High-pressure liquid-driven hydrogen compressor

Abstract

The invention relates to the technical field of supercharging equipment, in particular to a high-pressure liquid-driven hydrogen compressor. The oil cylinder comprises an oil cylinder body and two pressurizing cylinder bodies installed at the two ends of the oil cylinder body respectively, an oil cylinder piston assembly and a pressurizing cylinder piston assembly are arranged in inner cavities of the oil cylinder body and the pressurizing cylinder bodies in a sealed and sliding mode respectively, and the two ends of the oil cylinder piston assembly are in floating connection with piston rod bodies penetrating through the ends of the oil cylinder body in a sealed mode respectively. Under the combined action of the supporting ring and piston force, the piston rod body can generate floating fit relative to the oil cylinder body, the abutting end of the piston rod body and the pressure cylinder piston assembly is a convex spherical surface, and the abutting surface of the pressure cylinder piston assembly and the piston rod body is a plane perpendicular to the pressure cylinder body. The structure is stable in operation, and eccentric wear of a sealing piece can be effectively reduced.

Description

Technical Field

[0001] The invention relates to the technical field of boosting equipment, in particular to a high-pressure liquid-driven hydrogen compressor. Background Art

[0002] As a type of reciprocating compressor, liquid-driven compressor has the advantages of being able to start and stop under load, small footprint, easy maintenance, and low cost. It can meet the application requirements of high pressure and large flow, and is widely used in hydrogen production and hydrogenation fields such as water electrolyzer gas gathering and hydrogenation stations.

[0003] When the liquid-driven hydrogen compressor is working, the dynamic seal assembly is used to seal the dynamic gap between the boost cylinder and the piston and between the oil cylinder and the piston. Its airtightness is related to key issues such as the establishment of pressure in the cylinder, whether the oil and gas can be effectively isolated, and the maintenance cycle of the piston assembly. In particular, the dynamic seal assembly between the boost cylinder and the piston serves in a high-temperature and high-pressure hydrogen environment, and is always dry friction, which seriously affects its sealing characteristics and service life, and requires frequent replacement of the dynamic seal assembly. In order to solve the above technical problems, as recorded in the text of the Chinese patent publication number CN215719344U entitled A Liquid-Driven Compressor Piston Structure, the piston assembly is separated from the piston rod, which is conducive to the replacement and disassembly of the sealing ring and facilitates later maintenance. However, it does not take into account factors such as the inclination of the piston rod and the contact form between the piston rod and the piston. In actual implementation, the problem of eccentric wear of the piston is still difficult to solve, so it needs to be solved urgently. Summary of the invention

[0004] In order to avoid and overcome the technical problems existing in the prior art, the present invention provides a high-pressure liquid-driven hydrogen compressor, which has a stable structure and can effectively reduce eccentric wear of the piston.

[0005] To achieve the above object, the present invention provides the following technical solutions:

[0006] A high-pressure liquid-driven hydrogen compressor comprises an oil cylinder body and two booster cylinder bodies respectively mounted at both ends of the oil cylinder body, the inner cavities of the oil cylinder body and the booster cylinder body respectively sealingly and slidingly have an oil cylinder piston assembly and a booster cylinder piston assembly, the two ends of the oil cylinder piston assembly are respectively floatingly connected with a piston rod body sealingly penetrating the end of the oil cylinder body, so that the piston rod body can produce a floating fit relative to the oil cylinder body, the abutting end of the piston rod body and the booster cylinder piston assembly is a convex spherical surface, and the abutting surface of the booster cylinder piston assembly and the piston rod body is a plane perpendicular to the booster cylinder body.

[0007] As a further solution of the present invention: a guide ring mounted on the piston rod body is provided at the penetration point of the piston rod body on the cylinder body, and the guide ring has an open gap to form a floating space for the floating fit. The outer periphery of the cylinder piston assembly is also mounted with a guide ring with an open gap, so that the cylinder piston assembly can also produce an inclined floating fit relative to the cylinder body.

[0008] As a further solution of the present invention: the outer periphery of the booster cylinder piston assembly is also sleeved with a guide ring with an open gap, so that the booster cylinder piston assembly can produce an inclined floating fit relative to the booster cylinder body.

