JP2018077796A - High pressure fluid control valve and fuel cell system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a high pressure fluid control valve having an opening and closing function and a pressure regulating function.SOLUTION: A high pressure chamber, a low pressure chamber, and an intermediate chamber are formed on a housing, with a cut-off sheet part formed between the high pressure chamber and the intermediate chamber, and a pressure regulating sheet part formed between the intermediate chamber and the low pressure chamber. A valve body is slidably inserted into a valve body guide hole of the housing while extending from the high pressure chamber to the intermediate chamber, and a sliding seal part is formed to seal the high pressure chamber. A cut-off part, which abuts on the cut-off sheet part when the valve is fully closed and blocks communication between the high pressure chamber and intermediate chamber, and a pressure regulating part, which abuts on the pressure regulating sheet part when the valve is fully closed and blocks communication between the intermediate chamber and low pressure chamber, are formed on the valve body. The pressure regulating sheet part follows the movement of the valve body only for a prescribed distance when the valve opens from fully closed, and is displaceable or deformable. The cut-off sheet part has a cut-off sheet diameter which is larger than a pressure regulating sheet diameter, which is the sheet diameter of the pressure regulating sheet part, and which is also larger than an outer diameter of the valve body on the sliding seal part.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a high-pressure fluid control valve suitable for high-pressure fluid and a fuel cell system including the same.

  Patent Document 1 includes a hydrogen tank 2, a hydrogen supply passage 3 for supplying high-pressure hydrogen gas stored in the hydrogen tank 2 to the anode electrode of the fuel cell 1, and a hydrogen supply passage 3. A fuel cell system including a control valve 4 is disclosed. The control valve 4 is for adjusting the pressure of the hydrogen gas supplied to the fuel cell 1. Further, the fuel cell system includes an on-off valve 5 that shuts off the communication between the inside of the hydrogen tank 2 and the hydrogen supply passage 3 when the power generation of the fuel cell 1 is stopped (when the power is off) (paragraphs 0013 and 0014).

JP2013-134687A

  However, in Patent Document 1, the control valve 4 is disposed in the middle of the hydrogen supply passage 3, in other words, between the high-pressure pipe 3 </ b> A and the low-pressure pipe 3 </ b> B, while the on-off valve 5 is a gas extraction part of the hydrogen tank 2, In other words, the control valve 4 and the on-off valve 5 are individually provided at the connection portion between the hydrogen tank 2 and the high-pressure pipe 3 </ b> A of the hydrogen supply passage 3. Here, if the function of the on-off valve and the function of the pressure control valve can be integrated into an integrated control valve, the layout of piping and the like can be improved, and the number of parts and the manufacturing cost can be reduced.

  Accordingly, an object of the present invention is to provide a high-pressure fluid control valve that has both an opening / closing function and a pressure regulation function, and a fuel cell system that includes such a control valve in an anode system.

  In one embodiment of the present invention, a housing having a first port on the high pressure side and a second port on the low pressure side, a high pressure chamber communicating with the first port, a low pressure chamber communicating with the second port, a high pressure chamber, and a low pressure An intermediate chamber between the chambers is formed, a blocking sheet portion is formed between the high pressure chamber and the intermediate chamber, and a pressure adjusting sheet portion is formed between the intermediate chamber and the low pressure chamber. The valve body is accommodated in the housing so as to extend from the high-pressure chamber to the intermediate chamber, and is slidably inserted into the valve body guide hole of the housing, and a sliding seal portion for sealing the high-pressure chamber to the outside is provided. Form. Further, in the valve body, when the valve is fully closed, a blocking portion that contacts the blocking sheet portion to block communication between the high pressure chamber and the intermediate chamber, and when fully closed, the valve body contacts the pressure adjusting sheet portion and communicates between the intermediate chamber and the low pressure chamber. And a pressure adjusting unit that blocks the pressure. The pressure adjusting sheet portion can be displaced or deformed by following a predetermined distance with respect to the movement of the valve body during the valve opening operation from the fully closed state. The blocking sheet portion sets the blocking sheet diameter, which is the sheet diameter, to a value larger than the pressure adjusting sheet diameter, which is the seat diameter of the pressure adjusting sheet portion, and larger than the outer diameter of the valve body in the sliding seal portion.

  Furthermore, in another form, in the fuel cell system, the high-pressure fluid control valve is arranged so that the fuel stored in the fuel tank is introduced through the first port and the decompressed fuel is delivered from the second port. .

  ADVANTAGE OF THE INVENTION According to this invention, the high pressure fluid control valve which integrated the opening / closing function and the pressure regulation function is provided, The layout property of piping etc. can be improved, and it becomes possible to reduce the number of parts and manufacturing cost.

FIG. 1 is an overall configuration diagram of a fuel cell system to which a high-pressure fluid control valve according to an embodiment of the present invention is applied. FIG. 2 is a schematic cross-sectional view showing the overall configuration of the high pressure fluid control valve. FIG. 3 is an enlarged cross-sectional view showing a configuration of a main part of the high pressure fluid control valve. FIG. 4 is an explanatory view schematically showing the operation when the high pressure fluid control valve is opened from the fully closed state. FIG. 5 is an explanatory diagram showing a change in the seat pressure according to the position of the valve body in the opening direction. FIG. 6 is an explanatory diagram showing changes in drive energy supplied to the solenoid during the valve opening operation. FIG. 7 is an explanatory view showing a configuration of a blocking sheet portion according to another embodiment of the present invention. FIG. 8 is an explanatory view showing a configuration of a blocking sheet portion according to still another embodiment of the present invention. FIG. 9 is an explanatory diagram showing a configuration of a pressure adjusting sheet portion according to still another embodiment of the present invention.

  Embodiments of the present invention will be described below with reference to the drawings.

(Overall configuration of fuel cell system)
FIG. 1 shows a configuration of a fuel cell system 1 to which a high-pressure fluid control valve 5 according to a first embodiment of the present invention is applied, focusing on an anode system.

