Gas supercharger

Abstract

The utility model provides a gas supercharger. The gas supercharger comprises a driving unit and at least one supercharging cylinder, the pressure cylinder comprises a pressure cylinder barrel and a pressure piston arranged in the pressure cylinder barrel; the driving unit comprises a driving rod, and the driving rod extends into the pressurizing cylinder barrel and is connected with the pressurizing piston; an inner hole of the pressurizing cylinder barrel is in clearance fit with the pressurizing piston through tolerance control, the surface of the inner hole of the pressurizing cylinder barrel is covered with a diamond-like coating, the surface of the outer circle of the pressurizing piston is covered with a low-friction composite coating, and a friction pair is formed. According to the gas supercharger provided by the invention, friction heating and friction loss are reduced.

Description

TECHNICAL FIELD

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

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

[0003] A hydrogen pressurizer generally has high pressure and high frequency working characteristics, and can achieve rapid gas filling, but is also prone to cause the hydrogen pressurizer to have a high failure rate and a shortened service life, and frequent downtime for maintenance due to failure reduces overall gas filling efficiency. CONTENT OF THE INVENTION

[0004] The present disclosure provides a gas pressurizer.

[0005] In a first aspect, the present disclosure provides a gas pressurizer, comprising: a driving unit, at least one pressurizing cylinder;

[0006] The pressurizing cylinder comprises a pressurizing cylinder barrel and a pressurizing piston arranged in the pressurizing cylinder barrel.

[0007] The driving unit comprises a driving rod, which extends into the pressurizing cylinder barrel and is connected to the pressurizing piston.

[0008] The inner hole of the pressurizing cylinder barrel and the pressurizing piston are matched by a tolerance control gap, the inner hole surface of the pressurizing cylinder barrel is covered with a diamond-like carbon coating, and the outer circular surface of the pressurizing piston is covered with a low-friction composite coating, constituting a friction pair.

[0009] In some embodiments, the low-friction composite coating comprises a PTFE-based composite coating and / or a nylon-based composite coating.

[0010] In some embodiments, the driving unit comprises a hydraulic cylinder, the hydraulic cylinder comprises a hydraulic cylinder barrel and a driving piston, the driving rod is connected to the driving piston, and the inner hole of the hydraulic cylinder barrel and the driving piston are gap sealed by tolerance control.

[0011] In some embodiments, the outer circular surface of the driving piston is provided with at least one gap sealing groove, the gap sealing groove extends in the circumferential direction, and is used to store hydraulic oil.

[0012] In some embodiments, the hydraulic cylinder further comprises an end cover arranged between the hydraulic cylinder barrel and the booster cylinder barrel; a plurality of hydraulic suspension cavities are arranged on the inner hole surface of the end cover and distributed circumferentially; the end cover is further provided with a hydraulic annular loop extending circumferentially and a plurality of pressurizing ports distributed circumferentially, each of the pressurizing ports corresponding to one of the hydraulic suspension cavities; the pressurizing ports are in communication with the hydraulic annular loop and the corresponding hydraulic suspension cavities.

[0013] In some embodiments, each of the pressurizing ports is in communication with the hydraulic annular loop through a pressurizing channel; a throttle screw is arranged in the pressurizing channel to keep the pressure at each of the pressurizing ports consistent.

[0014] In some embodiments, each of the pressurizing ports corresponds to a pressure detection channel, the pressure detection channel being in communication with the pressurizing channel, and a pressure sensor being arranged in the pressure detection channel to detect the pressure in the corresponding hydraulic suspension cavity.

[0015] In some embodiments, the end cover comprises a hydraulic suspension ring arranged in the inner hole of the end cover, and the hydraulic suspension cavities are arranged on the inner hole surface of the hydraulic suspension ring.

[0016] In some embodiments, the hydraulic suspension ring is in clearance fit with the inner hole of the end cover; or the hydraulic suspension ring is formed in the inner hole of the end cover through a surfacing machining process.

[0017] In some embodiments, the inner hole surface of the hydraulic suspension ring is further provided with an oil storage structure in communication with the hydraulic suspension cavities.

[0018] In some embodiments, the oil storage structure comprises a plurality of parallel oil storage grooves distributed parallel to each other on the inner hole surface of the hydraulic suspension ring.

[0019] In some embodiments, the inner hole of the end cover away from the hydraulic cylinder barrel is further provided with a reverse dust seal for scraping oil on the driving rod in a direction close to the hydraulic cylinder barrel.

[0020] In some embodiments, the inner hole of the end cover is further provided with an oil scraping and storage groove on the side of the reverse dust seal close to the hydraulic cylinder barrel; the end cover is further provided with a drain channel, and the oil scraping and storage groove is in communication with the drain channel.

[0021] In some embodiments, the hydraulic cylinder further comprises a proximity switch for detecting the position of the driving piston.

[0022] In some embodiments, the booster cylinder comprises an isolation cavity on the side of the booster piston close to the driving unit; the gas inlet and outlet of the isolation cavity are respectively provided with a gas concentration sensor for detecting the gas concentration in the isolation cavity.

[0023] In some embodiments, the outer wall of the booster cylinder is further provided with a cooling water channel.

[0024] In some embodiments, the outer wall of the booster cylinder is provided with a helically extending flow guide, which separates the cooling water channel on the outer wall of the booster cylinder.

[0025] In some embodiments, the flow guide comprises an isolation copper pipe.

[0026] In some embodiments, the thickness of the DLC coating is 2-3 μm.

[0027] In some embodiments, the gas booster comprises two booster cylinders, i.e., a primary booster cylinder and a secondary booster cylinder; the primary booster cylinder comprises a primary booster cylinder and a primary booster piston arranged in the primary booster cylinder; the secondary booster cylinder comprises a secondary booster cylinder and a secondary booster piston arranged in the secondary booster cylinder.

[0028] The primary booster cylinder and the secondary booster cylinder are respectively arranged on the two sides of the driving unit.

