Hydraulic drive type gas supercharger

Abstract

The utility model provides a hydraulic drive type gas supercharger. The hydraulic drive type 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 liquid drive type gas supercharger, friction heating and friction loss are reduced.

Description

TECHNICAL FIELD

[0001] The present disclosure relates to the technical field of gas pressurization, in particular to a liquid-driven gas pressurizer. BACKGROUND

[0002] A gas pressurizer is a device for compressing low-pressure gas into high-pressure gas. For example, a hydrogen gas pressurizer is a device for compressing hydrogen gas, and is a core component of a hydrogen station and other devices.

[0003] A liquid-driven gas pressurizer is a gas pressurizer driven by hydraulic pressure. In order to ensure that gas and hydraulic oil are isolated from each other, a large number of sealing elements are required for sealing. During high-frequency reciprocating movement of the gas pressurizer, a large amount of heat is generated, which affects the service life and sealing effect of the sealing elements, thereby resulting in a high failure rate of the gas pressurizer. CONTENT OF THE UTILITY MODEL

[0004] The present disclosure provides a liquid-driven gas pressurizer.

[0005] In a first aspect, the present disclosure provides a liquid-driven gas pressurizer, comprising: a hydraulic cylinder, a primary pressurizing cylinder, and a secondary pressurizing cylinder; the hydraulic cylinder comprises a hydraulic cylinder barrel and end covers respectively arranged at both ends of the cylinder barrel; the primary pressurizing cylinder and the secondary pressurizing cylinder are respectively arranged on both sides of the hydraulic cylinder and are connected with 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 with the hydraulic piston.

[0007] The primary pressurizing cylinder comprises a primary pressurizing cylinder barrel and a primary pressurizing piston arranged in the primary pressurizing cylinder barrel; and the secondary pressurizing cylinder comprises a secondary pressurizing cylinder barrel and a secondary pressurizing piston arranged in the secondary pressurizing cylinder barrel.

[0008] The first piston rod extends into the primary pressurizing cylinder barrel and is connected with the primary pressurizing piston, and the second piston rod extends into the secondary pressurizing cylinder barrel and is connected with the secondary pressurizing piston.

[0009] The end cover is provided with at least one hydraulic suspension cavity on the inner hole surface of the end cover, for storing hydraulic oil with pressure, so that the first piston rod or the second piston rod is suspended in the inner hole of the end cover.

[0010] In some embodiments, a plurality of hydraulic suspension cavities are arranged on the inner hole surface of the end cover, and the plurality of hydraulic suspension cavities are distributed in a circumferential direction; the end cover is further provided with a hydraulic annular loop extending in the circumferential direction, and a plurality of pressurizing ports distributed in the circumferential direction, each of the pressurizing ports corresponding to one of the hydraulic suspension cavities; the pressurizing ports are in communication with the hydraulic annular loop and the corresponding hydraulic suspension cavities.

[0011] In some embodiments, each of the pressurizing ports is in communication with the hydraulic annular loop through a pressurizing channel; a throttle screw plug is arranged in the pressurizing 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 in communication with the pressurizing channel, and a pressure sensor is arranged in the pressure detection channel to detect the pressure in the corresponding hydraulic suspension cavity.

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

[0014] In some embodiments, the end cover comprises a hydraulic suspension ring arranged in the inner hole of the end cover, and the hydraulic suspension cavities are arranged on the inner hole surface of the hydraulic suspension ring.

[0015] In some embodiments, 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 through a surfacing process.

[0016] In some embodiments, the inner hole surface of the hydraulic suspension ring is further provided with an oil storage structure in communication with the hydraulic suspension cavities.

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

[0018] In some embodiments, the inner hole of the hydraulic cylinder barrel is in clearance fit with the hydraulic piston through tolerance control.

[0019] In some embodiments, the outer circular surface of the hydraulic piston is provided with at least one clearance fit groove extending in the circumferential direction for storing hydraulic oil.

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

[0021] In some embodiments, an oil scraping and storing groove is arranged on one side of the reverse dustproof ring close to the hydraulic cylinder barrel in the inner hole of the end cover; and an oil leaking passage is further arranged on the end cover, and the oil scraping and storing groove communicates with the oil leaking passage.

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

[0023] In some embodiments, an isolation cavity is arranged in the primary pressurizing cylinder barrel or the secondary pressurizing cylinder barrel on one side of the primary pressurizing piston or the secondary pressurizing piston close to the hydraulic cylinder; and a to-be-pressurized gas concentration sensor is arranged on the air inlet and air outlet of the isolation cavity respectively for detecting the concentration of the to-be-pressurized gas in the isolation cavity.

[0024] In some embodiments, a cooling water channel is further arranged on the outer wall of the primary pressurizing cylinder barrel or the secondary pressurizing cylinder barrel.

[0025] In some embodiments, a helically extending flow guide is arranged on the outer wall of the pressurizing cylinder barrel, and the flow guide separates the cooling water channel on the outer wall of the pressurizing cylinder barrel.

[0026] In some embodiments, the inner hole of the primary pressurizing cylinder barrel is matched with the primary pressurizing piston through a tolerance controlled gap, the inner hole surface of the primary pressurizing cylinder barrel is covered with a diamond-like coating, and the outer circular surface of the primary pressurizing piston is covered with a PTFE-based composite coating or a nylon-based composite coating.