  The fuel cell system 1 according to the present embodiment roughly includes a fuel cell 10, a cathode gas supply / discharge mechanism 12, and an anode gas supply / discharge mechanism 14. The fuel cell 10 constitutes a power generation device. The cathode gas supply / discharge mechanism 12 is a mechanism that supplies an oxidant to the cathode electrode of the fuel cell 10 and discharges the cathode off-gas after the power generation reaction from the fuel cell 10. The anode gas supply / discharge mechanism 14 supplies fuel to the anode electrode of the fuel cell 10, supplies the anode off-gas after the power generation reaction again to the anode electrode, and partially supplies the anode off-gas as needed in the fuel cell system 1. It is a mechanism for discharging to the outside.

  The fuel cell system 1 further includes a load device (not shown), and appropriately includes facilities necessary for the operation of the fuel cell 10 such as a heating / cooling mechanism. In the present embodiment, the fuel cell system 1 is mounted on a vehicle, and the load device is specifically an electric motor for running the vehicle. The fuel cell 10 constitutes a drive source for the fuel cell vehicle, and generates electric power necessary for traveling of the vehicle in addition to electric power supplied to the electric motor.

  The fuel cell 10 is configured by laminating fuel cell cells that are configured by sandwiching a membrane electrode assembly between a pair of separators, and is supplied with air through a cathode gas supply / exhaust mechanism 12 and also supplied with an anode gas. Hydrogen gas is supplied through the mechanism 14, and power is generated by a chemical reaction between oxygen and hydrogen in the air. In this embodiment, hydrogen is the fuel and oxygen in the air is the oxidant. Hydrogen gas is supplied from a high-pressure hydrogen tank 141 described later, and air is taken from the atmosphere through a compressor (not shown) or the like. Electricity generated by the power generation is supplied to an electric motor for running the vehicle and used for driving the electric motor.

  The cathode gas supply / discharge mechanism 12 includes a cathode gas supply passage 121 and a cathode gas discharge passage 122. The cathode gas supply passage 121 is a passage through which air supplied to the cathode electrode of the fuel cell 10 flows, and the cathode gas discharge passage 122 is a passage through which cathode off-gas discharged from the fuel cell 10 flows. Air in the atmosphere is supplied to the cathode electrode of the fuel cell 10 via the cathode gas supply passage 121, and cathode off-gas is released to the outside of the fuel cell system 1 via the cathode gas discharge passage 122.

  The anode gas supply / discharge mechanism 14 includes a high-pressure hydrogen tank 141, an anode gas supply passage 142, and an anode off-gas circulation passage 143. The high-pressure hydrogen tank 141 is a high-pressure gas container that stores hydrogen gas supplied to the anode electrode of the fuel cell 10 while maintaining a high pressure state, and constitutes a “fuel tank” according to the present embodiment. The anode gas supply passage 142 is a passage through which hydrogen gas supplied to the anode electrode of the fuel cell 10 flows. Between the gas outlet of the high-pressure hydrogen tank 141 and the gas inlet of the anode electrode of the fuel cell 10. It is connected. The anode gas supply passage 142 constitutes a “fuel supply pipe” according to the present embodiment, and a first fuel supply pipe 142 a upstream from the ejector 145 described later and a second fuel supply pipe downstream from the ejector 145. 142b. The anode off gas circulation passage 143 is a passage for supplying again the anode off gas discharged from the fuel cell 10 to the anode electrode, and is provided between the gas outlet of the anode electrode of the fuel cell 10 and the anode gas supply passage 142. It is connected to the.

  An integrated main stop valve 5, which is a “high pressure fluid control valve” according to the present embodiment, is attached to the gas outlet of the high pressure hydrogen tank 141. The integrated main stop valve 5 has an opening / closing function for blocking communication between the inside of the high-pressure hydrogen tank 141 and the anode gas supply passage 142, and a pressure reducing or pressure regulating function for controlling the pressure of hydrogen gas sent to the anode gas supply passage 142. It is what you have. The hydrogen gas stored in the high-pressure hydrogen tank 141 is sent to the anode gas supply passage 142 under the control of the integrated main stop valve 5 during the opening of the integrated main stop valve 5, and passes through the anode gas supply passage 142. It is supplied to the anode electrode of the fuel cell 10.

  Further, an ejector 145 is installed at a connection portion between the anode gas supply passage 142 and the anode off-gas circulation passage 143, and the hydrogen gas sent to the anode gas supply passage 142 is supplied to the nozzle portion of the ejector 145. On the other hand, the anode offgas containing hydrogen remaining without contributing to the power generation reaction at the anode electrode of the fuel cell 10 and impurities such as moisture and nitrogen leaked from the cathode electrode to the anode electrode during the power generation reaction is the anode offgas. It is supplied to the ejector 145 through the circulation passage 143. The anode off gas is sucked into the anode gas supply passage 142 under the action of a negative pressure formed by the jet of hydrogen gas through the nozzle portion inside the ejector 145, and is circulated to the anode electrode of the fuel cell 10 together with this hydrogen gas. The

  In the present embodiment, an anode offgas discharge passage 144 is connected to the anode offgas circulation passage 143. A part of the anode off-gas flows into the anode off-gas discharge passage 144 from the anode off-gas circulation passage 143 as required for discharging impurities from the fuel cell system 1, and the fuel cell system 1 passes through the anode off-gas discharge passage 144. It is discharged outside.

(Basic configuration of control system)
In the present embodiment, the operation of the fuel cell 10 is controlled by the control unit 101. The control unit 101 is configured as an electronic control unit including a central processing unit, a storage device, an input / output interface, and the like, and for operation control of the fuel cell 10, an operation request to the fuel cell system 1 and an actual operation of the fuel cell 10 Signals are input from various sensors 111 to 117 that detect the state.

  The accelerator sensor 111 outputs a signal indicating the amount of depression of the accelerator pedal by the driver of the vehicle. The HFR measuring device 112 outputs a signal indicating the degree of wetness (HFR measured value) of the electrolyte membrane constituting the cell of the fuel cell 10. The stack current sensor 113 outputs a signal indicating the current actually generated by the fuel cell 10. Furthermore, the start switch 114 outputs a signal indicating start and stop commands for the fuel cell system 1 in accordance with a driver's key operation.

