Piston sealing mechanism for piston type high-pressure hydrogen compressor and high-pressure hydrogen compressor

Abstract

The invention discloses a piston sealing mechanism for a piston type high-pressure hydrogen compressor and the high-pressure hydrogen compressor, and belongs to the field of compressors, the piston sealing mechanism comprises an air cylinder, a piston assembly is movably connected in one end of the air cylinder, an air valve is mounted at the other end of the air cylinder, and a compression cavity is formed between the piston assembly and the air valve; the side, close to the compression cavity, of the piston assembly is a high-pressure side, and the side, away from the compression cavity, of the piston assembly is a low-pressure side. The piston assembly comprises a piston and a piston ring, a plurality of piston ring grooves are formed in the piston, and the piston ring comprises an airtight ring and a second notch ring; the piston rings are fixed to the piston through the piston ring grooves and are sequentially arranged in the axis direction of the piston, airtight rings are arranged on the high-pressure sides, and second notch rings are arranged on the low-pressure sides. A communicating hole is formed in the end, close to the compression cavity, of the piston and communicates the piston ring grooves connected with the airtight rings; a support ring is arranged at the joint of the piston and the cylinder. The service life of the piston ring is prolonged while the hydrogen sealing performance is guaranteed.

Description

Technical Field

[0001] The invention belongs to the field of compressors and relates to a piston sealing mechanism for a piston type high pressure hydrogen compressor and a high pressure hydrogen compressor. Background Art

[0002] When filling a tank truck with hydrogen, a high-pressure hydrogen compressor is required to pressurize it. Since the diaphragm stroke of the diaphragm compressor is small, it cannot meet the demand for large-flow hydrogen filling. Therefore, the development of a reciprocating hydrogen filling compressor is a key step in achieving large-scale hydrogen storage and transportation.

[0003] When the compressor piston is working, in order to prevent the gas from overflowing along the moving piston, the existing solution is to set multiple sealing piston rings on the piston, and use the piston rings to abut against the inner wall of the cylinder to prevent gas leakage. However, the hydrogen used in the high-pressure hydrogen compressor has a very small molecular weight and a higher diffusion coefficient than other gases such as air. Under the same piston ring structure, hydrogen is more likely to leak than other large molecular gases. If a piston compressor is used to compress hydrogen, the piston ring seal must be oil-free lubricated. Since there is no continuous oil film between the contact surface of the oil-free lubricated piston ring and the cylinder to reduce its wear, its wear coefficient is significantly higher, and its service life is almost half of that of the oil-lubricated piston ring. When the oil-free lubricated piston ring is applied to a higher working pressure, the oil-free lubricated piston ring will quickly fail due to excessive wear rate. The design of the dynamic sealing mechanism of the hydrogen compressor piston ring must not only ensure the high sealing performance of the piston ring, but also consider the working life of the piston ring.

[0004] During operation, the piston ring is pressed against the cylinder mirror surface due to the pressure difference between the front of the ring (high-pressure side) and the back of the ring (low-pressure side). The contact pressure between the piston ring and the wall is the specific pressure. However, in actual operation, the high sealing performance of the piston ring leads to a delay in the conduction of the pressure difference, which makes the specific pressure distribution of each piston ring uneven. The dynamic pressure difference and the static pressure difference cause the specific pressure to be concentrated on the first piston ring on the cover side and the shaft side respectively. For the sealing of high-pressure hydrogen, the uneven distribution of specific pressure has more serious consequences. Under high-pressure and oil-free conditions, the friction heat of the concentrated load piston ring is much greater than that of the other rings. This friction heat cannot be quickly diffused through the self-lubricating material with low thermal conductivity, resulting in rapid thermal failure of the piston ring.

[0005] At present, the method of changing the piston ring cutout gap is often used to improve the specific pressure distribution problem of the piston ring group. However, in a high-pressure hydrogen environment, this method not only fails to effectively distribute the load, but also causes excessive leakage and fails to meet the hydrogen sealing requirements. Therefore, it is necessary to propose a new piston ring group sealing structure to achieve the purpose of reducing hydrogen leakage and extending service life. Summary of the invention

[0006] The object of the present invention is to provide a piston sealing mechanism for a piston-type high-pressure hydrogen compressor and a high-pressure hydrogen compressor, so as to ensure that hydrogen can be reliably sealed in the compression chamber under high-pressure conditions, thereby minimizing the possibility of leakage, and effectively reducing the wear and stress to which the piston ring is subjected during operation by optimizing the material selection of the piston ring, improving its structural design, and rationally planning its working environment, thereby significantly increasing the service life of the piston ring and overcoming the deficiencies of the prior art.

