WO2023179186A1 - 一种具有流量调节与稳压功能的供氢组合阀 - Google Patents

一种具有流量调节与稳压功能的供氢组合阀 Download PDF

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Publication number
WO2023179186A1
WO2023179186A1 PCT/CN2023/071680 CN2023071680W WO2023179186A1 WO 2023179186 A1 WO2023179186 A1 WO 2023179186A1 CN 2023071680 W CN2023071680 W CN 2023071680W WO 2023179186 A1 WO2023179186 A1 WO 2023179186A1
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Prior art keywords
valve
pressure
hydrogen
flow channel
throttling
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PCT/CN2023/071680
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English (en)
French (fr)
Inventor
钱锦远
于龙杰
盛侃
徐毅翔
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浙江大学
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Publication of WO2023179186A1 publication Critical patent/WO2023179186A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/20—Excess-flow valves
    • F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
    • F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
    • F16K17/26—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in either direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
    • F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/30—Details
    • F16K3/32—Means for additional adjustment of the rate of flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C13/00—Details of vessels or of the filling or discharging of vessels
    • F17C13/04—Arrangement or mounting of valves
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M8/00—Fuel cells; Manufacture thereof
    • H01M8/04—Auxiliary arrangements, e.g. for control of pressure or for circulation of fluids
    • H01M8/04082—Arrangements for control of reactant parameters, e.g. pressure or concentration
    • H01M8/04089—Arrangements for control of reactant parameters, e.g. pressure or concentration of gaseous reactants
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M8/00—Fuel cells; Manufacture thereof
    • H01M8/04—Auxiliary arrangements, e.g. for control of pressure or for circulation of fluids
    • H01M8/04082—Arrangements for control of reactant parameters, e.g. pressure or concentration
    • H01M8/04201—Reactant storage and supply, e.g. means for feeding, pipes
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M8/00—Fuel cells; Manufacture thereof
    • H01M8/04—Auxiliary arrangements, e.g. for control of pressure or for circulation of fluids
    • H01M8/04298—Processes for controlling fuel cells or fuel cell systems
    • H01M8/04694—Processes for controlling fuel cells or fuel cell systems characterised by variables to be controlled
    • H01M8/04746—Pressure; Flow
    • H01M8/04753—Pressure; Flow of fuel cell reactants

Definitions

  • the invention belongs to the field of valves, and in particular relates to a hydrogen supply combination valve with flow adjustment and pressure stabilizing functions.
  • High-pressure hydrogen storage bottles are used to store high-pressure gaseous hydrogen with a temperature above the critical temperature.
  • the ideal hydrogen supply combination valve needs to realize two functions: the first is to reduce the hydrogen pressure to the rated range; the second is to accurately control the hydrogen flow , can achieve stable pressure reduction and control the flow rate as needed.
  • double pressure reducing valves can be used to reduce the pressure.
  • the output pressure is relatively stable, but when the pressure is maintained unchanged Regulating flow is difficult.
  • the hydrogen supply combination valve usually consists of a pressure reducing valve, a solenoid valve, and a temperature and pressure sensor.
  • the pressure reducing valve achieves the stability of flow and pressure.
  • the solenoid valve is usually installed after the pressure reducing valve to realize the switching, opening and closing of the entire hydrogen supply circuit. .
  • the purpose of the present invention is to solve the problem in the prior art that the pressure reducing valve cannot simultaneously meet the two technical requirements of stabilizing output pressure and regulating hydrogen flow, thereby providing a hydrogen supply combination valve with flow adjustment and pressure stabilizing functions.
  • a hydrogen supply combination valve with flow adjustment and pressure stabilization functions which includes a combination valve body, a first-level pressure reducing valve, a second-level pressure reducing flow control valve and a second-level pressure reducing control valve, and the first-level pressure reducing valve,
  • the two-stage pressure reducing flow regulating valve and the two-stage pressure reducing regulating valve are respectively installed in the combination valve body through the first valve seat, the second valve seat and the third valve seat;
  • the combination valve body is provided with a primary outlet flow channel, a connection flow channel, a secondary outlet channel and a pressure regulating hydrogen storage channel;
  • the primary outlet channel is connected to the connecting channel, and the secondary outlet channel serves as the final output channel of the hydrogen supply combination valve;
  • the first-level pressure reducing valve is used to connect an external hydrogen source and perform first-level decompression of the input hydrogen gas, and input it into the first-level outlet flow channel;
  • the two-stage pressure reducing flow regulating valve includes a second sealing piston, a second actuator, a third spring, a second throttling base and a fourth spring; the second valve seat does not penetrate the combination valve body, so The second sealing piston is sealed and fixedly installed on the open end of the second valve seat, the second actuator and the second throttling base are installed in the second valve seat, and the second actuator is located on the second throttling base and the second throttling base.
  • the second sealing piston is provided with a protruding retaining ring on the side facing the second actuator; the inner cavity of the second valve seat is between the second sealing piston, the second actuator and the second Under the separation of the throttling base, independent first chambers, second chambers and third chambers are formed in sequence from the open end to the inner bottom surface; there is a compression state between the second actuator and the second throttling base.
  • a third spring, a fourth spring in a compressed state is provided between the second throttling base and the inner bottom surface of the second valve seat; a center of the second throttling base is provided for connecting the second chamber and the third In the secondary outlet flow channel of the chamber, one end of the second actuator is a second tapered structure, and the second tapered structure cooperates with the second throttling base at the entrance position of the secondary outlet flow channel to form a third Two throttling intervals;
  • the two-stage pressure reducing regulating valve includes a third sealing piston, a fifth spring, a third throttling base and a sixth spring; the third valve seat does not penetrate the combination valve body, and the third sealing piston seals
  • the third valve seat is fixedly installed on the open end of the third valve seat, the third throttling base is installed in the third valve seat, and the inner cavity of the third valve seat is separated by the third sealing piston and the third throttling base.
  • the open end inwardly forms an independent fourth chamber and a fifth chamber in sequence; a fifth spring in a compressed state is provided between the third sealing piston and the third throttling base; the third throttling base A sixth spring in a compressed state is provided between the third valve seat and the inner bottom surface of the third valve seat; a third-stage outlet flow channel is provided in the center of the third throttling base for connecting the fourth chamber and the fifth chamber.
  • the end of the three-seal piston is a third conical structure, and the third conical structure cooperates with the third throttling base at the entrance position of the third-stage outlet flow channel to form a third throttling interval;
  • the second chamber and the fourth chamber are connected to the connecting flow channel through the first channel and the second channel respectively; the third chamber and the fifth chamber are connected to the secondary outlet flow channel respectively; the first The chamber and the secondary outlet flow channel are connected to the pressure-regulating hydrogen storage flow channel through a third channel and a fourth channel respectively; and the first connection port between the pressure-regulating hydrogen storage flow channel and the third channel and the The pressure-regulating hydrogen storage flow channel is kept at a distance from the second connection port of the fourth channel, and the pressure-regulation hydrogen storage flow channel between the first connection port and the second connection port serves as a pressure regulation section; the pressure-regulation hydrogen storage flow channel is equipped with There is a controllable sliding piston forming a piston pair with the inner wall of the flow channel, and the sliding stroke of the controllable sliding piston in the pressure regulating hydrogen storage flow channel covers the pressure adjustment section; the controllable sliding piston slides in the pressure adjustment section During the process, the opening of the second throttling section is controlled by changing the pressure in the first chamber, thereby changing the hydrogen flow rate output by the
  • the first-stage pressure reducing valve includes an inlet flow channel, a first throttling base, a first actuator, an inner flow channel of the actuator, a first sealing piston, a first spring and a second spring; the first valve The seat penetrates the entire combination valve body.
  • the first throttling base and the first sealing piston are sealed and fixedly installed at the openings at both ends of the first valve seat.
  • the first valve seat is provided with a through inlet.
  • the first actuator is installed in the first valve seat and is located between the first throttling base and the first sealing piston, one end of the first actuator is a first tapered structure, and the first The tapered structure cooperates with the first throttling base at the outlet end of the inlet flow channel to form a first throttling section;
  • a first spring in a compressed state is provided between the first actuator and the first sealing piston.
  • a second spring in a compressed state is provided between the first actuator and the first throttle base, and the first spring and the second spring exert two pressures in opposite directions on the first actuator respectively;
  • the first actuator is provided with an internal flow channel of the actuator that is connected to the top surface of the first actuator.
  • the inlet end of the inlet flow channel is used to connect to an external hydrogen source.
  • the input hydrogen passes through the inlet flow channel, the The first throttling section and the inner flow channel of the actuator then enter the first-level outlet flow channel.
  • the first throttling base and the first sealing piston both have coaxial spring mounting holes at the location where the first spring is installed, and a bottom of the spring mounting hole of the first throttling base is placed to communicate with the internal flow of the actuator.
  • One end of the first spring is supported on the holed disc, and the other end is supported in the spring mounting hole of the first sealing piston.