[0029] The driving rod of the driving unit comprises a first driving rod and a second driving rod, the first driving rod extends into the primary booster cylinder and is connected with the primary booster piston; the second driving rod extends into the secondary booster cylinder and is connected with the secondary booster piston.

[0030] In the gas booster provided by the embodiments of the present disclosure, the inner hole surface of the booster cylinder and the outer circle of the booster piston are matched by controlling the tolerance gap, forming a low-friction and high-stability friction pair. In the case of high-frequency and rapid reciprocating motion of the booster piston, the friction heat and friction loss can be greatly reduced, which is conducive to reducing the failure rate of the gas booster, prolonging the service life of the gas booster, and improving the working efficiency. BRIEF DESCRIPTION OF DRAWINGS

[0031] Figure 1 is a sectional view of a gas booster in the embodiments of the present disclosure;

[0032] Figure 2 is a sectional view of another gas booster in the embodiments of the present disclosure;

[0033] Figure 3 is a schematic view of a gap sealing structure in the embodiments of the present disclosure.

[0034] Figure 4 is a schematic view of another hydraulic suspension structure in an embodiment of the present disclosure;

[0035] Figure 5 is a schematic view of a hydraulic annular loop in an end cap in an embodiment of the present disclosure;

[0036] Figure 6 is a cross-sectional view of a hydrogen pressure booster in an embodiment of the present disclosure;

[0037] Figure 7 is a perspective view of a hydrogen pressure booster in an embodiment of the present disclosure; DETAILED DESCRIPTION

[0038] In order to make the technical solution of the present disclosure better understood by those skilled in the art, the technical solution of the present disclosure will be described in detail below with reference to the drawings.

[0039] In the following, example embodiments will be described more fully with reference to the accompanying drawings, in which example embodiments can be embodied in different forms and should not be construed as being limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.

[0040] In the case of no conflict, each embodiment of the present disclosure and each feature in the embodiments can be combined with each other.

[0041] As used herein, the term "and / or" includes any and all combinations of one or more of the associated listed items.

[0042] The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the present disclosure. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof.

[0043] The embodiments described herein can be described with reference to plan views and / or cross-sectional views by virtue of the present disclosure being idealized schematic illustrations. Thus, the example illustrations can be modified according to manufacturing techniques and / or tolerances. Therefore, the embodiments are not limited to the embodiments illustrated in the drawings, but include modifications based on manufacturing processes. Thus, the regions illustrated in the drawings have schematic properties and the shapes of the regions illustrated in the drawings do not intend to be limiting, but illustrate specific shapes of regions of elements.

[0044] Unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and the present disclosure and will not be interpreted in an overly literal or overly formal sense unless expressly so defined herein.

[0045] Embodiment one

[0046] Figure 1 is a schematic diagram of a gas booster in an embodiment of the present disclosure.

[0047] As shown in Figure 1 , the gas booster comprises a driving unit 1 and at least one booster cylinder 2. The number of booster cylinders 2 in the gas booster is not particularly limited in the embodiments of the present disclosure. For example, the gas booster comprises one booster cylinder 2, or the gas booster comprises two booster cylinders 2. Figure 1 is a schematic diagram taken as an example that the gas booster comprises two booster cylinders 2.

[0048] The booster cylinder 2 comprises a booster cylinder barrel 21 and a booster piston 22 arranged in the booster cylinder barrel 21. The driving unit 1 comprises a driving rod 11 which is output by the driving unit 1 and extends into the booster cylinder barrel 21 and is connected with the booster piston 22. The driving unit 1 is not particularly limited in the embodiments of the present disclosure. For example, the driving unit 1 can be any one of an electric cylinder, a hydraulic cylinder and a pneumatic cylinder.

[0049] The inner hole surface of the booster cylinder barrel 21 is covered with a diamond like carbon (DLC) coating, and the outer circle surface of the booster piston 22 is covered with a low-friction composite coating, thereby forming a friction pair. The DLC coating process is applied to the inner hole surface of the booster cylinder barrel 21, which can not only improve the hardness of the inner hole of the booster cylinder barrel 21, for example, the hardness HV reaches more than 3000, but also reduce the roughness of the inner hole of the booster cylinder barrel 21; the low-friction composite coating has the characteristics of ultra-low friction, high hardness and low friction loss. The inner hole surface of the booster cylinder barrel 21 covered with the DLC coating and the outer circle of the booster piston 22 covered with the low-friction composite coating can form a low-friction and high-stability friction pair.

[0050] In some embodiments, a sealing element is used between the inner hole of the booster cylinder barrel 21 and the outer circle of the booster piston 22, the friction coefficient of the friction pair composed of the DLC coating and the low-friction composite coating is low, which can greatly reduce the friction heat and friction loss, and is beneficial to prolong the service life of the sealing element, enhance the sealing effect and reduce the risk of hydrogen leakage.

[0051] The low-friction composite coating is not specially limited in the embodiments of the present disclosure. In some embodiments, the low-friction composite coating is a low-friction plastic coating. In some embodiments, the low-friction plastic coating includes a PTFE-based composite coating or a nylon-based composite coating. For example, the low-friction plastic coating is a P80870 nylon-based composite coating.

[0052] In some embodiments, the thickness of the DLC coating is 2 to 3 μm.

[0053] In the present embodiment, the combination of the DLC coating and the low-friction composite coating is used to form a low-friction and high-stability friction pair between the inner hole surface of the plenum cylinder 21 and the outer circle of the plenum piston 22, which is conducive to achieving a high-precision inner hole in the plenum cylinder 21. The inner hole of the plenum cylinder 21 and the outer circle of the plenum piston 22 are fitted through a tolerance-controlled gap, which can significantly reduce the heat generated by friction, reduce the friction loss of the inner hole of the plenum cylinder 21 and the outer circle of the plenum piston 22, and is conducive to reducing the failure rate of the gas booster, prolonging the service life of the gas booster, and improving the work efficiency.

[0054] Embodiment Two

[0055] As shown in Figure 2 , the driving unit 1 in the present embodiment is a hydraulic cylinder.