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

[0028] In the liquid driven gas pressurizer provided by the embodiments of the present disclosure, at least one hydraulic suspension cavity is arranged on the inner hole surface of the end cover of the hydraulic cylinder for storing hydraulic oil with pressure, so that the piston rod is suspended in the inner hole of the end cover, and the hydraulic oil in the hydraulic suspension cavity can also play a sealing role, thereby reducing the use of sealing elements, and in the case of high frequency and rapid reciprocating motion of the pressurizing piston, the frictional heat generation and frictional loss can be greatly reduced, which is conducive to reducing the failure rate of the gas pressurizer, prolonging the service life of the gas pressurizer, and improving the working efficiency. BRIEF DESCRIPTION OF DRAWINGS

[0029] Figure 1 is a sectional view of a liquid driven gas pressurizer in the embodiments of the present disclosure;

[0030] Figure 2 is a sectional view of another liquid driven gas pressurizer in the embodiments of the present disclosure;

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

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

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

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

[0035] Figure 7 is a perspective schematic view of a liquid-driven hydrogen booster in an embodiment of the present disclosure. DETAILED DESCRIPTION

[0036] In order to make the technical personnel in the art better understand the technical solutions of the present disclosure, the technical solutions of the present disclosure will be described in detail below in conjunction with the drawings.

[0037] In the following, example embodiments will be described more fully with reference to the accompanying drawings, in which example embodiments can be embodied in different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.

[0038] The embodiments of the present disclosure and the features in the embodiments can be combined with each other without conflict.

[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" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will also be understood that the terms "comprise" and / or "consist of, when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof.

[0041] The embodiments described herein can be described with reference to plan views and / or cross-sectional views by virtue of the idealized illustrative representations of the underlying conventional materials, structures and devices. Accordingly, the example illustrations are intended to provide a conceptual illustration of the embodiments described herein. Accordingly, the dimensions of the example illustrations are not necessarily drawn to scale and are provided for purposes of conceptual illustration. Therefore, the embodiments are not limited by the illustrated ordering or configuration, but include modifications thereof based upon manufacturing processes and / or tolerances, which are intended to be a part of the application. Thus, the embodiments are not limited by the illustrated ordering or configuration, but include modifications based on manufacturing processes and / or tolerances, which are intended to be a part of the application. Accordingly, the illustrated zones are schematic and the shapes thereof do not necessarily illustrate the precise shape of the regions in practice. Thus, the regions illustrated in the figures are schematic and the shapes thereof do not necessarily illustrate the precise shape of the regions in practice.

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

[0043] Embodiment I

[0044] Figure 1 is a schematic diagram of a hydraulic gas booster in an embodiment of the present disclosure.

[0045] As shown in Figure 1 , the hydraulic gas booster comprises a hydraulic cylinder 1, a first-stage booster cylinder 2, and a second-stage booster cylinder 3. The hydraulic cylinder 1 comprises a hydraulic cylinder barrel 11 and end covers 12 arranged at both ends of the cylinder barrel, respectively. The first-stage booster cylinder 2 and the second-stage booster cylinder 3 are arranged on both sides of the hydraulic cylinder 1 and connected with the hydraulic cylinder 1 through the end covers 12. The hydraulic cylinder 1 further comprises a hydraulic piston 13, a first piston rod 14, and a second piston rod 15, wherein the first piston rod 14 and the second piston rod 15 are connected with the hydraulic piston 13. The first-stage booster cylinder 2 comprises 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 comprises 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 with the first-stage booster piston 22. The second piston rod 15 extends into the second-stage booster cylinder barrel 31 and is connected with the second-stage booster piston 32. At least one hydraulic suspension cavity 4 is arranged on the inner hole surface of the end cover 12 for storing hydraulic oil with pressure, so as to suspend the first piston rod 14 or the second piston rod 15 in the inner hole of the end cover 12.

[0046] In the embodiment, at least one hydraulic suspension cavity is arranged on the inner hole surface of the end cover of the hydraulic cylinder for storing hydraulic oil with pressure, so as to suspend the piston rod in the inner hole of the end cover. Meanwhile, the hydraulic oil in the hydraulic suspension cavity can also play a sealing role, thereby reducing the use of sealing elements. In the case of high-frequency and rapid reciprocating motion of the booster piston, the frictional heat and frictional loss can be greatly reduced, which is conducive to reducing the failure rate of the gas booster, prolonging the service life of the gas booster, and improving the working efficiency.

[0047] Embodiment Two

[0048] Figure 2 A 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] As shown in Figure 2 , the hydraulic cylinder 1 includes a hydraulic cylinder barrel 11 and a hydraulic piston 13, and the piston rods 14 and 15 are connected to the hydraulic piston 13. The inner hole of the hydraulic cylinder barrel 11 is gap sealed with the hydraulic piston 13 through tolerance control to form the friction pair A. By utilizing the throttling effect of the hydraulic oil in the gap between the inner hole of the hydraulic cylinder barrel 11 and the hydraulic piston 13, the oil pressure in the gap sealing can make the hydraulic piston 13 and the hydraulic cylinder barrel 11 have no contact or short contact movement. Since the reciprocating frequency of the hydraulic piston 13 in the hydraulic cylinder barrel 11 is very high, a short sealing effect can be formed between the hydraulic piston 13 and the hydraulic cylinder barrel 11 by utilizing the viscosity of the hydraulic oil, so as to replace the sealing element 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 is very small in one stroke of the hydraulic piston 13, which basically does not affect the effect of the hydraulic cylinder.

