Hydrogen compressor driven by closed hydraulic system

Abstract

The invention discloses a hydrogen compressor driven by a closed hydraulic system, which comprises a hydrogen pressure cylinder, air cylinder sections symmetrically arranged at the two ends in the hydrogen pressure cylinder, driving sections symmetrically arranged on the two sides of the middle part of the hydrogen pressure cylinder, and the closed hydraulic system for driving the hydrogen pressure cylinder to reciprocate, a piston rod penetrating through the air cylinder section and the driving section is arranged in the hydrogen pressure cylinder, a driving piston sleeve is fixedly connected to the side, located in the driving section, of the outer side wall of the piston rod, the driving section is divided into a driving oil cavity and an isolation cavity through the driving piston sleeve, and an end piston sleeve is fixedly connected to the end of the piston rod; the air cylinder section is divided into a first compression cavity and a second compression cavity through an end piston sleeve. Through cooperation of the hydrogen pressure cylinder, the closed variable pump assembly, the first main oil pipe and the second main oil pipe, throttling loss and backpressure loss are remarkably reduced, the hydraulic driving efficiency is improved, and the problem that an existing open type hydraulic system is low in energy efficiency is solved.

Description

Technical Field

[0001] This invention relates to the field of hydrogen compression technology, specifically to a hydrogen compressor driven by a closed hydraulic system. Background Technology

[0002] In hydrogen refueling stations and related hydrogen energy applications, hydrogen typically needs to be compressed to a high pressure level to meet storage and refueling requirements. Liquid-driven hydrogen compressors are widely used in hydrogen boosting systems because they can output higher pressures.

[0003] Existing hydraulically driven hydrogen compressors mostly employ open hydraulic system structures, where hydraulic oil is drawn from the tank by a hydraulic pump, drives the actuators via hydraulic components such as directional valves and throttle valves, and then flows back to the tank. Under this structure, the hydraulic oil needs to frequently enter and exit the tank and pass through multiple valves and pipelines during operation. This not only easily generates significant throttling and back pressure losses, resulting in low system efficiency, but also, under high-frequency reciprocating operation or high-flow conditions, the hydraulic pump suction side is prone to cavitation and vaporization, affecting the stability and reliability of the system operation.

[0004] In addition, open hydraulic systems typically switch the drive direction through a directional valve. During the switching process, the hydraulic oil flow direction changes abruptly, which can easily cause pressure fluctuations and shocks. This makes the reciprocating motion of the drive piston rod unstable, which is not conducive to the continuous and stable compression of hydrogen and further increases the system's energy consumption.

[0005] Therefore, how to reduce the energy loss of hydraulic oil in the system and improve the hydraulic drive efficiency while ensuring the stable operation of the liquid-driven hydrogen compressor has become a technical problem that urgently needs to be solved in this field. Summary of the Invention

[0006] To address the shortcomings of existing open hydraulic systems, which typically switch the drive direction via a reversing valve, causing abrupt changes in hydraulic oil flow during the reversing process, leading to pressure fluctuations and shocks, resulting in unstable reciprocating motion of the drive piston rod, which is detrimental to the continuous and stable compression of hydrogen and further increases system energy consumption, this invention provides a hydrogen compressor driven by a closed hydraulic system.

[0007] To solve the above-mentioned technical problems, the present invention provides the following technical solution: This invention discloses a hydrogen compressor driven by a closed hydraulic system, comprising a hydrogen booster cylinder, cylinder sections symmetrically arranged at both ends of the hydrogen booster cylinder, drive sections symmetrically arranged on both sides of the middle of the hydrogen booster cylinder, and a closed hydraulic system for driving the reciprocating motion of the hydrogen booster cylinder. A piston rod is disposed within the hydrogen booster cylinder, penetrating the cylinder sections and the drive section. A drive piston sleeve is fixedly connected to the outer wall of the piston rod on the side located within the drive section. The drive section is divided into a drive oil chamber and an isolation chamber by the drive piston sleeve. An end piston sleeve is fixedly connected to the end of the piston rod. The cylinder sections are divided into a first compression chamber and a second compression chamber by the end piston sleeve. The closed hydraulic system includes a closed variable pump assembly that is connected to both ends of the drive oil chamber and forms a closed main circuit, an oil tank, a flushing assembly connected to the closed variable pump assembly, a replenishing pump connected to the closed variable pump assembly and the oil tank, and a monitoring assembly. The closed-loop variable pump assembly includes a closed-loop variable piston pump and a first main oil pipe and a second main oil pipe that connect the closed-loop variable piston pump to both ends of the drive oil chamber.

