JP5779432B2 - Fuel gas supply system and pressure control method thereof - Google Patents

Description

  The present invention relates to a fuel gas supply system that supplies fuel gas stored in a tank to a fuel gas consumer, and a pressure control method therefor.

  As automobiles, there are gasoline cars that use gasoline and diesel cars that use light oil, but besides these, there are gas engine cars and fuel cell cars that use fuel gas such as compressed natural gas (CNG) and compressed hydrogen. Are known. In these gas engine vehicles and fuel cell vehicles, the fuel gas is stored in a high-pressure tank or the like, and the stored high-pressure fuel gas is supplied to the gas engine or fuel cell stack via the fuel gas supply system and consumed. Is done. As a system including a fuel gas supply system for a fuel cell vehicle, for example, a fuel cell system as in Patent Document 1 is known.

  In the fuel cell system described in Patent Document 1, two hydrogen pressure regulating valves are provided in parallel between a hydrogen cylinder and a fuel stack. In the fuel cell system, the supply pressure of hydrogen gas to the fuel stack is adjusted by adjusting the opening degree of the two hydrogen pressure regulating valves. These two hydrogen pressure control valves are configured so that the supply flow rate to the fuel stack is different. By using a combination of a large pressure control valve capable of supplying a large flow rate and a small pressure control valve capable of supplying a small flow rate. The required flow rate is supplied to the fuel stack.

JP 2002-231277 A

  The pressure regulating valve used in the fuel cell system described in Patent Document 1 has a complicated structure as compared with a pressure reducing valve and an on-off valve, and has a large number of components, so that the manufacturing cost is high. Therefore, when a plurality of pressure regulating valves are used, the system configuration becomes complicated and the manufacturing cost increases. Further, in order to obtain a desired supply pressure, it is necessary to combine the opening degrees of the two pressure regulating valves, which complicates pressure control in the entire system.

  Therefore, the present invention provides a fuel gas supply system capable of controlling the supply pressure to the fuel gas consumer with high accuracy in a wide range from a small flow rate to a large flow rate without performing complicated pressure control and with a simple system configuration. The purpose is that.

  The fuel gas supply system of the present invention is a fuel gas supply system that supplies fuel gas stored in a tank to a fuel gas consumer via a supply passage that branches into a first flow path and a second flow path and then merges into one. An electromagnetic on-off valve provided in the first flow path for opening and closing between the tank and the fuel gas consumer; and provided in the second flow path from the tank to the fuel gas consumer. An electromagnetic pressure regulating valve for regulating the introduced fuel gas, and the electromagnetic pressure regulating valve has a capacity coefficient smaller than that of the electromagnetic on-off valve.

  According to the present invention, when a large amount of fuel gas is required in the fuel gas consumer, a large amount of fuel gas is supplied to the fuel gas consumer by an electromagnetic on-off valve having a larger capacity coefficient than the electromagnetic pressure regulating valve. Then, the supply pressure to the fuel gas consumer can be regulated by the electromagnetic pressure regulating valve provided in the second flow path in parallel with the electromagnetic on-off valve. On the other hand, when the fuel gas required by the fuel gas consumer has a small flow rate, the first flow path can be closed by the electromagnetic on-off valve, and the supply pressure to the fuel gas consumer can be regulated by the electromagnetic pressure regulating valve. . As described above, the supply pressure can be controlled with high accuracy in a wide range from a small flow rate to a large flow rate without performing complicated pressure control with a simple system configuration using the electromagnetic on-off valve and the electromagnetic pressure regulating valve.

  Further, in the present invention, the capacity coefficient of the electromagnetic pressure regulating valve is made smaller than that of the electromagnetic on / off valve, thereby reducing the size of the electromagnetic pressure regulating valve having a more complicated configuration and more parts than the electromagnetic on / off valve. Can do. Thereby, the manufacturing cost of the electromagnetic pressure regulating valve can be reduced, and the manufacturing cost of the fuel gas supply system can be reduced.

  In the above invention, it is preferable that the capacity coefficient is a Cv value, and the electromagnetic pressure regulating valve has a Cv value of 50% or less of a Cv value of the electromagnetic on-off valve.