[0051] In some embodiments, as shown in Figure 3 , the outer circular surface of the hydraulic piston 13 is provided with at least one gap sealing groove 131 extending in the circumferential direction for storing hydraulic oil. The storage of hydraulic oil in the gap sealing groove 131 can improve the gap sealing effect and increase lubrication.

[0052] As shown in Figure 2 , the hydraulic cylinder further includes an end cover 12 arranged between the hydraulic cylinder barrel 11 and the supercharging cylinder barrel 21; and the inner hole surface of the end cover 12 is provided with at least one hydraulic suspension cavity 4. In the embodiments of the present disclosure, one hydraulic suspension cavity 4 extending in the circumferential direction can be arranged on the inner hole surface of the end cover 12, or a plurality of hydraulic suspension cavities 4 can be arranged on the inner hole surface of the end cover 12 in the circumferential direction. The embodiments of the present disclosure do not make special limitations on this. In some embodiments, the inner hole surface of the end cover 12 is provided with a plurality of hydraulic suspension cavities 4, and the plurality of hydraulic suspension cavities 4 are uniformly distributed in the circumferential direction. For example, the number of the hydraulic suspension cavities 4 is four.

[0053] As shown in Figure 2 , Figure 4 , the inner hole surface of the end cover 12 is provided with a plurality of hydraulic suspension cavities 4 distributed in the circumferential direction; and as shown in Figure 5As shown, the end cover 12 is further provided with a circumferentially extending hydraulic annular circuit and a plurality of circumferentially distributed pressurizing ports, each corresponding to a hydraulic suspension cavity 4; the pressurizing ports are in communication with the hydraulic annular circuit and the corresponding hydraulic suspension cavity 4.

[0054] As shown, Figure 5 The hydraulic annular circuit is in communication with the pressurizing ports W, X, Y, Z, and the hydraulic oil can flow through the hydraulic annular circuit to each pressurizing port from any one of the pressurizing ports, enter and store in the hydraulic suspension cavity 4, and generate hydrostatic pressure on the piston rod 14, 15, so that the piston rod 14, 15 is suspended in the inner hole of the end cover 12, realizing the frictionless contact between the piston rod 14, 15 and the inner hole of the end cover 12, and reducing the frictional heat generation between the friction pairs D, E formed by the piston rod 14, 15 and the inner hole of the end cover 12. After the hydraulic suspension support structure is provided, the piston rod 14, 15 no longer needs to be guided and supported by the guide support ring in the inner hole of the end cover 12, further reducing the frictional heat generation of the friction pairs D, E. In addition, in the hydraulic suspension support structure, the hydraulic oil in the hydraulic suspension cavity 4 and the hydraulic annular circuit is flowing, which can timely take away the heat generated by the friction of the friction pairs D, E.

[0055] In some embodiments, as shown, Figure 5 Each pressurizing port is in communication with the hydraulic annular circuit through a pressurizing channel; the pressurizing channel is provided with a throttling plug 6.

[0056] The throttling plug is a device that uses its adjustable internal aperture to control the flow resistance of the fluid, thereby affecting the pressure of the fluid; when the fluid passes through the throttling plug, if the plug is tightened, the aperture is reduced, and the resistance when the fluid passes through will increase, causing the pressure of the fluid before the throttling plug to rise; on the contrary, if the plug is loosened, the aperture is increased, and the resistance when the fluid passes through is reduced, the pressure of the fluid before the throttling plug will decrease; by changing the size of the aperture 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 is subjected to the liquid resistance effect of the throttling plug 6, and realizes proportional pressure drop at each pressurizing port, so that the pressure of the hydraulic oil at each pressurizing port, i.e. the pressure of the hydraulic oil in each hydraulic suspension cavity, remains consistent, thereby enabling the piston rod 14, 15 to automatically center in the inner hole of the end cover 12, and ensuring the frictionless contact between the piston rod 14, 15 and the inner hole of the end cover 12. In some embodiments, the end cover 12 is provided with a buffer ring, a separation ring, and a cylinder piston sealing ring, and the automatic centering of the piston rod 14, 15 also enables the buffer ring, the separation ring, and the cylinder piston sealing ring to be free from the radial eccentric load caused by the flexibility of the piston rod 14, 15, and to be free from the lateral force of the hydraulic oil pressure, thereby ensuring only a small constant residual friction, and further reducing the frictional heat generation.

[0058] In some embodiments, such as Figure 4 As shown, a pressure detection channel 7 is provided between the throttling plug 6 and the hydraulic suspension chamber 4. Each pressurization port corresponds to one pressure detection channel 7, which is connected to the pressure relief channel. A pressure sensor is installed in the pressure detection channel 7 to detect 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. The central hydraulic control system controls the electronic regulating valve to adjust the pressure at the pressure relief port based on the pressure data, thereby achieving real-time feedback regulation and ensuring that the pressure in the hydraulic suspension chamber 4 remains stable and consistent.

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

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

[0061] In some embodiments, the hydraulic suspension ring 120 is formed in the inner hole of the end cap 12 by a welding process. For example, copper is welded onto the inner hole of the end cap 12 before the hydraulic suspension cavity 4 is machined.

