Integrated cushion seal for an engineering machine cylinder

Abstract

The application discloses an integrated buffer seal engineering machinery oil cylinder and relates to the technical field of oil cylinders, which comprises a cylinder body, a piston and a piston rod, a buffer seal assembly is arranged outside the piston, the buffer seal assembly comprises a buffer column arranged at the front end and two lip-shaped sealing rings, a base is arranged at the bottom of the cylinder body, a buffer groove is formed in the base, and a throttle hole is formed in the base. The integrated design of the buffer and the sealing structure achieves multistage attenuation of impact load, dynamic adjustment of sealing force and self-adaptive control of oil flow, the cylinder hydraulic pressure dynamically adjusts the throttle hole diameter, cooperates with the multistage buffer structure, and reduces the impact pressure; meanwhile, the temperature self-adaptive flow control system can intelligently adjust the flow rate according to the change of the hydraulic oil viscosity, actively enhances the sealing tightness under high-temperature working conditions, effectively inhibits leakage, automatically optimizes the starting parameters in a low-temperature environment, and improves the equipment response speed.

Description

Technical Field

[0001] This invention relates to the field of hydraulic cylinder technology, and more particularly to an integrated buffer seal hydraulic cylinder for engineering machinery. Background Technology

[0002] In the field of engineering machinery, hydraulic cylinders, as power actuators, directly affect the stability and service life of equipment. Traditional hydraulic cylinders generally suffer from the following technical bottlenecks: Insufficient buffering effect: Existing buffering structures mostly rely on a single throttle orifice, which cannot achieve multi-stage damping buffering during high-speed movement. This leads to the piston impacting the cylinder bottom, generating severe vibration and noise, and even causing structural fatigue damage; Poor sealing adaptability: The preload of the lip seal ring is usually fixed and cannot be dynamically adjusted according to changes in piston movement direction or fluctuations in operating conditions, easily leading to seal failure and oil leakage; High maintenance costs: The buffering device and sealing components are set up independently, with a complex structure that is susceptible to the influence of oil impurities. After the throttle orifice becomes blocked or the seals wear out, the entire unit needs to be disassembled for maintenance, which is time-consuming and labor-intensive. Summary of the Invention

[0003] The purpose of this invention is to solve the problem of insufficient buffering and sealing performance in the prior art, and to propose an integrated buffer sealing hydraulic cylinder for engineering machinery.

[0004] To achieve the above objectives, the present invention adopts the following technical solution:

[0005] An integrated buffer seal hydraulic cylinder for engineering machinery includes a cylinder body, a piston, and a piston rod. A buffer sealing assembly is provided on the outer side of the piston. The buffer sealing assembly includes a buffer column at the front end and two lip-shaped sealing rings. A base is provided at the bottom of the cylinder body, and a buffer groove is formed within the base. A throttling orifice is formed on the base. An oil chamber is formed within the cylinder body, and hydraulic oil is contained in the oil chamber. The buffer groove communicates with the oil chamber inside the cylinder body through the throttling orifice. Both lip-shaped sealing rings are connected to the piston through a sealing structure, which maintains a seal between the cylinder and the piston. The base at the bottom of the cylinder body is connected to a flow regulating structure via a spring.

[0006] In the above-mentioned integrated buffer seal hydraulic cylinder for engineering machinery, the end of the buffer column is truncated cone-shaped, the inner wall of the buffer groove is provided with a spiral guide groove, and the throttling orifice is composed of a vertical hole and a horizontal hole, the diameter of the vertical hole and the horizontal hole gradually decreases from the inside to the outside.

[0007] In the above-mentioned integrated buffer seal of the hydraulic cylinder of engineering machinery, the sealing structure includes springs two evenly distributed along the piston circumference, and one end of each spring two is fixedly provided with a sliding plate. The lip-shaped sealing ring is provided with multiple adjustment grooves, and each sliding plate is slidably disposed in the corresponding adjustment groove. The two sets of sealing structures are distributed at intervals.

[0008] In the above-mentioned integrated buffer seal hydraulic cylinder for engineering machinery, multiple springs are provided between the two sides of the two lip-shaped sealing rings and the piston. When the piston moves, the multiple springs on the front side are stretched by force, while the opposite is true on the other side.