[0007] To achieve the above object, the present invention provides the following technical solutions: On the one hand, the present invention provides a piston sealing mechanism for a piston-type high-pressure hydrogen compressor, comprising a cylinder, one end of the cylinder is movably connected to a piston assembly, and the other end is equipped with a gas valve, and a compression chamber is formed between the piston assembly and the gas valve; the side of the piston assembly close to the compression chamber is the high-pressure side, and the side of the piston assembly away from the compression chamber is the low-pressure side; The piston assembly comprises a piston and a piston ring, wherein the piston is provided with a plurality of piston ring grooves, and the piston ring comprises an airtight ring and a second cut ring; the plurality of piston rings are fixed on the piston through the piston ring grooves and the piston rings are arranged in sequence along the piston axis direction, and the high-pressure side is provided with an airtight ring, and the low-pressure side is provided with a second cut ring; A connecting hole is provided at the end of the piston close to the compression chamber, and the connecting hole connects the piston ring grooves connected to several air-tight rings. The connecting hole reduces the sealing pressure difference borne by the air-tight ring close to the compression chamber side, reduces the pressure and friction borne by the air-tight ring, thereby slowing down the wear rate of the air-tight ring and extending the service life of the air-tight ring; a support ring is provided at the connection between the piston and the cylinder, and the support ring can support and position the piston, reduce the direct friction and collision between the piston and the cylinder wall during movement, and reduce the degree of wear of the piston and the cylinder wall.

[0008] Furthermore, the airtight ring includes a first cutout ring and an L-shaped ring; the L-shaped ring is provided with a positioning protrusion and a cutout at a relative position of the positioning protrusion, the L-shaped ring is superimposed on the first cutout ring, and the cutout of the first cutout ring is engaged with the positioning protrusion on the L-shaped ring. Through this overlapping structure, the amount of hydrogen leakage is effectively reduced, and the problem of high-pressure hydrogen easily leaking through the cutout is solved.

[0009] Furthermore, the connecting hole includes an axial longitudinal hole and a plurality of radial transverse holes, wherein the axial longitudinal hole is arranged at the center of the piston, and the plurality of radial transverse holes are evenly distributed on one side of the axial longitudinal hole, so as to connect the compression chamber with a plurality of airtight rings arranged on the high-pressure side. The gas enters the inner side of the airtight ring near the high-pressure side of the piston through the axial longitudinal hole and the radial transverse holes near the high-pressure side, and under the action of the gas pressure, the airtight ring is closely attached to the cylinder mirror surface, thereby enhancing the sealing effect of the airtight ring 51.

[0010] Furthermore, the aperture of the radial transverse hole near the high-pressure side is larger than that of the radial transverse hole near the low-pressure side; more high-pressure gas can enter the piston ring groove near the compression chamber 3 side through the radial transverse hole 72 with a larger aperture near the high-pressure side, which increases the pressure in the piston ring groove near the compression chamber 3 side, thereby reducing the sealing pressure difference on both sides of the airtight ring 51 on the high-pressure side.

[0011] Furthermore, the cutout gap of the second cutout ring close to the low-pressure side is larger than the cutout gap of the second cutout ring close to the high-pressure side. By controlling the cutout gap, high-pressure gas can be appropriately leaked to the low-pressure side, thereby balancing the pressure difference between the high-pressure and low-pressure sides, and the uniform specific pressure can reduce local excessive wear.

[0012] Furthermore, the cutout on the second cutout ring is a straight cutout or an oblique cutout. The straight cutout is simple to process and has a low cost. When gas leaks through a straight cutout, the path is relatively direct, and the leakage is easier to estimate and control; the oblique cutout increases the path length of gas leakage and improves the sealing performance. When gas passes through an oblique cutout, the flow resistance is greater, and the leakage is reduced relative to a straight cutout.

[0013] Furthermore, the thickness of the first cutout ring is smaller than the thickness of the second cutout ring.