[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 cavity 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, such as Figure 4 As shown, the inner surface of the hydraulic suspension ring 120 is also provided with multiple parallel oil reservoirs, which are connected to the hydraulic suspension chamber 4. When hydraulic oil enters the hydraulic suspension chamber 4 through the throttle plug 6, the hydraulic oil will fill the entire parallel oil reservoir through the hydraulic suspension support gap. Regardless of whether the piston rods 14 and 15 move to the left or right, the entire hydraulic suspension support gap will store pressurized hydraulic oil. The parallel oil reservoir increases the oil storage capacity of the hydraulic suspension support gap and increases the contact area with the end cap 12, which is conducive to generating a more uniform and stable support pressure, and provides a better support and centering effect for the piston rods 14 and 15. At the same time, the interface of the parallel oil reservoir increases the cross-sectional area of ​​the oil film, which can enhance the sealing effect, offset part of the pressure of the hydraulic oil in the hydraulic cylinder, 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, the end cover 12 is further provided with a reverse dustproof ring in the inner hole away from one end of the hydraulic cylinder barrel 12, which is used to scrape oil on the piston rod 14, 15 in the direction close to the hydraulic cylinder barrel 12.

[0065] In the present embodiment, the reverse dustproof ring can achieve the effect of reverse oil scraping. The reverse dustproof ring, as a sealing ring, cooperates with the remaining sealing rings to achieve the sealing effect and prevent oil in the oil chamber from entering the isolation chamber. The reverse dustproof ring can achieve the effect of scraping oil on the piston rod to prevent oil from adhering to the piston rod and entering the isolation chamber. If hydrogen gas leaks in the isolation chamber, contact with high-temperature hydraulic oil can cause the hydrogen gas to dissolve in the hydraulic oil, resulting in "cavitation phenomenon" and corrosion of the plating layer of the piston rod. In addition, as the pressure increases, the ignition point of hydrogen gas decreases, and there is a risk of combustion and explosion of high-temperature and high-pressure hydrogen gas in contact with the hydraulic oil of the piston rod.

[0066] In some embodiments, the reverse dustproof ring is further provided with an oil scraping and draining groove and a draining channel on the side close to the hydraulic cylinder barrel, which can drain the oil scraped by the reverse dustproof ring in time and prevent the oil pressure from directly impacting the reverse dustproof ring after the sealing fails, serving as a second guarantee for sealing.

[0067] In some embodiments, as shown in Figure 2 , the hydraulic cylinder further comprises a proximity switch for detecting the position of the hydraulic piston.

[0068] The proximity switch is added to the hydraulic cylinder barrel to determine when the hydraulic piston hits the bottom. The proximity switch signal is detected in real time by a matching hydraulic system processor to control the accurate and real-time pressurization of the oil chamber, control the timely reversal of the hydraulic piston, ensure the synchronization of the oil chamber pressurization and the air chamber inflation, avoid the lag of the movement of the two chambers, and improve the compression efficiency.

[0069] In some embodiments, as shown in Figure 2 , the booster cylinder barrel comprises an isolation chamber on the side of the booster piston close to the driving module; the gas inlet and outlet of the isolation chamber are respectively provided with a gas concentration sensor for detecting the gas concentration in the isolation chamber.

[0070] The hydrogen gas concentration sensor is added to the gas inlet and outlet of the isolation chamber to detect the hydrogen gas concentration in the isolation chamber in real time and feed back the data to the hydraulic system control center in real time. When the hydrogen gas leaks due to the failure of the cylinder piston, the isolation chamber will be filled with the leaked hydrogen gas. When the hydrogen gas reaches a certain concentration, it will trigger the sensor alarm device, and the signal will be transmitted to the central information processing system. The system will issue an instruction to stop the oil cylinder pressurization immediately, which can realize real-time early warning of hydrogen gas leakage and ensure the safety of operation.

[0071] Embodiment Three

[0072] Figure 1 and Figure 2This is a schematic diagram of a gas booster according to an embodiment of the present disclosure.

[0073] like Figure 1 As shown, the hydraulically 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 caps 12 respectively disposed at both ends of the cylinder barrel; the primary booster cylinder 2 and the secondary booster cylinder 3 are respectively disposed on both sides of the hydraulic cylinder 1 and connected to the hydraulic cylinder 1 through the end caps 12. The hydraulic cylinder 1 also includes a hydraulic piston 13, a first piston rod 14, and a second piston rod 15, the first piston rod 14 and the second piston rod 15 being connected to the hydraulic piston 13; the primary booster cylinder 2 includes a primary booster cylinder barrel 21 and a primary booster piston 22 disposed 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 disposed in the secondary booster cylinder barrel 31.

[0074] The inner surfaces of the booster cylinders 21 and 31 are coated with diamond-like carbon (DLC) coatings, while the outer surfaces of the booster pistons 22 and 32 are coated with low-friction composite coatings, thus forming a friction pair. Applying the DLC coating process to the inner surfaces of the booster cylinders 21 and 31 can both increase the hardness of the inner bores (e.g., achieving a hardness HV of 3000 or higher) and reduce the roughness of the inner bores. The low-friction composite coating features ultra-low friction, high hardness, and low frictional loss. The inner surfaces of the booster cylinders 21 and 31 coated with DLC and the outer surfaces of the booster pistons 22 and 32 coated with low-friction composite coatings form a low-friction, highly stable friction pair.