  The tank pressure sensor 115 is installed in the high-pressure hydrogen tank 141 and detects the pressure inside the high-pressure hydrogen tank 141, in other words, the pressure of hydrogen gas stored in the high-pressure hydrogen tank 141. The upstream pressure sensor 116 is installed in the first fuel supply pipe 142 a of the anode gas supply passage 142 and detects the pressure of hydrogen gas supplied to the ejector 145. The downstream pressure sensor 117 is installed in the second fuel supply pipe 142b of the anode gas supply passage 142, and detects the pressure of the anode gas sent from the ejector 145, in other words, the mixed gas of hydrogen gas and anode off gas. .

  The control unit 101 executes a predetermined calculation related to the operation control of the fuel cell 10 based on various input signals. Specifically, a start and stop command for the fuel cell system 1 is detected, a target generated power of the fuel cell 10 is calculated, and a drive signal is output to the integrated main stop valve 5.

(Overall configuration of high-pressure fluid control valve)
FIG. 2 is a cross-sectional view showing the overall configuration of the integrated main stop valve 5 which is a high-pressure fluid control valve according to the present embodiment. The integrated main stop valve 5 has both an opening / closing function and a pressure adjusting function, and is attached to the gas outlet of the high-pressure hydrogen tank 141. The overall configuration of the integrated main stop valve 5 will be described with reference to FIG.

  The integrated main stop valve 5 includes a housing 51, a valve body 52, and a solenoid 53.

  The housing 51 has a first port p1 on the high pressure side and a second port p2 on the low pressure side. The first port p1 is inside the high pressure hydrogen tank 141, and the second port p2 is the anode gas supply passage. 142 are each fluidly connected. The hydrogen gas stored in the high-pressure hydrogen tank 141 is introduced into the integrated main stop valve 5 from the first port p1, and after being subjected to a pressure reducing or pressure adjusting action corresponding to the position of the valve body 52 inside the housing 51, The gas is sent from the second port p2 to the anode gas supply passage 142. In the present embodiment, the pressure of the hydrogen gas stored in the high-pressure hydrogen tank 141 is set to several MPa to several tens of MPa (for example, 1 to 70 MPa). To about 1 MPa (for example, 0.005 to 0.2 MPa when there is no ejector 145). The pressure of hydrogen gas at the first port p1 is referred to as “primary pressure”, and the pressure at the second port p2 is referred to as “secondary pressure”.

  A high pressure chamber Ch, an intermediate chamber Cm, and a low pressure chamber Cl are formed in the housing 51 in order from the upstream side with respect to the direction in which the hydrogen gas flows, as spaces that define different pressures regarding the operation of the integrated main stop valve 5. ing. The high pressure chamber Ch communicates with the first port p1 and is a space into which hydrogen gas having a primary pressure P1 is introduced. Here, the pressure in the high pressure chamber Ch is set to a pressure P1 equal to the primary pressure. The low pressure chamber Cl is a space that communicates with the second port p2 and allows the hydrogen gas having the reduced secondary pressure P2 to pass through. The pressure of the low pressure chamber Cl is set to a pressure P3 equal to the secondary pressure. The intermediate chamber Cm is a space interposed between the high pressure chamber Ch and the low pressure chamber Cl. Inside the housing 51, a blocking sheet portion 511 is further formed between the high pressure chamber Ch and the intermediate chamber Cm, and a pressure adjusting sheet portion 512 is formed between the intermediate chamber Cm and the low pressure chamber Cl.

  The valve body 52 regulates the flow of hydrogen gas from the first port p1 to the second port p2, and is accommodated inside the housing 51 so as to be capable of reciprocating in the axial direction. In the present embodiment, the valve body 52 is embodied as a spool-like valve body that slides in the axial direction, and shuts off the communication between the high-pressure chamber Ch and the intermediate chamber Cm in the fully closed state shown in FIG. The communication between the intermediate chamber Cm and the low pressure chamber Cl is blocked.

  The valve body 52 includes a main shaft portion 521 formed in a cylindrical shape, a first rod-shaped portion 522 extending in the axial direction from one end of the main shaft portion 521, and a first rod-shaped portion 522 from the other end of the main shaft portion 521. A second rod-shaped portion 523 extending in the reverse direction. The valve body 52 further includes a blocking portion 524 extending in the radial direction from the vicinity of the middle portion of the main shaft portion 521, and a pressure adjusting portion 525 extending in the radial direction from the vicinity of the proximal end portion of the main shaft portion 521. Prepare.

  The main shaft portion 521 extends from the high-pressure chamber Ch to the intermediate chamber Cm on one end side, and is set to a length that extends to the valve body guide hole 51a of the housing 51 on the other end side. The first rod-shaped portion 522 extends from one end of the main shaft portion 521 to the distal end side and is set to a length penetrating one side wall of the housing 51, and the second rod-shaped portion 523 is proximal to the other end of the main shaft portion 521. And is set to a length penetrating the other side wall of the housing 51. The first rod-like portion 522 and the second rod-like portion 523 are slidably supported with respect to the annular seal member installed on the inner wall of the housing 51, so that the entire valve body 52 is supported with respect to the housing 51. . Further, an annular seal member 526 is installed on the inner wall of the housing 51 that forms the valve element guide hole 51a, and the main shaft portion 521 is slidably supported by the annular seal member 526. An additional support is formed on the valve body 52. Here, the annular seal member 526 and the main shaft portion 521 slidably in contact therewith form a “sliding seal portion” that seals the high-pressure chamber Ch from the outside of the housing 51.