  • the first sealing piston and the inner wall of the first valve seat, the first throttling base and the inner wall of the first valve seat, and the first throttling base and the first actuator are all sealed by a first sealing gasket.
  • the primary outlet flow channel and the connecting flow channel are drilled from the surface of the combination valve body to the inside, and their open ends located on the surface of the combination valve body are sealed by cylindrical seals. closed.
  • controllable sliding piston is provided with a control rod.
  • the control rod extends out of the combination valve body and maintains a dynamic seal in the contact position with the combination valve body.
  • connection port between the third channel and the first chamber side wall is within the height range of the baffle ring.
  • the second actuator includes a second conical structure connected below a circular plate, the side wall of the second valve seat has a stepped surface, and a second sealing gasket is placed on the stepped surface.
  • the circular plate moves toward the second throttling base, it can be pressed against the second sealing gasket to ensure that the first chamber and the second chamber are sealed and not connected.
  • controllable sliding piston can completely close the second throttling section during sliding in the pressure adjustment section.
  • the hydrogen pressure range of the external hydrogen source is 10-70MPa.
  • the pressure of the hydrogen is reduced to 2-3MPa.
  • the pressure of the hydrogen is reduced to The working pressure of the vehicle-mounted hydrogen fuel cell is reduced to the working pressure of the vehicle-mounted hydrogen fuel cell after passing through the secondary pressure reducing regulating valve.
  • the present invention realizes the adjustment of the outlet flow of the hydrogen supply combination valve while being as stable as possible by setting up a two-stage pressure reduction process, and setting up a two-stage pressure reduction flow regulating valve and a two-stage pressure reduction regulating valve in parallel in the second stage of pressure reduction.
  • Outlet pressure The outlet hydrogen flow is only regulated by the secondary pressure reducing flow regulating valve, while the secondary pressure reducing regulating valve maintains a continuous and stable flow output and buffers the pressure fluctuation caused by the flow regulation of the secondary pressure reducing flow regulating valve, thus greatly reducing the flow regulating process.
  • the fluctuation of the final outlet pressure of the entire valve not only reduces the hydrogen pressure to the rated range, but also accurately controls the hydrogen flow rate.
  • the present invention can be applied to fields such as vehicle-mounted hydrogen supply. It can adjust the output flow of the hydrogen supply combination valve and realize the power change of vehicle-mounted hydrogen supply on the premise of realizing the integration of dual-stage voltage reduction and stabilization and hydrogen combination valve.
  • Figure 1 is a schematic structural diagram of a hydrogen supply combination valve with flow adjustment and pressure stabilization functions.
  • Figure 2 is a schematic diagram of the flow channel and valve seat structure in the valve body of the combination valve.
  • Figure 3 is a schematic structural diagram of the first-stage pressure reducing valve.
  • Figure 4 is a schematic structural diagram of the secondary pressure reducing flow regulating valve.
  • Figure 5 is a schematic structural diagram of the secondary pressure reducing regulating valve.
  • Figure 6 is a schematic diagram of the three key control points of the controllable sliding piston in the pressure-regulating hydrogen storage flow channel.
  • the reference numbers in the figure are as follows: primary outlet channel 1, connecting channel 2, first channel 3, second channel 4, third channel 5, secondary outlet channel 6, pressure regulating hydrogen storage channel 7, Four channels 8, first valve seat 9, second valve seat 10, third valve seat 11, cylindrical seal 12, inlet flow channel 13, first throttling base 14, first actuator 15, actuator inner flow channel 16 , first sealing washer 17, first sealing piston 18, holed disc 19, first spring 20, second spring 21, second sealing piston 22, second actuator 23, second sealing washer 24, third spring 25.
  • first and second are only used for distinction and description purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features. . Therefore, features defined as “first” and “second” may explicitly or implicitly include at least one of these features.
  • a hydrogen supply combination valve with flow adjustment and pressure stabilization functions is provided. Its main components include a combination valve body and a first-stage pressure reducing valve I, Two-stage pressure reducing flow regulating valve II and two-stage pressure reducing regulating valve III. Among them, the function of the first-stage pressure reducing valve I is to perform the first-stage pressure reduction on the input high-pressure hydrogen, while the functions of the two-stage pressure reducing flow regulating valve II and the two-stage pressure reducing regulating valve III are to perform the first stage decompression on the input high-pressure hydrogen gas.
  • the compressed hydrogen undergoes a second stage of pressure reduction, but the two-stage pressure reduction regulator valve III only needs to reduce pressure, while the two-stage pressure reduction flow regulator valve II also needs to regulate the flow of passing hydrogen in addition to pressure reduction.
  • the purpose of setting the secondary pressure reducing flow regulating valve II and the secondary pressure reducing regulating valve III in parallel in the second stage of pressure reduction is to regulate the outlet flow of the hydrogen supply combination valve while stabilizing the outlet pressure as much as possible, in which the outlet hydrogen flow rate It is only regulated by the two-stage pressure reducing flow regulating valve II, while the two-stage pressure reducing regulating valve III maintains a continuous and stable flow output, thus greatly reducing the fluctuation of the outlet pressure during the flow regulating process.
  • the specific structures of the combination valve body and the primary pressure reducing valve I, the secondary pressure reducing flow regulating valve II and the secondary pressure reducing regulating valve III are described in detail below.
  • the combination valve body connects three regulating valves by opening a series of channels and valve seats to realize the function of the entire valve.
  • the combination valve body is provided with a primary outlet channel 1, a connecting channel 2, a first channel 3, a second channel 4, a third channel 5, a secondary outlet channel 6, and a pressure regulating hydrogen storage channel. 7.
  • the fourth channel 8 the first valve seat 9, the second valve seat 10, the third valve seat 11 and the cylindrical seal 12.
  • the horizontal direction shown in Figure 1 is called the length direction of the combination valve body
  • the vertical direction shown in Figure 1 is called the height direction of the combination valve body
  • the direction perpendicular to the paper surface of Figure 1 is called the combination The width direction of the valve body.
  • the first valve seat 9 adopts a through-step hole design, and the primary outlet flow channel 1 runs through the middle and upper part of the first valve seat 9.
  • the primary outlet flow channel 1 is arranged along the length direction of the combination valve body and connected with the connecting flow.
  • Road 2 is orthogonal to each other.
  • the connecting flow channel 2 is arranged along the height direction of the combination valve body and communicates with the first channel 3 and the second channel 4 in the inclined direction.
  • the first channel 3 and the second channel 4 communicate with the upper portions of the second valve seat 10 and the third valve seat 11 respectively.
  • the second valve seat 10 and the third valve seat 11 are symmetrically arranged in the height direction of the combination valve body.
  • the second valve seat 11 and the third valve seat 11 are first-level stepped holes, and the second-level outlet flow channel 6 is T-shaped. And the secondary outlet flow channel 6 communicates with the second valve seat 10 and the third valve seat 11 at the same time.
  • the pressure-regulated hydrogen storage flow channel 7 is provided on one side of the secondary outlet flow channel 6 along the width direction.
  • the pressure regulating hydrogen storage flow channel 7 is connected to the upper part of the second valve seat 10 and the secondary outlet flow channel 6 through the third channel 5 and the fourth channel 8 respectively. Since the primary outlet flow channel 1 and the connecting flow channel 2 are drilled from the surface of the combination valve body to the inside, when the remaining components are installed, their open ends located on the surface of the combination valve body are evenly spaced. It needs to be closed by cylindrical seal 12.
  • the primary pressure reducing valve I, the secondary pressure reducing flow regulating valve II and the secondary pressure reducing regulating valve III are respectively installed through the first valve seat 9, the second valve seat 10 and the third valve seat 11 in the combination valve body.
  • the combination valve body is provided with a primary outlet channel 1, a connecting channel 2, a secondary outlet channel 6 and a pressure regulating hydrogen storage channel 7.
  • the primary outlet channel 1 is connected to the connecting channel 2, and the secondary outlet channel 6 serves as the final output channel of the hydrogen supply combination valve.
  • the flow channel and valve seat can be processed as follows: first, the first valve seat 9, the connecting flow channel 2, the primary outlet flow channel 1, and the pressure regulating hydrogen storage flow channel are processed. 7. Make the connecting flow channel 2 and the primary outlet flow channel 1 vertically connected; then process the second valve seat 10 and the third valve seat 11, both of which are coaxially arranged; then process the T-shaped secondary outlet flow. Channel 6, the second valve seat 10 and the third valve seat 11 are connected through the two ends of the secondary outlet channel 6; the first channel 3 is finally processed to make the connecting channel 2 and the second valve seat 10 connected through.
  • the second channel 4 is processed so that the connection flow channel 2 is connected to the third valve seat 11, the third channel 5 is processed so that the second valve seat 10 is connected to the pressure regulating hydrogen storage flow channel 7, and the fourth channel 8 is processed so that the secondary outlet flow Channel 6 is connected to the pressure regulating hydrogen storage flow channel 7.
  • the above processing flow is only one implementation method, and other processing methods can also be used to implement it.