[0014] Furthermore, the gas-tight ring is made of polyetheretherketone (PEEK), which is a high-temperature resistant self-lubricating material that can prevent the high-pressure side piston ring from prematurely failing due to high temperature and effectively increase the service life of the gas-tight ring.

[0015] Furthermore, the second cutout ring is made of polytetrafluoroethylene, which is a low-friction material and can effectively increase the service life of the second cutout ring.

[0016] On the other hand, the present invention also provides a high-pressure hydrogen compressor, which uses the above-mentioned piston sealing mechanism.

[0017] Compared with the prior art, the present invention has the following beneficial technical effects: The present invention provides a piston sealing mechanism for a piston-type high-pressure hydrogen compressor, wherein a piston assembly movably connected inside a cylinder comprises a piston and a piston ring, wherein the piston ring comprises an airtight ring and a second cut ring, and the airtight ring is installed on the high-pressure side of the piston and fits closely with the cylinder mirror surface; the airtight ring is used in conjunction with a piston connecting hole structure, and hydrogen can only leak out from the gap between the airtight ring and the cylinder mirror surface, and the airtightness is extremely strong; the connecting hole connects the cylinder with the high-pressure side piston ring groove, so that high-pressure gas can enter the piston ring groove, thereby evenly distributing the specific pressure borne by the airtight ring. The uniform distribution of specific pressure avoids excessive local force on the airtight ring and reduces wear caused by excessive local pressure.

[0018] Specifically, the cutout gap of the second cutout ring close to the low-pressure side is larger than the cutout gap of the second cutout ring close to the high-pressure side; the second cutout rings with different cutout gaps are used together on the low-pressure side of the piston, and the static sealing pressure difference is balanced by adjusting the leakage of each cutout ring. When the pressure is high, the cutout ring with a relatively large leakage can release part of the pressure, making the pressure on each cutout ring more uniform, thereby slowing down the wear of the cutout ring.

[0019] Specifically, different self-lubricating materials are selected for the high-pressure side and low-pressure side piston rings, respectively, and optimized for different working conditions. This not only prevents the failure of the high-pressure side airtight ring, but also controls the wear of the low-pressure side cutout ring, thereby significantly extending the overall service life of the piston ring and reducing maintenance costs and replacement frequency. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 The figure is a schematic structural diagram of a piston sealing mechanism for a piston-type high-pressure hydrogen compressor in an embodiment of the present invention.

[0021] Figure 2 Schematic diagram of the explosion of the airtight ring in the embodiment of the present invention.

[0022] Figure 3 It is an enlarged schematic diagram of the second cutout ring in the embodiment of the present invention.

[0023] Figure 4 An enlarged schematic diagram of the connecting hole in the embodiment of the present invention In the figure, 1, cylinder; 2, piston; 3, compression chamber; 4, air valve; 5, piston ring; 51, airtight ring; 52, L-shaped ring; 53, positioning protrusion; 54, second cut ring; 55, first cut ring; 6, support ring; 7, connecting hole; 71, axial longitudinal hole; 72, radial transverse hole. DETAILED DESCRIPTION

[0024] In order to enable those skilled in the art to better understand the scheme of the present invention, the technical scheme in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings 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 should fall within the scope of protection of the present invention.

[0025] It should be noted that the terms "first", "second", etc. in the specification and claims of the present invention and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the data used in this way can be interchanged where appropriate, so that the embodiments of the present invention described herein can be implemented in an order other than those illustrated or described herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions, for example, a process, method, system, product or device that includes a series of steps or units is not necessarily limited to those steps or units that are clearly listed, but may include other steps or units that are not clearly listed or inherent to these processes, methods, products or devices.

[0026] Example 1 See also Figure 1 The present invention provides a piston sealing mechanism for a piston-type high-pressure hydrogen compressor, including a cylinder 1, a piston assembly, a compression chamber 3, an air valve 4 and a support ring 6; a piston assembly is movably connected to one end of the cylinder 1, and an air valve 4 is installed at the other end of the cylinder 1, and a compression chamber 3 is formed between the piston assembly and the air valve 4; a support ring 6 is provided at the connection between the piston 2 and the cylinder 1; the side of the piston assembly close to the compression chamber 3 is the high-pressure side, and the side of the piston assembly away from the compression chamber 3 is the low-pressure side. The inner surface of the cylinder 1 is processed to form a smooth cylinder mirror surface to ensure that the piston assembly can reciprocate smoothly therein; during the compression process, the gas in the compression chamber 3 is compressed and the pressure increases, so the high-pressure side will be subjected to a higher pressure; the side away from the compression chamber 3 is the low-pressure side, and its pressure is relatively low.