[0056] In the present embodiment, the gas booster containing two plenum cylinders 2 is provided with a friction pair A, a friction pair B, a friction pair C, a friction pair D, and a friction pair E. The friction pair B and the friction pair C use the combination of the DLC coating and the low-friction composite coating to fit the inner hole of the plenum cylinder 21 and the outer circle of the plenum piston 22 through a tolerance-controlled gap, thereby forming a low-friction and high-stability friction pair; the friction pair A adopts a gap sealing design; and the friction pair D and the friction pair E adopt a hydraulic suspension support structure.

[0057] As shown in Figure 2 , the hydraulic cylinder includes a hydraulic cylinder barrel 12 and a driving piston 13, and the driving rod 11 is connected to the driving piston 13. The inner hole of the hydraulic cylinder barrel 12 and the driving piston 13 are gap-sealed through a tolerance control to form the friction pair A. The oil pressure in the gap between the inner hole of the hydraulic cylinder barrel 12 and the driving piston 13 can make the driving piston 13 and the hydraulic cylinder barrel 12 have no contact or short contact movement due to the throttling effect of the hydraulic oil. Since the reciprocating frequency of the driving piston 13 in the hydraulic cylinder barrel 12 is very high, a short sealing effect can be formed in the gap between the driving piston 13 and the hydraulic cylinder barrel 12 by using the viscosity of the hydraulic oil, so that the sealing effect of the sealing member can be replaced. At the same time, since the reciprocating frequency of the driving piston 13 in the hydraulic cylinder barrel 12 is very high, the amount of hydraulic oil leakage is very small in one stroke of the driving piston 13, which basically does not affect the effect of the hydraulic cylinder.

[0058] In some embodiments, asFigure 3 As shown, the outer circumferential surface of the driving piston 13 is provided with at least one gap sealing groove 131, which extends circumferentially and is used to store hydraulic oil. Storing hydraulic oil in the gap sealing groove 131 can improve the gap sealing effect and increase lubrication.

[0059] like Figure 2 As shown, the hydraulic cylinder further includes an end cap 14 disposed between the hydraulic cylinder barrel 12 and the boost cylinder barrel 21; at least one hydraulic suspension cavity 141 is disposed on the inner surface of the end cap 14. In the disclosed embodiment, a single circumferentially extending hydraulic suspension cavity 141 may be disposed on the inner surface of the end cap 14, or multiple circumferentially spaced hydraulic suspension cavities 141 may be disposed on the inner surface of the end cap 14. This is not particularly limited in the disclosed embodiment. In some embodiments, multiple hydraulic suspension cavities 141 are disposed on the inner surface of the end cap 14, and the multiple hydraulic suspension cavities 141 are evenly distributed along the circumference. For example, the number of hydraulic suspension cavities 141 is four.

[0060] like Figure 2 、 Figure 4 As shown, a plurality of hydraulic suspension cavities 141 are provided on the inner surface of the end cover 14, and the plurality of hydraulic suspension cavities 141 are distributed along the circumferential direction; Figure 5 As shown, the end cover 14 is also provided with a hydraulic annular circuit extending along the circumferential direction and a plurality of pressurizing ports distributed along the circumferential direction, each pressurizing port corresponding to a hydraulic suspension cavity 141 ; the pressurizing ports are in communication with the hydraulic annular circuit and with the corresponding hydraulic suspension cavity 141 .

[0061] like Figure 5 As shown, the hydraulic annular circuit is connected to pressure ports W, X, Y, and Z. When pressure is applied from any of the pressure ports, hydraulic oil flows through the hydraulic annular circuit to each pressure port. The hydraulic oil enters and is stored in the hydraulic suspension chamber 141, exerting a hydrostatic pressure on the drive rod 11, thereby causing the drive rod 11 to suspend within the inner bore of the end cap 14. This achieves frictionless contact between the drive rod 11 and the inner bore of the end cap 14, reducing frictional heat generated between the friction pairs D and E formed by the drive rod 11 and the inner bore of the end cap 14. After the hydraulic suspension support structure is established, the drive rod 11 no longer requires a guide support ring for guidance and support within the inner bore of the end cap 14, further reducing frictional heat generated by the friction pairs D and E. In addition, in the hydraulic suspension support structure, the hydraulic oil in the hydraulic suspension chamber 141 and the hydraulic annular circuit is fluid, which can promptly remove the heat generated by friction between the friction pairs D and E.

[0062] In some embodiments, as Figure 5 As shown, each pressurizing port is connected to the hydraulic annular circuit through a pressure channel; a throttling screw plug 142 is provided in the pressure channel.

[0063] The throttle screw is a device that uses its adjustable internal aperture to control the flow resistance of the fluid, thereby affecting the pressure of the fluid. When the fluid passes through the throttle screw, if the screw is tightened, reducing the aperture, the resistance of the fluid passing through will increase, resulting in an increase in the pressure of the fluid before the throttle screw. Conversely, if the screw is loosened, increasing the aperture, the resistance of the fluid passing through will decrease, and the pressure of the fluid before the throttle screw will decrease. By changing the size of the aperture to control the fluid pressure, the throttle screw can maintain the stability of the output pressure within a relatively fixed range.

[0064] The hydraulic oil in the hydraulic annular circuit realizes proportional pressure drop at each pressurizing port through the hydraulic resistance effect of the throttle screw 142, so that the pressure of the hydraulic oil at each pressurizing port, i.e. the pressure of the hydraulic oil in each hydraulic suspension cavity, remains consistent, thereby enabling the drive rod 11 to be automatically centered in the inner hole of the end cover 14, ensuring that the drive rod 11 has no frictional contact with the inner hole of the end cover 14. In some embodiments, the end cover 14 is provided with a buffer ring, a separation ring, and a cylinder piston sealing ring, and the automatic centering of the drive rod 11 also enables the buffer ring, the separation ring, and the cylinder piston sealing ring to be free from the radial biasing load generated by the flexibility of the drive rod 11 and free from the lateral force of the hydraulic oil pressure, thereby ensuring only a very small constant residual friction, further reducing frictional heat generation.