  • the first-level pressure reducing valve I is used to connect the external hydrogen source and perform the first-level decompression of the input hydrogen, and input it into the first-level outlet flow channel 1. Its specific structure can be adopted in the existing technology. It can be realized with any pressure reducing valve structure, as long as it can realize the pressure reducing function of high-pressure hydrogen input from an external hydrogen source.
  • the components constituting the first-stage pressure reducing valve I mainly include an inlet flow channel 13, a first throttling base 14, a first actuator 15, and an inner flow channel 16 of the actuator. , the first sealing gasket 17, the first sealing piston 18, the holed disc 19, the first spring 20 and the second spring 21.
  • the first valve seat 9 penetrates the entire combination valve body, and is in the form of a through stepped hole on the combination valve body.
  • the first throttling base 14 and the first sealing piston 18 are respectively sealed and fixedly installed at the openings at both ends of the first valve seat 9. They form sealing pairs with the inner wall of the first valve seat 9 to prevent internal gas from escaping.
  • the first throttle base 14 , the first sealing piston 18 and the first valve seat 9 remain relatively fixed.
  • the center of the first valve seat 9 is provided with a through inlet flow channel 13.
  • the inlet end of the inlet flow channel 13 extends out of the outer wall of the combination valve and can be connected to an external hydrogen source, while the outlet end of the inlet flow channel 13 faces the combination valve. inside the body.
  • the first actuator 15 is installed in the first valve seat 9 and is located between the first throttle base 14 and the first sealing piston 18 .
  • the space between the first actuator 15 and the first sealing piston 18 communicates with the primary outlet flow channel 1 .
  • One end of the first actuator 15 is a first conical structure, and the other end is a cylindrical section connected to the first conical structure.
  • the cylindrical section of the first actuator 15 is installed on the first valve seat 9 below the primary outlet flow channel 1 , and can move up and down along the first valve seat 9 axis.
  • the first actuator 15 and the first throttling base 14 are the main throttling elements.
  • the first tapered structure of the first actuator 15 cooperates with the first throttling base 14 at the outlet end of the inlet flow channel 13 to form the first section. flow interval.
  • a first spring 20 in a compressed state is disposed between the first actuator 15 and the first sealing piston 18, and a second spring in a compressed state is disposed between the first actuator 15 and the first throttle base 14. 21.
  • the first spring 20 and the second spring 21 exert two pressures in opposite directions on the first actuator 15 respectively.
  • the first actuator 15 is also affected by the high-pressure inlet pressure and the low-pressure outlet pressure.
  • the high-pressure inlet pressure has a smaller area
  • the low-pressure outlet pressure has a smaller area. Larger area. Therefore, the entire first throttling section achieves a stable decompression effect under the action of four forces. Therefore, the first actuator 15 can be maintained in a relatively balanced position under the two opposite forces exerted by the first spring 20 and the second spring 21, and can also be reset after moving under the action of external force, thereby ensuring that the first actuator 15 can be maintained in a relatively balanced position.
  • a throttling interval can meet the target opening requirements.
  • the opening of the first throttling section changes with the distance between the first conical structure and the first throttling base 14. The smaller the distance, the smaller the corresponding flow area, and thus the smaller the opening. Inversely, the larger the distance, the larger the flow area, and thus the larger the opening.
  • the first spring 20 and the second spring 21 can be selected, and the spring force exerted by the two springs can be controlled to adjust the opening of the first throttling section, thereby adjusting the external high-pressure hydrogen gas to pass through the first throttling section. The amount of pressure afterwards.
  • the first actuator 15 is provided with an internal flow channel 16 connected to the top surface of the first actuator 15.
  • the flow channel 13 can communicate with the flow channel 16 in the actuator.
  • the inlet end of the inlet flow channel 13 is used to connect the external hydrogen source.
  • the input hydrogen passes through the inlet flow channel 13, the first throttling section, and the actuator inner flow channel 16, and then enters the first-level outlet flow channel 1 to complete the first stage. stress reliever.
  • first sealing washers 17 are provided at three different positions. Specifically, the first sealing piston 18 and the inner wall of the first valve seat 9 and the first throttling base 14 and the inner wall of the first valve seat 9, and the first throttling base 14 and the first actuator 15 are all sealed by a first sealing gasket 17.
  • first sealing gasket 17 can be adjusted according to actual conditions. If reliable sealing can be achieved through other sealing methods, the first sealing gasket 17 may not be provided.
  • the first throttling base 14 and the first sealing piston 18 are both provided with coaxial spring mounting holes at the position where the first spring 20 is installed, and the spring mounting holes of the first throttling base 14 are A perforated disc 19 is placed at the bottom and communicates with the internal flow channel 16 of the actuator.
  • One end of the first spring 20 is supported on the perforated disc 19 and the other end is supported in the spring mounting hole of the first sealing piston 18 . Therefore, by providing the perforated disk 19, a reliable installation point can be provided for the first spring 20 while ensuring that the inner flow channel 16 of the actuator can smoothly discharge air.
  • the secondary pressure reducing flow regulating valve II and the secondary pressure reducing regulating valve III are connected in parallel after the primary pressure reducing valve I, and are used to cooperate to realize the pressure and flow control of the outlet hydrogen.
  • the two-stage pressure reducing flow regulating valve II includes a second sealing piston 22, a second actuator 23, a third spring 25, a second throttling base 26 and a fourth Spring 27.
  • the second valve seat 10 is a stepped hole that does not penetrate the combination valve body. One end of the second valve seat 10 facing the outer wall of the combination valve is used as an open end.
  • the second sealing piston 22 is sealed and fixedly installed on the second valve seat 10 At the open end of the second valve seat 10 , the second actuator 23 and the second throttle base 26 are installed in the second valve seat 10 , and the second actuator 23 is located between the second throttle base 26 and the second sealing piston 22 .
  • the second sealing piston 22 is provided with a protruding blocking ring on the side facing the second actuator 23 to prevent the second actuator 23 from completely fitting the inner bottom surface of the second sealing piston 22 .
  • the second actuator 23 is composed of a circular plate connected to a second conical structure below.
  • the side wall of the second valve seat 10 has a stepped surface, and a second sealing gasket 24 is placed on the stepped surface. When the plate moves toward the second throttling base 26, it can be pressed against the second sealing gasket 24 to ensure that the first chamber and the second chamber are sealed and not connected.
  • the inner cavity of the second valve seat 10 is separated by the second sealing piston 22, the second actuator 23 and the second throttling base 26 to form independent first chambers, second chambers and Third chamber.
  • a third spring 25 in a compressed state is disposed between the second actuator 23 and the second throttle base 26
  • a fourth spring in a compressed state is disposed between the second throttle base 26 and the inner bottom surface of the second valve seat 10 27.
  • the center of the second throttling base 26 is provided with a secondary outlet flow channel for connecting the second chamber and the third chamber.
  • One end of the second actuator 23 is a second conical structure, and the second conical structure is in the secondary The inlet position of the outlet flow passage cooperates with the second throttling base 26 to form a second throttling section.
  • the opening of the second throttling section changes with the distance between the second conical structure and the second throttling base 26.
  • the smaller the distance, the corresponding flow area The smaller the gap, the smaller the opening, and the larger the distance, the larger the flow area, and the larger the opening.
  • the third spring 25 and the fourth spring 27 can be selected, and the spring force exerted by the two springs can be controlled to adjust the opening of the second throttling section, thereby adjusting the hydrogen gas after the first stage of decompression. The pressure after passing through the second throttling interval.
  • the two-stage pressure reducing regulating valve III includes a third sealing piston 28 , a fifth spring 29 , a third throttle base 30 and a sixth spring 31 .
  • the third valve seat 11 is a stepped hole, which does not penetrate the combination valve body.
  • the third sealing piston 28 is sealed and fixedly installed on the open end of the third valve seat 11
  • the third throttling base 30 is installed in the third valve seat 11
  • the inner cavity of the third valve seat 11 is between the third sealing piston 28 and the third valve seat 11 .
  • independent fourth chambers and fifth chambers are formed in sequence from the open end to the inner bottom surface.
  • the fourth chamber and the fifth chamber are not directly connected and can only be connected through the third throttling section.
  • a fifth spring 29 in a compressed state is disposed between the third sealing piston 28 and the third throttle base 30
  • a sixth spring in a compressed state is disposed between the third throttle base 30 and the inner bottom surface of the third valve seat 11 31.
  • a third-level outlet flow channel is provided in the center of the third throttling base 30 for connecting the fourth chamber and the fifth chamber.
  • the end of the third sealing piston 28 is a third conical structure, and the third conical structure cooperates with the third throttling base 30 at the entrance position of the third-stage outlet flow channel to form a third throttling section.
  • the opening of the third throttling section changes with the distance between the third conical structure and the third throttling base 30.
  • the smaller the distance, the corresponding flow area The smaller the gap, the smaller the opening, and the larger the distance, the larger the flow area, and the larger the opening.