  The blocking portion 524 is formed in an annular shape in a cross section perpendicular to the central axis of the valve body 52, and is in contact with the blocking sheet portion 511 when fully closed with respect to the housing 51. The pressure adjusting unit 525 is provided on the base end side with respect to the blocking unit 524, and is formed in an annular shape having a narrower width than the blocking unit 524 in a cross section perpendicular to the central axis of the valve body 52. The pressure adjusting unit 525 is in contact with the pressure adjusting sheet portion 512 when the housing 51 is fully closed. When the blocking portion 524 contacts the blocking sheet portion 511, the communication between the high pressure chamber Ch and the intermediate chamber Cm is blocked, and when the pressure adjusting portion 525 contacts the pressure adjusting sheet portion 512, the intermediate chamber Cm and the low pressure chamber Communication with Cl is blocked.

  The solenoid 53 electromagnetically drives the valve body 52, and is disposed adjacent to the proximal end side of the valve body 52 with respect to the housing 51.

  The solenoid 53 includes an electromagnetic coil 531, and a plunger 532 arranged concentrically on the inner side of the electromagnetic coil 531, and the plunger 532 receives the electromagnetic force generated by the electromagnetic coil 531 and moves linearly. The electromagnetic coil 531 and the plunger 532 are accommodated in a solenoid case 533, and the solenoid case 533 is fixed to the housing 51 via a holder 534. The solenoid 53 generates electromagnetic force when the energization of the electromagnetic coil 531 is turned on, and drives the plunger 532. The movement of the plunger 532 is transmitted to the valve body 52 via the second rod-shaped portion 523, and the valve body 52 is driven in the opening direction. Then, the blocking sheet portion 511 and the pressure regulating sheet portion 512 are opened according to the amount of movement of the valve body 52, in other words, the position of the valve body 52 in the opening direction.

  In the present embodiment, a valve return mechanism 54 is provided adjacent to the distal end side of the valve body 52 with respect to the housing 51. The valve return mechanism 54 elastically biases the valve body 52 from the side opposite to the solenoid 53, and when the energization to the electromagnetic coil 531 is turned off, the valve body 52 is driven in the closing direction. Return to the fully closed position.

  The valve return mechanism 54 includes a spring 541, a retainer 542 attached to the tip of the valve body 52, and a holder 543 installed on the opposite side of the spring 541 with respect to the retainer 542. The spring 541 is accommodated in the spring case 544 together with the retainer 542 and the holder 543, and the spring case 544 is directly fixed to the housing 51. With the spring case 544 fixed to the housing 51, the spring 541 is in a compressed state between the retainer 542 and the holder 543. Further, a disc-shaped diaphragm 545 is provided so as to be sandwiched between the valve body 52 and the retainer 542, and the outer periphery of the diaphragm 545 is sandwiched between the housing 51 and the spring case 543. The pressure P3 or the secondary pressure of the low pressure chamber Cl is introduced into the pressure chamber Cp of the valve return mechanism 54 through the pressure feedback passage 513, and this feedback pressure acts on the valve body 52 through the diaphragm 545. The driving force in the closing direction for 52 is assisted. In the present embodiment, the spring 541 is employed as a generation source of the driving force for returning the valve body 52 to the fully closed position. However, other elastic bodies such as rubber may be employed instead of the spring 541. Not only the body but also permanent magnets can be used.

  On / off of energization to the electromagnetic coil 531 is controlled by the control unit 101.

(Main part of high pressure fluid control valve)
FIG. 3 shows a configuration of a main part of the integrated main stop valve 5 in a cross section parallel to the central axis of the valve body 52, and FIG. 4 shows a valve opening operation from the fully closed state of the integrated main stop valve 5. It is schematically shown by the same cross section. With reference to FIG. 3 and 4, the shielding sheet part 511 and the pressure regulation sheet part 512 employ | adopted by this embodiment are further demonstrated.

  As described above, in this embodiment, the spool-shaped single valve body 52 is formed with the blocking portion 524 for realizing the opening / closing function and the pressure adjusting portion 525 for realizing the pressure adjusting function. On the other hand, a blocking sheet portion 511 that receives the blocking portion 524 and a pressure adjusting sheet portion 512 that receives the pressure adjusting portion 525 are formed in the housing 51.

  The blocking sheet portion 511 is based on the outer diameter of the valve body 52 in the sliding seal portion, in other words, the diameter (hereinafter referred to as “sliding seal diameter”) d1 of the main shaft portion 521 forming the sliding seal portion described above. Has a large sheet diameter (hereinafter referred to as “blocking sheet diameter”) d3. Here, the “blocking sheet diameter” refers to the diameter of the contact portion between the blocking portion 524 and the blocking sheet portion 511 of the valve body 52, and when the pressure receiving surface on which the primary pressure P 1 acts on the valve body 52 is determined. This is the standard size. Therefore, when the blocking portion 524 and the blocking sheet portion 511 are substantially in contact with each other instead of a line, the “blocking sheet diameter” refers to the diameter of the outer edge portion of the contact surface, in other words, the maximum diameter. .

  The blocking sheet portion 511 can be formed from, for example, a hard resin material that can ensure a predetermined blocking surface pressure. In this embodiment, such a resin material is formed into an annular shape, and this is formed into the housing 51. It is provided by being fitted to a concave part formed on the inner wall and fixed or fixed.

  The pressure adjusting sheet portion 512 has a sheet diameter (hereinafter referred to as “pressure adjusting sheet diameter”) d2 smaller than the blocking sheet diameter d3. In other words, the blocking sheet diameter d3 is set to a value larger than the pressure regulating sheet diameter d2. In the present embodiment, the pressure adjusting sheet portion 512 is not the housing 51 itself, but an accessory component of the housing 51, specifically, a cylindrical slide body 515 that is a “movable body”, and the slide body 515 and the housing 51. And a spring body 516 installed in a compressed state between the inner wall and the inner wall. The spring body 516 constitutes an “elastic body” and is set to exhibit elasticity that can achieve a predetermined valve closing surface pressure.