[0008] As a preferred embodiment of the present invention, a first intake check valve and a first exhaust check valve connected to the first compression chamber are provided on the side of the outer wall of the hydrogen booster cylinder near the first compression chamber. A second intake check valve and a second exhaust check valve connected to the second compression chamber are provided on the side of the outer wall of the hydrogen booster cylinder near the second compression chamber. The two second intake check valves are respectively connected to the two first exhaust check valves.

[0009] As a preferred embodiment of the present invention, the closed-loop variable pump assembly further includes a proportional control valve connected to the closed-loop variable piston pump.

[0010] As a preferred embodiment of the present invention, the flushing assembly includes a hot oil shuttle valve connected to both the first main oil pipe and the second main oil pipe, a throttle valve connected downstream of the hot oil shuttle valve, and a first overflow valve connected downstream of the throttle valve.

[0011] As a preferred embodiment of the present invention, an oil regulating component is provided between the first overflow valve and the oil tank, the oil regulating component including a heat exchanger and a filter.

[0012] As a preferred embodiment of the present invention, the monitoring component includes a pressure transmitter disposed on the first main oil pipe and the second main oil pipe.

[0013] As a preferred embodiment of the present invention, the monitoring component further includes a temperature transmitter and a level controller mounted on the oil tank.

[0014] As a preferred embodiment of the present invention, the oil tank is equipped with an air filter and an electric heater.

[0015] As a preferred embodiment of the present invention, a shut-off valve is provided between the oil replenishment pump and the oil tank.

[0016] In summary, this application has the following beneficial effects: 1. This invention, through the cooperation of a hydrogen booster cylinder, a closed variable pump assembly, a first main oil pipe, and a second main oil pipe, forms a closed main circuit between the closed variable piston pump and both ends of the drive oil chamber. During the reciprocating motion of the drive piston rod, the hydraulic oil always circulates between the closed variable piston pump and the drive oil chamber, avoiding frequent entry and exit of hydraulic oil from the oil tank, thereby significantly reducing throttling losses and back pressure losses, improving hydraulic drive efficiency, and overcoming the problem of low energy efficiency in existing open hydraulic systems. 2. This invention, through the cooperation of a closed variable displacement piston pump and a proportional control valve in a closed variable pump assembly, directly controls the pressure changes at both ends of the drive oil chamber by adjusting the displacement and direction of the closed variable displacement piston pump without relying on a directional valve. This enables the piston rod to achieve smooth directional switching and stepless speed regulation, avoiding pressure fluctuations and shocks caused by the action of the directional valve in traditional open hydraulic systems, and improving the continuity and stability of the hydrogen compression process. 3. This invention, by setting up a flushing component in a closed hydraulic system and using a hot oil shuttle valve to draw out the low-pressure side oil from the first and second main oil pipes, and then controlling the flow and pressure through a throttle valve and a first relief valve, allows a portion of the high-temperature oil in the closed main circuit to be continuously renewed, while avoiding additional energy loss caused by drawing oil from the high-pressure side. This achieves effective control of the oil temperature in the closed hydraulic system and improves the long-term stability of the system. 4. The present invention provides an oil regulating component between the first overflow valve and the oil tank, so that the hydraulic oil drawn out by the flushing component passes through the heat exchanger and filter in sequence and then flows back to the oil tank, thereby cooling and filtering the hydraulic oil, maintaining the cleanliness and suitable temperature of the hydraulic oil, reducing the wear of hydraulic components, and extending the service life of the closed hydraulic system. 5. By setting up a replenishing oil pump and connecting it to the closed variable pump assembly and the oil tank, the present invention can replenish hydraulic oil to the main circuit in a timely manner when the oil volume in the closed main circuit is reduced due to flushing or internal leakage during the operation of the closed hydraulic system, so that the closed variable piston pump is always in a positive pressure oil supply state, reducing the risk of cavitation and cavitation, and improving the reliability of system operation. 6. This invention, by setting up monitoring components in a closed hydraulic system and installing pressure transmitters on the first and second main oil pipes, and temperature transmitters and level controllers on the oil tank, monitors the pressure, temperature and oil level in real time during system operation, enabling the closed hydraulic system to maintain a stable and safe working state under high-frequency and long-term operating conditions. Attached Figure Description