[0065] In some embodiments, as shown in Figure 4 , a pressure detection channel 143 is provided between the throttle screw 142 and the hydraulic suspension cavity 141, with each pressurizing port corresponding to one pressure detection channel 143. The pressure detection channel 143 is in communication with the pressurizing channel, and a pressure sensor is provided in the pressure detection channel 143 for detecting the pressure in the corresponding hydraulic suspension cavity 141. In some embodiments, the pressure sensor detects the pressure in the hydraulic suspension cavity 141 in real time and feeds back to the central hydraulic control system, which controls the electronic regulating valve to adjust the pressure of the pressurizing port according to the pressure data, thereby achieving real-time feedback adjustment and ensuring that the pressure in the hydraulic suspension cavity 141 remains stable and consistent.

[0066] In some embodiments, as shown in Figure 2 , Figure 4 , the end cover 14 includes a hydraulic suspension ring 140 provided in the inner hole of the end cover 14, and the hydraulic suspension cavity 141 is provided on the inner hole surface of the hydraulic suspension ring 140.

[0067] In some embodiments, the hydraulic suspension ring 140 is in clearance fit with the inner hole of the end cover 14.

[0068] In some embodiments, the hydraulic suspension ring 140 is formed in the inner hole of the end cover 14 by a surfacing machining process. For example, copper is surfacing on the inner hole of the end cover 14, and then the hydraulic suspension cavity 141 is machined.

[0069] In some embodiments, an oil storage structure 144 is further provided on the inner surface of the hydraulic suspension ring 140 , and the oil storage structure 144 is in communication with the hydraulic suspension chamber 141 . For example, the oil storage structure 144 includes a plurality of parallel oil storage grooves distributed parallel to each other on the inner surface of the hydraulic suspension ring 140 .

[0070] In some embodiments, as Figure 4 As shown, a plurality of parallel oil storage tanks are provided on the inner hole surface of the hydraulic suspension ring 140, and the parallel oil storage tanks are connected to the hydraulic suspension chamber 141. After the hydraulic oil enters the hydraulic suspension chamber 141 through the throttling screw 142, the hydraulic oil will flow along the parallel oil storage tanks to fill the entire hydraulic suspension support gap. Regardless of whether the drive rod 11 moves left or right, the entire hydraulic suspension support gap will store pressurized hydraulic oil. The parallel oil storage tanks increase the oil storage capacity of the hydraulic suspension support gap and increase the contact area with the end cover 14, which is conducive to generating a more uniform and stable support pressure, and has a better support and centering effect on the drive rod 11. At the same time, the interface of the parallel oil storage tanks increases the cross-sectional area of ​​the oil film, which can enhance the sealing effect and offset a portion of the pressure of the hydraulic oil in the hydraulic cylinder barrel, thereby relieving the pressure of the seal between the hydraulic suspension ring 140 and the booster cylinder 2, which is conducive to extending the service life of the seal and improving the sealing effect.

[0071] In some embodiments, a reverse dust ring is further provided in the inner hole of the end cover 14 away from the hydraulic cylinder 12 , for scraping oil from the drive rod 11 in a direction close to the hydraulic cylinder 12 .

[0072] In this embodiment, a reverse dust ring is designed to achieve a reverse oil scraping effect. It acts as a sealing ring and cooperates with other sealing rings to achieve a sealing effect, preventing oil from entering the isolation chamber. The dust ring can also scrape oil from the piston rod, preventing oil from adhering to the piston rod and entering the isolation chamber. If hydrogen leaks into the isolation chamber, contact with the high-temperature hydraulic oil will cause the hydrogen to dissolve in the hydraulic oil, causing "cavitation" and corroding the piston rod coating. Furthermore, as the pressure increases, the ignition point of hydrogen decreases. Contact between high-temperature, high-pressure hydrogen and the piston rod hydraulic oil poses a risk of combustion and explosion.

[0073] In some embodiments, an oil scraping and drain groove and an oil drain channel are provided on the side of the reverse dust ring close to the hydraulic cylinder, which can discharge the oil scraped off by the reverse dust ring in time, and prevent the oil pressure from directly impacting the reverse dust ring after the seal fails, serving as a second guarantee for sealing.

[0074] In some embodiments, as Figure 2 As shown, the hydraulic cylinder further includes a proximity switch for detecting the position of the driving piston.

[0075] The proximity switch is added to the hydraulic cylinder barrel to determine when the driving piston hits the bottom, and the proximity switch signal is detected by the matching hydraulic system processor in real time to control the accurate and real-time pressure of the oil cavity, control the timely reversing of the driving piston, ensure the synchronization of the oil cavity pressure and the air cavity inflation, avoid the lag of the two cavities, and improve the compression efficiency.

[0076] In some embodiments, as shown in Figure 2 The booster cylinder includes an isolation cavity on the side of the booster piston close to the driving unit; the gas concentration sensor is arranged at the air inlet and outlet of the isolation cavity respectively to detect the gas concentration in the isolation cavity.

[0077] The hydrogen concentration sensor is added to the air inlet and outlet of the isolation cavity to detect the hydrogen concentration in the isolation cavity in real time, and the data is fed back to the hydraulic system control center in real time. When the hydrogen leaks due to the failure of the cylinder piston, the isolation cavity will be filled with leaked hydrogen. When the hydrogen reaches a certain concentration, the sensor alarm device will be triggered, and the signal will be transmitted to the central information processing system. The system will issue an instruction to stop the oil cylinder immediately. Real-time early warning of hydrogen leakage can be realized to ensure safe operation.

[0078] Embodiment Three

[0079] This embodiment takes a hydrogen booster with two-stage booster cylinders as an example for illustration. The hydrogen booster takes a hydraulic cylinder as the driving unit. Figure 6 The hydrogen booster is a cross-sectional view, Figure 7 is a schematic diagram of the hydrogen booster.

