Hydraulic drive type gas supercharger

Abstract

The invention provides a gas supercharger. The gas supercharger comprises a hydraulic cylinder, a first-stage pressure cylinder and a second-stage pressure cylinder, the hydraulic cylinder comprises a hydraulic cylinder barrel and an end cover; the first-stage pressure cylinder and the second-stage pressure cylinder are arranged on the two sides of the hydraulic cylinder correspondingly and connected with the hydraulic cylinder through end covers. The first piston rod and the second piston rod are connected with the hydraulic piston; the first-stage pressurizing cylinder comprises a first-stage pressurizing cylinder barrel and a first-stage pressurizing piston arranged in the first-stage pressurizing cylinder barrel; the second-stage pressurizing cylinder comprises a second-stage pressurizing cylinder barrel and a second-stage pressurizing piston arranged in the second-stage pressurizing cylinder barrel; the first piston rod extends into the first-stage pressurizing cylinder barrel to be connected with the first-stage pressurizing piston, and the second piston rod extends into the second-stage pressurizing cylinder barrel to be connected with the second-stage pressurizing piston; at least one hydraulic suspension cavity is formed in the surface of an inner hole of the end cover and used for storing hydraulic oil with pressure so that the first piston rod or the second piston rod can be suspended in the inner hole of the end cover. According to the gas supercharger provided by the invention, friction heating and friction loss are reduced.

Description

Technical Field

[0001] The present disclosure relates to the technical field of gas supercharging, and in particular to a liquid-driven gas supercharger. Background Art

[0002] A gas booster is a device that compresses low-pressure gas to turn it into high-pressure gas. For example, a hydrogen booster is a device used to compress and boost hydrogen, and is a core component of hydrogen refueling stations and other equipment.

[0003] Liquid-driven gas boosters are hydraulically driven gas boosters. In order to ensure that the gas and hydraulic oil are isolated from each other, a large number of seals are required for sealing. During the high-frequency reciprocating motion of the gas booster, a large amount of heat will be generated, which will affect the service life and sealing effect of the seals, resulting in a high failure rate of the gas booster. Summary of the invention

[0004] An embodiment of the present disclosure provides a liquid-driven gas booster.

[0005] In a first aspect, an embodiment of the present disclosure provides a liquid-driven gas booster, comprising: a hydraulic cylinder, a primary boosting cylinder, and a secondary boosting cylinder; the hydraulic cylinder comprises a hydraulic cylinder barrel and end covers respectively arranged at both ends of the cylinder barrel; the primary boosting cylinder and the secondary boosting cylinder are respectively arranged on both sides of the hydraulic cylinder, and are connected to the hydraulic cylinder through the end covers;

[0006] The hydraulic cylinder further comprises a hydraulic piston, a first piston rod and a second piston rod, wherein the first piston rod and the second piston rod are connected to the hydraulic piston;

[0007] The primary booster cylinder includes a primary booster cylinder barrel and a primary booster piston disposed in the primary booster cylinder barrel; the secondary booster cylinder includes a secondary booster cylinder barrel and a secondary booster piston disposed in the secondary booster cylinder barrel;

[0008] The first piston rod extends into the primary booster cylinder and is connected to the primary booster piston, and the second piston rod extends into the secondary booster cylinder and is connected to the secondary booster piston;

[0009] At least one hydraulic suspension chamber is provided on the inner hole surface of the end cover for storing hydraulic oil under pressure so as to suspend the first piston rod or the second piston rod in the inner hole of the end cover.

[0010] In some embodiments, a plurality of hydraulic suspension chambers are provided on the inner hole surface of the end cover, and the plurality of hydraulic suspension chambers are distributed circumferentially; the end cover is also provided with a hydraulic annular circuit extending circumferentially, and a plurality of pressurizing ports distributed circumferentially, and each pressurizing port corresponds to a hydraulic suspension chamber; the pressurizing port is connected to the hydraulic annular circuit and to the corresponding hydraulic suspension chamber.

[0011] In some embodiments, each of the pressurizing ports is connected to the hydraulic annular circuit via a pressure-pressing channel; a throttling screw plug is provided in the pressure-pressing channel to keep the pressure at each of the pressurizing ports consistent.

[0012] In some embodiments, each of the pressurizing ports corresponds to a pressure detection channel, the pressure detection channel is connected to the pressure-breaking channel, and a pressure sensor is disposed in the pressure detection channel for detecting the pressure in the corresponding hydraulic suspension chamber.

[0013] In some embodiments, the inner holes of the two end covers are respectively loosely matched with the first piston rod and the second piston rod.

[0014] In some embodiments, the end cover includes a hydraulic suspension ring disposed in an inner hole of the end cover, and the hydraulic suspension cavity is disposed on an inner hole surface of the hydraulic suspension ring.

[0015] In some embodiments, the hydraulic suspension ring is gap-matched with the inner hole of the end cover; or the hydraulic suspension ring is formed in the inner hole of the end cover by a surfacing process.

[0016] In some embodiments, an oil storage structure is further provided on the inner hole surface of the hydraulic suspension ring, and the oil storage structure is communicated with the hydraulic suspension cavity.

[0017] In some embodiments, the oil storage structure includes a plurality of parallel oil storage grooves distributed parallel to each other on the inner hole surface of the hydraulic suspension ring.

[0018] In some embodiments, the inner hole of the hydraulic cylinder and the hydraulic piston are gap-sealed by tolerance control.

[0019] In some embodiments, the outer circumferential surface of the hydraulic piston is provided with at least one gap sealing groove, and the gap sealing groove extends in the circumferential direction and is used for storing hydraulic oil.

[0020] In some embodiments, a reverse dust ring is further provided in the inner hole of the end cover away from the hydraulic cylinder barrel, for scraping oil from the first piston rod or the second piston rod in a direction close to the hydraulic cylinder barrel.

[0021] In some embodiments, an oil scraper storage tank is provided in the inner hole of the end cover on the side of the reverse dust ring close to the hydraulic cylinder barrel; an oil drain channel is also provided on the end cover, and the oil scraper storage tank is connected to the oil drain channel.

[0022] In some embodiments, the hydraulic cylinder further comprises a proximity switch for detecting a position of the hydraulic piston.

[0023] In some embodiments, the first-stage booster cylinder and the second-stage booster cylinder include an isolation chamber located on the side of the first-stage booster piston or the second-stage booster piston close to the hydraulic cylinder; the inlet and outlet ports of the isolation chamber are respectively provided with a concentration sensor of the gas to be pressurized, which is used to detect the concentration of the gas to be pressurized in the isolation chamber.

[0024] In some embodiments, cooling water channels are also provided on the outer walls of the primary boost cylinder and the secondary boost cylinder.