  The slide body 515 is urged in the opening direction by the spring body 516, and its tip end abuts on the pressure regulating portion 512 of the valve body 52, and the pressure regulating sheet serves as an abutting portion between the slide body 515 and the pressure regulating portion 512. A portion 512 is formed. By setting the diameter d2 of the slide body 515 at the contact portion to a value smaller than the blocking sheet diameter d3, it is possible to set the pressure regulating sheet diameter d2 that defines the relationship (d3> d2). A concave guide portion is formed on the inner wall of the housing 51 that defines the low-pressure chamber Cl, and the enlarged diameter portion provided on the proximal end side of the slide body 515 is accommodated in the concave guide portion, so that the slide body 515 is a valve body. 52 is installed in the low pressure chamber Cl so as to be movable in the opening direction. A predetermined gap g is formed between the slide body 515 and the inner wall of the housing 51 in a fully closed state. Here, since the slide body 515 is urged in the opening direction of the valve body 52 by the spring body 516, the movement of the valve body 52 during the valve opening operation is a distance corresponding to the predetermined interval g. It can move following the valve body 52.

  Further, in the present embodiment, the pressure adjusting sheet diameter d2 is set to a value equal to the sliding seal diameter d1.

  Turning to the description of FIG. 4, FIG. 4A shows the state of the integrated main stop valve 5 when it is “fully closed”, and FIG. 4B shows the shut-off seat portion in the process of opening the valve from the fully closed state. FIG. 4 (C) shows the state in the “valve closing” state in which the pressure adjustment sheet portion 512 remains blocked even though 511 is opened. FIG. The state at the time of “valve opening” in which both 512 are opened is shown.

  The integrated main stop valve 5 controls the electric energy supplied to the solenoid 53 (hereinafter referred to as “driving energy”) to move the valve body 52 in the opening direction and the closing direction, and between the high pressure chamber Ch and the intermediate chamber Cm. The flow area (hereinafter referred to as “opening degree of the shut-off sheet part”) is controlled, and the flow area (hereinafter referred to as “opening degree of the pressure regulating sheet part”) between the intermediate chamber Cm and the low pressure chamber Cl is controlled. To do. Driving in the opening direction of the valve body 52 is based on electromagnetic force of the electromagnetic coil 531, and driving in the closing direction is based on restoring force based on the elasticity of the spring 541.

  In the fully closed state shown in FIG. 4A, the blocking portion 524 of the valve body 52 comes into contact with the blocking sheet portion 511 and the pressure adjusting portion 525 comes into contact with the pressure adjusting sheet portion 512 (the tip portion of the slide body 515). The blocking sheet portion 511 and the pressure adjusting sheet portion 512 are in a closed state, and their opening degrees are all 0 (zero). The high pressure chamber Ch receives the pressure inside the high pressure hydrogen tank 141 through the first port p1, and a high pressure (primary pressure) P1 acts on the high pressure chamber Ch. On the other hand, the pressure (secondary pressure) P3 acting on the low pressure chamber Cl is extremely lower than the primary pressure because the second port p2 is connected to the anode gas supply passage 142. A pressure P2 between the primary pressure P1 and the secondary pressure P3 acts on the intermediate chamber Cm. The shut-off sheet portion 511 is required to completely shut off the fluid when fully closed, whereas the pressure-adjusting sheet portion 512 has a slight leak within a range that does not hinder the safety from the viewpoint of safety. Permissible. Therefore, when a sufficient time has elapsed since the previous stop of the system 1, the pressure P2 in the intermediate chamber Cm greatly decreases from the pressure immediately after the stop, and is closer to the secondary pressure P3 than the primary pressure P1. Is in a state. Since the blocking sheet diameter d3 is larger than the sliding seal diameter d1, a force corresponding to the difference between the blocking sheet diameter d3 and the sliding seal diameter d1 acts on the valve body 52 in the closing direction based on the primary pressure P1. (Hereinafter, the force acting on the valve body 52 in the closing direction is referred to as “valve closing force”, and conversely, the force acting in the opening direction is referred to as “valve opening force”). In order to move the valve body 52 in the fully closed state in the opening direction, the electromagnetic coil 531 needs to generate an electromagnetic force that can overcome the valve closing force based on the primary pressure P1.

  When the valve shown in FIG. 4B is closed, the shut-off portion 524 of the valve body 52 is separated from the shut-off sheet portion 511 and the shut-off sheet portion 511 is opened, while the pressure regulating portion 525 is in contact with the pressure regulating seat portion 512. The opening degree of the pressure regulation sheet part 512 is still 0 by staying in contact. By opening the blocking sheet portion 511, a flow from the high pressure chamber Ch to the intermediate chamber Cm occurs, and the pressures P1 and P2 are balanced in the high pressure chamber Ch and the intermediate chamber Cm (P1 = P2). Since the pressure regulating sheet diameter (outer diameter of the slide body 515) d2 is equal to the sliding seal diameter d1, the influence of the primary pressure P1 on the valve body 52 is offset. When the valve is closed, the diameter-enlarged portion of the slide body 515 is in contact with the inner wall of the housing 51, and the valve body 52 is not affected by the elastic force of the spring body 516, so that the valve body 52 acts on the valve body 52. The force is substantially only the elastic force of the spring 541. Therefore, in order to further move the valve body 52 in the opening direction, an electromagnetic force that overcomes this relatively small valve closing force may be generated.

  At the time of valve opening shown in FIG. 4C, the pressure adjusting unit 525 is further separated from the pressure adjusting sheet unit 512 from the closed state, and both the blocking sheet unit 511 and the pressure adjusting sheet unit 512 are opened. As a result, hydrogen gas flows into the low pressure chamber Cl from the intermediate chamber Cm, and supply of hydrogen gas to the components (for example, the ejector 145) provided on the downstream side of the integrated main stop valve 5 is started. The pressure of the hydrogen gas supplied to the downstream part is controlled by adjusting the opening of the pressure regulating sheet portion 512. Since the influence of the primary pressure P1 on the valve body 52 is canceled after the blocking sheet portion 511 is opened, the valve body 52 can be moved with relatively small driving energy.

  FIG. 5 shows changes in surface pressure acting on the blocking sheet portion 511 and the pressure regulating sheet portion 512 during the valve opening operation from the fully closed state.