[0075] In some embodiments, a seal is used between the inner bore of the booster cylinders 21 and 31 and the outer circle of the booster pistons 22 and 32. The friction pair composed of DLC coating and low-friction composite coating has a low coefficient of friction, which can significantly reduce frictional heat generation and frictional loss, thus extending the life of the seal, enhancing the sealing effect, and reducing the risk of hydrogen leakage.

[0076] This disclosure does 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 thickness of the DLC coating is 2 to 3 μm.

[0078] In the embodiment, the combination of the DLC coating and the low-friction composite coating is used to form a low-friction and high-stability friction pair between the inner hole surface of the supercharging cylinder 21, 31 and the outer circle of the supercharging piston 22, 32, which is beneficial to realize a high-precision inner hole in the supercharging cylinder 21, and the inner hole of the supercharging cylinder 21, 31 and the outer circle of the supercharging piston 22, 32 are matched by a tolerance control gap, which can greatly reduce the friction heat generation, reduce the friction loss of the inner hole of the supercharging cylinder 21, 31 and the outer circle of the supercharging piston 22, 32, and is beneficial to reduce the failure rate of the gas supercharger, prolong the service life of the gas supercharger, and improve the working efficiency.

[0079] Embodiment four

[0080] Figure 6 It is a sectional view of a liquid-driven hydrogen gas supercharger, Figure 7 It is a schematic perspective view of the liquid-driven hydrogen gas supercharger.

[0081] As shown in Figure 6 , Figure 7 , the hydrogen gas supercharger comprises a hydraulic cylinder 100, a primary supercharging cylinder 200, and a secondary supercharging cylinder 300; the primary supercharging cylinder 200 comprises a primary supercharging cylinder 201 and a primary supercharging piston 202 arranged in the primary supercharging cylinder 201; the secondary supercharging cylinder 300 comprises a secondary supercharging cylinder 301 and a secondary supercharging piston 302 arranged in the secondary supercharging cylinder 301; the primary supercharging cylinder 201 and the secondary supercharging cylinder 301 are arranged on both sides of the hydraulic cylinder 100 respectively. The hydraulic cylinder 100 comprises a hydraulic piston 101, a first piston rod 102, a second piston rod 103, and a hydraulic cylinder 104, the first piston rod 102 extends into the primary supercharging cylinder 201 and is connected with the primary supercharging piston 202; the second piston rod 103 extends into the secondary supercharging cylinder 301 and is connected with the secondary supercharging piston 302. In the embodiment, the hydrogen gas supercharger pressurizes low-pressure hydrogen gas to high-pressure hydrogen gas through two-stage supercharging cylinders, for example, pressurizes through the primary supercharging cylinder 200, and the outlet pressure of the primary supercharging cylinder 200 is 45 MPa; then enters the secondary supercharging cylinder 300 for pressurization, and the outlet pressure of the secondary supercharging cylinder 300 is 90 MPa.

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

[0083] In the friction pair A, the gap sealing design is used for the hydraulic piston 101. The throttling effect of the oil through the gap between the gap sealing sleeve and the piston rod replaces the common pressurized sealing to achieve the sealing effect. In addition, the oil storage groove is added to the surface of the hydraulic piston 101 to increase the lubrication. The short contact or non-contact movement of the hydraulic piston 101 and the hydraulic cylinder barrel 104 can be realized by using the oil pressure. The frequency of the reciprocating movement of the oil cylinder is very fast. The short sealing effect can be formed between the gap of the inner wall of the hydraulic piston 101 and the hydraulic cylinder barrel 104 by using the viscosity of the hydraulic oil. Since the frequency of the movement of the hydraulic piston 101 in the hydraulic cylinder 100 is very high, the leakage of the hydraulic oil in the gap sealing during a stroke process is very small, which does not affect the effect of the whole hydraulic cylinder 100.

[0084] In the friction pair B and the friction pair C, the outer peripheral surface of the primary pressurizing piston 202 and the secondary pressurizing piston 302 is sprayed with a low-friction composite coating such as a PTFE-based composite coating or a nylon-based composite coating. 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. The inner peripheral surface of the secondary pressurizing cylinder barrel 301 and the primary pressurizing cylinder barrel 201 is sprayed with a DLC coating. The DLC coating can increase the hardness of the cylinder barrel hole and reduce the roughness of the cylinder barrel hole, which cooperates with the PTFE-based or nylon-based composite coating to form a low-friction and high-stability friction pair.

[0085] In the friction pair D and the friction pair E, the hydraulic suspension support structure is designed. The oil is injected from the pressing port and flows to each pressurizing port through the hydraulic annular circuit, and then the proportional pressure reduction is realized by the liquid resistance effect of the throttling screw plug. The liquid suspension ring and the hydraulic piston 101 are cooperated to control the tolerance and the gap, so that the hydraulic oil is stored in the internal suspension isolation cavity of the liquid suspension ring, thereby suspending the hydraulic piston 101. The fluid static pressure effect can automatically center the piston rod to realize the 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 is taken away by the hydraulic oil circulating injected into the pressing port, thereby avoiding the generation of more heat. Due to the automatic centering of the piston rod, the buffer ring, the isolation ring, and the cylinder piston sealing ring in the end cover are not subjected to the radial bias load generated by the flexibility of the piston rod and the lateral force generated by the oil pressure, so only a small constant residual friction is generated, and the heat generated is very small.