[0025] In some embodiments, a spirally extending flow guide is provided on the outer wall of the boost cylinder, and the flow guide separates the cooling water channel on the outer wall of the boost cylinder.

[0026] In some embodiments, the inner hole of the primary booster cylinder is matched with the primary booster piston through a tolerance controlled clearance, the inner hole surface of the primary booster cylinder is covered with a diamond-like coating, and the outer cylindrical surface of the primary booster piston is covered with a PTFE-based composite coating or a nylon-based composite coating;

[0027] The inner hole of the secondary booster cylinder is matched with the secondary booster piston through a tolerance controlled clearance. The inner hole surface of the secondary booster cylinder is covered with a diamond-like coating, and the outer cylindrical surface of the secondary booster piston is covered with a PTFE-based composite coating or a nylon-based composite coating.

[0028] In the liquid-driven gas booster provided in the embodiment of the present disclosure, at least one hydraulic suspension chamber is provided on the inner hole surface of the end cover of the hydraulic cylinder for storing pressurized hydraulic oil, so that the piston rod is suspended in the inner hole of the end cover; at the same time, the hydraulic oil in the hydraulic suspension chamber can also play a sealing role, thereby reducing the use of seals, and in the case of high-frequency and rapid reciprocating motion of the booster piston, frictional heat generation and friction loss can be greatly reduced, which is beneficial to reducing the failure rate of the gas booster, extending the service life of the gas booster, and improving work efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Figure 1 is a cross-sectional view of a liquid-driven gas supercharger in an embodiment of the present disclosure;

[0030] Figure 2 is a cross-sectional view of another liquid-driven gas supercharger in an embodiment of the present disclosure;

[0031] Figure 3 is a schematic diagram of a gap sealing structure in an embodiment of the present disclosure;

[0032] Figure 4 is a schematic diagram of another hydraulic suspension support structure in an embodiment of the present disclosure;

[0033] Figure 5 is a schematic diagram of a hydraulic annular circuit in an end cover in an embodiment of the present disclosure;

[0034] Figure 6 is a cross-sectional view of a liquid-driven hydrogen supercharger in an embodiment of the present disclosure;

[0035] Figure 7 It is a three-dimensional schematic diagram of a liquid-driven hydrogen booster in an embodiment of the present disclosure. DETAILED DESCRIPTION

[0036] In order to enable those skilled in the art to better understand the technical solution of the present disclosure, the technical solution of the present disclosure is described in detail below with reference to the accompanying drawings.

[0037] Example embodiments will be described more fully below with reference to the accompanying drawings, but the example embodiments may be embodied in different forms and should not be construed as limited to the embodiments set forth herein. On the contrary, the purpose of providing these embodiments is to make the present disclosure thorough and complete and to enable those skilled in the art to fully understand the scope of the present disclosure.

[0038] In the absence of conflict, the various embodiments of the present disclosure and the various features therein may be combined with each other.

[0039] As used herein, the term "and / or" includes any and all combinations of one or more of the associated listed items.

[0040] The terms used herein are only used to describe specific embodiments and are not intended to limit the present disclosure. As used herein, the singular forms "a", "an" and "the" are also intended to include the plural forms, unless the context clearly indicates otherwise. It will also be understood that when the terms "comprising" and / or "made of" are used in this specification, the presence of the features, wholes, steps, operations, elements and / or components is specified, but the presence or addition of one or more other features, wholes, steps, operations, elements, components and / or groups thereof is not excluded.

[0041] The embodiments described herein may be described with reference to plan views and / or cross-sectional views by means of idealized schematic diagrams of the present disclosure. Therefore, the example illustrations may be modified according to manufacturing techniques and / or tolerances. Therefore, the embodiments are not limited to the embodiments shown in the accompanying drawings, but include modifications of the configurations formed based on the manufacturing process. Therefore, the regions illustrated in the accompanying drawings have schematic properties, and the shapes of the regions shown in the figures illustrate the specific shapes of the regions of the elements, but are not intended to be limiting.

[0042] Unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by those of ordinary skill in the art. It will also be understood that terms such as those defined in commonly used dictionaries should be interpreted as having a meaning consistent with their meaning in the context of the relevant art and the present disclosure, and will not be interpreted as having an idealized or overly formal meaning unless explicitly defined as such herein.

[0043] Embodiment 1

[0044] Figure 1 It is a schematic diagram of a liquid-driven gas supercharger in an embodiment of the present disclosure.

[0045] like Figure 1 As shown, the liquid-driven gas booster includes: a hydraulic cylinder 1, a primary booster cylinder 2, and a secondary booster cylinder 3; the hydraulic cylinder 1 includes a hydraulic cylinder barrel 11 and end covers 12 respectively arranged at both ends of the cylinder barrel; the primary booster cylinder 2 and the secondary booster cylinder 3 are respectively arranged on both sides of the hydraulic cylinder 1, and are connected to the hydraulic cylinder 1 through the end covers 12. The hydraulic cylinder 1 also includes a hydraulic piston 13, a first piston rod 14, and a second piston rod 15, and the first piston rod 14 and the second piston rod 15 are connected to the hydraulic piston 13; the first-stage booster cylinder 2 includes a first-stage booster cylinder barrel 21 and a first-stage booster piston 22 arranged in the first-stage booster cylinder barrel 21; the second-stage booster cylinder 3 includes a second-stage booster cylinder barrel 31 and a second-stage booster piston 32 arranged in the second-stage booster cylinder barrel 31; the first piston rod 14 extends into the first-stage booster cylinder barrel 21 and is connected to the first-stage booster piston 22, and the second piston rod 15 extends into the second-stage booster cylinder barrel 31 and is connected to the second-stage booster piston 32; at least one hydraulic suspension chamber 4 is provided on the inner hole surface of the end cover 12, which is used to store pressurized hydraulic oil so that the first piston rod 14 or the second piston rod 15 is suspended in the inner hole of the end cover 12.

[0046] In this embodiment, at least one hydraulic suspension chamber is provided on the inner hole surface of the end cover of the hydraulic cylinder for storing pressurized hydraulic oil, so that the piston rod is suspended in the inner hole of the end cover. At the same time, the hydraulic oil in the hydraulic suspension chamber can also play a sealing role, thereby reducing the use of seals. When the booster piston moves back and forth at high frequency and quickly, frictional heat generation and friction loss can be greatly reduced, which is beneficial to reducing the failure rate of the gas booster, extending the service life of the gas booster, and improving work efficiency.

[0047] Embodiment 2

[0048] Figure 2 Schematic diagram of a liquid-driven gas supercharger in this embodiment.

[0049] In this embodiment, the liquid-driven gas supercharger is provided with friction pair A, friction pair B, friction pair C, friction pair D, and friction pair E. Friction pair A adopts a gap sealing design; friction pair D and friction pair E adopt a hydraulic suspension support structure.