  • the fifth spring 29 and the sixth spring 31 can be selected, and the spring force exerted by the two springs can be controlled to adjust the opening of the third throttling section, thereby adjusting the hydrogen gas after the first stage of decompression. The pressure after passing through the third throttling interval.
  • the secondary pressure reducing regulating valve III only needs to reduce pressure, while the secondary pressure reducing flow regulating valve II needs to reduce the pressure of the passing hydrogen gas flow. adjust. Therefore, the additional hydrogen flow adjustment function in the secondary pressure reducing flow regulating valve II compared to the secondary pressure reducing regulating valve III is achieved by cooperating with the pressure regulating hydrogen storage flow channel 7 .
  • the second chamber and the fourth chamber are connected to the connecting flow channel 2 through the first channel 3 and the second channel 4 respectively.
  • the connecting flow channel 2 is connected after the first-level outlet flow channel 1 and can store the first-level
  • the decompressed hydrogen gas and the hydrogen gas stored in the connecting flow channel 2 can enter the second chamber and the fourth chamber through the first channel 3 and the second channel 4 respectively, and pass through the second throttling section and the third throttling section.
  • the third chamber and the fifth chamber are respectively connected to the secondary outlet flow channel 6 , and the hydrogen gas decompressed in the second stage is finally output through the secondary outlet flow channel 6 .
  • first chamber and the secondary outlet flow channel 6 are connected to the pressure-regulating hydrogen storage flow channel 7 through the third channel 5 and the fourth channel 8 respectively, so the hydrogen in the pressure-regulated hydrogen storage flow channel 7 can pass through
  • the third channel 5 is pressed into the first chamber of the two-stage pressure reducing flow regulating valve II.
  • the second actuator 23 will be pushed downward to reduce the opening of the second throttling section, thereby reducing the amount of energy passed through the secondary reduction.
  • Pressure flow control valve II output hydrogen flow.
  • valve III itself continues to output a stable hydrogen flow and pressure, so it can regulate the secondary pressure reducing flow.
  • the pressure fluctuation caused by valve II acts as a buffer to keep the outlet pressure of the secondary outlet channel 6 as stable as possible.
  • the hydrogen output flow rate in the present invention mainly depends on the pressure exerted by the pressure-regulating hydrogen storage flow channel 7 on the first chamber.
  • the first connection port of the pressure-regulating hydrogen storage flow channel 7 and the third channel 5 and the second connection port of the pressure-regulating hydrogen storage flow channel 7 and the fourth channel 8 are kept apart, so that the first connection port and The pressure regulating hydrogen storage flow channel 7 between the second connection ports can be used as a pressure regulating section.
  • the pressure-regulating hydrogen storage flow channel 7 is provided with a controllable sliding piston 32 that forms a piston pair with the inner wall of the flow channel.
  • the so-called controllable sliding piston 32 refers to a piston that can controllably slide in the pressure-regulating hydrogen storage flow channel 7 .
  • controllable sliding piston 32 can be equipped with a control rod.
  • the control rod extends out of the combination valve body and maintains a dynamic seal in contact with the combination valve body. Therefore, the controllable sliding piston 32 can be driven by the control rod. of sliding.
  • the sliding stroke of the controllable sliding piston 32 in the pressure-regulating hydrogen storage flow channel 7 needs to cover the aforementioned pressure adjustment section. Therefore, the controllable sliding piston 32 is controlled by changing the pressure in the first chamber during the sliding process in the pressure adjustment section.
  • the opening of the second throttling interval changes the hydrogen flow rate output by the secondary outlet flow channel 6 .
  • the controllable sliding piston 32 has three important positions in the entire stroke, where the A position is the initial position at the bottom of the pressure regulating hydrogen storage flow channel 7, and the B position is the controllable sliding piston. 32 is about to block the second connection port, and position C is the position where the controllable sliding piston 32 is about to block the first connection port. Under normal conditions, the controllable sliding piston 32 can be in position A. At this time, the entire valve outputs hydrogen at a stable pressure according to the maximum flow rate; when the hydrogen flow rate at the outlet of the valve needs to be adjusted, the controllable sliding piston 32 can be driven to move upward.
  • the controllable sliding piston 32 is in the pressure regulating section.
  • the second throttle interval should be completely closed. This can be achieved by adjusting the volume of the aforementioned pressure regulating section.
  • connection port between the channel 5 and the first chamber side wall is preferably set within the height range of the blocking ring on the second sealing piston 22, thereby ensuring that the connection port between the third channel 5 and the first chamber side wall will not be blocked.
  • the second actuator 23 covers.
  • the above-mentioned hydrogen supply combination valve with flow adjustment and pressure stabilizing functions of the present invention only provides a combination valve that can achieve two-stage pressure reduction, has stable output pressure and adjustable output flow. , but its specific pressure reduction range and flow adjustment can be adjusted according to actual needs.
  • the corresponding output parameter control can be achieved by optimizing the structural parameters of the first throttling interval, the second throttling interval and the third throttling interval.
  • One application scenario of the hydrogen supply combination valve of the present invention is to supply hydrogen to a vehicle-mounted hydrogen fuel cell.
  • the working pressure of vehicle-mounted hydrogen fuel cells is generally 0.16MPa. Therefore, the combined hydrogen bottle mouth valve of vehicle-mounted hydrogen fuel cells must achieve a stable and large pressure drop of hydrogen from 70MPa to 0.16MPa.
  • the structural parameters of the first throttling interval, the second throttling interval and the third throttling interval can be optimized so that the hydrogen pressure range of the external hydrogen source is 10-70MPa, and the hydrogen undergoes one-stage decompression The pressure of the hydrogen gas after valve I is reduced to 2 ⁇ 3MPa.
  • the pressure of the hydrogen gas is reduced to the working pressure of the vehicle-mounted hydrogen fuel cell.
  • the pressure of the hydrogen gas is reduced.
  • the working pressure of the vehicle hydrogen fuel cell is 0.16MPa.
  • the input high-pressure hydrogen pressure range is 10 ⁇ 70MPa.
  • the first-stage pressure reducing valve I is controlled to have a smaller opening and a larger flow resistance coefficient than the second-stage pressure reducing flow regulating valve II and the second-stage pressure reducing regulating valve III. , so the pressure of the hydrogen gas is reduced to 2 ⁇ 3MPa after passing through the first-stage pressure reducing valve.
  • the throttling area of the two-stage pressure reducing regulating valve III is relatively large, so it can reduce the pressure from 2 to 3MPa to 0.16MPa, and the flow rate of the two-stage pressure reducing regulating valve III can be maintained unchanged.
  • the throttling area of the secondary pressure reducing flow regulating valve II is relatively large, and can also achieve pressure reduction from 2 to 3MPa to 0.16MPa, and by adjusting the pressure of the pressure regulating hydrogen storage channel 7, the secondary pressure reducing flow regulation can be adjusted By adjusting the opening of valve II, the flow rate through this valve can be adjusted. By adjusting the piston, the secondary pressure reducing flow regulating valve II can be fully closed to achieve the minimum flow rate for hydrogen transportation.