[0009] In the aforementioned integrated buffer seal hydraulic cylinder for engineering machinery, a flange is fixedly installed at the open end of the cylinder body, and a steel cover is installed on the flange. One end of the piston rod slides through the cylinder body, the flange, and the steel cover and is fixedly installed with an ear. The ear is mechanically hinged to an external machine via a pin. The flange is used to fix the cylinder body and connect to an external hydraulic pipeline.

[0010] In the above-mentioned integrated buffer seal hydraulic cylinder for engineering machinery, the flow adjustment structure includes a sealing plate fixedly disposed at one end of the spring three, a rotating groove is provided on one side of the sealing plate, and a sealing adjustment ring is slidably disposed on one side of the rotating groove.

[0011] In the above-mentioned integrated buffer seal hydraulic cylinder for engineering machinery, the sealing adjustment ring is provided with a squeezing groove, a limit plate is fixedly installed in the throttling hole, two springs are fixedly installed in the squeezing groove, and the lower ends of the two springs are jointly fixedly installed with a plug, which slides in the squeezing groove. A sealing retaining ring is slidably provided on one side of the sealing adjustment ring. Both the sealing retaining ring and the plug are provided with sliding grooves, and the limit plate is slidably installed in the two sliding grooves.

[0012] In the above-mentioned integrated buffer seal hydraulic cylinder of engineering machinery, a scraper is fixedly provided on one side of the sealing retaining ring, and a counterweight groove is provided on the sealing adjusting ring. The scraper is always slidable in the counterweight groove. A microporous filter plate is provided on the sealing adjusting ring to cooperate with the counterweight groove. The aperture of the microporous filter plate is adjusted so that hydraulic oil with good flowability flows into the counterweight groove.

[0013] In the above-mentioned integrated buffer seal hydraulic cylinder of engineering machinery, the width of the sealing adjustment ring is the same as the diameter of the vertical hole in the throttling orifice. When hydraulic oil enters the counterweight groove, the sealing adjustment ring will rotate under the action of gravity. The sealing retaining ring, the sealing adjustment ring and the sealing plate all slide in the horizontal hole of the throttling orifice.

[0014] In the above-mentioned integrated buffer seal hydraulic cylinder of engineering machinery, the buffer seal assembly, including the buffer column, sealing adjustment ring, spring, and sealing retaining ring, forms a multi-stage damping structure. When the piston rod moves to the end of its stroke, the buffer column first enters the buffer groove at the bottom of the cylinder body, and the oil flow through the throttle orifice gradually decreases. Furthermore, the orifice size is adaptively adjusted according to the piston rod's movement speed and the hydraulic oil temperature.

[0015] Compared with existing technologies, the advantages of this invention are as follows: Through the integrated design of buffer and sealing structures, it achieves multi-stage attenuation of impact loads, dynamic adjustment of sealing force, and adaptive control of oil flow. By dynamically adjusting the throttling orifice diameter through in-cylinder hydraulic pressure, combined with the multi-stage buffer structure, the impact pressure is reduced. At the same time, its temperature-adaptive flow control system can intelligently adjust the flow rate according to changes in hydraulic oil viscosity: actively enhancing sealing tightness under high-temperature conditions to effectively suppress leakage; automatically optimizing starting parameters in low-temperature environments to improve equipment response speed. In addition, the innovative double-spring linkage sealing structure can realize real-time dynamic adjustment of pre-tightening force. Compared with traditional sealing solutions, the amount of oil leakage is significantly reduced, the service life of the seals is extended, and the reliability and durability of the cylinder under complex working conditions are improved. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the structure of an integrated buffer seal hydraulic cylinder for engineering machinery proposed in this invention;

[0017] Figure 2 This is a perspective view of the present invention;

[0018] Figure 3 This is a schematic diagram of the piston structure in this invention;

[0019] Figure 4 In this invention Figure 3 Top view;

[0020] Figure 5 In this invention Figure 4 Cross-sectional view of the structure along the AA direction;

[0021] Figure 6 In this invention Figure 5 Enlarged structural diagram of part a;

[0022] Figure 7 This is a side view of the base in this invention;

[0023] Figure 8 In this invention Figure 7 Cross-sectional view of the structure along the BB direction;

[0024] Figure 9 This is a schematic diagram of the internal structure of the base in this invention;

[0025] Figure 10 In this invention Figure 9 A structural decomposition diagram.