[0080] As shown in Figure 6 , Figure 7 The hydrogen booster includes a hydraulic cylinder 100, a first-stage booster cylinder 200, and a second-stage booster cylinder 300. The first-stage booster cylinder 200 includes a first-stage booster cylinder barrel 201 and a first-stage booster piston 202 arranged in the first-stage booster cylinder barrel 201. The second-stage booster cylinder 300 includes a second-stage booster cylinder barrel 301 and a second-stage booster piston 302 arranged in the second-stage booster cylinder barrel 301. The first-stage booster cylinder barrel 201 and the second-stage booster cylinder barrel 301 are arranged on both sides of the hydraulic cylinder 100. The hydraulic cylinder 100 includes a driving piston 101, a first driving rod 102, a second driving rod 103, and a hydraulic cylinder barrel 104. The first driving rod 102 extends into the first-stage booster cylinder barrel 201 and is connected with the first-stage booster piston 202. The second driving rod 103 extends into the second-stage booster cylinder barrel 301 and is connected with the second-stage booster piston 302. In this embodiment, the hydrogen booster increases the pressure of low-pressure hydrogen to high-pressure hydrogen through two-stage booster cylinders. For example, the low-pressure hydrogen is first boosted by the first-stage booster cylinder 200, and the outlet pressure of the first-stage booster cylinder 200 is 45 MPa. Then, the hydrogen enters the second-stage booster cylinder 300 for further boosting, and the outlet pressure of the second-stage booster cylinder 300 is 90 MPa.

[0081] As shown in Figure 6 Friction pair A, friction pair B, friction pair C, friction pair D, friction pair E are arranged in the hydrogen booster. Friction pair B and friction pair C constitute a friction pair system, aiming to reduce the friction heat and friction loss of the hydrogen booster during high-frequency reciprocating operation.

[0082] In the friction pair A, a clearance seal design is used for the driving piston 101. The throttling effect of the oil through the gap between the clearance seal sleeve and the piston rod replaces the ordinary pressurized seal to achieve the sealing effect. In addition, the oil storage groove is added to the surface of the driving piston 101 to increase the lubrication. The short contact or non-contact movement of the driving piston 101 and the hydraulic cylinder barrel 104 can be achieved by using oil pressure. The reciprocating frequency of the oil cylinder is very fast. A short sealing effect can be formed between the gap of the driving piston 101 and the inner wall of the hydraulic cylinder barrel 104 by using the viscosity of the hydraulic oil. Since the driving piston 101 in the hydraulic cylinder 100 has a high movement frequency, the amount of hydraulic oil leakage in the gap during a stroke is very small, which does not affect the overall effect of the hydraulic cylinder 100.

[0083] In the friction pair B and the friction pair C, the outer peripheral surface of the primary booster piston 202 and the secondary booster piston 302 is sprayed with a low-friction composite coating such as PTFE-based composite coating or nylon-based composite coating. The low-friction composite coating has the characteristics of ultra-low friction, high hardness, and low wear. The low-friction composite coating can be PTFE-based and / or nylon-based composite coating. The inner peripheral surface of the secondary booster cylinder 301 and the primary booster cylinder 201 is sprayed with a DLC coating. The DLC coating can not only improve the hardness of the cylinder bore, but also reduce the roughness of the cylinder bore, cooperating with the PTFE-based or nylon-based composite coating to form a low-friction and high-stability friction pair.

[0084] In the friction pair D and the friction pair E, a hydraulic suspension support structure is designed. The oil is injected from the pressing port and flows through the hydraulic annular circuit to each pressurizing port, and then realizes proportional pressure reduction through the liquid resistance effect of the throttling screw plug. Cooperating with the tolerance control and gap between the hydraulic suspension ring and the driving piston 101, the hydraulic oil can be stored in the internal suspension isolation cavity of the hydraulic suspension ring, so that the driving piston 101 is suspended, and the fluid static pressure can automatically center the driving rod to realize the frictionless contact between the driving piston 101 and the end cover. In this way, the guide support ring is removed, and the heat generated during the movement of the piston rod is taken away by the hydraulic oil circulating into the pressing port, avoiding the generation of more heat. Due to the automatic centering of the driving rod, the buffer ring, the isolation ring, and the cylinder piston sealing ring in the end cover are not subjected to the radial bias load generated by the flexibility of the piston rod and the lateral force generated by the oil pressure, so only a small constant residual friction is generated, and the heat generated is very small.

[0085] Through the hydraulic suspension effect of friction pairs D and friction pairs E and the mutual influence and cooperation between the low-friction friction pairs at friction pairs A, friction pairs B, and friction pairs C, the hydrogen supercharger can achieve high-frequency, high-efficiency, and low-friction movement.

[0086] like Figure 6 As shown, in the hydrogen booster cylinder, the secondary booster cylinder 300 includes a secondary booster cylinder barrel 301 and a secondary booster piston 302. The secondary booster piston 302 is fixedly connected to the second drive rod piston 103 via fasteners such as bolts. The secondary booster piston 302 reciprocates within the secondary booster cylinder barrel 301, so that the outer diameter of the secondary booster piston 302 and the inner bore surface of the secondary booster cylinder barrel 301 form a friction pair.

[0087] A cooling water circulation system is provided on the outer peripheral side of the secondary boost cylinder 301. Figure 6 As shown, the cooling water circulation system includes a water inlet 303, a guide member 304, and a water outlet 305. The guide member 304 is arranged on the outer peripheral side of the secondary boost cylinder 301. The guide member 304 is arranged around the outer peripheral side of the secondary boost cylinder 301, and a cooling water channel is separated on the outer periphery of the secondary boost cylinder 301. The cooling water channel is connected with the water inlet 303 and the water outlet 305. The cooling water enters the cooling water channel from the water inlet 303 and is discharged from the water outlet 305, thereby cooling the secondary boost cylinder 301.

[0088] In some embodiments, the flow guide 304 is a baffle.

[0089] In some embodiments, the flow guide 304 is an insulated copper tube.