[0050] like Figure 2 As shown, the hydraulic cylinder 1 includes a hydraulic cylinder barrel 11 and a hydraulic piston 13, and piston rods 14 and 15 are connected to the hydraulic piston 13; the inner hole of the hydraulic cylinder barrel 11 and the hydraulic piston 13 are gap-sealed by tolerance control to form a friction pair A. By utilizing the gap throttling effect of the hydraulic oil between the inner hole of the hydraulic cylinder barrel 11 and the hydraulic piston 13, the oil pressure in the gap seal can make the hydraulic piston 13 and the hydraulic cylinder barrel 11 move without contact or with short contact. Since the reciprocating frequency of the hydraulic piston 13 in the hydraulic cylinder barrel 11 is very high, the viscosity of the hydraulic oil can form a short-term sealing effect in the gap between the hydraulic piston 13 and the hydraulic cylinder barrel 11, so that the sealing member can be replaced for sealing; at the same time, since the reciprocating frequency of the hydraulic piston 13 in the hydraulic cylinder barrel 11 is very high, the amount of hydraulic oil leakage in one stroke of the hydraulic piston 13 is very small, which basically does not affect the effect of the hydraulic cylinder.

[0051] In some embodiments, Figure 3 As shown, the outer circumferential surface of the hydraulic piston 13 is provided with at least one gap sealing groove 131, which extends circumferentially and is used to store hydraulic oil. Storing hydraulic oil in the gap sealing groove 131 can improve the gap sealing effect and increase lubrication.

[0052] like Figure 2 As shown, the hydraulic cylinder also includes an end cover 12 disposed between the hydraulic cylinder barrel 11 and the boost cylinder barrel 21; at least one hydraulic suspension chamber 4 is disposed on the inner hole surface of the end cover 12. In the embodiment of the present disclosure, a hydraulic suspension chamber 4 extending in the circumferential direction may be disposed on the inner hole surface of the end cover 12, or a plurality of hydraulic suspension chambers 4 may be disposed in the circumferential direction at intervals on the inner hole surface of the end cover 12. The embodiment of the present disclosure does not specifically limit this. In some embodiments, a plurality of hydraulic suspension chambers 4 are disposed on the inner hole surface of the end cover 12, and the plurality of hydraulic suspension chambers 4 are evenly distributed in the circumferential direction. For example, the number of the hydraulic suspension chambers 4 is 4.

[0053] like Figure 2 , Figure 4 As shown, a plurality of hydraulic suspension chambers 4 are provided on the inner hole surface of the end cover 12, and the plurality of hydraulic suspension chambers 4 are distributed along the circumferential direction; Figure 5As shown, the end cover 12 is also provided with a hydraulic annular circuit extending in the circumferential direction and a plurality of pressurizing ports distributed in the circumferential direction, each pressurizing port corresponding to a hydraulic suspension chamber 4 ; the pressurizing port is connected to the hydraulic annular circuit and to the corresponding hydraulic suspension chamber 4 .

[0054] like Figure 5 As shown, the hydraulic annular circuit is connected with the pressure ports W, X, Y, and Z. When pressure is applied from any of the pressure ports, the hydraulic oil can flow to each pressure port through the hydraulic annular circuit, and the hydraulic oil enters and is stored in the hydraulic suspension chamber 4, generating a hydrostatic pressure effect on the piston rods 14 and 15, so that the piston rods 14 and 15 are suspended in the inner hole of the end cover 12, achieving frictionless contact between the piston rods 14 and 15 and the inner hole of the end cover 12, and reducing the friction heat generated between the friction pairs D and E formed by the piston rods 14 and 15 and the inner hole of the end cover 12. After the hydraulic suspension support structure is set, the piston rods 14 and 15 no longer need a guide support ring for guiding support in the inner hole of the end cover 12, thereby further reducing the friction heat generated by the friction pairs D and E. In addition, in the hydraulic suspension support structure, the hydraulic oil in the hydraulic suspension chamber 4 and the hydraulic annular circuit is flowing, which can take away the heat generated by the friction of the friction pairs D and E in time.

[0055] In some embodiments, Figure 5 As shown, each pressurizing port is connected to the hydraulic annular circuit through a pressure channel; a throttling screw plug 6 is provided in the pressure channel.

[0056] The throttling plug is a device that uses its internal adjustable aperture to control the flow resistance of the fluid and thus affect the pressure of the fluid. When the fluid passes through the throttling plug, if the plug is tightened to reduce the aperture, the resistance of the fluid passing through will increase, causing the pressure of the fluid in front of the throttling plug to increase. On the contrary, if the plug is loosened to increase the aperture, the resistance of the fluid passing through will decrease, and the pressure of the fluid in front of the throttling plug will decrease. By changing the aperture size to control the fluid pressure, the throttling plug can maintain the stability of the output pressure within a relatively fixed range.

[0057] The hydraulic oil in the hydraulic annular circuit realizes proportional pressure drop at each pressurizing port through the liquid resistance effect of the throttling screw plug 6, so that the pressure of the hydraulic oil at each pressurizing port, that is, the pressure of the hydraulic oil in each hydraulic suspension chamber, remains consistent, so that the piston rods 14 and 15 can be automatically centered in the inner hole of the end cover 12, ensuring that the piston rods 14 and 15 are in frictionless contact with the inner hole of the end cover 12. In some embodiments, a buffer ring, a spacer ring, and a cylinder piston seal ring are provided in the end cover 12. The automatic centering of the piston rods 14 and 15 can also prevent the buffer ring, the spacer ring, and the cylinder piston seal ring from being subjected to radial eccentric loads caused by the flexibility of the piston rods 14 and 15, and do not bear the lateral force of the hydraulic oil pressure, thereby ensuring that only a small constant residual friction is generated, further reducing friction heat generation.

[0058] In some embodiments, Figure 4 As shown, a pressure detection channel 7 is provided between the throttling screw plug 6 and the hydraulic suspension chamber 4, each pressurizing port corresponds to a pressure detection channel 7, the pressure detection channel 7 is connected to the pressure-breaking channel, and a pressure sensor is provided in the pressure detection channel 7 for detecting the pressure in the corresponding hydraulic suspension chamber 4. In some embodiments, the pressure sensor detects the pressure in the hydraulic suspension chamber 4 in real time and feeds it back to the central hydraulic control system, which controls the electronic regulating valve according to the pressure data to adjust the pressure of the pressure-breaking port, thereby realizing real-time feedback adjustment to ensure that the pressure in the hydraulic suspension chamber 4 remains stable and consistent.