[0009] As a further solution of the present invention: the outer periphery of the oil cylinder piston assembly is provided with three oil cylinder piston rings distributed at intervals, and the guide ring on the oil cylinder piston assembly includes two oil cylinder guide rings respectively distributed at two intervals of the oil cylinder piston rings; both ends of the oil cylinder piston assembly have inner concave cavities, the piston rod body is inserted into the inner concave cavities, and the bottom of the inner concave cavity is provided with a cylinder plunger pad abutting against the piston rod body; there is a gap between the outer periphery of the piston rod body and the cavity wall of the inner concave cavity, a retaining ring is fixed to the outside of the insertion end of the piston rod body, and a cylinder nut coaxially distributed with the piston rod body with a gap is fixed at the cavity mouth of the inner concave cavity by a cylindrical pin, and the retaining ring is confined in the inner concave cavity by the cylinder nut to realize the floating connection between the piston rod body and the oil cylinder piston assembly.

[0010] As a further solution of the present invention: three oil-gas isolation sealing rings sleeved on the piston rod body are arranged at the penetration point of the piston rod body on the cylinder body, and the guide ring of the cylinder body located at the penetration point of the piston rod body is arranged as three piston rod guide rings respectively distributed adjacent to the three oil-gas isolation sealing rings.

[0011] As a further solution of the present invention: the guide rings on the boost cylinder piston assembly include a front boost cylinder guide ring and two rear boost cylinder guide rings spaced apart, the two rear boost cylinder guide rings are arranged adjacent to the return end of the boost cylinder piston assembly, the front boost cylinder guide ring is arranged adjacent to the forward end of the boost cylinder piston assembly via a guide support ring, and a piston ring assembly is provided on the outer periphery of the boost cylinder piston assembly between the rear boost cylinder guide ring and the front boost cylinder guide ring.

[0012] As a further solution of the present invention: the width of the guide ring is L i The calculation formula is:

[0013]

[0014] in,

[0015] When i=1, L i D is the width of the guide ring on the piston rod body (20); i is the inner diameter of the oil cylinder body (30) and the part where the piston rod body (20) penetrates; d i is the diameter of the piston rod body (20);

[0016] When i = 2, L i D is the width of the guide ring on the cylinder piston assembly (32);i is the inner diameter of the cylinder body (30); d i is the diameter of the cylinder piston assembly (32);

[0017] When i=3, L i D is the width of the guide ring on the booster cylinder piston assembly (12); i is the inner diameter of the boost cylinder (10); d i is the diameter of the booster cylinder piston assembly (12);

[0018] Q is the permissible load of the guide ring;

[0019] k is the guide ring opening clearance;

[0020] ε is the design pressure ratio;

[0021] C f is the safety factor;

[0022] P d is the exhaust pressure.

[0023] As a further solution of the present invention: two liquid-oil isolation chambers are arranged at intervals at the penetration point of the piston rod body on the cylinder body, and the two liquid-oil isolation chambers are respectively located at two intervals of the three oil-gas isolation sealing rings; the cylinder body is provided with a dust ring sleeved on the piston rod body at the interval between the two liquid-oil isolation chambers.

[0024] As a further solution of the present invention: buffer chambers are provided at both ends of the inner cavity of the booster cylinder body and both ends of the inner cavity of the oil cylinder body, and anti-collision pads are provided at both ends of the inner cavity of the oil cylinder body; the buffer chamber of the booster cylinder body adjacent to the oil cylinder body constitutes an air-oil isolation chamber, and the oil cylinder body is also provided with a dust ring sleeved on the piston rod body at the interval between the liquid-oil isolation chamber and the air-oil isolation chamber.

[0025] As a further solution of the present invention: the outer periphery of the boost cylinder body is provided with a cooling coil assembly, the boost cylinder body includes a one-way exhaust valve and a one-way intake valve arranged at its process chamber and a pressure relief hole arranged at the return chamber; the oil cylinder body includes oil holes arranged in both its process chamber and return chamber.