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Abstract

一种具有流量调节与稳压功能的供氢组合阀，属于阀门领域。该供氢组合阀中包括一级减压阀(I)、二级减压流量调节阀(II)和二级减压调节阀(III)。其中一级减压阀(I)实现主要的节流降压作用，将高压氢气进行第一级降压；二级减压流量调节阀(II)可进一步对第一级降压后的氢气进行第二级降压，并可实现调节流量；二级减压调节阀(III)可进一步对第一级降压后的氢气进行第二级降压，并通过持续输出稳定流量和压力的氢气，来缓冲二级减压流量调节阀(II)流量调节过程中对最终出口氢气压力造成的扰动，实现调节流量的同时保证出口压力稳定。该组合阀能在实现双级降压稳压与氢气组合阀集成化的前提下，调节供氢组合阀的输出流量，可用于实现车载供氢的功率变化。

Description

一种具有流量调节与稳压功能的供氢组合阀 技术领域
本发明属于阀门领域，特别涉及一种具有流量调节与稳压功能的供氢组合阀。
背景技术
高压储氢气瓶用来储存温度在临界温度以上的高压气态氢气，理想的供氢组合阀需要实现的功能包括两方面：第一方面是将氢气压力降低额定范围；第二方面是精确控制氢气流量，能实现稳定降压，根据需要控制流量大小。目前，为确保进入燃料电池的氢气压力在正常范围内，防止加氢过程中出现过压的情况，可采用双减压阀进行减压，输出压力较为稳定，但在维持压力不变的情况下调节流量是难题。阀门间的连接越多，管路越复杂，存在越多的安全隐患，因此，供氢组合阀的集成式组合研究具有重要意义。供氢组合阀通常包括减压阀、电磁阀、温度与压力传感器组成，其中减压阀实现流量与压力的稳定，电磁阀通常安装于减压阀之后，实现整个供氢回路的开关与启闭。
发明内容
本发明的目的在于解决现有技术中降压阀无法同时满足稳定输出压力和调节氢气流量两种技术需求的问题，由此提供了一种具有流量调节与稳压功能的供氢组合阀。
为了实现上述目的，本发明采用的技术方案是：
一种具有流量调节与稳压功能的供氢组合阀，其包括组合阀阀体以及一级减压阀、二级减压流量调节阀和二级减压调节阀，且一级减压阀、二级减压流量调节阀和二级减压调节阀分别通过第一阀座、第二阀座和第三阀座安装于组合阀体内；所述组合阀阀体内设有一级出口流道、连接流道、二级出口流道和调压储氢流道；所述一级出口流道与连接流道连通，所述二级出口流道作为供氢组合阀的最终输出流道；
所述一级减压阀用于连接外部氢气源并对输入氢气进行第一级减压，并输入一级出口流道中；
所述二级减压流量调节阀包括第二密封活塞、第二执行器、第三弹簧、第二节流底座和第四弹簧；所述第二阀座不贯通所述组合阀阀体，所述第二密封活塞密封式固定安装于第二阀座的开口端，所述第二执行器和第二节流底座安装于第二阀座内，且第二执行器位于第二节流底座和第二密封活塞之间，所述第二密封活塞朝向第二执行器一侧设有凸出的挡环；所述第二阀座的内腔在第二密封活塞、第二执行器和第二节流底座的分隔下由开口端向内底面 依次形成独立的第一腔室、第二腔室和第三腔室；所述第二执行器与第二节流底座之间设有处于压缩状态的第三弹簧，所述第二节流底座与第二阀座内底面之间设有处于压缩状态的第四弹簧；所述第二节流底座中心开设有用于连通第二腔室和第三腔室的二级出口流道，所述第二执行器的一端为第二锥形结构，且所述第二锥形结构在二级出口流道的入口位置与第二节流底座配合构成第二节流区间；
所述二级减压调节阀包括第三密封活塞、第五弹簧、第三节流底座和第六弹簧；所述第三阀座不贯通所述组合阀阀体，所述第三密封活塞密封式固定安装于第三阀座的开口端，所述第三节流底座安装于第三阀座内，且第三阀座的内腔在第三密封活塞和第三节流底座的分隔下由开口端向内底面依次形成独立的第四腔室和第五腔室；所述第三密封活塞和第三节流底座之间设有处于压缩状态的第五弹簧，所述第三节流底座与第三阀座内底面之间设有处于压缩状态的第六弹簧；所述第三节流底座中心开设有用于连通第四腔室和第五腔室的三级出口流道，所述第三密封活塞的端部为第三锥形结构，且所述第三锥形结构在三级出口流道的入口位置与第三节流底座配合构成第三节流区间；
所述第二腔室和第四腔室分别通过第一通道和第二通道连通所述连接流道；所述第三腔室和第五腔室分别连通二级出口流道；所述第一腔室和所述二级出口流道分别通过第三通道和第四通道连通所述调压储氢流道；且所述调压储氢流道与第三通道的第一连接口和所述调压储氢流道与第四通道的第二连接口保持间隔，第一连接口和第二连接口之间的调压储氢流道作为压力调节段；所述调压储氢流道中设有与流道内壁构成活塞副的可控滑动活塞，且可控滑动活塞在调压储氢流道内的滑动行程覆盖所述压力调节段；所述可控滑动活塞在所述压力调节段内滑动过程中通过改变所述第一腔室内的压力来控制所述第二节流区间的开度，从而改变所述二级出口流道输出的氢气流量。
作为优选，所述一级减压阀包括进口流道、第一节流底座、第一执行器、执行器内流道、第一密封活塞、第一弹簧和第二弹簧；所述第一阀座贯通整个组合阀阀体，所述第一节流底座和第一密封活塞分别密封式固定安装于所述第一阀座的两端开口处，所述第一阀座中设有贯通的进口流道；所述第一执行器安装于所述第一阀座中且位于第一节流底座和第一密封活塞之间，第一执行器一端为第一锥形结构，且所述第一锥形结构在进口流道的出口端与第一节流底座配合构成第一节流区间；所述第一执行器与第一密封活塞之间设有一条处于压缩状态的第一弹簧，所述第一执行器与第一节流底座之间设有一条处于压缩状态的第二弹簧，所述第一弹簧和所述第二弹簧分别对第一执行器施加两个相反方向的压力；所述第一执行器中开设有连通至第一执行器顶面的执行器内流道，所述进口流道的入口端用于连接外部氢气源，输入的氢气依次通过所述进口流道、所述第一节流区间、所述执行器内流道后进入所述一级 出口流道中。
作为优选，所述第一节流底座和第一密封活塞均在安装第一弹簧的位置开设同轴的弹簧安装孔，且第一节流底座的弹簧安装孔底部放置有一个连通执行器内流道的带孔圆盘，第一弹簧的一端支顶于带孔圆盘上，另一端支顶于第一密封活塞的弹簧安装孔中。
作为优选，所述第一密封活塞与第一阀座内壁、第一节流底座与第一阀座内壁、第一节流底座与第一执行器之间均通过第一密封垫圈构成密封连接。
作为优选，所述一级出口流道和连接流道均从所述组合阀阀体表面向内部进行钻孔加工而成，且其位于所述组合阀阀体表面的开口端均通过圆柱密封进行封闭。
作为优选，所述可控滑动活塞上带有控制杆，控制杆伸出组合阀阀体且与组合阀阀体接触位置保持动密封。
作为优选，所述第三通道与所述第一腔室侧壁的连接口位置处于所述挡环的高度范围内。
作为优选，所述第二执行器包括由圆形板下方连接第二锥形结构组成，所述第二阀座侧壁具有一个阶梯面，所述阶梯面上放置有第二密封垫圈，所述圆形板向第二节流底座方向移动时能压合在第二密封垫圈上，保证第一腔室和第二腔室之间密闭不连通。
作为优选，所述可控滑动活塞在所述压力调节段内滑动过程中，能完全封闭所述第二节流区间。
作为优选，所述外部氢气源的氢气压力范围为10～70MPa，氢气经过一级减压阀后氢气的压力减压至2～3MPa，经二级减压流量调节阀后氢气的压力减压至车载氢燃料电池的工作压力，经二级减压调节阀后氢气的压力减压至车载氢燃料电池的工作压力。
相对于现有技术而言，本发明的有益效果如下：
(1)本发明通过设置两级减压流程，且第二级减压中并行设置二级减压流量调节阀和二级减压调节阀来实现供氢组合阀出口流量调节的同时尽可能稳定出口压力。出口氢气流量仅通过二级减压流量调节阀进行调节，而二级减压调节阀保持持续稳定的流量输出缓冲二级减压流量调节阀流量调节造成的压力波动，由此大大降低流量调节过程中整个阀门最终出口压力的波动，既实现将氢气压力降低额定范围，同时又能够精确控制氢气流量。
(2)本发明可应用于车载供氢等领域，能在实现双级降压稳压与氢气组合阀集成化的前提下，调节供氢组合阀的输出流量，实现车载供氢的功率变化。
附图说明
图1为一种具有流量调节与稳压功能的供氢组合阀的结构示意图。
图2为组合阀阀体内的流道和阀座结构示意图。
图3为一级减压阀结构示意图。
图4为二级减压流量调节阀结构示意图。
图5为二级减压调节阀结构示意图。
图6为可控滑动活塞在调压储氢流道内的三个关键控制位点示意图。
图中附图标记如下：一级出口流道1、连接流道2、第一通道3、第二通道4、第三通道5、二级出口流道6、调压储氢流道7、第四通道8、第一阀座9、第二阀座10、第三阀座11、圆柱密封12、进口流道13、第一节流底座14、第一执行器15、执行器内流道16、第一密封垫圈17、第一密封活塞18、带孔圆盘19、第一弹簧20、第二弹簧21、第二密封活塞22、第二执行器23、第二密封垫圈24、第三弹簧25、第二节流底座26、第四弹簧27、第三密封活塞28、第五弹簧29、第三节流底座30、第六弹簧31、可控滑动活塞32。