[0059] In some embodiments, Figure 2 , Figure 4 As shown, the end cover 12 includes a hydraulic suspension ring 120 disposed in the inner hole of the end cover 12 , and the hydraulic suspension chamber 4 is disposed on the inner hole surface of the hydraulic suspension ring 120 .

[0060] In some embodiments, the hydraulic suspension ring 120 is clearance-matched with the inner hole of the end cover 12 .

[0061] In some embodiments, the hydraulic suspension ring 120 is formed in the inner hole of the end cover 12 by a cladding process. For example, copper is clad on the inner hole of the end cover 12, and then the hydraulic suspension chamber 4 is processed.

[0062] In some embodiments, an oil storage structure 121 is further provided on the inner surface of the hydraulic suspension ring 120 , and the oil storage structure 121 is connected to the hydraulic suspension chamber 4 . For example, the oil storage structure 121 includes a plurality of parallel oil storage grooves distributed parallel to each other on the inner surface of the hydraulic suspension ring 120 .

[0063] In some embodiments, Figure 4 As shown, a plurality of parallel oil storage tanks are also provided on the inner hole surface of the hydraulic suspension ring 120, and the parallel oil storage tanks are connected with the hydraulic suspension chamber 4. After the hydraulic oil enters the hydraulic suspension chamber 4 through the throttling screw plug 6, the hydraulic oil will fill the entire parallel oil storage tank through the hydraulic suspension support gap. No matter whether the piston rods 14 and 15 move to the left or to the right, the entire hydraulic suspension support gap will store pressurized hydraulic oil. The parallel oil storage tanks increase the oil storage capacity of the hydraulic suspension support gap and increase the contact area with the end cover 12, which is conducive to generating a more uniform and stable support pressure, and has a better support and centering effect on the piston rods 14 and 15; at the same time, the interface of the parallel oil storage tanks increases the cross-sectional area of ​​the oil film, which can enhance the sealing effect, offset a part of the pressure of the hydraulic oil in the hydraulic cylinder barrel, thereby relieving the pressure of the seal between the hydraulic suspension ring 120 and the booster cylinder 2, which is conducive to extending the service life of the seal and improving the sealing effect.

[0064] In some embodiments, a reverse dust ring is further provided in the inner hole of the end cover 12 away from the hydraulic cylinder barrel 12 , for scraping oil from the piston rods 14 , 15 in a direction close to the hydraulic cylinder barrel 12 .

[0065] In this embodiment, the reverse dust ring is designed to achieve a reverse oil scraping effect. The reverse dust ring acts as a sealing ring and cooperates with other sealing rings to achieve a sealing effect to prevent the oil in the oil chamber from entering the isolation chamber; the dust ring can achieve an oil scraping effect on the piston rod to prevent the oil from adhering to the piston rod and entering the isolation chamber. If hydrogen leaks in the isolation chamber, contact with high-temperature hydraulic oil will cause hydrogen to dissolve in the hydraulic oil, resulting in "cavitation" and corrosion of the piston rod coating. In addition, as the pressure increases, the ignition point of hydrogen will decrease, and the high-temperature and high-pressure hydrogen will come into contact with the piston rod hydraulic oil, which has the risk of combustion and explosion.

[0066] In some embodiments, an oil scraper and drain groove and an oil drain channel are provided on the side of the reverse dust ring close to the hydraulic cylinder barrel, which can discharge the oil scraped off by the reverse dust ring in time and prevent the oil pressure from directly impacting the reverse dust ring after the seal fails, serving as a second guarantee for sealing.

[0067] In some embodiments, Figure 2 As shown, the hydraulic cylinder also includes a proximity switch for detecting the position of the hydraulic piston.

[0068] A proximity switch is added to the hydraulic cylinder to determine when the hydraulic piston hits the bottom. The matching hydraulic system processor detects the proximity switch signal in real time to control the precise real-time pressurization of the oil chamber, control the timely reversal of the hydraulic piston, ensure that the oil chamber pressurization and air chamber inflation are synchronized, avoid lag in the movement of the two chambers, and improve compression efficiency.

[0069] In some embodiments, Figure 2 As shown, the boost cylinder includes an isolation chamber located on the side of the boost piston close to the drive module; the inlet and exhaust ports of the isolation chamber and the inlet and exhaust ports of the isolation chamber are respectively provided with gas concentration sensors for detecting the gas concentration in the isolation chamber.

[0070] A hydrogen concentration sensor is added to the inlet and outlet of the isolation chamber to detect the hydrogen concentration in the isolation chamber in real time, and the data is fed back to the hydraulic system control center in real time. When the cylinder piston fails and causes hydrogen leakage, the isolation chamber will be filled with leaked hydrogen. When the hydrogen reaches a certain concentration, the sensor alarm device will be triggered, and the signal will be transmitted to the central information processing system. The system will issue a command to stop immediately stopping the cylinder pressurization, which can achieve real-time early warning of hydrogen leakage and ensure safe operation.

[0071] Embodiment 3

[0072] Figure 1 and Figure 2Schematic diagram of a gas booster in an embodiment of the present disclosure.

[0073] like Figure 1 As shown, the liquid-driven gas booster includes: a hydraulic cylinder 1, a primary booster cylinder 2, and a secondary booster cylinder 3; the hydraulic cylinder 1 includes a hydraulic cylinder barrel 11 and end covers 12 respectively arranged at both ends of the cylinder barrel; the primary booster cylinder 2 and the secondary booster cylinder 3 are respectively arranged on both sides of the hydraulic cylinder 1, and are connected to the hydraulic cylinder 1 through the end covers 12. The hydraulic cylinder 1 also includes a hydraulic piston 13, a first piston rod 14, and a second piston rod 15, and the first piston rod 14 and the second piston rod 15 are connected to the hydraulic piston 13; the primary booster cylinder 2 includes a primary booster cylinder barrel 21 and a primary booster piston 22 arranged in the primary booster cylinder barrel 21; the secondary booster cylinder 3 includes a secondary booster cylinder barrel 31 and a secondary booster piston 32 arranged in the secondary booster cylinder barrel 31.

[0074] The inner bore surface of the boost cylinder 21, 31 is covered with a diamond-like carbon (DLC) coating, and the outer circumference surface of the boost piston 22, 32 is covered with a low-friction composite coating, thereby forming a friction pair. Applying the DLC coating process to the inner bore surface of the boost cylinder 21, 31 can not only improve the hardness of the inner bore of the boost cylinder 21, 31, for example, the hardness HV reaches more than 3000, but also reduce the roughness of the inner bore of the boost cylinder 21, 31; the low-friction composite coating has the characteristics of ultra-low friction, high hardness, and low friction loss. The inner bore surface of the boost cylinder 21, 31 covered with the DLC coating and the outer circumference of the boost piston 22, 32 covered with the low-friction composite coating can form a low-friction, high-stability friction pair.