[0017] The accompanying drawings are provided to further illustrate the invention and form part of the specification. They are used in conjunction with embodiments of the invention to explain the invention and do not constitute a limitation thereof. In the drawings: Figure 1 This is a schematic diagram of the structure of a hydrogen compressor driven by a closed hydraulic system according to the present invention; Figure 2 This is a schematic diagram of the hydrogen booster cylinder structure of a hydrogen compressor driven by a closed hydraulic system according to the present invention. Figure 3 This is a schematic diagram of the closed hydraulic system structure of a hydrogen compressor driven by a closed hydraulic system according to the present invention.

[0018] Explanation of reference numerals in the attached figures: 1. Hydrogen booster cylinder; 2. Cylinder section; 21. First compression chamber; 22. Second compression chamber; 3. Drive section; 31. Drive oil chamber; 32. Isolation chamber; 4. Closed-loop hydraulic system; 41. Closed-loop variable pump assembly; 411. Closed-loop variable piston pump; 412. First main oil pipe; 413. Second main oil pipe; 414. Proportional control valve; 42. Oil tank; 43. Flushing assembly; 431. Hot oil shuttle valve; 432. Throttle valve; 433. First relief valve; 44. 45. Oil pump; 45. Monitoring components; 451. Pressure transmitter; 452. Temperature transmitter; 453. Level controller; 46. Oil conditioning components; 461. Heat exchanger; 462. Filter; 48. Air filter; 49. Electric heater; 410. Shut-off valve; 5. Piston rod; 6. Drive piston sleeve; 7. End piston sleeve; 8. First inlet check valve; 9. First outlet check valve; 10. Second inlet check valve; 11. Second outlet check valve. Detailed Implementation

[0019] The preferred embodiments of the present invention will be described below with reference to the accompanying drawings. It should be understood that the preferred embodiments described herein are for illustration and explanation only and are not intended to limit the present invention.

[0020] Example: Please refer to Figure 1 and Figure 2The present invention discloses a hydrogen compressor driven by a closed hydraulic system, comprising a hydrogen booster cylinder 1, cylinder sections 2 symmetrically arranged at both ends of the hydrogen booster cylinder 1, a drive section 3 symmetrically arranged on both sides of the middle of the hydrogen booster cylinder 1, and a closed hydraulic system 4 for driving the reciprocating motion of the hydrogen booster cylinder 1. A piston rod 5 is provided in the hydrogen booster cylinder 1, penetrating the cylinder section 2 and the drive section 3. A drive piston sleeve 6 is fixedly connected to the outer side of the piston rod 5 located in the drive section 3. The drive section 3 is divided into a drive oil chamber 31 and an isolation chamber 32 by the drive piston sleeve 6. An end piston sleeve 7 is fixedly connected to the end of the piston rod 5. The cylinder section 2 is divided into a first compression chamber 21 and a second compression chamber 22 by the end piston sleeve 7. Both the drive piston sleeve 6 and the end piston sleeve 7 are provided with sealing structures on their outer sides to ensure the sealing between the drive piston sleeve 6 and the drive section 3 and the sealing between the end piston sleeve 7 and the cylinder section 2. A first inlet check valve 8 and a first outlet check valve 9, which are connected to the first compression chamber 21, are provided on the outer wall of the hydrogen booster cylinder 1 near the first compression chamber 21. A second inlet check valve 10 and a second outlet check valve 11, which are connected to the second compression chamber 22, are provided on the outer wall of the hydrogen booster cylinder 1 near the second compression chamber 22. The two second inlet check valves 10 are respectively connected to the two first outlet check valves 9. The first inlet check valves 8 are all connected to the hydrogen inlet through pipelines. The second outlet check valves 11 are all connected to the hydrogen outlet through pipelines. The first outlet check valves 9 and the second inlet check valves 10 are all connected to each other through pipelines. The isolation chamber 32 is located on the opposite side of the drive oil chamber 31 and is used to structurally isolate the drive oil chamber 31 from other chambers. When the sealing structure on the drive piston sleeve 6 malfunctions, the hydraulic oil first enters the isolation chamber 32, thereby minimizing the risk of the hydraulic oil directly entering the cylinder section 2 and contaminating the hydrogen circuit, and providing a buffer space for subsequent processing.