[0026] Compared with the prior art, the present invention has the following beneficial effects:

[0027] 1. The piston rod body is connected to the oil cylinder piston assembly in a floating manner, and the piston rod body and the booster cylinder piston assembly are in non-fixed point contact and abutment, and the piston rod body can also produce a floating fit relative to the oil cylinder body. When the oil cylinder piston assembly tilts, even if the piston rod body is driven to tilt, the penetration point between the piston rod body and the oil cylinder body is used as a fulcrum to produce a tilting action opposite to the tilting direction of the oil cylinder piston assembly. Compared with the coaxial rotation and tilting with the piston rod body, the tilting amplitude is smaller, so that the radial force on the piston rod body and the oil cylinder piston assembly is smaller, which effectively reduces the friction between the piston rod body, the oil cylinder piston assembly and the oil cylinder body, and further reduces the wear of the seal during its sealing movement. In addition, the booster cylinder piston assembly does not hinder the floating of the piston rod body, and in the process of the piston rod body sliding with the oil cylinder piston assembly to push the booster cylinder piston assembly to move, the ratio of the axial force to the radial force of the piston rod body on the booster cylinder piston assembly is larger, thereby further reducing the wear of the peripheral seal of the booster cylinder piston assembly and facilitating the automatic centering of the booster cylinder piston assembly.

[0028] 2. Both the oil cylinder piston assembly and the booster cylinder piston assembly can float relative to the oil cylinder body and the booster cylinder body respectively. The buffering effect of the floating cooperation of the oil cylinder piston assembly and the booster cylinder piston assembly is utilized to effectively reduce the radial rigid friction during the sliding process of the oil cylinder piston assembly and the booster cylinder piston assembly, thereby reducing the wear of the peripheral seals of the oil cylinder piston assembly and the booster cylinder piston assembly, and improving the service life of the oil cylinder piston assembly and the booster cylinder piston assembly.

[0029] 3. According to the relevant parameters of the hydrogen compressor, the minimum width of the guide ring is designed and calculated accordingly, so that the structure layout can be more compact while ensuring the stability and wear resistance of the guide ring. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] Figure 1 It is a schematic diagram of the structure of the present invention.

[0031] Figure 2 It is a schematic diagram of the distribution structure of the booster cylinder piston assembly and the piston rod body in the present invention.

[0032] Figure 3 It is a schematic diagram of the connection structure between the oil cylinder piston assembly and the piston rod body in the present invention.

[0033] Figure 4 It is a schematic diagram of the distribution structure of the piston rod body, the booster cylinder body and the oil cylinder body in the present invention.

[0034] Figure 5 It is a structural schematic diagram of the inclined force state of the booster cylinder piston assembly in the present invention.

[0035] In the figure: 10, boost cylinder body; 11, cooling coil assembly; 12, boost cylinder piston assembly; 121, rear boost cylinder guide ring; 122, piston ring assembly; 123, guide support ring; 124, front boost cylinder guide ring; 13, one-way exhaust valve; 14, one-way intake valve; 15, gas-oil isolation chamber; 20, piston rod body; 21, piston rod guide ring; 22, dust ring; 23, oil-gas isolation sealing ring; 30, cylinder body; 31, anti-collision pad; 32, cylinder piston assembly; 321, cylinder piston ring; 322, cylinder guide ring; 323, retaining ring; 324, cylinder nut; 325, cylindrical pin; 326, cylinder plunger pad; 33, liquid-oil isolation chamber. DETAILED DESCRIPTION

[0036] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0037] For ease of understanding, the specific structure and working mode of the present invention are further described below in conjunction with the accompanying drawings:

[0038] The specific structure of the present invention refers to Figure 1-5As shown, its main structure includes a cylinder body 30 and two booster cylinder bodies 10 respectively installed at both ends of the cylinder body 30. Among them, the inner cavities of the cylinder body 30 and the booster cylinder body 10 are respectively sealed and slid with a cylinder piston assembly 32 and a booster cylinder piston assembly 12, and the two ends of the cylinder piston assembly 32 are respectively floatingly connected with a piston rod body 20 that seals and penetrates the end of the cylinder body 30; while ensuring that the piston rod body 20 moves synchronously with the cylinder piston assembly 32, it also prevents the piston rod body 20 from coaxially tilting with the tilt of the cylinder piston assembly 32. In addition, the piston rod body 20 can produce an inclined floating fit relative to the cylinder body 30. When the cylinder piston assembly 32 is tilted, even if the piston rod body 20 is driven to tilt, the penetration point of the piston rod body 20 and the cylinder body 30 is used as a fulcrum to produce a tilting action opposite to the tilting direction of the cylinder piston assembly 32. Compared with the coaxial rotation and tilting with the piston rod body 20, the tilting amplitude is smaller, so that the radial force on the piston rod body 20 and the cylinder piston assembly 32 is smaller, effectively reducing the friction between the piston rod body 20, the cylinder piston assembly 32 and the cylinder body 30, and further reducing the wear of the seal during its sealing movement. In addition, the piston rod body 20 and the booster cylinder piston assembly 12 are also non-fixed free-style piston structures, and the abutting ends of the piston rod body 20 and the booster cylinder piston assembly 12 are convex spherical surfaces, and the abutting surfaces of the booster cylinder piston assembly 12 and the piston rod body 20 are planes perpendicular to the booster cylinder body 10, so that the booster cylinder piston assembly 12 and the piston rod body 20 are always in point contact. This arrangement not only ensures that the booster cylinder piston assembly 12 does not hinder the tilting and floating of the piston rod body 20, but also, in the process of the piston rod body 20 sliding with the oil cylinder piston assembly 32 to push the booster cylinder piston assembly 12 to move, the ratio of the axial force and radial force of the piston rod body 20 on the booster cylinder piston assembly 12 is larger, thereby further reducing the wear of the peripheral seals of the booster cylinder piston assembly 12 and facilitating the automatic centering of the booster cylinder piston assembly 12.