[0026] In the diagram: 1. Cylinder body; 2. Base; 3. Steel cover; 4. Ear ring; 5. Flange; 6. Piston; 7. Piston rod; 8. Buffer column; 9. Lip seal ring; 10. Spring 1; 11. Spring 2; 12. Buffer groove; 13. Throttling orifice; 14. Sealing retaining ring; 15. Spring 3; 16. Sealing adjustment ring; 17. Spring 4; 18. Rotary groove; 19. Limiting plate; 20. Slide groove; 21. Insert; 22. Extrusion groove; 23. Sealing plate; 24. Counterweight groove; 25. Scraper; 26. Microporous filter plate; 27. Adjustment groove. Detailed Implementation

[0027] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0028] Reference Figures 1-3An integrated buffer seal hydraulic cylinder for engineering machinery includes a cylinder body 1, a piston 6, and a piston rod 7. A buffer sealing assembly is provided on the outer side of the piston 6. The buffer sealing assembly includes a buffer column 8 at the front end and two lip-shaped sealing rings 9. The lip-shaped sealing rings 9 are made of gradient hardness polyurethane material (Shore 80A on the inner side and Shore 95A on the outer side). The inner soft layer adapts to the slight wobble of the piston 6 (allowing radial runout ±0.03mm), while the outer hard layer resists the erosion of high-pressure oil (pressure resistance 35MPa). Compared with traditional nitrile rubber seals, the wear rate is reduced by 50%. A base 2 is provided at the bottom of the cylinder body 1, and a buffer groove 12 is formed inside the base 2. The end of the buffer column 8 is frustoconical. The inner wall of the buffer groove 12 is provided with a spiral guide groove. The spiral guide groove guides the oil to move in a spiral motion along the groove. The oil forms three-dimensional turbulence in the spiral guide groove, consuming kinetic energy through intermolecular friction and shearing action with the groove wall, further reducing the speed of the piston 6, while suppressing noise generated by oil cavitation. When the piston rod 7 moves too fast (e.g., >1.5m / s), the throttle orifice 13 is composed of a vertical hole and a horizontal hole. The diameter of the vertical hole and the horizontal hole gradually decreases from the inside to the outside (the inside is the part connected to the oil chamber of the cylinder body 1). A flange 5 is fixedly installed at the open end of the cylinder body 1. One end of the piston rod 7 slides through the cylinder body 1, the flange 5, and the steel cover 3 and is fixedly installed with an ear ring 4. The flange 5 is fixedly connected to the steel cover 3 by bolts. A cleaning filter plate (arranged in a ring) is installed inside the steel cover 3 to prevent external dust from entering the inside of the cylinder body 1. The steel cover 3 can be disassembled separately, and the cleaning filter plate can be replaced without disassembling the entire cylinder 1, which shortens maintenance time and reduces downtime costs. At the same time, the steel cover 3 ensures the structural strength of the open end of the cylinder body 1 and provides an installation reference for the piston rod 7 and the ear ring 4. The ear ring 4 is hinged to the external machinery through a pin to ensure the stable transmission of external mechanical loads. The flange 5 is used to fix the cylinder body 1 and connect to the hydraulic pipeline.

[0029] Reference Figures 4-10 The base 2 has a throttle hole 13, and the cylinder 1 has an oil chamber containing hydraulic oil. The buffer groove 12 is connected to the oil chamber inside the cylinder 1 through the throttle hole 13. Both lip seal rings 9 are connected to the piston 6 through a sealing structure. The sealing structure is used to maintain the seal between the oil cylinder and the piston 6. The sealing structure includes springs 11 evenly distributed around the piston 6. One end of each spring 11 is fixedly provided with a sliding plate. Multiple adjustment grooves 27 are provided on the lip seal rings 9, and each sliding plate is slidably set in the corresponding adjustment groove 27. The two sets of sealing structures are spaced apart. Multiple springs 10 are provided between the two sides of the lip seal rings 9 and the piston 6.