[0021] Reference Figure 1 and Figure 3 The closed hydraulic system 4 includes a closed variable pump assembly 41 that is connected to both ends of the drive oil chamber 31 and forms a closed main circuit, an oil tank 42, a flushing assembly 43 connected to the closed variable pump assembly 41, a replenishing pump 44 and a monitoring assembly 45 connected to the closed variable pump assembly 41 and the oil tank 42, a shut-off valve 410 is provided between the replenishing pump 44 and the oil tank 42, and an air filter 48 and an electric heater 49 are provided on the oil tank 42. The closed-loop variable pump assembly 41 includes a closed-loop variable piston pump 411 and a first main oil pipe 412 and a second main oil pipe 413 respectively connecting the closed-loop variable piston pump 411 and the two ends of the drive oil chamber 31. The closed-loop variable piston pump 411 is connected to the two ends of the drive oil chamber 31 through the first main oil pipe 412 and the second main oil pipe 413 respectively, thereby forming a closed main circuit between the closed-loop variable piston pump 411 and the drive oil chamber 31 without passing through the oil tank 42. The closed-loop variable piston pump 411 can... Drive oil is pumped into the drive oil chamber 31. When the closed variable piston pump 411 outputs high-pressure hydraulic oil to the first main oil pipe 412, the hydraulic oil enters one side of the drive oil chamber 31 through the first main oil pipe 412, generating an axial thrust on the drive piston sleeve 6. At the same time, the hydraulic oil in the other side of the drive oil chamber 31 flows back to the closed variable piston pump 411 through the second main oil pipe 413, thereby forming a pressure difference at both ends of the drive oil chamber 31, causing the drive piston sleeve 6 to drive the piston rod 5 to move axially. Reference Figure 1 , Figure 2 and Figure 3 When it is necessary to reverse the movement of piston rod 5, the discharge direction of closed variable piston pump 411 is adjusted by proportional control valve 414, so that high pressure hydraulic oil enters the other side of drive oil chamber 31 through second main oil pipe 413, while hydraulic oil in first main oil pipe 412 flows back to closed variable piston pump 411, thereby reversing the pressure direction at both ends of drive oil chamber 31 and realizing the reverse movement of piston rod 5. In this way, the hydraulic oil always circulates between the closed variable piston pump 411 and the drive oil chamber 31, avoiding frequent entry and exit of the hydraulic oil into and out of the oil tank 42, thereby reducing throttling losses and back pressure losses, improving drive efficiency and reducing the risk of air suction. During use, the flow rate of the closed variable piston pump 411 can be changed by controlling the proportional control valve 414, thereby realizing the switching of drive direction and the adjustment of movement speed. The closed variable pump assembly 41 also includes a proportional control valve 414 connected to the closed variable piston pump 411. The proportional control valve 414 can adjust the flow rate of hydraulic oil pumped by the closed variable piston pump 411. The first main oil pipe 412 and the second main oil pipe 413 are respectively connected to the two ends of the drive oil chamber 31. Reference Figure 1 , Figure 2 and Figure 3 When the piston rod 5 moves away from the first compression chamber 21 under the drive of the closed hydraulic system 4, the effective volume of the first compression chamber 21 gradually increases, and a negative pressure is formed in the first compression chamber 21. The unpressurized hydrogen gas enters the first compression chamber 21 through the first inlet check valve 8 under the action of pressure difference, while the first outlet check valve 9 remains closed during this process, thereby completing the first stage of intake process. When the piston rod 5 moves toward the first compression chamber 21, the effective volume of the first compression chamber 21 gradually decreases, the first inlet check valve 8 closes, the hydrogen in the first compression chamber 21 is compressed to a medium pressure, and under the pressure, it is discharged from the first compression chamber 21 through the first outlet check valve 9. When the medium-pressure hydrogen gas discharged from the first compression chamber 21 enters the second intake one-way valve 10 through the first outlet one-way valve 9, the second compression chamber 22 draws in the medium-pressure hydrogen gas under the negative pressure generated by the movement of the end piston sleeve 7. When the piston rod 5 continues to move and reduces the effective volume of the second compression chamber 22, the hydrogen gas in the second compression chamber 22 is further compressed to form a higher pressure, and is discharged through the second outlet check valve 11 under the pressure, thereby completing the two-stage continuous compression process. By dividing the compression process into two stages, namely the first compression chamber 21 and the second compression chamber 22, the single-stage compression ratio can be effectively reduced, the pressure fluctuation during the compression process can be reduced, and the stability and safety of hydrogen compression can be improved. The monitoring component 45 includes a pressure transmitter 451 installed on the first main oil pipe 412 and the second main oil pipe 413. The monitoring component 45 also includes a temperature transmitter 452 and a level controller 453 installed on the oil tank 42. The flushing assembly 43 includes a hot oil shuttle valve 431 connected to both the first main oil pipe 412 and the second main oil pipe 413, a throttle valve 432 connected downstream of the hot oil shuttle valve 431, and a first overflow valve 433 connected downstream of the throttle valve 432. An oil regulating assembly 46 is provided between the first overflow valve 433 and the oil tank 42. The oil regulating assembly 46 includes a heat exchanger 461 and a filter 462. When the closed hydraulic system 4 is running, some hydraulic oil is drawn out from the low-pressure side of the first main oil pipe 412 or the second main oil pipe 413 through the hot oil shuttle valve 431, so as to avoid taking oil from the high-pressure side and causing additional energy loss. The drawn hydraulic oil enters the first relief valve 433 after the flow is limited by the throttle valve 432 to prevent the pressure of the flushing circuit from rising abnormally. The hydraulic oil discharged through the first relief valve 433 enters the oil regulating component 46, and is cooled by the heat exchanger 461 and filtered by the filter 462 before flowing back to the oil tank 42, thereby achieving continuous regulation of the hydraulic oil temperature and cleanliness. During the operation of the closed hydraulic system 4, due to the presence of oil priming in the flushing circuit and minor leakage inside the system, the amount of oil in the closed main circuit may gradually decrease. Therefore, hydraulic oil is replenished from the oil tank 42 to the closed variable pump assembly 41 by the replenishing oil pump 44. A shut-off valve 410 is installed between the replenishing oil pump 44 and the oil tank 42 to facilitate the control of the replenishing process. The pressure transmitter 451 in the monitoring component 45 is respectively installed on the first main oil pipe 412 and the second main oil pipe 413 to monitor the pressure status of the closed main circuit in real time. The temperature transmitter 452 is used to monitor the temperature of the hydraulic oil in the oil tank 42. The level controller 453 is used to monitor the oil level in the oil tank 42. The air filter 48 on the oil tank 42 is used to filter the gas connected between the oil tank and the outside. The electric heater 49 is used to heat the hydraulic oil in the oil tank 42 under low temperature conditions, thereby ensuring that the closed hydraulic system 4 can operate stably under different working conditions.