  According to the above configuration, it is possible to reduce the size of the electromagnetic pressure regulating valve by reducing the Cv value of the electromagnetic pressure regulating valve to 50% or less of the Cv value of the electromagnetic opening / closing valve, thereby reducing the manufacturing cost of the electromagnetic pressure regulating valve. Can be suppressed. Thereby, the manufacturing cost of the fuel gas supply system can be further reduced. On the other hand, since the Cv value of the electromagnetic on-off valve can be ensured, a larger flow rate can be passed to the fuel gas consumer.

  In the above invention, a control device for controlling the opening / closing operation of the electromagnetic on-off valve and the pressure adjustment operation of the electromagnetic pressure regulating valve is provided, and the control device includes a supply pressure and a target pressure of the fuel gas of the fuel gas consumer When the differential pressure is more than a specified value, the supply pressure of the fuel gas consumer is increased by opening the first flow path by the electromagnetic on-off valve, and when the differential pressure is less than a specified value, It is preferable that the first flow path is closed by the electromagnetic on-off valve and the supply pressure of the fuel gas consumer is regulated by the electromagnetic pressure regulating valve.

  According to the above configuration, when the differential pressure between the supply pressure and the target pressure is equal to or higher than the specified value, the control device opens the first flow path to supply a large flow of fuel gas to the fuel gas so that the supply pressure approaches the target pressure. Supply to the consumer and increase the supply pressure significantly. In addition, when the differential pressure is less than the specified value, the control device opens the first flow path with the electromagnetic on-off valve because the flow rate to be supplied is not large, and the supply pressure with the electromagnetic pressure regulating valve that can supply a small flow rate. adjust. Thus, the supply pressure can be adjusted with high accuracy in a wide range from a small flow rate to a large flow rate only by the opening / closing operation of the electromagnetic on-off valve and the pressure adjustment operation of the electromagnetic pressure regulating valve. Therefore, pressure control in the control device is easy.

  In the above invention, when the differential pressure is equal to or higher than a specified value and the supply pressure is increased, the previous control device is configured to perform the operation even if the differential pressure becomes less than a specified value until the previous supply pressure reaches a target pressure. It is preferable to maintain the open state of the electromagnetic on-off valve.

  According to the above configuration, when the differential pressure exceeds the specified value and a large amount of fuel gas needs to be supplied, for example, at the start of operation, the supply pressure is increased even if the supply pressure is increased and the differential pressure becomes less than the specified value. Until the pressure is reached, the electromagnetic on-off valve is held open. Also, during high load operation, a large amount of fuel gas is consumed and the differential pressure between the supply pressure and the target pressure once exceeds the specified value.Then, the first flow path is opened by the electromagnetic on-off valve, and the differential pressure becomes the specified value. Even when recovering below, the electromagnetic on-off valve is held open until the supply pressure reaches the target pressure. As a result, rapid pressure-up support is possible, and the supply pressure can be quickly raised to the target pressure. Therefore, the responsiveness of the fuel gas supply system is improved.

  In the above invention, the apparatus further includes a supply pressure detector that detects a supply pressure to the fuel gas consumer, and the control device obtains a supply pressure to the fuel gas consumer from a detection result of the supply pressure detector. It is preferable that it is such.

  According to the above configuration, the supply pressure can be feedback-controlled, and the supply pressure can be accurately controlled by the pressure corresponding to the command value.

  In the above invention, it is preferable that a pressure reducing valve is provided on the upstream side of the electromagnetic on-off valve in the first flow path and depressurizes the fuel gas supplied from the tank to a predetermined pressure.

  According to the above configuration, even when the tank pressure is high, the fuel gas of a predetermined pressure can be supplied from the electromagnetic on-off valve after the pressure is reduced to a low pressure by the pressure reducing valve. In contrast, a high-pressure tank can be applied. Further, the pressure of the fuel gas supplied from the electromagnetic on-off valve to the fuel gas consumer is stabilized by using the pressure reducing valve.