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

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

[0088] A cooling water circulation system is arranged on the outer periphery of the secondary pressurizing cylinder barrel 301. As shown, Figure 6 the cooling water circulation system includes a water inlet 303, a flow guide 304, and a water outlet 305. The flow guide 304 is arranged on the outer periphery of the secondary pressurizing cylinder barrel 301, and is arranged around the outer periphery of the secondary pressurizing cylinder barrel 301 to divide the outer periphery of the secondary pressurizing cylinder barrel 301 into cooling water channels. The cooling water channels are in communication with the water inlet 303 and the water outlet 305. Cooling water enters the cooling water channels from the water inlet 303 and is discharged from the water outlet 305, thereby cooling the secondary pressurizing cylinder barrel 301.

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

[0090] In some embodiments, the flow guide 304 is a copper pipe.

[0091] The secondary pressurizing piston 302 includes a body portion and a cylindrical portion located on one side of the body portion and surrounding the central axis of the secondary pressurizing piston 302. The cylindrical portion forms a recess, and the second piston rod 103 is fitted in the recess. An annular groove is formed on the corresponding end of the second piston rod 103, and a fitting member is embedded in the groove. The fasteners that pass through the fitting member and are screwed into the cylindrical portion fixedly connect the secondary pressurizing piston 302 with the second piston rod 103.

[0092] On the other side of the body portion of the secondary pressurizing piston 302, a sealing member is fixed to the body portion of the secondary pressurizing piston 302 through fasteners such as screws. A groove is formed on the outer peripheral surface of the secondary pressurizing piston 302 to accommodate the sealing member. Of course, the structure of the secondary pressurizing piston 302 and the connection mode with the second piston rod 103 are not limited thereto.

[0093] To reduce the friction between the secondary supercharging piston 302 and the secondary supercharging cylinder 301, a PTFE-based or nylon-based composite coating is sprayed on the outer circumferential surface of the secondary supercharging piston 302, one example of which is the P80870 nylon-based composite coating, but not limited to this. 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 supercharging cylinder 301, which not only can improve the hardness of the cylinder inner hole, in one embodiment, the cylinder inner hole hardness can reach HV≥3000, but also can reduce the roughness of the cylinder inner hole, in one embodiment, the roughness of the cylinder inner hole can reach Ra0.05 or even higher. The secondary supercharging piston 302 sprayed with the PTFE-based or nylon-based composite coating and the secondary supercharging cylinder 301 sprayed with the DLC coating form a low-friction and high-stability friction pair.

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

[0095] A cooling water circulation system is provided on the outer circumferential side of the primary supercharging cylinder 201, which is similar to the cooling water circulation system of the above-mentioned secondary supercharging cylinder 301, which will not be described here.

[0096] The primary supercharging piston 202 includes a body portion and a cylindrical portion located on one side of the body portion and surrounding the central axis of the primary supercharging piston 202, and the cylindrical portion and the cylindrical portion have different inner diameters to form a step between them, specifically, the inner diameter of the cylindrical portion is smaller than the inner diameter of the cylindrical portion, and the cylindrical portion and the cylindrical portion form a recess, and the first piston rod 102 is fitted in the recess. An annular groove is formed on the corresponding end of the first piston rod 102, and the fitting member is embedded in the groove. The fasteners that pass through the fitting member and are screwed into the cylindrical portion fixedly connect the primary supercharging piston 202 with the first piston rod 102.

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

[0098] In order to reduce the friction between the first-stage supercharged piston 202 and the first-stage supercharged cylinder 201 due to the movement of the piston, a PTFE-based or nylon-based composite coating is sprayed on the outer surface of the first-stage supercharged piston 202 of the utility model, one example of which is a P80870 nylon-based composite coating, but not limited to this. As described 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 peripheral surface of the first-stage supercharged cylinder 201, which not only improves the hardness of the cylinder bore to HV≥3000, but also reduces the roughness of the cylinder bore to Ra0.05 or even higher. The first-stage supercharged piston 202 sprayed with the PTFE-based or nylon-based composite coating and the first-stage supercharged cylinder 201 sprayed with the DLC diamond-like carbon coating form a low-friction and high-stability friction pair.

[0099] In addition, the present embodiment improves the DLC coating manufacturing process through an integrated process of plasma enhancement and deposition. Specifically, first, the substrate surface is bombarded by plasma to enhance the active sites of the substrate and improve the bonding capacity of the substrate. Carbon ions are generated by a high-energy ion source and injected into the substrate surface. By precisely controlling the energy, dose and angle of ion implantation, a carbon-rich transition layer can be formed on the substrate surface, which can improve the interface bonding between the coating and the substrate, reduce the stress within the coating, and provide a good foundation for the subsequent deposition process. Then, a microwave plasma source is used to generate a carbon-rich plasma, and by reasonably controlling the power, pressure, gas flow of the plasma and using a magnetic field to control the plasma motion, a stable and dense DLC carbon coating structure with excellent performance and good control of the coating thickness can be generated. Through annealing and laser modification processes, the surface finish and lubrication of the coating are improved.

[0100] A high-precision polishing process can be used on the inner peripheral 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. Its principle is that under the action of a magnetic field, the magnetic particles in the magnetorheological fluid are polarized to form a chain structure, and the hardness and stiffness 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 workpiece surface reach atomic level flatness. By adding specific chemical reagents to the polishing liquid, a 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. By combining these two polishing methods, first, magnetorheological polishing is used for rough polishing to quickly reduce the roughness of the workpiece surface, and then chemical mechanical polishing is used 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 interferometer or atomic force microscope is 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 of the magnetorheological polishing, the polishing liquid flow rate, the polishing pressure of the chemical mechanical polishing, the polishing time, etc. Through this intelligent control, the polishing of the workpiece surface can be accurately realized, and the roughness target of 0.1 microns can be ensured.