[0075] In some embodiments, a seal is used between the inner hole of the boost cylinder 21, 31 and the outer circle of the boost piston 22, 32. The friction pair composed of the DLC coating and the low-friction composite coating has a low friction coefficient, which can greatly reduce frictional heat and friction loss, which is beneficial to extend the life of the seal, enhance the sealing effect, and reduce the risk of hydrogen leakage.

[0076] The embodiments of the present disclosure do not specifically limit the low-friction composite coating. In some embodiments, the low-friction composite coating is a low-friction plastic coating. For example, the low-friction plastic coating includes a PTFE-based composite coating and / or a nylon-based composite coating. For example, the low-friction plastic coating is a P80870 nylon-based composite coating.

[0077] In some embodiments, the DLC coating has a thickness of 2 to 3 μm.

[0078] In this embodiment, a combination of DLC coating and low-friction composite coating is used to form a low-friction, high-stability friction pair between the inner hole surface of the booster cylinder 21, 31 and the outer circle of the booster piston 22, 32, which is beneficial to achieving a high-precision inner hole in the booster cylinder 21. The inner hole of the booster cylinder 21, 31 and the booster piston 22, 32 are matched through tolerance control clearance, which can greatly reduce frictional heat and reduce friction loss between the inner hole of the booster cylinder 21, 31 and the outer circle of the booster piston 22, 32, which is beneficial to reducing the failure rate of the gas booster, extending the service life of the gas booster, and improving work efficiency.

[0079] Embodiment 4

[0080] Figure 6 This is a cross-sectional view of a liquid-driven hydrogen supercharger. Figure 7 It is a three-dimensional schematic diagram of the liquid-driven hydrogen booster.

[0081] like Figure 6 , Figure 7 As shown, the hydrogen booster includes a hydraulic cylinder 100, a primary boosting cylinder 200, and a secondary boosting cylinder 300; the primary boosting cylinder 200 includes a primary boosting cylinder barrel 201 and a primary boosting piston 202 disposed in the primary boosting cylinder barrel 201; the secondary boosting cylinder 300 includes a secondary boosting cylinder barrel 301 and a secondary boosting piston 302 disposed in the secondary boosting cylinder barrel 301; the primary boosting cylinder barrel 201 and the secondary boosting cylinder barrel 301 are respectively disposed on both sides of the hydraulic cylinder 100. The hydraulic cylinder 100 includes a hydraulic piston 101, a first piston rod 102, a second piston rod 103, and a hydraulic cylinder barrel 104, wherein the first piston rod 102 extends into the primary boosting cylinder barrel 201 and is connected to the primary boosting piston 202; the second piston rod 103 extends into the secondary boosting cylinder barrel 301 and is connected to the secondary boosting piston 302. In this embodiment, the hydrogen booster boosts low-pressure hydrogen to high-pressure hydrogen through a two-stage boosting cylinder. For example, after being boosted by the first-stage boosting cylinder 200, the outlet pressure of the first-stage boosting cylinder 200 is 45MPa; then it enters the second-stage boosting cylinder 300 for boosting, and the outlet pressure of the second-stage boosting cylinder 300 is 90MPa.

[0082] like Figure 6 As shown, the hydrogen supercharger is provided with friction pair A, friction pair B, friction pair C, friction pair D, and friction pair E. Friction pair B and friction pair C constitute a friction pair system, which is intended to reduce friction heat generation and friction loss of the hydrogen supercharger during high-frequency reciprocating operation.

[0083] In friction pair A, a gap seal design is used for the hydraulic piston 101. The oil is throttled through the gap between the gap seal sleeve and the piston rod to replace the ordinary pressurized seal to achieve the sealing effect. In addition, adding an oil storage tank on the surface of the hydraulic piston 101 can increase lubrication. The oil pressure can be used to achieve short contact or non-contact movement between the hydraulic piston 101 and the hydraulic cylinder barrel 104. The reciprocating frequency of the oil cylinder is very fast. The viscosity of the hydraulic oil can form a short-term sealing effect between the hydraulic piston 101 and the inner wall of the hydraulic cylinder barrel 104. Since the movement frequency of the hydraulic piston 101 in the hydraulic cylinder 100 is very high, the amount of hydraulic oil leakage during a stroke of the gap seal is very small, which does not affect the effect of the entire hydraulic cylinder 100.

[0084] At the friction pair B and friction pair C, a low-friction composite coating such as a PTFE-based composite coating or a nylon-based composite coating is sprayed on the outer peripheral surface of the primary booster piston 202 and the secondary booster piston 302. The low-friction composite coating has the characteristics of ultra-low friction, high hardness, and low wear. The low-friction composite coating can be a PTFE-based and / or nylon-based composite coating. A DLC coating is sprayed on the inner peripheral surface of the secondary booster cylinder 301 and the primary booster cylinder 201. The DLC coating can both increase the hardness of the inner hole of the cylinder and reduce the roughness of the inner hole of the cylinder. In combination with the PTFE-based or nylon-based composite coating, a low-friction, high-stability friction pair is formed.

[0085] In friction pair D and friction pair E, a hydraulic suspension support structure is designed. Oil is injected from the pressure port, circulated to each pressure port through the hydraulic annular circuit, and then proportional pressure reduction is achieved through the liquid resistance effect of the throttling screw 401. With the tolerance control and clearance matching between the hydraulic suspension ring 402 and the hydraulic piston 101, the hydraulic oil can be stored in the internal suspension isolation chamber 403 in the hydraulic suspension ring 402, so that the hydraulic piston 101 is suspended, and the hydrostatic pressure can automatically center the piston rod to achieve frictionless contact between the hydraulic piston 101 and the end cover. In this way, the guide support ring is removed, and the heat generated during the movement of the piston rod will be taken away by the hydraulic oil circulated and injected into the pressure port, avoiding the generation of more heat. Due to the automatic centering of the piston rod, the buffer ring, isolation ring and cylinder piston seal ring in the end cover are not subject to the radial offset load caused by the flexibility of the piston rod, and do not bear the lateral force generated by the oil pressure, so only a small constant residual friction is generated, and very little heat is generated.

[0086] Through the hydraulic suspension effect of friction pair D and friction pair E and the mutual influence and cooperation between the low-friction friction pairs at friction pair A, friction pair B and friction pair C, the hydrogen supercharger can achieve high-frequency, high-efficiency and low-friction movement.

[0087] like Figure 6As shown, in the hydrogen boosting cylinder, the secondary boosting cylinder 300 includes a secondary boosting cylinder barrel 301 and a secondary boosting piston 302, wherein the secondary boosting piston 302 is fixedly connected to the second piston rod piston 103 by fasteners such as bolts. The secondary boosting piston 302 reciprocates in the secondary boosting cylinder barrel 301, so that the outer circle of the secondary boosting piston 302 and the inner hole surface of the secondary boosting cylinder barrel 301 form a friction pair.