[0039] Specifically, Figure 4 As shown, a guide ring is provided on the piston rod body 20 at the penetration point of the cylinder body 30, which is sleeved on the piston rod body 20. The guide ring constitutes a support structure for the sliding of the piston rod body 20, and the guide ring has an open gap to form a floating space for floating fit. Figure 3 As shown, the outer periphery of the oil cylinder piston assembly 32 is also sleeved with a guide ring with an open gap, so that the oil cylinder piston assembly 32 can also produce an inclined floating fit relative to the oil cylinder body 30. The buffering of the floating fit of the oil cylinder piston assembly 32 effectively reduces the radial rigid friction of the oil cylinder piston assembly 32 during the sliding process, thereby reducing the wear of the outer peripheral seal of the oil cylinder piston assembly 32 and prolonging the service life of the oil cylinder piston assembly 32. Figure 2As shown, the outer periphery of the booster cylinder piston assembly 12 is also sleeved with a guide ring with an open gap, so that the booster cylinder piston assembly 12 can produce an inclined floating fit relative to the booster cylinder body 10. Similar to the oil cylinder piston assembly 32, the floating fit buffer of the booster cylinder piston assembly 12 is utilized to effectively reduce the radial rigid friction during the sliding process of the booster cylinder piston assembly 12, thereby reducing the wear of the outer peripheral seal of the booster cylinder piston assembly 12 and improving the service life of the booster cylinder piston assembly 12.

[0040] Further, such as Figure 3 As shown, the outer periphery of the cylinder piston assembly 32 is provided with three cylinder piston rings 321 which are spaced apart, and the guide ring on the cylinder piston assembly 32 includes two cylinder guide rings 322 which are respectively distributed at two intervals of the cylinder piston ring 321. The cylinder piston assembly 32 is supported in a dispersed manner by the spaced apart cylinder guide rings 322, and the cylinder piston rings 321 are evenly distributed on both sides of each cylinder guide ring 322 to ensure the sealing effect at both ends of the cylinder guide ring 322. In addition, both ends of the cylinder piston assembly 32 have inner concave cavities, the piston rod body 20 is inserted into the inner concave cavities, and the bottom of the inner concave cavity is provided with a cylinder plunger pad 326 which abuts against the piston rod body 20, so as to be used for buffering between the piston rod body 20 and the bottom of the inner concave cavity. There is a gap between the outer periphery of the piston rod body 20 and the cavity wall of the inner concave cavity, a snap ring 323 is fixed to the outside of the insertion end of the piston rod body 20, and a cylinder nut 324 coaxially distributed with the piston rod body 20 is fixed at the cavity opening of the inner concave cavity through a cylindrical pin 325, and the snap ring 323 is restricted in the inner concave cavity by the cylinder nut 324 to achieve a floating connection between the piston rod body 20 and the cylinder piston assembly 32. This floating connection form can not only ensure that the piston rod body 20 can achieve a floating connection, but also make the piston rod body 20 and the cylinder piston assembly 32 have a good shock absorbing and buffering effect.