[0030] When piston 6 moves, the multiple springs 10 on the front side are stretched, while the opposite occurs on the other side. Multiple springs 10 are also installed between the piston 6 and both sides of the two lip seal rings 9. When piston 6 moves, the multiple springs 10 on the front side are stretched, while the opposite occurs on the other side. When piston 6 is stationary, springs 10 provide initial preload, ensuring the lip seal rings 9 adhere to the inner wall of cylinder 1 with constant pressure, preventing static leakage. When piston 6 moves to one side, the springs 10 on the front side of the movement are stretched, while those on the rear side are compressed. The deformation of the springs 10 forcibly adjusts the contact pressure of the lip seal rings 9. When piston 6 moves to the right, the right-side spring 10 is stretched by 2-3 mm, increasing the preload by 20%, and the contact pressure of the right-side lip seal ring 9 increases to 0.9-1.0 MPa; the left-side spring 10 is compressed by 2-3 mm, decreasing the preload by 10%, and the contact pressure of the left-side lip seal ring 9 remains at 0.4-0.5 MPa, preventing excessive wear. After the lip seal ring 9 wears (e.g., the lip thickness is reduced by 0.2mm), the elastic restoring force of the second spring 11 can push the lip seal ring 9 to continuously adhere to the inner wall of the cylinder 1, realizing automatic compensation for wear (compensation stroke 2-3mm), extending the life of the lip seal ring 9 to more than 8000 hours (the life of the traditional structure is 4000 hours): by the linkage between the fixed spring 10 providing the basic force and the sliding spring 11 compensating for the deviation, it is coupled in real time with parameters such as the piston 6 movement direction, oil characteristics, and impact load, realizing an adaptive sealing solution without the need for electronic control components or sensors, significantly improving the reliability of the cylinder 1 under complex working conditions; the sliding connection of the second spring 11 allows the lip seal ring 9 to rotate slightly in the circumference after wear, so that the wear is evenly distributed around the circumference of the lip seal ring 9, avoiding local rapid wear through.

[0031] The cylinder body 1 has a base 2 at its bottom. The base 2 is connected to a flow regulating structure via a spring 3 15. The flow regulating structure adjusts the flow rate of hydraulic oil according to the moving speed of the piston rod 7. The flow regulating structure includes a sealing plate 23 fixedly installed at one end of the spring 3 15. A groove 18 is opened on one side of the sealing plate 23, and a sealing adjustment ring 16 is slidably installed on one side of the groove 18. The clearance between the sealing adjustment ring 16 and the groove 18 is 0.03~0.05mm, allowing a small amount of oil lubrication and preventing dry friction from causing jamming. The sealing adjustment ring 16 has an opening on its upper part. The device includes an extrusion groove 22, a limiting plate 19 fixedly installed inside the throttling orifice 13, and two springs 17 fixedly installed inside the extrusion groove 22. A plug 21 is fixedly installed at the lower end of both springs 17 and slides within the extrusion groove 22. The elastic floating plug 21 of the springs 17 can tolerate impurity particles smaller than 0.1mm, preventing slippage and jamming. A sealing retaining ring 14 is slidably installed on one side of the sealing adjusting ring 16. Both the sealing retaining ring 14 and the plug 21 have sliding grooves 20. The limiting plate 19 slides... The system is designed to operate within two sliding grooves 20. A limiting plate 19 restricts the sealing ring 14, sealing adjusting ring 16, and sealing plate 23 to slide only within the throttling orifice 13. A scraper 25 is fixedly mounted on one side of the sealing ring 14. A counterweight groove 24 is provided on the sealing adjusting ring 16. When the buffer column 8 is inserted into the buffer groove 12, the flow rate surges. The spiral guide groove automatically limits the upper limit of the flow rate through turbulence. Simultaneously, the sealing adjusting ring 16 rotates according to the oil weight in the counterweight groove 24, further reducing the orifice diameter and preventing system pressure overload. The scraper 25 always slides within the counterweight groove 24. A microporous filter plate 26, used in conjunction with the counterweight groove 24, is provided on the sealing adjustment ring 16. Adjusting the aperture of the microporous filter plate 26 allows hydraulic oil of suitable flowability to flow into the counterweight groove 24. The width of the sealing adjustment ring 16 and the sealing retaining ring 14 is the same as the diameter of the vertical hole in the throttle orifice 13. When hydraulic oil enters the counterweight groove 24, the sealing adjustment ring 16 rotates. The sealing retaining ring 14, the sealing adjustment ring 16, and the sealing plate 23 all slide within the horizontal hole of the throttle orifice 13. The buffer column 8, the sealing adjustment ring 16, the spring 10, and the sealing retaining ring 14 of the buffer sealing assembly form a multi-stage damping structure. When the piston rod 7 moves to the end of its stroke, the buffer column 8 first enters the buffer groove 12 at the bottom of the cylinder 1. The oil flow through the throttle orifice 13 gradually decreases, and the aperture size of the throttle orifice 13 is adaptively adjusted according to the speed of the piston rod 7 and the temperature of the hydraulic oil.