[0022] The implementation principle of this invention is as follows: During operation, after the equipment is put into operation, the closed hydraulic system 4 starts working. The closed variable displacement piston pump 411 in the closed variable pump assembly 41 operates under the control of the proportional control valve 414, causing the hydraulic oil to form a closed main circuit with the two ends of the drive oil chamber 31 through the first main oil pipe 412 and the second main oil pipe 413 respectively. The hydraulic oil circulates between the closed variable displacement piston pump 411 and the drive oil chamber 31. When the hydraulic oil enters one side of the drive oil chamber 31 through the first main oil pipe 412, the hydraulic pressure acts on the drive piston sleeve 6, and the drive piston sleeve 6 drives the piston rod 5 to move axially. At the same time, the hydraulic oil in the other side of the drive oil chamber 31... Hydraulic oil flows back to the closed variable piston pump 411 via the second main oil pipe 413. When the displacement direction of the closed variable piston pump 411 changes, the hydraulic oil enters the other side of the drive oil chamber 31 via the second main oil pipe 413, while the hydraulic oil in the first main oil pipe 412 flows back to the closed variable piston pump 411. This causes the pressure direction at both ends of the drive oil chamber 31 to change periodically, thereby realizing the reciprocating motion of the piston rod 5. Since the hydraulic oil always forms a closed loop between the closed variable piston pump 411 and the drive oil chamber 31, the hydraulic oil is prevented from frequently entering and leaving the oil tank 42, thereby reducing throttling losses and back pressure losses and reducing the risk of cavitation. During the reciprocating motion of piston rod 5, drive piston sleeve 6 moves axially under hydraulic pressure. Isolation chamber 32 is located on the opposite side of drive oil chamber 31. When the sealing structure on drive piston sleeve 6 is in normal condition, hydraulic oil only acts in drive oil chamber 31. When the sealing structure is damaged and the sealing performance is reduced, hydraulic oil preferentially enters isolation chamber 32, thereby avoiding hydraulic oil from directly entering cylinder section 2 and contaminating hydrogen circuit as much as possible. As the piston rod 5 reciprocates, the end piston sleeve 7 moves axially within the cylinder section 2. When the end piston sleeve 7 moves in one direction, the effective volume of the first compression chamber 21 increases and forms a negative pressure. Hydrogen enters the first compression chamber 21 through the first intake check valve 8. When the end piston sleeve 7 moves in the opposite direction, the effective volume of the first compression chamber 21 decreases, the first intake check valve 8 closes, and the hydrogen in the first compression chamber 21 is compressed and discharged through the first exhaust check valve 9. At the same time, when the effective volume of the second compression chamber 22 increases, the medium-pressure hydrogen discharged through the first exhaust check valve 9 enters the second compression chamber 22 through the second intake check valve 10. When the end piston sleeve 7 continues to move, causing the effective volume of the second compression chamber 22 to decrease, the hydrogen in the second compression chamber 22 is further compressed to form a higher pressure and is discharged through the second exhaust check valve 11, thus completing the staged compression process of hydrogen. During the continuous operation of the closed hydraulic system 4, a portion of the hydraulic oil in the closed main circuit is drawn out through the flushing assembly 43. The hot oil shuttle valve 431 automatically selects the low-pressure side oil in the first main oil pipe 412 and the second main oil pipe 413 for diversion to avoid energy loss caused by taking oil from the high-pressure side. The drawn-out hydraulic oil is limited by the throttle valve 432 and then enters the first relief valve 433 for pressure control. Subsequently, the hydraulic oil enters the oil regulating assembly 46 and is then heat-exchanged by the heat exchanger 461 and filtered by the filter 462 before flowing back to the oil tank 42 to achieve the regulation of hydraulic oil temperature and cleanliness. Due to the flushing process and the presence of minor leaks inside the system, the total amount of hydraulic oil in the closed main circuit may change. Hydraulic oil is replenished from the oil tank 42 to the closed variable pump assembly 41 by the replenishing oil pump 44. The shut-off valve 410 between the replenishing oil pump 44 and the oil tank 42 is used to control the replenishment of hydraulic oil. During equipment operation, the monitoring component 45 monitors the operating status of the closed hydraulic system 4 in real time. The pressure transmitter 451 is used to monitor the pressure status in the first main oil pipe 412 and the second main oil pipe 413, the temperature transmitter 452 is used to monitor the temperature of the hydraulic oil in the oil tank 42, the level controller 453 is used to monitor the level status of the oil tank 42, the air filter 48 on the oil tank 42 is used to filter the oil tank 42 when it is connected to the outside gas, and the electric heater 49 is used to heat the hydraulic oil in the oil tank 42 under low temperature conditions, thereby ensuring that the closed hydraulic system 4 can operate stably under different operating conditions, so that the piston rod 5 can continuously reciprocate, thereby driving hydrogen to continuously complete staged compression in the first compression chamber 21 and the second compression chamber 22.