[0041] Further, such as Figure 4 As shown, three oil-gas isolating sealing rings 23 sleeved on the rod body of the piston rod body 20 are provided at the penetration point of the piston rod body 20 on the cylinder body 30, and the guide ring of the cylinder body 30 located at the penetration point of the piston rod body 20 is set as three piston rod guide rings 21 respectively distributed adjacent to the three oil-gas isolating sealing rings 23. The three piston rod guide rings 21 are used to share the supporting force on the piston rod body 20, and the oil-gas isolating sealing rings 23 are sequentially arranged between the three piston rod guide rings 21 to realize multi-stage sealing, thereby ensuring the stability of supporting and sealing the piston rod body 20.

[0042] Further, such as Figure 2As shown, the guide rings on the booster cylinder piston assembly 12 include a front booster cylinder guide ring 124 and two rear booster cylinder guide rings 121 that are spaced apart. The two rear booster cylinder guide rings 121 are arranged adjacent to the return end of the booster cylinder piston assembly 12, and the front booster cylinder guide ring 124 is arranged adjacent to the forward end of the booster cylinder piston assembly 12 through a guide support ring 123. A piston ring assembly 122 is sleeved on the outer circumference of the booster cylinder piston assembly 12 between the rear booster cylinder guide ring 121 and the front booster cylinder guide ring 124. Through the arrangement of the front booster cylinder guide ring 124 and the two rear booster cylinder guide rings 121, the supporting force during the sliding process of the booster cylinder piston assembly 12 is shared, ensuring the stability of the support for the piston rod body 20.

[0043] It is worth mentioning that the guide ring is made of filled PTFE material. In this application, the piston rod body 20, the oil cylinder piston assembly 32 and the booster cylinder piston assembly 12 are all tiltable floating structures, such as Figure 5 As shown, taking the cooperation between the piston rod body 20 and the booster cylinder piston assembly 12 as an example, the piston rod body 20 in the tilted state exerts a driving force F on the booster cylinder piston assembly 12. h It can be decomposed into the axial driving force F on the booster cylinder piston assembly 12 a And the radial driving force F on the booster cylinder piston assembly 12 r .

[0044] Specifically, the width of the guide ring is L i , where when i is equal to 1, 2, and 3, L i They are respectively the width of the guide ring on the piston rod body 20, the width of the guide ring on the oil cylinder piston assembly 32, and the width of the guide ring on the booster cylinder piston assembly 12, L i The calculation formula is:

[0045]

[0046] and Substituting into the above formula, we get:

[0047]

[0048] in,

[0049] When i=1, L i D is the width of the guide ring on the piston rod body (20); i is the inner diameter of the oil cylinder body (30) and the part where the piston rod body (20) penetrates; d i is the diameter of the piston rod body (20);

[0050] When i = 2, L i D is the width of the guide ring on the cylinder piston assembly (32); iis the inner diameter of the cylinder body (30); d i is the diameter of the cylinder piston assembly (32);

[0051] When i=3, L i D is the width of the guide ring on the booster cylinder piston assembly (12); i is the inner diameter of the boost cylinder (10); d i is the diameter of the booster cylinder piston assembly (12);

[0052] Q is the permissible load of the guide ring;

[0053] F r The radial load borne by the guide ring;

[0054] k is the guide ring opening clearance;

[0055] ε is the design pressure ratio;

[0056] C f is the safety factor. When the working pressure in the corresponding cylinder is ≤15MPa, C f =2, when the working pressure in the corresponding cylinder is greater than 15MPa, C f =4;

[0057] P d is the exhaust pressure.

[0058] It is worth noting that, taking the guide ring on the oil cylinder piston assembly 32 as an example, the width of the guide ring obtained by the above formula is the sum of the widths of the two oil cylinder guide rings 322 .

[0059] According to the calculation of the minimum width of the guide ring, the layout of the structure can be made more compact while ensuring the stability and wear resistance of the guide ring.

[0060] On the basis of the above, in order to further prevent the hydraulic oil in the oil cylinder 30 from flowing into the booster cylinder 10, as Figure 4 As shown, two liquid-oil isolation chambers 33 are arranged at intervals at the penetration point of the piston rod body 20 on the cylinder body 30, and the two liquid-oil isolation chambers 33 are respectively located at two intervals of the three oil-gas isolation sealing rings 23; in addition, the cylinder body 30 is provided with a dust ring 22 sleeved on the piston rod body 20 at the interval between the two liquid-oil isolation chambers 33, and a multi-pass sealing isolation barrier is formed by the liquid-oil isolation chamber 33, the dust ring 22 and the oil-gas isolation sealing ring 23.