[0032] In the initial state, the sealing plate 23 partially obstructs the throttling orifice 13, resulting in a small diameter (e.g., 0.8–1 mm). This small-orifice throttling effect limits the initial flow rate, preventing the piston 6 from "creeping" or impacting due to excessive flow velocity at startup. As the internal pressure gradually increases, the hydraulic oil pushes the sealing plate 23 to compress the spring 15. The sealing plate 23 then moves the sealing adjusting ring 16 below the vertical hole of the throttling orifice 13. The "notch" formed on the sealing adjusting ring 16 connects with the vertical hole of the throttling orifice 13, and the diameter of the throttling orifice 13 increases linearly with the pressure (e.g., 1–3 mm). By increasing the flow area, the flow rate is proportionally increased, ensuring that the piston 6 maintains a stable speed (speed fluctuation ≤ ±5%) within its normal working stroke. When the hydraulic pressure exceeds a threshold (the specific threshold depends on the installation environment and the size of the cylinder 1), the sealing plate 23 moves the sealing retaining ring 14 below the vertical hole of the throttling orifice 13 via the sealing adjustment ring 16. At this time, the diameter of the throttling orifice 13 decreases (e.g., from 3mm to 1.5mm). Utilizing the variable cross-section throttling to generate nonlinear damping force, the piston 6 is forced to reduce speed near the end of its stroke, achieving buffer braking (end speed ≤ 0.1m / s). In the low-pressure or medium-pressure stage: the larger diameter of the throttling orifice 13 allows for rapid oil flow, meeting the rapid operation requirements of construction machinery (e.g., rapid extension of the excavator bucket); in the high-pressure stage: the smaller diameter of the throttling orifice 13 forces the establishment of back pressure, which, together with the buffer column 8 and the spiral guide groove, forms a composite buffer of turbulent energy dissipation and viscous damping, effectively protecting the cylinder 1 and external machinery.

[0033] When the temperature of the hydraulic oil in cylinder 1 rises, its viscosity decreases. The microporous filter plate 26 is designed to filter only the more viscous hydraulic oil. When the hydraulic oil viscosity is lower, it passes through the microporous filter plate 26 and enters the counterweight groove 24. The higher the temperature and the lower the viscosity, the more oil flows into the counterweight groove 24. The increase in hydraulic oil in the counterweight groove 24 causes the normally balanced sealing adjustment ring 16 to rotate. This rotation of the sealing adjustment ring 16 blocks the throttle orifice 13. The more oil flows into the counterweight groove 24, the greater the rotation angle of the sealing adjustment ring 16, and the more severe the blockage of the throttle orifice 13, until it reaches the maximum blockage position. This design avoids the traditional "all-or-nothing" blockage mode of a fixed throttle orifice 13, achieving steplessly adjustable flow damping. Meanwhile, the bottom of the counterweight groove 24 is equipped with an inclined bottom plate. When the viscosity of the hydraulic oil increases relatively, the amount of hydraulic oil entering the counterweight groove 24 decreases. At this time, when the combined elastic force of the four springs 17 is greater than the gravitational torque of the oil in the counterweight groove 24, it drives the sealing adjustment ring 16 to rotate. When the sealing adjustment ring 16 starts to rotate, the oil is quickly discharged along the inclined surface due to gravity. The scraper 25 scrapes the bottom of the counterweight groove 24 to improve the discharge speed. After the viscosity recovers, the sealing adjustment ring 16 resets and the throttle orifice 13 is fully opened to avoid excessive starting resistance caused by high viscosity. Under high temperature conditions, the throttle orifice 13 is blocked, causing the piston 6 to start to decelerate before the end of its stroke. The buffer column 8 achieves dual braking of "pre-buffering and end-buffering" to reduce impact pressure.

[0034] To further clarify, the aforementioned fixed connection should be interpreted broadly unless otherwise explicitly specified and limited. For example, it may be welding, gluing, or integral molding, or other conventional methods well known to those skilled in the art.