[0090] The secondary booster piston 302 comprises a main body and a cylindrical portion located to one side of the main body and surrounding the central axis of the secondary booster piston 302. The cylindrical portion defines a recess into which the second drive rod 103 fits. An annular groove is formed at one end of the second drive rod 103, into which a mating piece fits. A fastener threaded through the mating piece and into the cylindrical portion securely connects the secondary booster piston 302 to the second drive rod 103.

[0091] On the other side of the main body of the secondary booster piston 302, a seal is secured to the main body of the secondary booster piston 302 via fasteners such as screws. A groove is formed on the outer circumferential surface of the secondary booster piston 302 to accommodate the seal. Of course, the structure of the secondary booster piston 302 and its connection to the second drive rod 103 are not limited to this.

[0092] To reduce the friction between the secondary supercharging piston 302 and the secondary supercharging cylinder 301, a PTFE-based or nylon-based composite coating is sprayed on the outer circumferential surface of the secondary supercharging piston 302, one example of which is the P80870 nylon-based composite coating, but not limited to this. The PTFE-based or nylon-based composite coating has the characteristics of ultra-low friction, high hardness, and low wear. In addition, a DLC coating is sprayed on the inner hole surface of the secondary supercharging cylinder 301, which not only can improve the hardness of the cylinder inner hole, in one embodiment, the cylinder inner hole hardness can reach HV≥3000, but also can reduce the roughness of the cylinder inner hole, in one embodiment, the roughness of the cylinder inner hole can reach Ra0.05 or even higher. The secondary supercharging piston 302 sprayed with the PTFE-based or nylon-based composite coating and the secondary supercharging cylinder 301 sprayed with the DLC coating form a low-friction and high-stability friction pair.

[0093] The primary supercharging cylinder 200 includes a primary supercharging cylinder 201 and a primary supercharging piston 202, wherein the primary supercharging piston 202 is fixedly connected with the first driving rod 102 through fasteners such as bolts. The primary supercharging piston 202 reciprocates in the primary supercharging cylinder 201, so that the outer circumferential surface of the primary supercharging piston 202 and the inner circumferential surface of the primary supercharging cylinder 201 form a friction pair.

[0094] A cooling water circulation system is provided on the outer circumferential side of the primary supercharging cylinder 201, which is similar to the cooling water circulation system of the above-mentioned secondary supercharging cylinder 301, which will not be described here.

[0095] The primary supercharging piston 202 includes a body portion and a cylindrical portion located on one side of the body portion and surrounding the central axis of the primary supercharging piston 202, and the cylindrical portion and the cylindrical portion have different inner diameters to form a step between them, specifically, the inner diameter of the cylindrical portion is smaller than the inner diameter of the cylindrical portion, and the cylindrical portion and the cylindrical portion form a recess, and the first driving rod 102 is fitted in the recess. An annular groove is formed on the corresponding end of the first driving rod 102, and a fitting member is embedded in the groove. The fasteners that pass through the fitting member and are screwed into the cylindrical portion fixedly connect the primary supercharging piston 202 with the first driving rod 102.

[0096] On the other side of the body portion of the primary supercharging piston 202, a sealing member is fixed to the body portion of the primary supercharging piston 202 by fasteners such as screws. A groove is formed on the outer circumferential surface of the primary supercharging piston 202 to accommodate the sealing member. Of course, the structure of the primary supercharging piston 202 and the connection method with the first driving rod 102 are not limited to this. Moreover, the structure of the primary supercharging piston 202 can be mutually exchanged with the structure of the secondary supercharging piston 302.

[0097] In order to reduce the friction between the first-stage supercharged piston 202 and the first-stage supercharged cylinder 201 due to the movement of the piston, a PTFE-based or nylon-based composite coating is sprayed on the outer surface of the first-stage supercharged piston 202 of the utility model, one example of which is a P80870 nylon-based composite coating, but not limited to this. As described above, the PTFE-based or nylon-based composite coating has the characteristics of ultra-low friction, high hardness and low wear. In addition, a DLC coating is sprayed on the inner peripheral surface of the first-stage supercharged cylinder 201, which not only improves the hardness of the cylinder bore to HV≥3000, but also reduces the roughness of the cylinder bore to Ra0.05 or even higher. The first-stage supercharged piston 202 sprayed with the PTFE-based or nylon-based composite coating and the first-stage supercharged cylinder 201 sprayed with the DLC diamond-like carbon coating form a low-friction and high-stability friction pair.

[0098] In addition, the embodiment improves the DLC coating manufacturing process through the integration of plasma enhancement and deposition. Specifically, first, the substrate surface is bombarded by plasma to enhance the active sites of the substrate and improve the bonding capacity of the substrate. Carbon ions are generated by a high-energy ion source and injected into the substrate surface. By precisely controlling the energy, dose and angle of ion implantation, a carbon-rich transition layer can be formed on the substrate surface, which can improve the interface bonding between the coating and the substrate, reduce the stress within the coating, and provide a good foundation for the subsequent deposition process. Then, a microwave plasma source is used to generate carbon-rich plasma, and by reasonably controlling the power, gas pressure, gas flow and using a magnetic field to control the plasma motion, a stable and dense DLC carbon coating structure with excellent performance and good control of the coating thickness can be generated. Through annealing and laser modification processes, the surface finish and lubrication of the coating are improved.

[0099] A high-precision polishing process can be used on the inner peripheral surface of the cylinder. Specifically, first, a composite process combining magnetorheological polishing and chemical mechanical polishing is used. Magnetorheological polishing uses the rheological properties of magnetorheological fluid in a magnetic field to form a "flexible polishing mold" with high shear force, which can quickly remove the material on the surface of the workpiece. Its principle is that under the action of a magnetic field, the magnetic particles in the magnetorheological fluid are polarized to form a chain structure, and the hardness and stiffness of the chain structure can be adjusted by the magnetic field, thereby achieving high-precision removal of the workpiece material. Chemical mechanical polishing uses the synergistic effect of chemical corrosion and mechanical grinding to make the workpiece surface reach atomic level flatness. By adding specific chemical reagents to the polishing liquid, a reaction occurs with the workpiece surface material to generate a product that is easy to remove. At the same time, the polishing pad mechanically grinds the workpiece surface to remove the reaction product. By combining these two polishing methods, first, magnetorheological polishing is used for rough polishing to quickly reduce the roughness of the workpiece surface, and then chemical mechanical polishing is used for fine polishing to achieve a surface roughness of 0.1 microns.