[0088] A cooling water circulation system is provided on the outer peripheral side of the secondary boost cylinder 301. Figure 6 As shown, the cooling water circulation system includes a water inlet 303, a guide member 304, and a water outlet 305. The guide member 304 is arranged on the outer peripheral side of the secondary boost cylinder 301. The guide member 304 is arranged around the outer peripheral side of the secondary boost cylinder 301, and a cooling water channel is separated on the outer periphery of the secondary boost cylinder 301. The cooling water channel is connected with the water inlet 303 and the water outlet 305. The cooling water enters the cooling water channel from the water inlet 303 and is discharged from the water outlet 305, thereby cooling the secondary boost cylinder 301.

[0089] In some embodiments, the flow guide 304 is a baffle.

[0090] In some embodiments, the flow guide 304 is an insulated copper tube.

[0091] The secondary booster piston 302 includes a body and a cylindrical portion located on one side of the body and surrounding the central axis of the secondary booster piston 302. The cylindrical portion forms a recessed portion, and the second piston rod 103 fits in the recessed portion. An annular groove is formed at one end of the second piston rod 103, and a fitting is embedded in the groove. A fastener that penetrates the fitting and is screwed into the cylindrical portion securely connects the secondary booster piston 302 to the second piston rod 103.

[0092] On the other side of the body of the secondary booster piston 302, a seal is fixed to the body of the secondary booster piston 302 by fasteners such as screws. A groove is formed on the outer peripheral surface of the secondary booster piston 302 to accommodate the seal. Of course, the structure of the secondary booster piston 302 and the connection method with the second piston rod 103 are not limited to this.

[0093] In order to reduce the friction generated between the secondary boosting piston 302 and the secondary boosting cylinder 301, a PTFE-based or nylon-based composite coating is sprayed on the outer cylindrical surface of the secondary boosting piston 302. An example of the coating is a P80870 nylon-based composite coating, but it is not limited thereto. The PTFE-based or nylon-based composite coating has the characteristics of ultra-low friction, high hardness, and low wear. In addition, a DLC coating is sprayed on the inner hole surface of the secondary boosting cylinder 301. The DLC coating can not only improve the hardness of the cylinder bore, in one embodiment, the hardness of the cylinder bore can reach HV≥3000, but also reduce the roughness of the cylinder bore. In one embodiment, the roughness of the cylinder bore can reach Ra0.05 or even higher. The secondary boosting piston 302 sprayed with a PTFE-based or nylon-based composite coating and the secondary boosting cylinder 301 sprayed with a DLC coating constitute a friction pair with low friction and high stability.

[0094] The primary booster cylinder 200 includes a primary booster cylinder barrel 201 and a primary booster piston 202, wherein the primary booster piston 202 is fixedly connected to the first piston rod 102 by fasteners such as bolts. The primary booster piston 202 reciprocates in the primary booster cylinder barrel 201, so that the outer circumferential surface of the primary booster piston 202 and the inner circumferential surface of the primary booster cylinder barrel 201 form a friction pair.

[0095] A cooling water circulation system is provided on the outer peripheral side of the primary boost cylinder 201 . The system is similar to the cooling water circulation system of the secondary boost cylinder 301 , and will not be described in detail here.

[0096] The primary booster piston 202 includes a body portion and a cylindrical portion and a cylindrical portion located on one side of the body portion and surrounding the central axis of the primary booster piston 9. The cylindrical portion and the cylindrical portion have different inner diameters so that a step is formed between the two. Specifically, the inner diameter of the cylindrical portion is smaller than the inner diameter of the cylindrical portion. The cylindrical portion and the cylindrical portion form a recess, and the first piston rod 102 fits in the recess. An annular groove is formed at the corresponding end of the first piston rod 102, and a fitting is embedded in the groove. A fastener that penetrates the fitting and is screwed into the cylindrical portion fixedly connects the primary booster piston 202 to the first piston rod 102.

[0097] On the other side of the main body of the primary booster piston 202, a seal is fixed to the main body of the primary booster piston 202 by fasteners such as screws. A groove is formed on the outer peripheral surface of the primary booster piston 202 to accommodate the seal. Of course, the structure of the primary booster piston 202 and the connection method with the first piston rod 102 are not limited to this. Moreover, the structure of the primary booster piston 202 can be interchangeable with the structure of the secondary booster piston 302.

[0098] In order to reduce the friction between the primary boosting piston 202 and the primary boosting cylinder 201 due to the piston movement, a PTFE-based or nylon-based composite coating is sprayed on the outer circumferential surface of the primary boosting piston 202 of the present invention. An example of the coating is a P80870 nylon-based composite coating, but it is not limited to this. As mentioned above, the PTFE-based or nylon-based composite coating has the characteristics of ultra-low friction, high hardness and low wear. In addition, a DLC coating is sprayed on the inner circumferential surface of the primary boosting cylinder 201. The DLC coating can not only increase the hardness of the cylinder bore to HV≥3000, but also reduce the roughness of the cylinder bore to Ra0.05 or even higher. The primary boosting piston 202 sprayed with a PTFE-based or nylon-based composite coating and the primary boosting cylinder 201 sprayed with a DLC diamond-like carbon coating constitute a low-friction, high-stability friction pair.

[0099] In addition, this embodiment improves the DLC coating manufacturing process through the plasma enhancement and deposition integration process. Specifically, the surface of the substrate is first bombarded with plasma to enhance the active sites of the substrate and improve the bonding ability of the substrate. A high-energy ion source is used to generate a carbon ion beam, and the carbon ions are implanted into the surface of the substrate. By accurately controlling the energy, dosage and angle of the ion implantation, a carbon-rich transition layer can be formed on the surface of the substrate. This transition layer can improve the interface bonding between the coating and the substrate, reduce the stress inside the coating, and provide a good foundation for the subsequent deposition process. Then, a microwave plasma source is used to generate carbon-rich ions. By reasonably controlling the power, gas pressure, gas flow rate of the plasma and using a magnetic field to regulate the plasma movement, a stable and dense DLC carbon coating structure with excellent performance and good control of the coating thickness can be generated, and then the coating surface finish and lubrication can be improved through annealing and laser modification processes.

