chamber (32) to the first oil chamber (31).

2. The multi-stage buffer cylinder for liquid-gas separation according to claim 1, characterized in that, The piston (3) is provided with an annular groove (6), and the slider (8) slides along the piston (3) axis and slides in cooperation with the groove (6). The one-way valve assembly (13) 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), and the slider (8) is provided with a second limiting step (25). The first limiting step (24) and the second limiting step (25) cooperate with each other.

3. The multi-stage buffer cylinder for liquid-gas separation according to claim 2, characterized in that, The slider (8) has a limiting groove on its outer side wall. A nut (7) is threadedly connected to the opening of the groove (6). The nut (7) is located inside the groove (6). 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 for liquid-gas separation according to claim 2, characterized in that, A sealing ring is provided between the inner wall and outer wall of the slider (8) and the side wall of the groove (6).

5. The multi-stage buffer cylinder for liquid-gas separation according to claim 1, characterized in that, The floating piston (4) is provided with an insertion hole (21) for the valve cylinder (14) to be inserted. The floating piston (4) is provided with a first mating surface (19). The slider (8) is provided with a second mating surface (20). Both the first mating surface (19) and the second mating surface (20) are set as inclined surfaces. The end of the first mating surface (19) and the second mating surface near the bottom of the cylinder (1) is inclined in a direction away from the axis of the cylinder (1).

6. The multi-stage buffer cylinder for liquid-gas separation according to claim 1, characterized in that, The bottom of the cylinder (1) is connected to a buffer column (5), which is inserted into the through hole on the piston (3). The side wall of the buffer column (5) is conical.

7. The multi-stage buffer cylinder for liquid-gas separation according to claim 1, characterized in that, A retaining ring (27) is provided inside the cylinder (1) near the cylinder opening. A positioning step (26) is provided on the piston rod (2). A positioning groove (29) for locking the retaining ring (27) is provided on the inner side 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).

8. The multi-stage buffer cylinder for liquid-gas separation according to claim 7, characterized in that, A wire snap ring (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 snap ring (28) is bent toward the retaining ring (27) and inserted into the outer wall of the retaining ring (27).

9. The multi-stage buffer cylinder for 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 groove is provided at the end of the piston (3) or the piston rod (2). A protrusion (23) adapted to the groove is provided on the anti-loosening washer (22).

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