[0035] The above description is only a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. An integrated cushion seal construction machine oil cylinder comprising a cylinder body (1), a piston (6) and a piston rod (7), characterized in that, The piston (6) is provided with a buffer sealing assembly outside, which comprises a buffer column (8) arranged at the front end and two lip-shaped sealing rings (9), the bottom of the cylinder body (1) is provided with a base (2), the buffer groove (12) is arranged in the base (2), the throttle hole (13) is arranged on the base (2), the oil cavity is arranged in the cylinder body (1), the hydraulic oil is arranged in the oil cavity, and the buffer groove (12) is communicated with the oil cavity in the cylinder body (1) through the throttle hole (13); the two lip-shaped sealing rings (9) are connected with the piston (6) through sealing structures, and the sealing structures are used for maintaining the sealing between the oil cylinder and the piston (6); the bottom of the cylinder body (1) is provided with the base (2), and the base (2) is connected with the flow adjusting structure through the spring three (15). The end of the buffer column (8) is in the shape of a truncated cone, the inner wall of the buffer groove (12) is provided with a spiral guide groove, and the throttle hole (13) is composed of a vertical hole and a horizontal hole, and the diameters of the vertical hole and the horizontal hole gradually decrease from the inside to the outside. The sealing structure comprises a plurality of spring twos (11) uniformly distributed in the circumferential direction of the piston (6), one end of each of the plurality of spring twos (11) is fixedly provided with a sliding plate, a plurality of adjusting grooves (27) are arranged on the lip-shaped sealing ring (9), each sliding plate is slidingly arranged in the corresponding adjusting groove (27), and the two groups of sealing structures are distributed at intervals. The flow adjusting structure comprises a sealing plate (23) fixedly arranged at one end of the spring three (15), one side of the sealing plate (23) is provided with a rotating groove (18), and one side of the rotating groove (18) is slidingly provided with a sealing adjusting ring (16). The sealing adjusting ring (16) is provided with an extrusion groove (22), the throttle hole (13) is fixedly provided with a limiting plate (19), two spring fours (17) are fixedly arranged in the extrusion groove (22), the lower ends of the two spring fours (17) are fixedly connected with an insert (21), the insert (21) is slidingly arranged in the extrusion groove (22), one side of the sealing adjusting ring (16) is slidingly provided with a sealing blocking ring (14), the sealing blocking ring (14) and the insert (21) are both provided with sliding grooves (20), and the limiting plate (19) is slidingly arranged in the two sliding grooves (20).

2. An integrated cushion seal construction for an engineering machinery cylinder according to claim 1, characterised in that, A plurality of spring ones (10) are arranged between the two sides of the two lip-shaped sealing rings (9) and the piston (6), when the piston (6) moves, the plurality of spring ones (10) on the front side are stretched under the action of force, and the other side is opposite.

3. An integrated cushion seal construction for an engineering machinery cylinder as claimed in claim 1, characterised in that, The open end of the cylinder body (1) is fixedly provided with a flange (5), the flange (5) is provided with a steel cover (3), one end of the piston rod (7) is slidingly arranged through the cylinder body (1), the flange (5) and the steel cover (3) and is fixedly provided with an earring (4), the earring (4) is hingedly connected with an external machine through a pin shaft, and the flange (5) is used for fixing the cylinder body (1) and is connected with an external hydraulic pipeline.

4. An integrated cushion seal construction for an engineering machinery cylinder as claimed in claim 1, characterised in that, One side of the sealing baffle ring (14) is fixedly provided with a scraper (25), the sealing adjusting ring (16) is provided with a counterweight groove (24), the scraper (25) is always used in sliding in the counterweight groove (24), the sealing adjusting ring (16) is provided with a microporous filter plate (26) used in cooperation with the counterweight groove (24), the aperture of the microporous filter plate (26) is adjusted, so that the hydraulic oil meeting the flowability flows into the counterweight groove (24).

5. An integrated cushion seal construction for an engineering machinery cylinder as claimed in claim 4, characterised in that, The width of the sealing adjusting ring (16) is the same as the diameter of the vertical hole in the throttle hole (13), when the hydraulic oil enters the counterweight groove (24), the sealing adjusting ring (16) will rotate under the action of gravity, the sealing baffle ring (14), the sealing adjusting ring (16) and the sealing plate (23) all slide in the horizontal hole of the throttle hole (13).

6. An integrated cushion seal construction for an engineering machinery cylinder according to claim 5, characterised in that, The buffer column (8), the sealing adjusting ring (16), the spring one (10) and the sealing baffle ring (14) of the buffer sealing assembly form a multi-stage damping structure, when the piston rod (7) moves to the end of stroke, the buffer column (8) first enters the buffer groove (12) at the bottom of the cylinder body (1), the oil flow through the throttle hole (13) is gradually reduced, and the aperture size of the throttle hole (13) is adaptively adjusted with the movement speed of the piston rod (7) and the temperature of the hydraulic oil.

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