  In the present embodiment, during the valve opening operation, the slide body 515 follows the movement of the valve body 52 by a predetermined distance corresponding to the interval g, so that the valve body 52 starts moving as shown in FIG. Thereafter, the blocking sheet portion 511 is first opened, and then the pressure regulating sheet portion 512 is opened when the diameter-expanded portion of the slide body 515 comes into contact with the inner wall of the housing 51. The valve positions at which the blocking portion 524 and the pressure adjusting portion 525 of the valve body 52 are separated from the blocking sheet portion 511 and the pressure adjusting sheet portion 512 are indicated as “sitting points”, respectively.

  The shut-off sheet portion 511 is formed of a hard resin material, and when fully closed, a valve closing force based on the primary pressure P1 acts on the shut-off portion 524 of the valve body 52 to exceed a predetermined shut-off surface pressure. Is in contact with the blocking portion 524. When energization to the electromagnetic coil 531 is turned on and the valve opening force acting on the valve body 52 exceeds the valve closing force based on the primary pressure P1, the valve body 52 starts to move, and accordingly, the surface of the blocking sheet portion 511 Pressure decreases rapidly. After the seating point, the surface pressure of the blocking sheet portion 511 is 0 (zero).

  The pressure adjusting sheet portion 512 includes a slide body 515 and a spring body 516, and the spring body 516 is set to exhibit elasticity that can achieve a predetermined valve closing surface pressure. Therefore, when fully closed, the slide body 515 is pressed against the pressure adjusting portion 525 of the valve body 52 with a surface pressure exceeding a predetermined valve closing surface pressure by the elastic force of the spring body 516. As the slide body 515 moves following the valve body 52, the amount of displacement of the spring body 516 decreases and the elastic force decreases, so the surface pressure of the pressure adjusting sheet portion 512 also decreases. The decrease in the surface pressure of the pressure adjusting sheet portion 512 is more gradual than that of the blocking sheet portion 511. After the seating point, the surface pressure of the pressure-adjusting sheet portion 512 is also zero as with the blocking sheet portion 511. In the present embodiment, the surface pressure immediately after the pressure adjusting portion 525 of the valve body 52 is seated on the pressure adjusting seat portion 512 or immediately before being separated is defined as the valve closing surface pressure.

  During the valve closing operation from the valve opening, the surface pressures of the shut-off sheet portion 511 and the pressure regulating sheet portion 512 exhibit changes opposite to those during the valve opening operation. However, since the spring 541 of the valve return mechanism 54 cannot generate a valve closing force that resists the repulsive force of the blocking sheet portion 511, the surface pressure after the blocking portion 524 is seated on the blocking sheet portion 511 is reduced. The increase corresponds to an increase in the differential pressure between the high pressure chamber Ch and the intermediate chamber Cm.

  FIG. 6 shows a change in drive energy supplied to the solenoid 53 during the valve opening operation from the fully closed state.

  In the present embodiment, in the period A (time t0 to t1) after the operation is started, a large valve opening force that can overcome the valve closing force based on the primary pressure P1 is generated. Is supplied with a large valve opening energy E1. The magnitude of the valve opening energy E1 is changed according to the primary pressure P1, in other words, the pressure inside the high-pressure hydrogen tank 141. Specifically, the valve opening energy E1 is increased as the storage amount or remaining capacity of the high-pressure hydrogen tank 141 is larger and the primary pressure P1 is higher.

  When the valve body 52 starts moving and a slight gap is generated between the blocking portion 524 and the blocking sheet portion 511, a flow from the high pressure chamber Ch to the intermediate chamber Cm occurs, and the pressure P2 in the intermediate chamber Cm increases. . As the pressure difference between the high pressure chamber Ch and the intermediate chamber Cm decreases, the valve closing force decreases. In a state where the pressure is balanced between the high-pressure chamber Ch and the intermediate chamber Cm (P1 = P2), the influence of the primary pressure P1 on the valve body 52 is canceled out, and the valve body 52 is relatively large enough to overcome the elastic force of the spring 541. It can be moved with a small opening force. Therefore, in this embodiment, the valve body 52 starts to move and the drive energy is reduced as the shut-off portion 524 starts to move away from the shut-off sheet portion 511, and the pressure regulation is significantly lower than the valve opening energy E1. Switch to energy E2 (time t2).

  After the switching, the pressure regulation energy E2 is increased (time t3, t5) or decreased (time t4, t6) to control the hydrogen gas supply flow rate to the fuel cell 10. When the fuel cell system 1 is stopped, the drive energy is set to 0 and the energization to the electromagnetic coil 531 is stopped (time t7).

(Explanation of effects)
The above is the description regarding the integrated main stop valve 5, and the effects obtained by this embodiment will be summarized below.

  First, the opening / closing function and the pressure regulating function can be integrated into one control valve (integrated main stop valve 5).

  By making the sheet diameter (blocking sheet diameter) d3 of the blocking sheet portion 511 larger than the outer diameter (sliding seal diameter) d1 of the valve body 52 in the sliding seal portion, the surface corresponding to these differences is reduced to the primary pressure. The blocking function when fully closed can be secured by the pressure (primary pressure) P1 that functions as a pressure receiving surface and acts on the pressure receiving surface.

  Furthermore, the blocking sheet diameter d3 is larger than the sheet diameter (pressure adjusting sheet diameter) d2 of the pressure adjusting sheet portion 512, in other words, the pressure adjusting sheet diameter d2 is smaller than the blocking sheet diameter d3, so that the blocking sheet portion After opening 511, the influence of the primary pressure P1 on the valve body 52 is reduced, and the valve body 52 can be driven with a relatively small valve opening force (electromagnetic force of the solenoid 53). Thereby, controllability of the valve body 52 at the time of pressure regulation can be ensured, and power consumption can be suppressed.

  And, by integrating the opening / closing function and the pressure adjusting function, the layout of piping and the like can be improved, and the number of parts and the manufacturing cost can be reduced.