[0023] Finally, it should be noted that the above descriptions are merely preferred embodiments of the present invention and are not intended to limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments and make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A hydrogen compressor driven by a closed hydraulic system, comprising a hydrogen booster cylinder (1), cylinder sections (2) symmetrically arranged at both ends inside the hydrogen booster cylinder (1), drive sections (3) symmetrically arranged on both sides of the middle part of the hydrogen booster cylinder (1), and a closed hydraulic system (4) for driving the hydrogen booster cylinder (1) to reciprocate, characterized in that: The hydrogen booster cylinder (1) is provided with a piston rod (5) that runs through the cylinder section (2) and the drive section (3). The outer side of the piston rod (5) is fixedly connected to a drive piston sleeve (6) on the side inside the drive section (3). The drive section (3) is divided into a drive oil chamber (31) and an isolation chamber (32) by the drive piston sleeve (6). The end of the piston rod (5) is fixedly connected to an end piston sleeve (7). The cylinder section (2) is divided into a first compression chamber (21) and a second compression chamber (22) by the end piston sleeve (7). The closed hydraulic system (4) includes a closed variable pump assembly (41) that is connected to both ends of the drive oil chamber (31) and forms a closed main circuit, an oil tank (42), a flushing assembly (43) connected to the closed variable pump assembly (41), a replenishing pump (44) connected to the closed variable pump assembly (41) and the oil tank (42), and a monitoring assembly (45). The closed variable pump assembly (41) includes a closed variable piston pump (411) and a first main oil pipe (412) and a second main oil pipe (413) respectively connecting the closed variable piston pump (411) and the two ends of the drive oil chamber (31).