[0100] A high-precision online detection and feedback control system is also incorporated throughout the polishing process. High-precision measuring equipment such as laser interferometers and atomic force microscopes monitor the workpiece surface roughness in real time, feeding the measurement data back to the control system. Based on this feedback, the control system automatically adjusts polishing parameters, such as magnetic field intensity and polishing fluid flow rate for magnetorheological polishing, and polishing pressure and time for chemical mechanical polishing. This intelligent control ensures precise polishing of the workpiece surface, ensuring a roughness target of 0.1 micron.

[0101] To ensure a stable polishing environment, an ultra-clean, constant temperature and humidity environment is constructed. Within a closed polishing chamber, an air filtration system removes dust and impurities, maintaining an air cleanliness level of at least Class 100. Temperature and humidity control devices maintain the ambient temperature within ±0.1°C and the humidity within ±2%. This stable environment prevents external factors from interfering with the polishing process and reduces the occurrence of surface defects, which is crucial for achieving ultra-precision polishing results down to 0.1 microns.

[0102] The high-precision inner hole of the cylinder can significantly reduce the frictional heat generated by the sealing ring, increase the service life of the seal, enhance the sealing effect of the seal, and reduce the risk of high-pressure hydrogen leakage.

[0103] In the hydraulic cylinder 100, the driving piston 101 reciprocates in the hydraulic cylinder barrel 104, so that the outer circumferential surface of the driving piston 101 and the inner circumferential surface of the hydraulic cylinder barrel 104 form a friction pair, such as Figure 6 Middle friction pair A.

[0104] At friction pair A, a gap seal design is employed for the drive piston 101. Specifically, a plurality of spaced-apart annular oil storage grooves are provided on the outer circumferential surface of the drive piston 101. In this embodiment, the cross-sectional shape of the oil storage grooves is rectangular, but this shape is not limited and can be adapted to specific applications, such as semicircular, semi-elliptical, V-shaped, U-shaped, and so on.

[0105] Compared with sealing with sealing ring, the throttling effect of oil through the gap between the gap sealing sleeve and the piston rod is used to replace the ordinary pressurized seal to achieve the sealing effect. Adding an oil storage tank on the piston surface can increase lubrication. The oil pressure can achieve short contact or contactless movement between the piston and the cylinder. The reciprocating frequency of the cylinder is very fast. By utilizing the viscosity of the hydraulic oil, the hydraulic oil can form a short sealing effect between the gap between the piston and the inner wall of the cylinder. Since the movement frequency of the cylinder is very high, the amount of oil leakage in the gap seal during a stroke is very small, which does not affect the effect of the entire cylinder.

[0106] The hydraulic cylinder 100 also includes a hydraulic suspension ring, such as Figure 6As shown in the friction pair D, the hydraulic suspension ring is arranged between the outer peripheral surface of the driving piston 101 and the inner hole surface of the end cover as the hydraulic cylinder barrel 104. A plurality of pressing ports 5 are arranged in the outer peripheral surface of the end cover, and the pressing ports 5 extend to the inner peripheral surface of the end cover in the radial direction through the hydraulic passages. Four hydraulic suspension pressing ports are arranged in the hydraulic suspension ring at equal intervals in the circumferential direction, but the number of the pressing ports is not limited to four, and can be one, two, three, five or more.

[0107] Each pressing port is communicated with each other through a hydraulic ring circuit. A throttling screw plug is arranged in each hydraulic passage, and the throttling screw plug has a liquid resistance effect, so as to realize proportional pressure reduction. A passage communicated with the hydraulic passage in the transverse direction is arranged on the downstream side of the throttling screw plug in the oil liquid direction, the passage is communicated with a detection passage extending to the outer peripheral surface of the end cover in the radial direction, and the detection passage is terminated at a pressure detection port in the outer peripheral surface of the end cover, so that the pressure in the passage can be detected through the pressure detection port.

[0108] A plurality of hydraulic holes penetrating through the hydraulic suspension ring in the radial direction are arranged in the hydraulic suspension ring, and each hydraulic hole is communicated with each hydraulic passage respectively. A hydraulic suspension oil storage groove communicated with the plurality of hydraulic holes is arranged in the inner periphery of the hydraulic suspension ring, and each hydraulic suspension oil storage groove extends at least a part in the circumferential direction of the hydraulic suspension ring in the cross section. In an embodiment, each hydraulic suspension oil storage groove is independent and not communicated with each other. In an embodiment, each hydraulic suspension oil storage groove is communicated with each other, and forms a gap between the hydraulic suspension ring and the driving rod.

[0109] A plurality of oil discharge grooves corresponding to the hydraulic suspension oil storage groove are formed in the inner peripheral surface of the end cover at one end of the hydraulic suspension ring, and each oil discharge groove is communicated with a corresponding oil discharge passage extending to the outer peripheral surface of the end cover in the radial direction. The oil discharge passage is terminated at a discharge port in the outer peripheral surface of the end cover, so that the oil liquid in the passage can be discharged through the discharge port.