[0100] A high-precision polishing process can be used for the inner surface of the cylinder. Specifically, first, a composite process combining magnetorheological polishing and chemical mechanical polishing is used. Magnetorheological polishing uses the rheological properties of magnetorheological fluid in a magnetic field to form a "flexible polishing mold" with high shear force, which can quickly remove the material on the surface of the workpiece. The principle is that under the action of the magnetic field, the magnetic particles in the magnetorheological fluid are polarized to form a chain structure. The hardness and rigidity of the chain structure can be adjusted by the magnetic field, thereby achieving high-precision removal of the workpiece material. Chemical mechanical polishing uses the synergistic effect of chemical corrosion and mechanical grinding to make the surface of the workpiece flat at the atomic level. By adding specific chemical reagents to the polishing liquid, a chemical reaction occurs with the workpiece surface material to generate a product that is easy to remove. At the same time, the polishing pad mechanically grinds the workpiece surface to remove the reaction product. Combining these two polishing methods, first use magnetorheological polishing for rough polishing to quickly reduce the roughness of the workpiece surface, and then use chemical mechanical polishing for fine polishing to achieve a surface roughness of 0.1 microns.

[0101] At the same time, a high-precision online detection and feedback control system is introduced throughout the polishing process. High-precision measuring equipment such as laser interferometers or atomic force microscopes are used to monitor the surface roughness of the workpiece in real time, and the measurement data is fed back to the control system. The control system automatically adjusts the polishing parameters according to the feedback data, such as the magnetic field strength and polishing liquid flow rate of magnetorheological polishing, and the polishing pressure and polishing time of chemical mechanical polishing. Through this intelligent control, the surface of the workpiece can be polished accurately to ensure that the roughness target of 0.1 microns is achieved.

[0102] In order to ensure the stability of the polishing environment, an ultra-clean, constant temperature and humidity polishing environment is constructed. In a closed polishing studio, dust and impurity particles are removed through an air filtration system to maintain the air cleanliness of more than 100 levels. The temperature and humidity adjustment device is used to control the ambient temperature within ±0.1℃ and the humidity within ±2%. A stable environment can prevent external factors from interfering with the polishing process and reduce the generation of surface defects, which is crucial to achieving an ultra-precision polishing effect of 0.1 microns.

[0103] The high-precision inner hole of the cylinder can significantly reduce the frictional heat generated by the sealing ring, increase the service life of the seal, enhance the sealing effect of the seal, and reduce the risk of high-pressure hydrogen leakage.

[0104] In the hydraulic cylinder 100, the hydraulic piston 101 reciprocates in the hydraulic cylinder barrel 104, so that the outer circumferential surface of the hydraulic piston 101 and the inner circumferential surface of the hydraulic cylinder barrel 6 form a friction pair, such as Figure 6 Middle friction pair A.

[0105] At the friction pair A, a gap seal design is used for the hydraulic piston 101. Specifically, a plurality of spaced annular oil storage grooves are provided on the outer peripheral surface of the hydraulic piston 101. In this embodiment, the cross-sectional shape of the oil storage groove is rectangular, but the shape is not limited and can be different shapes according to specific applications, such as semicircular, semi-elliptical, V-shaped, U-shaped, etc.

[0106] Compared with sealing ring sealing, the throttling effect of the oil through the gap between the gap sealing sleeve and the piston rod is utilized to replace the ordinary pressurized seal to achieve the sealing effect. Adding an oil storage tank on the piston surface can increase lubrication. The oil pressure can realize short contact or non-contact movement between the piston and the cylinder. The reciprocating motion frequency of the cylinder is very fast. By utilizing the viscosity of the hydraulic oil, the hydraulic oil can form a short-term sealing effect between the gap between the piston and the inner wall of the cylinder. Since the movement frequency of the cylinder is very high, the amount of oil leakage in the gap seal during a stroke is very small, which does not affect the effect of the entire cylinder.

[0107] The hydraulic cylinder 100 also includes a hydraulic suspension ring, such as Figure 6As shown in the friction pair D of FIG. 1 , the hydraulic suspension ring is arranged between the outer peripheral surface of the hydraulic piston 101 and the inner hole surface of the end cover as the hydraulic cylinder barrel 104. A plurality of pressure ports 5 are arranged in the outer peripheral surface of the end cover, and the pressure ports 5 extend radially to the inner peripheral surface of the end cover via the hydraulic channel. A total of four hydraulic suspension pressurization ports are arranged in the hydraulic suspension ring at equal intervals in the circumferential direction, but the number of pressurization ports is not limited to four, but can be one, two, three, five or more.

[0108] Each pressurizing port is connected to each other through a hydraulic annular circuit. A throttling screw plug is provided in each hydraulic channel, and the throttling screw plug has a liquid resistance effect, thereby realizing proportional pressure reduction. A channel that is transversely connected to the hydraulic channel is provided on the downstream side of the throttling screw plug along the oil direction, and the channel is connected to a detection channel that extends radially to the outer peripheral surface of the end cover, and the detection channel ends at a pressure detection port located in the outer peripheral surface of the end cover, so that the pressure in the channel can be detected through the pressure detection port.

[0109] A plurality of hydraulic holes are provided in the hydraulic suspension ring, which penetrate the hydraulic suspension ring radially, and each hydraulic hole is connected to each hydraulic channel. A hydraulic suspension oil storage tank connected to the plurality of hydraulic holes is provided on the inner circumference of the hydraulic suspension ring, and each hydraulic suspension oil storage tank extends at least a portion along the circumference of the hydraulic suspension ring in a cross section. In one embodiment, each hydraulic suspension oil storage tank is independent of each other and is not connected to each other. In one embodiment, each hydraulic suspension oil storage tank is connected to each other, forming a gap between the hydraulic suspension ring and the piston rod.

[0110] At one end of the hydraulic suspension ring, a plurality of oil discharge grooves are formed in the inner peripheral surface of the end cover corresponding to the hydraulic suspension oil storage groove, and each oil discharge groove is connected to a corresponding oil discharge channel extending radially to the outer peripheral surface of the end cover. The oil discharge channel ends at an oil discharge port located in the outer peripheral surface of the end cover, so that the oil in the channel can be discharged through the oil discharge port.

[0111] As described above, the present invention is provided with a hydraulic suspension support structure. Before the oil cylinder moves, pressure is injected from the hydraulic suspension pressurization port, which is circulated to each pressurization port through the hydraulic annular circuit, and then proportional pressure reduction is achieved through the liquid resistance effect of the throttling screw plug. Through the tolerance control and clearance matching between the hydraulic suspension ring and the piston rod, the oil pressure can be stored in the internal suspension isolation chamber in the hydraulic suspension ring, so that the piston rod is suspended, and the hydrostatic pressure can automatically center the piston rod. In this way, frictionless contact between the piston rod and the end cover is achieved, the guide support ring is removed, and the heat generated during the movement of the piston rod will be taken away by the hydraulic oil circulated and injected into the pressurization port, avoiding the generation of more heat. Due to the automatic centering of the piston rod, the buffer ring, isolation ring and cylinder piston seal ring in the end cover are not subject to the radial offset load generated by the flexibility of the main oil cylinder piston, and are not subjected to the lateral force generated by the oil pressure, so only a small constant residual friction is generated, and thus very little heat is generated.