  Second, when the pressure regulating sheet diameter d2 is equal to the sliding seal diameter d1, the shut-off sheet portion 511 is opened, but the pressure regulating sheet portion 512 is still closed (see FIG. 4 (B)), the force that the pressure P1 of the high-pressure chamber Ch and the pressure P2 (= P1) of the intermediate chamber Cm act on the valve body 52 in the closing direction and the force that acts in the opening direction are balanced with each other. To do. Thus, after the blocking sheet portion 511 is opened, it becomes possible to cancel the influence of the primary pressure P1, and the controllability of the valve body 52 during pressure regulation can be further enhanced.

  Third, the pressure regulating sheet portion 512 can be realized by a simple structure using the slide body 515 and the spring body 516. Then, while the slide body 515 follows the movement of the valve body 52 during the valve opening operation, it is possible to maintain the surface pressure necessary to suppress excessive leakage through the pressure adjusting sheet portion 512 by the spring body 516. At the same time, by adjusting the elastic force, it is possible to easily set and ensure the surface pressure necessary for suppressing the leakage.

(Description of other embodiments)
FIG. 7 shows the configuration of the integrated main stop valve 5 according to the second embodiment of the present invention, centering on the blocking sheet portion 511.

  In 1st Embodiment shown previously, the interruption | blocking sheet | seat part 511 was made to contact with the interruption | blocking part 524 of the valve body 52 with a line | wire (for example, FIG. 3). In the case of line contact, the drive energy required for reopening the valve body 52 within a short time after the shut-off portion 524 of the valve body 52 contacts the shut-off sheet portion 511 during the valve closing operation. It can be kept small. This is because the valve closing force and the valve opening force based on the primary pressure P1 are still close to each other because the pressure P2 in the intermediate chamber Cm has not decreased so much from P1. However, the blocking sheet portion 511 and the blocking portion 524 may be brought into contact with a surface having a width in the radial direction.

  In the present embodiment, the blocking portion 524 of the valve body 52 is formed to be inclined with respect to the central axis or the opening direction, and the blocking sheet portion 511 is in surface contact with the inclined surface when fully closed. As in the first embodiment, the blocking sheet portion 511 is made of a hard resin material that can secure a predetermined blocking surface pressure. In the fully closed state shown in FIG. 7A, the maximum diameter d3max and It has a minimum diameter d3min. As is clear from the figure, the maximum diameter d3max is a reference dimension for determining the pressure-receiving surface on which the primary pressure P1 acts on the valve body 52, and therefore corresponds to the blocking sheet diameter d3, and slides. It is set to a value larger than the seal diameter d1 and the pressure regulating sheet diameter d2. On the other hand, the minimum diameter d3min is set to a value equal to the sliding seal diameter d1 and the pressure regulating sheet diameter d2.

  Thus, the blocking sheet portion 511 is in surface contact with the blocking portion 524 of the valve body 52, and the maximum diameter d3max of the contact surface (in other words, the blocking sheet diameter d3) is larger than the sliding seal diameter d1. Thus, it is possible to exert a blocking function by the primary pressure P1 immediately after the fully closed state. If it is due to line contact, immediately after the full closure, the pressure P2 in the intermediate chamber Cm is equal to the primary pressure P1, and the valve closing force and the valve opening force based on the primary pressure P1 are in balance with each other. As the pressure P2 in the intermediate chamber Cm decreases with time and the differential pressure between the high pressure chamber Ch and the intermediate chamber Cm increases, the valve closing force increases relative to the valve opening force, and the desired cutoff A surface pressure is formed, and a blocking function is exhibited. On the other hand, when the surface contact is adopted and the maximum diameter d3max is made larger than the sliding seal diameter d1, the pressure receiving surface of the primary pressure P1 becomes larger on the valve closing side by the amount of the contact surface, and is opened by that much. A valve closing force larger than the valve force can be secured.

  And since the minimum diameter d3min of a contact surface is equal to the pressure regulation sheet diameter d2, the influence of the pressure P2 of the intermediate chamber Cm can be canceled when fully closed.

  FIG. 8 shows the configuration of the blocking sheet portion 511 of the integrated main stop valve 5 according to the third embodiment of the present invention.

  In this embodiment, as in the second embodiment, in addition to bringing the blocking sheet portion 511 and the blocking portion 524 of the valve body 52 into surface contact, the blocking sheet portion 511 is protruded in the opening direction by a predetermined length l. ing. Thereby, the blocking sheet portion 511 has a projection area in the opening direction equal to the contact surface over a predetermined length l, and the maximum diameter d3max is constant within the range of the length l. In this way, the change in the maximum diameter d3max can be suppressed against the wear of the material forming the blocking sheet portion 511, and the valve closing force based on the primary pressure P1 can be stably generated.

  FIG. 9 shows the configuration of the integrated main stop valve 5 according to the fourth embodiment of the present invention, centering on the pressure regulating seat portion 512.

  In the first embodiment, the pressure adjusting sheet portion 512 is configured not by the housing 51 itself but by the slide body 515 and the spring body 516 which are incidental parts of the housing 51. However, the pressure adjusting sheet portion 512 can be configured by the housing 51 itself, in other words, as a part of the housing 51.

  In the present embodiment, the pressure adjusting sheet portion 512 is formed of, for example, a resin material exhibiting sufficient elasticity to ensure a predetermined valve closing surface pressure, and like the blocking sheet portion 511, such a resin material is circular. It is formed in an annular shape and fixed or fixed to a concave portion formed on the inner wall of the housing 51.

  The pressure regulation sheet portion 512 is compressed and deformed in the fully closed state shown in FIG. 9A, and comes into surface contact with the pressure regulation portion 525 of the valve body 52. The contact surface has a certain width in the radial direction, the maximum diameter d2max defined by the outer edge portion is equal to the blocking sheet diameter d3, and the minimum diameter d2min defined by the inner edge portion is equal to the sliding seal diameter d1. Therefore, also in this embodiment, the blocking sheet diameter d3 has a larger value than the sliding seal diameter d1. During the valve opening operation from the fully closed state, the pressure adjusting sheet portion 512 gradually recovers its shape as the valve body 52 moves, and immediately before the pressure adjusting portion 525 is separated from the pressure adjusting sheet portion 512 (FIG. 9 ( b)), the pressure adjusting part 525 is in contact with the pressure adjusting sheet part 512 at its inner edge.