具体实施方式
为使本发明的上述目的、特征和优点能够更加明显易懂，下面结合附图对本发明的具体实施方式做详细的说明。在下面的描述中阐述了很多具体细节以便于充分理解本发明。但是本发明能够以很多不同于在此描述的其它方式来实施，本领域技术人员可以在不违背本发明内涵的情况下做类似改进，因此本发明不受下面公开的具体实施例的限制。本发明各个实施例中的技术特征在没有相互冲突的前提下，均可进行相应组合。
在本发明的描述中，需要理解的是，当一个元件被认为是“连接”另一个元件，可以是直接连接到另一个元件或者是间接连接即存在中间元件。相反，当元件为称作“直接”与另一元件连接时，不存在中间元件。
在本发明的描述中，需要理解的是，术语“第一”、“第二”仅用于区分描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。
如图1所示，在本发明的一个较佳实施例中，提供了一种具有流量调节与稳压功能的供氢组合阀，其主要部件包括组合阀阀体以及一级减压阀I、二级减压流量调节阀II和二级减压调节阀III。其中，一级减压阀I的作用是对输入的高压氢气进行第一级减压，而二级减压流量调节阀II和二级减压调节阀III的作用均是对经过第一级减压后的氢气进行第二级减压，但是二级减压调节阀III仅需要进行减压，而二级减压流量调节阀II除了减压作用外还需要对通过的氢气流量进行调节。本发明在第二级减压中并行设置二级减压流量调节阀II和二级减压调节阀III的目的是实现供氢组合阀出口流量调节的同时尽可能稳定出口压力，其中出口氢气流量仅通过二级减压流量调节阀II进行调节，而二级减压调节阀III保持持续稳定的流量输出，由此大大降低流量调节过程中出口压力的波动。下面对组合阀阀体以及一级减压阀I、二级减压流量调节阀II和二级减压调节阀III的具体结构进行详细展开描述。
如图2所示，组合阀阀体中通过开设一系列的通道和阀座来连接三个调节阀，从而实现整个阀门的功能。具体而言，组合阀阀体中设有一级出口流道1、连接流道2、第一通道3、第二通道4、第三通道5、二级出口流道6、调压储氢流道7、第四通道8、第一阀座9、第二阀座10、第三阀座11和圆柱密封12。为了便于描述，下面将图1所示的水平方向称为组合阀阀体的长度方向，图1所示的垂直方向称为组合阀阀体的高度方向，垂直图1的纸面方向称为组合阀阀体的宽度方向。由此，第一阀座9采用贯通阶梯孔设计，而一级出口流道1贯通第一阀座9的中上部，一级出口流道1沿组合阀阀体的长度方向设置并与连接流道2正交相通。连接流道2沿组合阀阀体的高度方向设置，并与倾斜方向的第一通道3、第二通道4相通。第一通道3、第二通道4分别与第二阀座10、第三阀座11的上部相相通。第二阀座10、第三阀座11在组合阀阀体的高度方向上对称设置，第二阀座11和第三阀座11为一级阶梯孔，二级出口流道6为T型，并且二级出口流道6同时连通第二阀座10和第三阀座11。调压储氢流道7设置在二级出口流道6沿宽度方向的一侧。调压储氢流道7分别通过第三通道5、第四通道8与第二阀座10上部、二级出口流道6相连。由于一级出口流道1和连接流道2均是从组合阀阀体表面向内部进行钻孔加工而成的，因此当其余的组件安装完毕后，其位于组合阀阀体表面的开口端均需要通过圆柱密封12进行封闭。
在组合阀阀体中，一级减压阀I、二级减压流量调节阀II和二级减压调节阀III分别通过第一阀座9、第二阀座10和第三阀座11安装于组合阀体内。而组合阀阀体内设有一级出口流道1、连接流道2、二级出口流道6和调压储氢流道7。一级出口流道1与连接流道2连通，二级出口流道6作为供氢组合阀的最终输出流道。
本发明的上述供氢组合阀中，其中的流道和阀座可按下述方法加工：首先加工第一阀座9、连接流道2、一级出口流道1、调压储氢流道7，使连接流道2与一级出口流道1垂直贯通相连；然后加工第二阀座10和第三阀座11，两者加工采用同轴心布置；再加工T型的二级出口流道6，由二级出口流道6的两个端部将第二阀座10和第三阀座11贯通连接；最后加工第一通道3使得连接流道2与第二阀座10贯通相连，加工第二通道4使得连接流道2与第三阀座11贯通相连，加工第三通道5使第二阀座10与调压储氢流道7相连，加工第四通道8使得二级出口流道6与调压储氢流道7相连。当然，上述加工流程仅仅为一种实现方式，也可以采用其他的加工方式来实现。
在该供氢组合阀中，一级减压阀I用于连接外部氢气源并对输入氢气进行第一级减压，并输入一级出口流道1中，其具体结构可采用现有技术中任意的减压阀结构来实现，只要能够实现对外部氢气源输入的高压氢气的减压功能即可。
在本发明的一实施例中，如图3所示，构成一级减压阀I的组件主要包括进口流道13、 第一节流底座14、第一执行器15、执行器内流道16、第一密封垫圈17、第一密封活塞18、带孔圆盘19、第一弹簧20和第二弹簧21。其中，第一阀座9贯通整个组合阀阀体，且在组合阀阀体上为贯通的阶梯孔形式。第一节流底座14和第一密封活塞18分别密封式固定安装于第一阀座9的两端开口处，两者与第一阀座9的内壁均构成密封副，防止内部气体外溢。第一节流底座14和第一密封活塞18与第一阀座9之间保持相对固定状态。第一阀座9中心位置设有贯通的进口流道13，进口流道13的入口端伸出组合阀阀体外壁，能够连接外部氢气源，而进口流道13的出口端则朝向组合阀阀体内部。第一执行器15安装于第一阀座9中且位于第一节流底座14和第一密封活塞18之间。第一执行器15与第一密封活塞18之间的空间连通一级出口流道1。第一执行器15一端为第一锥形结构，另一端为与第一锥形结构相连的圆柱段，第一执行器15的圆柱段安装于一级出口流道1下方的第一阀座9中，且能够沿第一阀座9轴向上下移动。第一执行器15和第一节流底座14是主要的节流元件，第一执行器15的第一锥形结构在进口流道13的出口端与第一节流底座14配合构成第一节流区间。第一执行器15与第一密封活塞18之间设有一条处于压缩状态的第一弹簧20，而第一执行器15与第一节流底座14之间设有一条处于压缩状态的第二弹簧21，第一弹簧20和第二弹簧21分别对第一执行器15施加两个相反方向的压力。当然，在工作过程中，第一执行器15除了受到两弹簧力之外，第一执行器15还受到高压进口压力和低压出口压力的影响，高压进口压力作用面积较小，低压出口压力的作用面积较大。因此，第一节流区间整体在4个力的作用下，实现稳定的减压效果。由此第一执行器15在第一弹簧20和第二弹簧21所施加的两个相反作用力下，能够维持在一个相对平衡的位置，且在外力作用下移动后也可以复位，从而保证第一节流区间能够满足目标开度要求。第一节流区间的开度是随着第一锥形结构与第一节流底座14之间的间距来改变的，间距越小对应的过流面积也越小，进而开度也越小，反之间距越大对应的过流面积也越大，进而开度也越大。本发明中可通过对第一弹簧20和第二弹簧21进行选型，通过控制两者所施加的弹簧力来调节第一节流区间的开度，进而调节外部高压氢气经过第一节流区间之后的压力大小。第一执行器15中开设有连通至第一执行器15顶面的执行器内流道16，第一锥形结构底部外侧壁与第一阀座9侧壁之间存在间隙空间，从而使进口流道13能够连通执行器内流道16。进口流道13的入口端用于连接外部氢气源，输入的氢气依次通过进口流道13、第一节流区间、执行器内流道16后进入一级出口流道1中，完成第一级减压。
另外，为了保证一级减压阀I的密封性能，在三个不同位置都设置了第一密封垫圈17，具体而言，第一密封活塞18与第一阀座9内壁、第一节流底座14与第一阀座9内壁、第一节流底座14与第一执行器15之间均通过第一密封垫圈17构成密封连接。当然，第一密封垫 圈17的具体设置位置可根据实际进行调整，若能够通过其他的密封方式实现可靠密封，亦可不设置第一密封垫圈17。
另外，为了便于实现可靠地安装，上述第一节流底座14和第一密封活塞18均在安装第一弹簧20的位置开设同轴的弹簧安装孔，且第一节流底座14的弹簧安装孔底部放置有一个连通执行器内流道16的带孔圆盘19，第一弹簧20的一端支顶于带孔圆盘19上，另一端支顶于第一密封活塞18的弹簧安装孔中。由此，通过设置带孔圆盘19，在保证执行器内流道16能够顺利出气的情况下，能够为第一弹簧20提供可靠的安装位点。
本发明中，二级减压流量调节阀II和二级减压调节阀III并接在一级减压阀I之后，用于配合实现出口氢气的压力和流量控制。