[0112] Example embodiments have been disclosed herein, and although specific terms are employed, they are used and should be interpreted only in a general illustrative sense and not for limiting purposes. In some instances, it will be apparent to those skilled in the art that, unless otherwise expressly noted, features, characteristics, and / or elements described in conjunction with a particular embodiment may be used alone or in combination with features, characteristics, and / or elements described in conjunction with other embodiments. Therefore, those skilled in the art will appreciate that various changes in form and detail may be made without departing from the scope of the present disclosure as set forth in the appended claims.

Claims

1. A liquid-driven gas supercharger, comprising: A hydraulic cylinder, a first-stage booster cylinder, and a second-stage booster cylinder; the hydraulic cylinder comprises a hydraulic cylinder barrel and end covers respectively arranged at both ends of the cylinder barrel; the first-stage booster cylinder and the second-stage booster cylinder are respectively arranged on both sides of the hydraulic cylinder and connected to the hydraulic cylinder through the end covers; The hydraulic cylinder further comprises a hydraulic piston, a first piston rod and a second piston rod, wherein the first piston rod and the second piston rod are connected to the hydraulic piston; The primary booster cylinder includes a primary booster cylinder barrel and a primary booster piston disposed in the primary booster cylinder barrel; the secondary booster cylinder includes a secondary booster cylinder barrel and a secondary booster piston disposed in the secondary booster cylinder barrel; The first piston rod extends into the primary booster cylinder and is connected to the primary booster piston, and the second piston rod extends into the secondary booster cylinder and is connected to the secondary booster piston; At least one hydraulic suspension chamber is provided on the inner hole surface of the end cover for storing hydraulic oil under pressure so as to suspend the first piston rod or the second piston rod in the inner hole of the end cover.

2. The liquid-driven gas booster according to claim 1, wherein: A plurality of hydraulic suspension chambers are arranged on the inner hole surface of the end cover, and the plurality of hydraulic suspension chambers are distributed along the circumferential direction; the end cover is also provided with a hydraulic annular circuit extending along the circumferential direction, and a plurality of pressurizing ports distributed along the circumferential direction, and each of the pressurizing ports corresponds to one of the hydraulic suspension chambers; the pressurizing ports are connected to the hydraulic annular circuit and to the corresponding hydraulic suspension chambers.

3. The liquid-driven gas booster according to claim 2, wherein: Each of the pressurizing ports is connected to the hydraulic annular circuit via a pressure-pressing channel; a throttling screw plug is provided in the pressure-pressing channel to keep the pressure at each of the pressurizing ports consistent.

4. The liquid-driven gas booster according to claim 3, wherein: Each of the pressurizing ports corresponds to a pressure detection channel, the pressure detection channel is communicated with the pressure-pressing channel, and a pressure sensor is provided in the pressure detection channel for detecting the pressure in the corresponding hydraulic suspension chamber.

5. The liquid-driven gas booster according to claim 2, wherein: The inner holes of the two end covers are respectively clearance-matched with the first piston rod and the second piston rod.

6. The liquid-driven gas booster according to any one of claims 1 to 5, wherein: The end cover comprises a hydraulic suspension ring arranged in the inner hole of the end cover, and the hydraulic suspension cavity is arranged on the inner hole surface of the hydraulic suspension ring.

7. The liquid-driven gas booster according to claim 6, characterized in that: The hydraulic suspension ring is in clearance fit with the inner hole of the end cover; or The hydraulic suspension ring is formed in the inner hole of the end cover by a surfacing process.

8. The liquid-driven gas booster according to claim 6, wherein: An oil storage structure is also provided on the inner hole surface of the hydraulic suspension ring, and the oil storage structure is communicated with the hydraulic suspension cavity.

9. The liquid-driven gas booster according to claim 6, characterized in that: The oil storage structure comprises a plurality of parallel oil storage grooves which are distributed parallel to each other on the inner hole surface of the hydraulic suspension ring.

10. The liquid-driven gas booster according to any one of claims 1 to 5, wherein: The inner hole of the hydraulic cylinder and the hydraulic piston are gap-sealed by tolerance control.

11. The liquid-driven gas booster according to claim 10, wherein: The outer circumferential surface of the hydraulic piston is provided with at least one clearance sealing groove, and the clearance sealing groove extends in the circumferential direction and is used for storing hydraulic oil.

12. The liquid-driven gas booster according to any one of claims 1 to 5, wherein: A reverse dust ring is also provided in the inner hole of the end cover away from the hydraulic cylinder barrel, which is used to scrape oil from the first piston rod or the second piston rod in a direction close to the hydraulic cylinder barrel.

13. The liquid-driven gas booster according to claim 12, wherein: An oil scraper storage tank is also provided in the inner hole of the end cover, on the side of the reverse dust ring close to the hydraulic cylinder barrel; an oil drain channel is also provided on the end cover, and the oil scraper storage tank is connected to the oil drain channel.

14. The liquid-driven gas booster according to any one of claims 1 to 5, wherein: The hydraulic cylinder also includes a proximity switch for detecting the position of the hydraulic piston.

15. The liquid-driven gas booster according to any one of claims 1 to 5, wherein: The first-stage booster cylinder and the second-stage booster cylinder include an isolation chamber located on the side of the first-stage booster piston or the second-stage booster piston close to the hydraulic cylinder; the inlet and outlet ports of the isolation chamber are respectively provided with a concentration sensor of the gas to be pressurized, which is used to detect the concentration of the gas to be pressurized in the isolation chamber.

16. The liquid-driven gas booster according to any one of claims 1 to 5, wherein: Cooling water channels are also provided on the outer walls of the first-stage boost cylinder and the second-stage boost cylinder.

17. The liquid-driven gas booster according to claim 16, characterized in that: A spirally extending flow guide is arranged on the outer wall of the boost cylinder, and the flow guide separates the cooling water channel on the outer wall of the boost cylinder.

18. The liquid-driven gas booster according to any one of claims 1 to 5, wherein: The inner hole of the primary booster cylinder is matched with the primary booster piston through a tolerance control clearance, the inner hole surface of the primary booster cylinder is covered with a diamond-like coating, and the outer cylindrical surface of the primary booster piston is covered with a PTFE-based composite coating or a nylon-based composite coating; The inner hole of the secondary booster cylinder is matched with the secondary booster piston through a tolerance controlled clearance. The inner hole surface of the secondary booster cylinder is covered with a diamond-like coating, and the outer cylindrical surface of the secondary booster piston is covered with a PTFE-based composite coating or a nylon-based composite coating.

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