[0027] The piston assembly includes a piston 2 and a piston ring 5. The piston 2 is provided with a plurality of piston ring grooves. The piston ring 5 includes an airtight ring 51 and a second cutout ring 54. The piston ring groove is used to install the airtight ring 51 and the second cutout ring 54. The plurality of piston rings 5 ​​are fixed to the piston 2 through the piston ring grooves and the piston rings 5 ​​are arranged in sequence along the axial direction of the piston 2. The high-pressure side is provided with an airtight ring 51. The airtight ring 51 has good sealing performance and can effectively prevent high-pressure hydrogen from leaking from the gap between the piston 2 and the cylinder wall, thereby ensuring the sealing of the compression chamber 3. The low-pressure side is provided with a second cutout ring 54. The cutout structure of the second cutout ring 54 allows a certain amount of gas leakage. By reasonably designing the cutout gap, the low-pressure side of the piston assembly can be adjusted. pressure distribution, balancing the pressure difference, and also helping to reduce the friction and wear between the piston ring 5 and the cylinder wall; a connecting hole 7 is provided at the end of the piston 2 close to the compression chamber 3, and the connecting hole 7 connects the piston ring grooves connected to several air-tight rings 51; on the one hand, the connecting hole 7 makes the pressure in the piston ring grooves where the air-tight rings 51 are located tend to be uniform, avoiding uneven force on the air-tight rings 51 due to excessively high or low local pressure, thereby extending the service life of the air-tight rings 51 and ensuring the stability of the sealing effect; on the other hand, the connecting hole 7 can allow the high-pressure gas to better transfer pressure between the air-tight rings 51, so that the air-tight rings 51 can fit more closely to the cylinder wall, further improving the sealing performance on the high-pressure side and reducing the possibility of hydrogen leakage.

[0028] It should be noted that when a double-acting cylinder is working, air can enter both sides of the piston to push the piston to move. Generally, when the shaft-side cylinder enters air to push the piston, the other side (rod side) exhausts air to form a low-pressure side; differential cylinders usually have piston chambers of different diameters, and the balance chamber is used to balance the axial force, which should be considered as the scope of protection of this patent.

[0029] For example, nine piston rings 5 ​​and one support ring 6 are installed on the piston 2 to form a piston sealing structure, wherein five airtight rings 51 are arranged at the high-pressure side of the piston 2, and four second cut rings 54 are arranged at the low-pressure side of the piston 2.

[0030] Example 2 In traditional piston ring seal structures, the cutout is often the main way for high-pressure hydrogen to leak out, because high-pressure hydrogen has strong penetrability and can easily leak out through the tiny gap at the cutout.

[0031] See also Figures 2 to 3On the basis of Example 1, the airtight ring 51 and the second notch ring 54 are further described; the airtight ring 51 includes a first notch ring 55 and an L-shaped ring 52, the L-shaped ring 52 is provided with a positioning protrusion 53 and the positioning protrusion 53 has a notch at a relative position, and when superimposed, the notch of the first notch ring 55 is just engaged with the positioning protrusion 53 on the L-shaped ring 52; ensure that the notch of the first notch ring 55 is staggered with the notch on the L-shaped ring 52, and the notch on the L-shaped ring 52 is surrounded and sealed by the L-shaped ring 52. Through this overlapping structure, the possibility of leakage of high-pressure hydrogen is greatly reduced, and the setting of multiple sealing links, such as staggered notches and surrounding sealing of the L-shaped ring itself, all play a role in hindering the leakage of hydrogen, so that hydrogen encounters many resistances when trying to leak, thereby effectively reducing the leakage amount.

[0032] For example, the cut gap of the second cut ring 54 close to the low-pressure side is larger than the cut gap of the second cut ring 54 close to the high-pressure side. By controlling the cut gap, high-pressure gas can leak moderately to the low-pressure side, thereby balancing the pressure difference between the high and low pressure sides. The uniform specific pressure can reduce local excessive wear. The cut on the second cut ring 54 is a straight cut or an oblique cut.