[0110] As described above, the utility model is provided with the hydraulic suspension support structure, and the pressure is punched into the hydraulic suspension pressing port before the oil cylinder moves, and is circulated to each pressing port through the hydraulic ring circuit, and then the proportional pressure reduction is realized through the liquid resistance effect of the throttling screw plug, and the tolerance control and gap cooperation between the hydraulic suspension ring and the driving rod can make the oil pressure stored in the internal suspension isolation cavity of the hydraulic suspension ring, so that the driving rod is suspended, and the hydrostatic pressure action can make the driving rod automatically centered. In this way, the frictionless contact between the driving rod and the end cover is realized, the guide support ring is removed, and the heat generated in the movement process of the driving rod can be taken away by the hydraulic oil circulatingly injected into the pressing port, so that more heat is avoided. Due to the automatic centering of the piston rod, the buffer ring, the isolation ring and the cylinder piston sealing ring in the end cover are not subjected to the radial eccentric load generated by the flexibility of the main oil cylinder piston, and are not subjected to the lateral force generated by the oil pressure, so that only a small constant residual friction is generated, and the heat generated is small.

[0111] Example embodiments have been disclosed herein and, although the specific terms are employed, they are used in a generic sense only and should not be construed to be limited to the specific embodiments described herein. In some instances, those of ordinary skill in the art will appreciate that a feature, structure, or characteristic described in connection with a particular embodiment can be used in connection with another embodiment unless expressly mixed in contradiction thereto. Changes in form and detail can be made without departing from the scope of the disclosure as set forth in the accompanying claims.

Claims

1. A gas booster, comprising: A drive unit, at least one boosting cylinder; the boosting cylinder includes a boosting cylinder barrel and a boosting piston disposed in the boosting cylinder barrel; the drive unit includes a drive rod, the drive rod extends into the boosting cylinder barrel and is connected to the boosting piston; characterized in that, The inner hole of the booster cylinder and the booster piston are matched with each other through a tolerance-controlled clearance. The inner hole surface of the booster cylinder is covered with a diamond-like coating, and the outer cylindrical surface of the booster piston is covered with a low-friction composite coating, forming a friction pair.

2. The gas booster according to claim 1, characterized in that The low-friction composite coating includes a PTFE-based composite coating and / or a nylon-based composite coating.

3. The gas booster according to claim 2, characterized in that: The driving unit includes a hydraulic cylinder, which includes a hydraulic cylinder barrel and a driving piston. The driving rod is connected to the driving piston. The inner hole of the hydraulic cylinder barrel and the driving piston are gap-sealed through tolerance control.

4. The gas booster according to claim 3, characterized in that: The outer circumferential surface of the driving piston is provided with at least one gap sealing groove, which extends in a circumferential direction and is used for storing hydraulic oil.

5. The gas booster according to claim 3, characterized in that: The hydraulic cylinder also includes an end cover arranged between the hydraulic cylinder barrel and the booster cylinder barrel; a plurality of hydraulic suspension chambers are arranged on the inner hole surface of the end cover, and the plurality of hydraulic suspension chambers are distributed along the circumferential direction; the end cover is also provided with a hydraulic annular circuit extending along the circumferential direction, and a plurality of pressurizing ports distributed along the circumferential direction, each of the pressurizing ports corresponds to one of the hydraulic suspension chambers; the pressurizing ports are connected to the hydraulic annular circuit and to the corresponding hydraulic suspension chambers.

6. The gas booster according to claim 5, characterized in that: Each of the pressurizing ports is communicated with the hydraulic annular circuit via a pressure channel; a throttling screw plug is provided in the pressure channel for keeping the pressure at each of the pressurizing ports consistent.

7. The gas booster according to claim 6, characterized in that Each of the pressurizing ports corresponds to a pressure detection channel, which is communicated with the pressure-pressing channel. A pressure sensor is provided in the pressure detection channel for detecting the pressure in the corresponding hydraulic suspension chamber.

8. The gas booster according to any one of claims 5 to 7, characterized in that: The end cover comprises a hydraulic suspension ring arranged in the inner hole of the end cover, and the hydraulic suspension cavity is arranged on the inner hole surface of the hydraulic suspension ring.

9. The gas booster according to claim 8, characterized in that The hydraulic suspension ring is in clearance fit with the inner hole of the end cover; or The hydraulic suspension ring is formed in the inner hole of the end cover by a surfacing process.

10. The gas booster according to claim 8, characterized in that An oil storage structure is also provided on the inner hole surface of the hydraulic suspension ring, and the oil storage structure is communicated with the hydraulic suspension cavity.

11. The gas booster according to claim 10, characterized in that The oil storage structure includes a plurality of parallel oil storage grooves distributed parallel to each other on the inner hole surface of the hydraulic suspension ring.

12. The gas booster according to any one of claims 5 to 7, characterized in that: A reverse dust ring is further provided in the inner hole of the end cover away from the hydraulic cylinder barrel, for scraping oil from the drive rod in a direction close to the hydraulic cylinder barrel.

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

14. The gas booster according to any one of claims 5 to 7, characterized in that: The hydraulic cylinder further includes a proximity switch for detecting the position of the driving piston.

15. The gas booster according to any one of claims 1 to 7, characterized in that: The booster cylinder includes an isolation chamber located on the side of the booster piston close to the drive unit; the inlet and exhaust ports of the isolation chamber and the inlet and exhaust ports of the isolation chamber are respectively provided with gas concentration sensors for detecting the gas concentration in the isolation chamber.

16. The gas booster according to any one of claims 1 to 7, characterized in that: A cooling water channel is also provided on the outer wall of the boost cylinder.

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

18. The gas booster according to any one of claims 1 to 7, characterized in that: The thickness of the diamond-like carbon coating is 2 to 3 μm.

19. The gas booster according to any one of claims 1 to 7, characterized in that: The gas booster includes two boosting cylinders, a primary boosting cylinder and a secondary boosting cylinder; the primary boosting cylinder includes a primary boosting cylinder barrel and a primary boosting piston disposed in the primary boosting cylinder barrel; the secondary boosting cylinder includes a secondary boosting cylinder barrel and a secondary boosting piston disposed in the secondary boosting cylinder barrel; The first-stage boost cylinder and the second-stage boost cylinder are respectively arranged on both sides of the drive unit; The driving rod of the driving unit includes a first driving rod and a second driving rod. The first driving rod extends into the primary boosting cylinder and is connected to the primary boosting piston; the second driving rod extends into the secondary boosting cylinder and is connected to the secondary boosting piston.

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