[0102] In order to ensure the stability of the polishing environment, a super-clean constant temperature and humidity polishing environment is constructed. In a closed polishing workshop, dust and impurity particles are removed by an air filtration system to maintain air cleanliness above 100 levels. The temperature and humidity adjusting device is used to control the environmental temperature within ±0.1℃ and the humidity within ±2%. Stable environment can prevent external factors from interfering with the polishing process, reduce the generation of surface defects, and is crucial for achieving 0.1 micron ultra-precision polishing effect.

[0103] High-precision cylinder bore can greatly reduce the friction heat of the sealing ring, improve the service life of the sealing element, enhance the sealing effect of the sealing element, 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 surface of the hydraulic piston 101 and the inner peripheral surface of the hydraulic cylinder barrel 104 form a friction pair, such as Figure 6 Friction pair A.

[0105] At the friction pair A, a gap sealing design is used for the hydraulic piston 101. Specifically, a plurality of annular oil storage grooves are arranged 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 different shapes can be used according to specific applications, such as semicircular, semi-elliptical, V-shaped, U-shaped, etc.

[0106] Compared with the sealing ring sealing, the oil liquid is throttled through the gap between the gap sealing sleeve and the piston rod, thereby replacing the ordinary pressurized sealing element to achieve the sealing effect. The increase of the oil storage groove on the piston surface can increase the lubrication, and the use of oil pressure can realize the short contact or non-contact movement of the piston and the cylinder barrel. The frequency of the oil cylinder reciprocating motion is very fast, and the viscosity of the hydraulic oil can form a short sealing effect between the gap between the piston and the cylinder barrel. Due to the high frequency of the oil cylinder movement, the oil leakage in the gap sealing during a stroke process is very small, which does not affect the overall effect of the oil cylinder.

[0107] The hydraulic cylinder 100 also includes a hydraulic suspension ring, such as Figure 6As shown in the friction pair D, the hydraulic suspension ring is arranged between the outer circumferential surface of the hydraulic piston 101 and the inner hole surface of the end cover as the hydraulic cylinder barrel 104. A plurality of pressing ports are arranged in the outer circumferential surface of the end cover, and the pressing ports extend to the inner circumferential surface of the end cover in the radial direction through the hydraulic passages. Four hydraulic suspension pressing ports are arranged in the hydraulic suspension ring in a circumferential equidistant distribution, but the number of the pressing ports is not limited to four, and can be one, two, three, five or more.

[0108] Each pressing port is communicated with each other through a hydraulic ring circuit. A throttling screw plug is arranged in each hydraulic passage, and the throttling screw plug has a liquid resistance effect, so as to realize proportional pressure reduction. A passage communicated with the hydraulic passage in the transverse direction is arranged on the downstream side of the throttling screw plug in the oil direction, the passage is communicated with a detection passage extending to the outer circumferential surface of the end cover in the radial direction, and the detection passage terminates at a pressure detection port in the outer circumferential surface of the end cover, so that the pressure in the passage can be detected through the pressure detection port.

[0109] A plurality of hydraulic holes penetrating through the hydraulic suspension ring in the radial direction are arranged in the hydraulic suspension ring, and each hydraulic hole is communicated with each hydraulic passage. A hydraulic suspension oil storage groove communicated with the plurality of hydraulic holes is arranged in the inner circumferential surface of the hydraulic suspension ring, and each hydraulic suspension oil storage groove extends at least a part along the circumferential direction of the hydraulic suspension ring in the cross section. In one embodiment, each hydraulic suspension oil storage groove is independent of each other and is not communicated with each other. In one embodiment, each hydraulic suspension oil storage groove is communicated with each other, and forms a gap between the hydraulic suspension ring and the piston rod.

[0110] A plurality of oil discharge grooves corresponding to the hydraulic suspension oil storage groove are formed in the inner circumferential surface of the end cover at one end of the hydraulic suspension ring, and each oil discharge groove is communicated with a corresponding oil discharge passage extending to the outer circumferential surface of the end cover in the radial direction. The oil discharge passage terminates at a discharge port in the outer circumferential surface of the end cover, so that the oil in the passage can be discharged through the discharge port.

[0111] As described above, the utility model is provided with a hydraulic suspension support structure, and before the oil cylinder moves, the pressure is punched into the hydraulic suspension pressing port, and then is circulated to each pressing port through the hydraulic ring circuit, and then the proportional pressure reduction is realized through the liquid resistance effect of the throttling screw plug. Through the tolerance control and gap cooperation between the hydraulic suspension ring and the piston rod, the oil pressure can be stored in the internal suspension isolation cavity of the hydraulic suspension ring, so that the piston rod is suspended, and the fluid static pressure action can automatically center the piston rod. In this way, the frictionless contact between the piston rod and the end cover is realized, the guide support ring is removed, and the heat generated in the movement process of the piston rod can be taken away by the hydraulic oil circulatingly injected into the pressing port, so that more heat is avoided. Due to the automatic centering of the piston rod, the buffer ring, the isolation ring and the cylinder piston sealing ring in the end cover are not subjected to the radial eccentric 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 that only a small constant residual friction is generated, and the generated heat is small.