  The fuel gas supply system pressure control method of the present invention is a fuel that supplies fuel gas stored in a tank to a fuel gas consumer via a supply passage that branches into the first and second flow paths and then merges into one. A pressure control method for a gas supply system, wherein a differential pressure calculation step of calculating a differential pressure between a supply pressure of a fuel gas of the fuel gas consumer and a target pressure, and when the differential pressure is equal to or greater than a specified value, A pressure increasing step of opening the first flow path by an electromagnetic on-off valve provided in one flow path to lead the fuel gas consumer from the tank to increase the supply pressure, and the differential pressure is less than a specified value In the case of the above, the first flow path is closed by the electromagnetic on-off valve, and the supply pressure is regulated by an electromagnetic pressure regulating valve provided in the second flow path and having a capacity coefficient smaller than that of the electromagnetic on-off valve. And a pressure adjusting step.

  According to the pressure control method of the fuel gas supply system of the present invention, when the pressure difference between the fuel gas supply pressure of the fuel gas consumer and the target pressure is equal to or higher than a specified value, an electromagnetic method is used to bring the supply pressure closer to the target pressure. By opening the first flow path by the on-off valve, a large flow rate of fuel gas is supplied to the fuel gas consumer to greatly increase the supply pressure. In addition, when the differential pressure is less than the specified value, the control device does not require a large amount of flow to be supplied. Therefore, the control device opens the first flow path with an electromagnetic on-off valve and supplies it with an electromagnetic pressure regulating valve that can supply a small flow rate. Adjust pressure. Thus, the supply pressure can be adjusted to the target pressure with high accuracy in a wide range from a small flow rate to a large flow rate only by the opening / closing operation of the electromagnetic on-off valve and the pressure adjustment operation of the electromagnetic pressure regulating valve. Therefore, pressure control in the control device is easy.

  In the present invention, there is provided a valve-opening holding step for holding the open state of the electromagnetic on-off valve even if the differential pressure becomes less than a specified value until the supply pressure boosted by the pressure-boosting step reaches the target pressure. And it is preferable that the said pressure regulation process is performed after the said valve-opening holding process.

  According to the above configuration, when the differential pressure exceeds the specified value and a large amount of fuel gas needs to be supplied, for example, at the start of operation, the first flow path is opened by the electromagnetic on-off valve, and the supply pressure and the target pressure are reduced. Even when the differential pressure becomes less than the specified value, the electromagnetic on-off valve is held open until the supply pressure reaches the target pressure. Also, for example, during high-load operation, a large amount of fuel gas is consumed, and the differential pressure between the supply pressure and the target pressure once exceeds the specified value. Even when recovering below the specified value, the electromagnetic on-off valve is held open until the supply pressure reaches the target pressure. As a result, rapid pressure-up support is possible, and the supply pressure can be quickly raised to the target pressure. Therefore, the responsiveness of the fuel gas supply system is improved.

  According to the present invention, the supply pressure to the fuel gas consumer can be controlled with high accuracy in a wide range from a small flow rate to a large flow rate without performing complicated pressure control and with a simple system configuration.

1 is a hydraulic circuit diagram showing a configuration of a fuel gas supply system according to an embodiment of the present invention. It is sectional drawing which shows the electromagnetic pressure regulation valve with which the fuel gas supply system of FIG. 1 is equipped. It is a flowchart which shows the procedure at the time of supplying fuel gas by the fuel gas supply system of FIG. (A) target pressure when supplying fuel gas according to the target pressure input by the fuel gas supply system of FIG. 1, (b) current supplied to the electromagnetic pressure regulating valve, (c) to the electromagnetic on-off valve It is a graph shown about the time-dependent change of the voltage supplied, (d) the flow volume of each flow path, and (e) supply pressure. It is a flowchart which shows the procedure at the time of supplying fuel gas by another supply method with the fuel gas supply system of FIG.

  Hereinafter, a fuel gas supply system (hereinafter also simply referred to as “fuel gas supply system”) 1 according to an embodiment of the present invention will be described with reference to the drawings described above. The fuel gas supply system 1 described below is only one embodiment of the present invention, and the present invention is not limited to the embodiment, and can be added, deleted, and changed without departing from the spirit of the invention. is there.