如图4所示，在本发明的一实施例中，二级减压流量调节阀II包括第二密封活塞22、第二执行器23、第三弹簧25、第二节流底座26和第四弹簧27。第二阀座10为一个阶梯孔，其不贯通组合阀阀体，第二阀座10朝向组合阀阀体外壁的一端作为开口端，第二密封活塞22密封式固定安装于第二阀座10的开口端，第二执行器23和第二节流底座26安装于第二阀座10内，且第二执行器23位于第二节流底座26和第二密封活塞22之间。第二密封活塞22朝向第二执行器23一侧设有凸出的挡环，防止第二执行器23完全贴合第二密封活塞22的内底面。在本实施例中，第二执行器23包括由圆形板下方连接第二锥形结构组成，第二阀座10侧壁具有一个阶梯面，阶梯面上放置有第二密封垫圈24，圆形板向第二节流底座26方向移动时能压合在第二密封垫圈24上，保证第一腔室和第二腔室之间密闭不连通。第二阀座10的内腔在第二密封活塞22、第二执行器23和第二节流底座26的分隔下由开口端向内底面依次形成独立的第一腔室、第二腔室和第三腔室。第一腔室和第二腔室之间保持不连通状态，第二腔室和第三腔室之间不直接连通，需要通过第二节流区间连通。第二执行器23与第二节流底座26之间设有处于压缩状态的第三弹簧25，第二节流底座26与第二阀座10内底面之间设有处于压缩状态的第四弹簧27。第二节流底座26中心开设有用于连通第二腔室和第三腔室的二级出口流道，第二执行器23的一端为第二锥形结构，且第二锥形结构在二级出口流道的入口位置与第二节流底座26配合构成第二节流区间。同样的，与第一节流区间类似，第二节流区间的开度是随着第二锥形结构与第二节流底座26之间的间距来改变的，间距越小对应的过流面积也越小，进而开度也越小，反之间距越大对应的过流面积也越大，进而开度也越大。本发明中可通过对第三弹簧25和第四弹簧27进行选型，通过控制两者所施加的弹簧力来调节第二节流区间的开度，进而调节经过第一级减压后的氢气经过第二节流区间之后的压力大小。
如图5所示，二级减压调节阀III包括第三密封活塞28、第五弹簧29、第三节流底座30 和第六弹簧31。其中，第三阀座11为一个阶梯孔，其不贯通组合阀阀体。第三密封活塞28密封式固定安装于第三阀座11的开口端，第三节流底座30安装于第三阀座11内，且第三阀座11的内腔在第三密封活塞28和第三节流底座30的分隔下由开口端向内底面依次形成独立的第四腔室和第五腔室。第四腔室和第五腔室之间不直接连通，仅能通过第三节流区间连通。第三密封活塞28和第三节流底座30之间设有处于压缩状态的第五弹簧29，第三节流底座30与第三阀座11内底面之间设有处于压缩状态的第六弹簧31。第三节流底座30中心开设有用于连通第四腔室和第五腔室的三级出口流道。第三密封活塞28的端部为第三锥形结构，且第三锥形结构在三级出口流道的入口位置与第三节流底座30配合构成第三节流区间。同样的，与第二节流区间类似，第三节流区间的开度是随着第三锥形结构与第三节流底座30之间的间距来改变的，间距越小对应的过流面积也越小，进而开度也越小，反之间距越大对应的过流面积也越大，进而开度也越大。本发明中可通过对第五弹簧29和第六弹簧31进行选型，通过控制两者所施加的弹簧力来调节第三节流区间的开度，进而调节经过第一级减压后的氢气经过第三节流区间之后的压力大小。
在本发明中，按照三个减压阀的功能设计，二级减压调节阀III仅需要进行减压，而二级减压流量调节阀II除了减压作用外还需要对通过的氢气流量进行调节。因此，二级减压流量调节阀II中相对于二级减压调节阀III额外增加的氢气流量调节功能是通过配合调压储氢流道7来实现的。具体而言，第二腔室和第四腔室分别通过第一通道3和第二通道4连通连接流道2，连接流道2连接在一级出口流道1之后，能够存储经过第一级减压后的氢气，而连接流道2中存储的氢气可分别通过第一通道3和第二通道4进入第二腔室和第四腔室，经过第二节流区间和第三节流区间分别继续第二级降压至目标出口压力。第三腔室和第五腔室分别连通二级出口流道6，经过第二级降压后的氢气最终通过二级出口流道6向外输出。特别需要注意的是，第一腔室和二级出口流道6分别通过第三通道5和第四通道8连通调压储氢流道7，因此调压储氢流道7中的氢气可以通过第三通道5压入二级减压流量调节阀II的第一腔室中。当第一腔室中的压力增大时，由于第一腔室是密闭的，因此会推动第二执行器23向下移动，减小第二节流区间的开度，从而减少经过二级减压流量调节阀II输出的氢气流量。虽然该流量调节过程中会造成最终二级出口流道6出口压力的波动，但是由于二级减压调节阀III自身是持续输出稳定的氢气流量和压力的，因此能够对二级减压流量调节阀II造成的压力波动起到缓冲作用，尽可能保持二级出口流道6出口压力的稳定。
因此，本发明中的氢气输出流量主要是依赖于调压储氢流道7对第一腔室施加的压力来调节的。为了保证调节效果，调压储氢流道7与第三通道5的第一连接口和调压储氢流道7与第四通道8的第二连接口保持间隔，由此第一连接口和第二连接口之间的调压储氢流道7 可以作为压力调节段。调压储氢流道7中设有与流道内壁构成活塞副的可控滑动活塞32，所谓可控滑动活塞32是指能够可控地在调压储氢流道7内滑动的活塞。本实施例中，可控滑动活塞32上可带有控制杆，控制杆伸出组合阀阀体且与组合阀阀体接触位置保持动密封，由此通过控制杆即可驱动可控滑动活塞32的滑动。可控滑动活塞32在调压储氢流道7内的滑动行程需要覆盖前述的压力调节段，由此可控滑动活塞32在压力调节段内滑动过程中通过改变第一腔室内的压力来控制第二节流区间的开度，从而改变二级出口流道6输出的氢气流量。如图6所示，在实际应用时，可控滑动活塞32的整个行程中具有三个重要位置，其中A位置为位于调压储氢流道7底部的初始位置，B位置为可控滑动活塞32即将封堵第二连接口的位置，C位置为可控滑动活塞32即将封堵第一连接口的位置。常规状态下可控滑动活塞32可处于A位置，此时整个阀门按照最大流量对外输出稳定压力的氢气；当需要对阀门的出口氢气流量进行调节时，可以驱动可控滑动活塞32向上移动，当可控滑动活塞32从A位置滑动到B位置期间，由于第四通道8的存在调压储氢流道7内的压力并不会改变，但是当可控滑动活塞32从B位置滑动到C位置期间，调压储氢流道7内的压力随之上升，进而同步促使第一腔室内的压力上升，推动第二执行器23向下移动，减小第二节流区间的开度，从而减少经过二级减压流量调节阀II输出的氢气流量。当可控滑动活塞32处于C位置时，二级减压流量调节阀II输出的氢气流量最小。因此，作为一种优选方式，假如需要完全关闭二级减压流量调节阀II，即使得通过二级减压流量调节阀II输出的氢气流量为0，则可控滑动活塞32在压力调节段内滑动过程中，应当能完全封闭第二节流区间。这可以通过调整前述的压力调节段的体积来实现。
由于在二级减压流量调节阀II的流量调节过程中，需要通过将调压储氢流道7内的气体压入上述第一腔室内来实现对第二执行器23的驱动，因此第三通道5与第一腔室侧壁的连接口位置优选设置于前述第二密封活塞22上的挡环的高度范围内，从而保证第三通道5与第一腔室侧壁的连接口不会被第二执行器23覆盖。
另外，需要说明的是，本发明的上述具有流量调节与稳压功能的供氢组合阀中，其仅仅提供了一种能够实现两级降压、具有稳定输出压力且输出流量可调的组合阀门，但是其具体的降压范围和流量调节可以根据实际需要调节。对于不同的降压范围和流量调节等输出参数，可以通过优化第一节流区间、第二节流区间和第三节流区间的结构参数来实现相应的输出参数控制。
本发明的供氢组合阀的一种应用场景是对车载氢燃料电池进行供氢。车载氢燃料电池的工作压力一般在0.16MPa，因此对于车载氢燃料电池的组合式氢气瓶口阀要实现氢气从70MPa到0.16MPa的稳定大压降。在该应用场景中，可通过对第一节流区间、第二节流区间 和第三节流区间的结构参数优化，使得外部氢气源的氢气压力范围为10～70MPa，氢气经过一级减压阀I后氢气的压力减压至2～3MPa，经二级减压流量调节阀II后氢气的压力减压至车载氢燃料电池的工作压力，经二级减压调节阀III后氢气的压力减压至车载氢燃料电池的工作压力0.16MPa。具体的工作流程如下：
S1.输入的高压氢气压力范围为10～70MPa，控制一级减压阀I相较于二级减压流量调节阀II和二级减压调节阀III的开度更小，流阻系数更大，因此氢气经过一级减压阀后氢气的压力减压至2～3MPa。
S2.二级减压调节阀III节流区域相对较大，因此可实现由2～3MPa减压至0.16MPa，并且二级减压调节阀III的流量可维持不变。
S3.二级减压流量调节阀II节流区域相对较大，同样可实现2～3MPa减压至0.16MPa，并且通过调节调压储氢流道7的压力可实现调节二级减压流量调节阀II的开度，从而实现调节通过此阀门的流量大小，通过活塞调节可将二级减压流量调节阀II全关，达到氢气输送的最小流量。
当然，上述参数范围可根据实际的工况需要进行调节，此处仅仅为一种优选实现方式。