[0033] Preferably, the material of the airtight ring 51 is polyetheretherketone material; during operation, the temperature of the hydrogen in the compression chamber 3 increases due to compression, so the temperature borne by the airtight ring 51 is higher than the temperature of the second cut ring 54. The polyetheretherketone material is a high-temperature resistant self-lubricating material, which can prevent the airtight ring 51 from premature failure due to high temperature and increase the service life of the airtight ring. Preferably, the second cut ring 54 is made of polytetrafluoroethylene. During operation, the temperature borne by the second cut ring 54 is lower than the temperature borne by the airtight ring 51. Therefore, the friction coefficient is the main consideration when selecting the material. Polytetrafluoroethylene is a low friction coefficient material, which can effectively increase the service life of the second cut ring 54.

[0034] Preferably, the thickness of the first notch ring 55 is smaller than the thickness of the second notch ring 54 .

[0035] Example 3 See also Figure 4 On the basis of Example 2, the connecting hole 7 is further described. The connecting hole 7 includes an axial longitudinal hole 71 and a plurality of radial transverse holes 72. The axial longitudinal hole 71 extends along the central axis of the piston 2 and is the main channel for gas transmission inside the piston 2. The radial transverse holes 72 are perpendicular to the axial longitudinal hole 71, connecting the axial longitudinal hole 71 with the piston ring groove on the high-pressure side, so that the gas in the cylinder can enter each piston ring groove through the axial longitudinal hole 71 and the radial transverse holes 72.

[0036] Preferably, the cutout gap of the second cutout ring 54 near the low-pressure side is larger than the cutout gap of the second cutout ring 54 near the high-pressure side. During the operation of the piston-type high-pressure hydrogen compressor, there is an obvious pressure difference between the high-pressure side and the low-pressure side of the piston assembly. The gas pressure near the high-pressure side is higher, while the gas pressure near the low-pressure side is lower. The cutout gap of the second cutout ring 54 near the low-pressure side is designed to be larger than the cutout gap of the second cutout ring 54 near the high-pressure side, and the cutout gap can be used to adjust the gas leakage, thereby balancing the pressure at different positions.

[0037] Preferably, the diameter of the radial transverse hole 72 close to the high-pressure side is larger than that of the radial transverse hole 72 close to the low-pressure side.

[0038] During operation, the gas in the compression chamber 3 is in a high-pressure state. Since the diameter of the radial transverse hole 72 near the high-pressure side is larger than that near the low-pressure side, more high-pressure gas can enter the piston ring groove near the compression chamber 3 through the radial transverse hole 72 near the high-pressure side with a larger diameter, which increases the pressure in the piston ring groove near the compression chamber 3, that is, the pressure in the piston ring groove near the high-pressure side increases, thereby reducing the sealing pressure difference on both sides of the airtight ring 51 on the high-pressure side. At the same time, the gas enters the inner side of the airtight ring 51 near the high-pressure side of the piston through the axial longitudinal hole 71 and the radial transverse hole 72 near the high-pressure side, and under the action of the gas pressure, the airtight ring 51 is closely attached to the cylinder mirror surface.

[0039] By reducing the sealing pressure difference on both sides of the airtight ring 51 close to the high-pressure side, the pressure and friction force on the airtight ring 51 are reduced, thereby slowing down its wear rate, which helps to extend the service life of the airtight ring 51 and reduce the decline in sealing performance and equipment failure caused by the wear of the airtight ring 51. At the same time, the specific pressure borne by each airtight ring 51 tends to be uniform, avoiding the problem of excessive wear or sealing failure of some airtight rings due to uneven distribution of specific pressure, and ensuring that all airtight rings 51 can operate under relatively balanced working conditions.

[0040] The pressure is introduced into the inner side of the airtight ring 51 close to the high pressure side, so that the airtight ring 51 is close to the cylinder mirror surface, thereby enhancing the sealing effect of the airtight ring 51. This can effectively prevent the high pressure gas from leaking from the gap between the piston 2 and the cylinder wall, thereby improving the sealing performance of the entire piston sealing mechanism.

[0041] Preferably, the present invention also provides a high-pressure hydrogen compressor, using the above-mentioned piston sealing mechanism.