[0112] Example embodiments have been disclosed herein and, although the specific terms are employed, they are used in a generic sense only and should not be construed to be limited to the specific embodiments described herein. In some instances, those of ordinary skill in the art will appreciate that a feature, structure, or characteristic described in connection with a particular embodiment can be used in connection with another embodiment unless expressly mixed in contradiction thereto. Changes in form and detail can be made without departing from the scope of the disclosure as set forth in the accompanying claims.

Claims

1. A liquid-driven gas booster 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 arranged at both ends of the cylinder barrel respectively; the first-stage booster cylinder and the second-stage booster cylinder are arranged at both sides of the hydraulic cylinder respectively and connected with 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 with the hydraulic piston; The first-stage booster cylinder comprises a first-stage booster cylinder barrel and a first-stage booster piston arranged in the first-stage booster cylinder barrel; the second-stage booster cylinder comprises a second-stage booster cylinder barrel and a second-stage booster piston arranged in the second-stage booster cylinder barrel; The first piston rod extends into the first-stage booster cylinder barrel and is connected with the first-stage booster piston, and the second piston rod extends into the second-stage booster cylinder barrel and is connected with the second-stage booster piston; At least one hydraulic suspension cavity is arranged on the inner hole surface of the end cover, which is used to store hydraulic oil with 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 intensifier according to claim 1, wherein, A plurality of hydraulic suspension cavities are arranged on the inner hole surface of the end cover, and the plurality of hydraulic suspension cavities are distributed in a circumferential direction; the end cover is further provided with a hydraulic annular loop extending in the circumferential direction and a plurality of pressurizing ports distributed in the circumferential direction, each of the pressurizing ports corresponding to one of the hydraulic suspension cavities; the pressurizing ports are in communication with the hydraulic annular loop and the corresponding hydraulic suspension cavities.

3. The liquid-driven gas intensifier according to claim 2, wherein, Each of the pressurizing ports is in communication with the hydraulic annular loop through a pressurizing channel; a throttling plug is arranged in the pressurizing channel, which is used to keep the pressure at each of the pressurizing ports consistent.

4. The liquid-driven gas intensifier according to claim 3, wherein, Each of the pressurizing ports corresponds to a pressure detection channel, the pressure detection channel is in communication with the pressurizing channel, and a pressure sensor is arranged in the pressure detection channel, which is used to detect the pressure in the corresponding hydraulic suspension cavity.

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

6. The liquid-driven gas intensifier 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 cavities are arranged on the inner hole surface of the hydraulic suspension ring.

7. The liquid-driven gas intensifier according to claim 6, wherein 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 through a surfacing machining process.

8. The liquid-driven gas intensifier according to claim 6, wherein, An oil storage structure is further arranged on the inner hole surface of the hydraulic suspension ring, and the oil storage structure is in communication with the hydraulic suspension cavities.

9. The liquid-driven gas intensifier according to claim 8, wherein, The oil storage structure comprises a plurality of parallel oil storage grooves distributed in parallel on the inner hole surface of the hydraulic suspension ring.

10. The liquid-driven gas intensifier according to any one of claims 1 to 5, wherein, The inner hole of the hydraulic cylinder barrel is in clearance seal with the hydraulic piston through tolerance control.

11. The liquid-driven gas intensifier according to claim 10, wherein, At least one clearance seal groove is arranged on the outer circular surface of the hydraulic piston, and the clearance seal groove extends in the circumferential direction and is used to store hydraulic oil.

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

13. The liquid-driven gas intensifier according to claim 12, wherein, An oil scraping and storing groove is arranged in the inner hole of the end cover on the side of the reverse dustproof ring close to the hydraulic cylinder barrel.

14. The liquid-driven gas intensifier according to any one of claims 1 to 5, wherein, The hydraulic cylinder further comprises a proximity switch for detecting the position of the hydraulic piston.

15. The liquid-driven gas intensifier according to any one of claims 1 to 5, wherein, The primary and secondary pressurizing cylinder barrels comprise an isolation chamber on the side of the primary or secondary pressurizing piston close to the hydraulic cylinder.

16. The liquid-driven gas intensifier according to any one of claims 1 to 5, wherein, Cooling water channels are further arranged on the outer walls of the primary and secondary pressurizing cylinder barrels.

17. The liquid-driven gas intensifier according to claim 16, wherein, Spirally extending flow guides are arranged on the outer walls of the pressurizing cylinder barrels, which divide the cooling water channels on the outer walls of the pressurizing cylinder barrels.

18. The liquid-driven gas intensifier according to any one of claims 1 to 5, wherein, The inner hole of the primary pressurizing cylinder barrel is matched with the primary pressurizing piston through a tolerance controlled gap, the inner hole surface of the primary pressurizing cylinder barrel is covered with a diamond-like carbon coating, and the outer circular surface of the primary pressurizing piston is covered with a PTFE-based composite coating or a nylon-based composite coating. The inner hole of the secondary pressurizing cylinder barrel is matched with the secondary pressurizing piston through a tolerance controlled gap, the inner hole surface of the secondary pressurizing cylinder barrel is covered with a diamond-like carbon coating, and the outer circular surface of the secondary pressurizing piston is covered with a PTFE-based composite coating or a nylon-based composite coating.

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