应当明确，所描述的实施例仅是本发明的一部分实施例，而不是全部实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，均属于本发明保护的范围。

Claims (10)

  1. 一种具有流量调节与稳压功能的供氢组合阀，其特征在于，包括组合阀阀体以及一级减压阀(I)、二级减压流量调节阀(II)和二级减压调节阀(III)，且一级减压阀(I)、二级减压流量调节阀(II)和二级减压调节阀(III)分别通过第一阀座(9)、第二阀座(10)和第三阀座(11)安装于组合阀体内；所述组合阀阀体内设有一级出口流道(1)、连接流道(2)、二级出口流道(6)和调压储氢流道(7)；所述一级出口流道(1)与连接流道(2)连通，所述二级出口流道(6)作为供氢组合阀的最终输出流道；
    所述一级减压阀(I)用于连接外部氢气源并对输入氢气进行第一级减压，并输入一级出口流道(1)中；
    所述二级减压流量调节阀(II)包括第二密封活塞(22)、第二执行器(23)、第三弹簧(25)、第二节流底座(26)和第四弹簧(27)；所述第二阀座(10)不贯通所述组合阀阀体，所述第二密封活塞(22)密封式固定安装于第二阀座(10)的开口端，所述第二执行器(23)和第二节流底座(26)安装于第二阀座(10)内，且第二执行器(23)位于第二节流底座(26)和第二密封活塞(22)之间，所述第二密封活塞(22)朝向第二执行器(23)一侧设有凸出的挡环；所述第二阀座(10)的内腔在第二密封活塞(22)、第二执行器(23)和第二节流底座(26)的分隔下由开口端向内底面依次形成独立的第一腔室、第二腔室和第三腔室；所述第二执行器(23)与第二节流底座(26)之间设有处于压缩状态的第三弹簧(25)，所述第二节流底座(26)与第二阀座(10)内底面之间设有处于压缩状态的第四弹簧(27)；所述第二节流底座(26)中心开设有用于连通第二腔室和第三腔室的二级出口流道，所述第二执行器(23)的一端为第二锥形结构，且所述第二锥形结构在二级出口流道的入口位置与第二节流底座(26)配合构成第二节流区间；
    所述二级减压调节阀(III)包括第三密封活塞(28)、第五弹簧(29)、第三节流底座(30)和第六弹簧(31)；所述第三阀座(11)不贯通所述组合阀阀体，所述第三密封活塞(28)密封式固定安装于第三阀座(11)的开口端，所述第三节流底座(30)安装于第三阀座(11)内，且第三阀座(11)的内腔在第三密封活塞(28)和第三节流底座(30)的分隔下由开口端向内底面依次形成独立的第四腔室和第五腔室；所述第三密封活塞(28)和第三节流底座(30)之间设有处于压缩状态的第五弹簧(29)，所述第三节流底座(30)与第三阀座(11)内底面之间设有处于压缩状态的第六弹簧(31)；所述第三节流底座(30)中心开设有用于连通第四腔室和第五腔室的三级出口流道，所述第三密封活塞(28)的端部为第三锥形结构，且所述第三锥形结构在三级出口流道的入口位置与第三节流底座(30)配合构 成第三节流区间；
    所述第二腔室和第四腔室分别通过第一通道(3)和第二通道(4)连通所述连接流道(2)；所述第三腔室和第五腔室分别连通二级出口流道(6)；所述第一腔室和所述二级出口流道(6)分别通过第三通道(5)和第四通道(8)连通所述调压储氢流道(7)；且所述调压储氢流道(7)与第三通道(5)的第一连接口和所述调压储氢流道(7)与第四通道(8)的第二连接口保持间隔，第一连接口和第二连接口之间的调压储氢流道(7)作为压力调节段；所述调压储氢流道(7)中设有与流道内壁构成活塞副的可控滑动活塞(32)，且可控滑动活塞(32)在调压储氢流道(7)内的滑动行程覆盖所述压力调节段；所述可控滑动活塞(32)在所述压力调节段内滑动过程中通过改变所述第一腔室内的压力来控制所述第二节流区间的开度，从而改变所述二级出口流道(6)输出的氢气流量。
  2. 如权利要求1所述的具有流量调节与稳压功能的供氢组合阀，其特征在于，所述一级减压阀(I)包括进口流道(13)、第一节流底座(14)、第一执行器(15)、执行器内流道(16)、第一密封活塞(18)、第一弹簧(20)和第二弹簧(21)；所述第一阀座(9)贯通整个组合阀阀体，所述第一节流底座(14)和第一密封活塞(18)分别密封式固定安装于所述第一阀座(9)的两端开口处，所述第一阀座(9)中设有贯通的进口流道(13)；所述第一执行器(15)安装于所述第一阀座(9)中且位于第一节流底座(14)和第一密封活塞(18)之间，第一执行器(15)一端为第一锥形结构，且所述第一锥形结构在进口流道(13)的出口端与第一节流底座(14)配合构成第一节流区间；所述第一执行器(15)与第一密封活塞(18)之间设有一条处于压缩状态的第一弹簧(20)，所述第一执行器(15)与第一节流底座(14)之间设有一条处于压缩状态的第二弹簧(21)，所述第一弹簧(20)和所述第二弹簧(21)分别对第一执行器(15)施加两个相反方向的压力；所述第一执行器(15)中开设有连通至第一执行器(15)顶面的执行器内流道(16)，所述进口流道(13)的入口端用于连接外部氢气源，输入的氢气依次通过所述进口流道(13)、所述第一节流区间、所述执行器内流道(16)后进入所述一级出口流道(1)中。
  3. 如权利要求2所述的具有流量调节与稳压功能的供氢组合阀，其特征在于，所述第一节流底座(14)和第一密封活塞(18)均在安装第一弹簧(20)的位置开设同轴的弹簧安装孔，且第一节流底座(14)的弹簧安装孔底部放置有一个连通执行器内流道(16)的带孔圆盘(19)，第一弹簧(20)的一端支顶于带孔圆盘(19)上，另一端支顶于第一密封活塞(18)的弹簧安装孔中。
  4. 如权利要求2所述的具有流量调节与稳压功能的供氢组合阀，其特征在于，所述第一密封活塞(18)与第一阀座(9)内壁、第一节流底座(14)与第一阀座(9)内壁、第一节 流底座(14)与第一执行器(15)之间均通过第一密封垫圈(17)构成密封连接。
  5. 如权利要求1所述的具有流量调节与稳压功能的供氢组合阀，其特征在于，所述一级出口流道(1)和连接流道(2)均从所述组合阀阀体表面向内部进行钻孔加工而成，且其位于所述组合阀阀体表面的开口端均通过圆柱密封(12)进行封闭。
  6. 如权利要求1所述的具有流量调节与稳压功能的供氢组合阀，其特征在于，所述可控滑动活塞(32)上带有控制杆，控制杆伸出组合阀阀体且与组合阀阀体接触位置保持动密封。
  7. 如权利要求1所述的具有流量调节与稳压功能的供氢组合阀，其特征在于，所述第三通道(5)与所述第一腔室侧壁的连接口位置处于所述挡环的高度范围内。
  8. 如权利要求1所述的具有流量调节与稳压功能的供氢组合阀，其特征在于，所述第二执行器(23)包括由圆形板下方连接第二锥形结构组成，所述第二阀座(10)侧壁具有一个阶梯面，所述阶梯面上放置有第二密封垫圈(24)，所述圆形板向第二节流底座(26)方向移动时能压合在第二密封垫圈(24)上，保证第一腔室和第二腔室之间密闭不连通。
  9. 如权利要求1所述的具有流量调节与稳压功能的供氢组合阀，其特征在于，所述可控滑动活塞(32)在所述压力调节段内滑动过程中，能完全封闭所述第二节流区间。
  10. 如权利要求1所述的具有流量调节与稳压功能的供氢组合阀，其特征在于，所述外部氢气源的氢气压力范围为10～70MPa，氢气经过一级减压阀(I)后氢气的压力减压至2～3MPa，经二级减压流量调节阀(II)后氢气的压力减压至车载氢燃料电池的工作压力，经二级减压调节阀(III)后氢气的压力减压至车载氢燃料电池的工作压力。
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JP2017045176A (ja) * 2015-08-25 2017-03-02 愛三工業株式会社 圧力調整弁
CN106090363A (zh) * 2016-08-31 2016-11-09 常德翔宇设备制造有限公司 一种二级气体减压阀
CN108087602A (zh) * 2017-12-15 2018-05-29 上海瀚氢动力科技有限公司 一种集成减压阀
CN210461828U (zh) * 2019-07-09 2020-05-05 上海艾维科阀门股份有限公司 一种流量压差整定阀
CN111365503A (zh) * 2020-01-02 2020-07-03 上海艾维科阀门股份有限公司 一种气体用核电减压阀
CN114688324A (zh) * 2022-03-24 2022-07-01 浙江大学 一种具有流量调节与稳压功能的供氢组合阀

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