2. A hydrogen compressor driven by a closed hydraulic system according to claim 1, characterized in that: The outer wall of the hydrogen booster cylinder (1) near the first compression chamber (21) is provided with a first inlet check valve (8) and a first outlet check valve (9) connected to the first compression chamber (21). The outer wall of the hydrogen booster cylinder (1) near the second compression chamber (22) is provided with a second inlet check valve (10) and a second outlet check valve (11) connected to the second compression chamber (22). The two second inlet check valves (10) are respectively connected to the two first outlet check valves (9).

3. A hydrogen compressor driven by a closed hydraulic system according to claim 1, characterized in that: The closed variable pump assembly (41) also includes a proportional control valve (414) connected to the closed variable piston pump (411).

4. A hydrogen compressor driven by a closed hydraulic system according to claim 1, characterized in that: The flushing assembly (43) includes a hot oil shuttle valve (431) connected to both the first main oil pipe (412) and the second main oil pipe (413), a throttle valve (432) connected downstream of the hot oil shuttle valve (431), and a first overflow valve (433) connected downstream of the throttle valve (432).

5. A hydrogen compressor driven by a closed hydraulic system according to claim 4, characterized in that: An oil regulating assembly (46) is provided between the first overflow valve (433) and the oil tank (42), and the oil regulating assembly (46) includes a heat exchanger (461) and a filter (462).

6. A hydrogen compressor driven by a closed hydraulic system according to claim 1, characterized in that: The monitoring component (45) includes a pressure transmitter (451) disposed on the first main oil pipe (412) and the second main oil pipe (413).

7. A hydrogen compressor driven by a closed hydraulic system according to claim 6, characterized in that: The monitoring component (45) also includes a temperature transmitter (452) and a level controller (453) mounted on the oil tank (42).

8. A hydrogen compressor driven by a closed hydraulic system according to claim 1, characterized in that: An air filter (48) and an electric heater (49) are provided on the oil tank (42).

9. A hydrogen compressor driven by a closed hydraulic system according to claim 8, characterized in that: A shut-off valve (410) is provided between the oil replenishment pump (44) and the oil tank (42).

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