[0061] like Figure 4As shown, both ends of the inner cavity of the booster cylinder 10 and both ends of the inner cavity of the oil cylinder 30 are provided with buffer cavities, and both ends of the inner cavity of the oil cylinder 30 are provided with anti-collision pads 31, which respectively realize the buffering of the oil cylinder piston assembly 32 and the booster cylinder piston assembly 12 during the sliding process. In addition, the gas-oil isolation cavity 15 is formed by the buffer cavity of the booster cylinder 10 near the oil cylinder 30, and the oil cylinder 30 is also provided with a dust ring 22 sleeved on the piston rod body 20 at the interval between the liquid-oil isolation cavity 33 and the gas-oil isolation cavity 15, so as to further prevent the gaseous oil mist from entering the compression cavity of the booster cylinder 10.

[0062] In actual implementation, a buffer distance X is set at both ends of the inner cavity of the booster cylinder 10 and the inner cavity of the oil cylinder 30. Where S is the piston stroke, T is the time for the piston to reciprocate once, and t1 is the response time of the position switch.

[0063] In addition, if Figure 1 As shown, the outer periphery of the supercharged cylinder 10 is provided with a cooling coil assembly 11 for cooling the supercharged cylinder 10. The supercharged cylinder 10 includes a one-way exhaust valve 13 and a one-way intake valve 14 provided at its process chamber for intake and exhaust of the process chamber, and a pressure relief hole provided at the return chamber for pressure relief and exhaust of the return chamber. The oil cylinder 30 includes oil holes provided at both its process chamber and return chamber for communication between the process chamber and the return chamber of the oil cylinder 30 and an external oil tank.

[0064] Of course, it is obvious to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, but also includes the same or similar structures that can be implemented in other specific forms without departing from the spirit or essential features of the present invention. Therefore, no matter from which point of view, the embodiments should be regarded as exemplary and non-limiting, and the scope of the present invention is defined by the appended claims rather than the above description, and it is intended that all changes falling within the meaning and scope of the equivalent elements of the claims are included in the present invention. Any reference numerals in the claims should not be regarded as limiting the claims involved.

[0065] In addition, it should be understood that although the present specification is described according to implementation modes, not every implementation mode contains only one independent technical solution. This description of the specification is only for the sake of clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment may also be appropriately combined to form other implementation modes that can be understood by those skilled in the art.

[0066] The techniques, shapes, and structural parts not described in detail in the present invention are all well-known techniques.

Claims

1. A high-pressure liquid-driven hydrogen compressor, characterized in that: The invention comprises an oil cylinder body (30) and two booster cylinder bodies (10) respectively mounted at two ends of the oil cylinder body (30); the inner cavities of the oil cylinder body (30) and the booster cylinder body (10) are respectively sealed and slidably provided with an oil cylinder piston assembly (32) and a booster cylinder piston assembly (12); the two ends of the oil cylinder piston assembly (32) are respectively floatingly connected with a piston rod body (20) which seals and penetrates the end of the oil cylinder body (30), so that the piston rod body (20) can produce a floating fit relative to the oil cylinder body (30); the abutting end of the piston rod body (20) and the booster cylinder piston assembly (12) is a convex spherical surface, and the abutting surface of the booster cylinder piston assembly (12) and the piston rod body (20) is a plane perpendicular to the booster cylinder body (10).

2. A high-pressure liquid-driven hydrogen compressor according to claim 1, characterized in that: A guide ring sleeved on the piston rod body (20) is provided on the cylinder body (30) at the penetration point of the piston rod body (20), and the guide ring has an open gap to form a floating space for the floating fit. The outer periphery of the cylinder piston assembly (32) is also sleeved with a guide ring with an open gap, so that the cylinder piston assembly (32) can also produce a floating fit relative to the cylinder body (30).

3. A high-pressure liquid-driven hydrogen compressor according to claim 2, characterized in that: The outer periphery of the booster cylinder piston assembly (12) is also sleeved with a guide ring with an open gap, so that the booster cylinder piston assembly (12) can produce an inclined floating fit relative to the booster cylinder body (10).