[0042] Compared with the traditional sealing structure, the present invention proposes a piston through hole 7, and by combining piston rings 5 ​​with different structures and materials, while ensuring the air tightness of the piston ring 5, improvements are made in terms of uniform pressure distribution, improved high temperature resistance and reduced wear. While effectively controlling the hydrogen leakage, the piston ring group pressure distribution is uniformly distributed, the wear rate of the piston ring group is reduced, and the service life of the piston ring 5 is greatly improved.

[0043] It should be noted that, in this article, the terms "include", "comprises" or any other variations thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements includes not only those elements, but also includes other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, an element defined by the sentence "comprises a ..." does not exclude the presence of other identical elements in the process, method, article or device including the element.

[0044] Although embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the appended claims and their equivalents.

Claims

1. A piston sealing mechanism for a piston-type high-pressure hydrogen compressor, characterized in that: The cylinder (1) comprises a piston assembly movably connected to one end of the cylinder (1), and a gas valve (4) is installed at the other end, and a compression chamber (3) is formed between the piston assembly and the gas valve (4); the side of the piston assembly close to the compression chamber (3) is a high-pressure side, and the side of the piston assembly away from the compression chamber (3) is a low-pressure side; The piston assembly comprises a piston (2) and a piston ring (5), the piston (2) being provided with a plurality of piston ring grooves, the piston ring (5) comprising an airtight ring (51) and a second cutout ring (54); the plurality of piston rings (5) are fixed to the piston (2) via the piston ring grooves, the piston rings (5) are arranged in sequence along the axial direction of the piston (2), the high-pressure side being provided with the airtight ring (51), and the low-pressure side being provided with the second cutout ring (54); A connecting hole (7) is provided at the end of the piston (2) close to the compression chamber (3), and the connecting hole (7) connects piston ring grooves connected to a plurality of airtight rings (51); a supporting ring (6) is provided at the connection between the piston (2) and the cylinder (1).

2. The piston sealing mechanism for a piston type high pressure hydrogen compressor according to claim 1, characterized in that: The airtight ring (51) comprises a first notch ring (55) and an L-shaped ring (52); a positioning protrusion (53) is provided on the L-shaped ring (52) and a notch is provided at a relative position of the positioning protrusion (53); the L-shaped ring (52) is superimposed on the first notch ring (55) and the notch of the first notch ring (55) is engaged with the positioning protrusion (53) on the L-shaped ring (52).

3. The piston sealing mechanism for a piston type high pressure hydrogen compressor according to claim 1, characterized in that: The communication hole (7) comprises an axial longitudinal hole (71) and a plurality of radial transverse holes (72); the axial longitudinal hole (71) is arranged at the center of the piston (2); and the plurality of radial transverse holes (72) are evenly distributed on one side of the axial longitudinal hole (71) to connect the compression chamber (3) with a plurality of airtight rings (51) arranged on the high-pressure side.

4. The piston sealing mechanism for a piston type high pressure hydrogen compressor according to claim 3, characterized in that: The diameter of the radial transverse hole (72) close to the high-pressure side is larger than the diameter of the radial transverse hole (72) close to the low-pressure side.

5. The piston sealing mechanism for a piston type high pressure hydrogen compressor according to claim 1, characterized in that: The cutout gap of the second cutout ring (54) close to the low-pressure side is larger than the cutout gap of the second cutout ring (54) close to the high-pressure side.

6. The piston sealing mechanism for a piston type high pressure hydrogen compressor according to claim 5, characterized in that: The cut on the second cut ring (54) is a straight cut or an oblique cut.

7. The piston sealing mechanism for a piston type high pressure hydrogen compressor according to claim 2, characterized in that: The thickness of the first notch ring (55) is smaller than the thickness of the second notch ring (54).

8. The piston sealing mechanism for a piston type high pressure hydrogen compressor according to claim 1, characterized in that: The material of the airtight ring (51) is polyetheretherketone material.

9. The piston sealing mechanism for a piston type high pressure hydrogen compressor according to claim 1, characterized in that: The second cutout ring (54) is made of polytetrafluoroethylene.

10. A high-pressure hydrogen compressor, characterized in that: A piston sealing mechanism as described in any one of claims 1 to 9 is used.

Images