  According to such a configuration, since the blocking sheet diameter d3 is larger than the sliding seal diameter d1, the primary pressure P1 acts in the closing direction with the surface corresponding to these differences as the pressure receiving surface of the primary pressure, and is fully closed. It is possible to ensure a time-off function.

  Further, since the minimum diameter d2min of the pressure adjusting sheet portion 512 is smaller than the blocking sheet diameter d3, the influence of the primary pressure P1 on the valve body 52 is reduced after the blocking sheet portion 511 is opened, and the valve body 52 during pressure adjustment is reduced. As well as ensuring controllability, power consumption can be suppressed. Since the minimum diameter d2min is equal to the sliding seal diameter d1, the valve closing force based on the primary pressure P1 and the valve opening force are balanced, and the valve body 52 can be moved with a smaller electromagnetic force. The controllability of the body 52 can be further enhanced.

  In this way, the pressure regulating sheet portion 512 can be realized by the housing 51 itself regardless of the accessory parts such as the slide body 515, and the layout of piping and the like can be improved by integrating the opening / closing function and the pressure regulating function. The number of parts and manufacturing cost can be reduced.

  In the above description, the case where the present invention is applied to a fuel cell vehicle has been described as an example. However, the present invention is not limited to this, and is applied to a natural gas vehicle as an integrated main stop valve having a pressure regulating valve function. It is also possible to do.

  Although the embodiments of the present invention have been described above, the present invention is not limited to these embodiments, and various changes and modifications can be made within the scope of the matters described in the claims. Not too long.

DESCRIPTION OF SYMBOLS 1 ... Fuel cell system 5 ... Integrated main stop valve (high pressure fluid control valve)
DESCRIPTION OF SYMBOLS 51 ... Housing 51a ... Valve body guide hole 511 ... Blocking sheet part 512 ... Pressure regulation sheet part Ch ... High pressure chamber Cm ... Intermediate | middle chamber Cl ... Low pressure chamber 52 ... Valve body 521 ... Main shaft part 524 ... Blocking part 525 ... Pressure regulation part 526 ... annular seal member 53 ... solenoid 531 ... electromagnetic coil 532 ... plunger 54 ... valve return mechanism p1 ... first port p2 ... second port 12 ... cathode gas supply / discharge mechanism 121 ... cathode gas supply passage 122 ... cathode off-gas discharge passage 14 ... Anode gas supply / exhaust mechanism 141 High-pressure hydrogen tank (fuel tank)
142 ... Anode gas supply passage 143 ... Anode off gas circulation passage 101 ... Control unit

Claims (6)

A first port on the high pressure side and a second port on the low pressure side,
A high-pressure fluid control valve that depressurizes the high-pressure fluid introduced through the first port and sends it out from the second port;
A housing, a valve body that is housed in the housing and controls the flow of the high-pressure fluid from the first port toward the second port, and a solenoid that drives the valve body,
The housing is formed with a high-pressure chamber communicating with the first port, a low-pressure chamber communicating with the second port, and an intermediate chamber between the high-pressure chamber and the low-pressure chamber,
A blocking sheet portion formed between the high pressure chamber and the intermediate chamber, and a pressure adjusting sheet portion formed between the intermediate chamber and the low pressure chamber,
The valve body extends from the high-pressure chamber to the intermediate chamber, and is slidably inserted into the valve body guide hole of the housing to seal the high-pressure chamber from the outside. And a contact portion that contacts the blocking sheet portion when fully closed and blocks communication between the high pressure chamber and the intermediate chamber, and a contact portion that contacts the pressure adjusting sheet portion when fully closed, and the intermediate chamber, A pressure adjusting unit that blocks communication with the low-pressure chamber,
The pressure adjusting sheet portion can be displaced or deformed by following a predetermined distance with respect to the movement of the valve body during the valve opening operation from the fully closed state,
The blocking sheet portion has a blocking sheet diameter that is a sheet diameter larger than a pressure adjusting sheet diameter that is a sheet diameter of the pressure adjusting sheet portion, and is larger than an outer diameter of the valve body in the sliding seal portion,
High pressure fluid control valve.   The high pressure fluid control valve according to claim 1, wherein the pressure regulating seat diameter is equal to an outer diameter of the valve body in the sliding seal portion. A movable body disposed in the low-pressure chamber and the movable body so as to abut against the pressure regulating portion of the valve body when fully closed and to form a gap corresponding to the predetermined distance with respect to the housing. An elastic body biasing in the opening direction of the valve body,
The high-pressure fluid control valve according to claim 1, wherein the pressure adjusting sheet portion is formed as a contact portion of the movable body with respect to the pressure adjusting portion. The blocking portion of the valve body is formed to be inclined with respect to the opening direction,
The blocking sheet portion is in surface contact with the blocking portion when fully closed,
The contact surface of the said interruption | blocking sheet | seat part is larger than the outer diameter of the said valve body in the said sliding seal | sticker part, and the minimum diameter is any one of Claims 1-3 equal to the said pressure regulation sheet | seat diameter. The high-pressure fluid control valve described.   The high-pressure fluid control valve according to claim 4, wherein the blocking sheet portion has a convex shape in the opening direction, and a projected area in the opening direction is equal to the contact surface over a predetermined length. A fuel cell that generates electricity by receiving fuel and an oxidant; and
A fuel tank for storing the fuel;
6. The fuel cell according to claim 1, wherein the fuel tank is interposed between the fuel tank and the fuel cell, introduces the fuel through the first port, and delivers the decompressed fuel from the second port. The high-pressure fluid control valve described,
A fuel supply pipe connecting the second port of the high pressure fluid control valve and the anode electrode of the fuel cell;
An operation state sensor for detecting an operation state of the fuel cell;
A controller for inputting an output signal of the operation state sensor and outputting a drive signal for the solenoid;
A fuel cell system comprising:

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