4. A high-pressure liquid-driven hydrogen compressor according to claim 2, characterized in that: The outer periphery of the oil cylinder piston assembly (32) is sleeved with three oil cylinder piston rings (321) distributed at intervals, and the guide ring on the oil cylinder piston assembly (32) includes two oil cylinder guide rings (322) respectively distributed at two intervals of the oil cylinder piston ring (321); both ends of the oil cylinder piston assembly (32) have inner concave cavities, the piston rod body (20) is inserted into the inner concave cavities, and the bottom of the inner concave cavity is provided with an oil cylinder plunger pad (326) abutting against the piston rod body (20). There is a gap between the outer periphery of the piston rod body (20) and the cavity wall of the inner concave cavity, a retaining ring (323) is fixed to the outside of the insertion end of the piston rod body (20), and a cylinder nut (324) coaxially distributed with the piston rod body (20) is fixed at the cavity opening of the inner concave cavity through a cylindrical pin (325), and the retaining ring (323) is restricted in the inner concave cavity by the cylinder nut (324) to realize the floating connection between the piston rod body (20) and the cylinder piston assembly (32).

5. A high-pressure liquid-driven hydrogen compressor according to claim 2, characterized in that: The penetration point of the piston rod body (20) on the oil cylinder body (30) is provided with three oil and gas isolation sealing rings (23) sleeved on the rod body of the piston rod body (20), and the guide ring of the oil cylinder body (30) located at the penetration point of the piston rod body (20) is provided as three piston rod guide rings (21) respectively distributed adjacent to the three oil and gas isolation sealing rings (23).

6. A high-pressure liquid-driven hydrogen compressor according to claim 3, characterized in that: The guide rings on the booster cylinder piston assembly (12) include a front booster cylinder guide ring (124) and two rear booster cylinder guide rings (121) spaced apart from each other. The two rear booster cylinder guide rings (121) are arranged adjacent to the return end of the booster cylinder piston assembly (12), and the front booster cylinder guide ring (124) is arranged adjacent to the forward end of the booster cylinder piston assembly (12) via a guide support ring (123). A piston ring assembly (122) is sleeved on the outer periphery of the booster cylinder piston assembly (12) between the rear booster cylinder guide ring (121) and the front booster cylinder guide ring (124).

7. A high-pressure liquid-driven hydrogen compressor according to any one of claims 3 to 6, characterized in that: The width of the guide ring is L i The calculation formula is: in, When i=1, L i D is the width of the guide ring on the piston rod body (20); i is the inner diameter of the oil cylinder body (30) and the part where the piston rod body (20) penetrates; d i is the diameter of the piston rod body (20); When i = 2, L i D is the width of the guide ring on the cylinder piston assembly (32); i is the inner diameter of the cylinder body (30); d i is the diameter of the cylinder piston assembly (32); When i=3, L i D is the width of the guide ring on the booster cylinder piston assembly (12); i is the inner diameter of the boost cylinder (10); d i is the diameter of the booster cylinder piston assembly (12); Q is the permissible load of the guide ring; k is the guide ring opening clearance; ε is the design pressure ratio; C f is the safety factor; P d is the exhaust pressure.

8. A high-pressure liquid-driven hydrogen compressor according to claim 6, characterized in that: Two oil-liquid isolation chambers (33) are arranged at intervals at the penetration point of the piston rod body (20) on the oil cylinder body (30). The two oil-liquid isolation chambers (33) are respectively located at two intervals of the three oil-gas isolation sealing rings (23). The oil cylinder body (30) is provided with a dust ring (22) sleeved on the piston rod body (20) at the interval between the two oil-liquid isolation chambers (33).

9. A high-pressure liquid-driven hydrogen compressor according to claim 8, characterized in that: Buffer chambers are provided at both ends of the inner cavity of the boost cylinder (10) and the inner cavity of the oil cylinder (30), and anti-collision pads (31) are provided at both ends of the inner cavity of the oil cylinder (30); the buffer chamber of the boost cylinder (10) adjacent to the oil cylinder (30) forms an air-oil isolation chamber (15), and the oil cylinder (30) is also provided with a dust ring (22) sleeved on the piston rod body (20) at the interval between the liquid-oil isolation chamber (33) and the air-oil isolation chamber (15).

10. A high-pressure liquid-driven hydrogen compressor according to any one of claims 1 to 6, characterized in that: The outer periphery of the boost cylinder (10) is provided with a cooling coil assembly (11), and the boost cylinder (10) includes a one-way exhaust valve (13) and a one-way intake valve (14) arranged at its process chamber, and a pressure relief hole arranged at the return chamber; the oil cylinder (30) includes oil holes arranged in both its process chamber and return chamber.

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