  A vehicle such as a compressed natural gas vehicle or a hydrogen gas vehicle has a gas engine, and a driving force is obtained by burning fuel gas (compressed natural gas (CNG), hydrogen gas, etc.) in the gas engine. The drive wheels are moved. The fuel cell automobile has a fuel cell stack. The fuel cell stack consumes fuel gas to generate electric power, and the generated electric power is supplied to a motor to generate driving force. A fuel gas consumer 2 that consumes fuel gas and generates driving force, such as a gas engine or a fuel cell stack, is connected to a high-pressure tank 3 via a fuel gas supply system 1. The high-pressure tank 3 can store a high-pressure fuel gas of 35 to 70 MPa or more, for example. The fuel gas supply system 1 supplies the fuel gas stored in the high-pressure tank 3 to the fuel gas consumer 2. Below, the structure of the fuel gas supply system 1 is demonstrated.

<Fuel gas supply system>
The fuel gas supply system 1 adjusts the amount of fuel gas supplied to the fuel gas consumer 2 in accordance with command values from input means (not shown) such as an accelerator pedal and a throttle grip. The fuel gas supply system 1 includes a supply passage 4, a pressure reducing valve 5, an electromagnetic on-off valve 6, an electromagnetic pressure regulating valve 7, a pressure sensor 8, and a control device 9. The supply passage 4 is a passage through which fuel gas flows, and is connected to the high-pressure tank 3 at one end and the fuel gas consumer 2 at the other end. Further, the supply passage 4 is branched into a first flow path 11 and a second flow path 12 in the middle. The first flow path 11 is provided with a pressure reducing valve 5 and an electromagnetic on-off valve 6, and the second flow path 12 is provided with an electromagnetic pressure regulating valve 7. In addition, the first flow path 11 and the second flow path 12 are merged at a merge point 13 via an electromagnetic on-off valve 6 and an electromagnetic pressure regulating valve 7 to form one merge flow path 14 and fuel. It is connected to the gas consumer 2.

  The pressure reducing valve 5 is a mechanical pressure reducing valve, and the primary side is connected to the high pressure tank 3. The pressure reducing valve 5 depressurizes the high-pressure fuel gas flowing out from the high-pressure tank 3 to a set pressure, specifically, a constant pressure that is equal to or lower than the allowable maximum pressure of the fuel gas consumer 2 and discharges it to the secondary side (downstream). It is like that. An electromagnetic on-off valve 6 is provided on the secondary side of the pressure reducing valve 5. The electromagnetic on-off valve 6 is a so-called electromagnetic on-off valve, and opens and closes the first flow path 11 in accordance with an open / close command input from a control device 9 described later.

  On the other hand, the electromagnetic pressure regulating valve 7 is provided in the second flow path 12 in parallel with the electromagnetic on-off valve 6, and the primary side is connected to the high-pressure tank 3. The electromagnetic pressure regulating valve 7 regulates the high pressure fuel gas flowing out from the high pressure tank 3 to a low pressure corresponding to the current flowing therethrough and outputs it to the secondary side (downstream side). The electromagnetic pressure regulating valve 7 has a capacity coefficient, specifically, a Cv value smaller than that of the electromagnetic on-off valve 6, and is configured to have a smaller flow rate that can be discharged than the electromagnetic on-off valve 6. The Cv value of the electromagnetic pressure regulating valve 7 is set to 50% or less of the Cv value of the electromagnetic on-off valve 6.

  The two flow paths 11 and 12 in which the three valves 5 to 7 are configured as described above are connected at the junction 13 on the downstream side of the three valves 5 to 7, and the downstream side thereof. The pressure sensor 8 is provided in the merging flow path 14. The pressure sensor 8 detects the gas pressure of the fuel gas in the merging flow path 14, that is, the supply pressure supplied to the fuel gas consumer 2. The pressure sensor 8 is electrically connected to the control device 9, and the detection result of the pressure sensor 8 is transmitted to the control device 9.

The control device 9 is connected to an electronic arithmetic circuit (hereinafter referred to as ECU) (not shown) and a pressure sensor 8. The control device 9 receives a target pressure with respect to the supply pressure supplied to the fuel gas consumer 2. Based on the pressure difference between the pressure detected by the pressure sensor 8 and the target pressure, the control device 9 gives an opening / closing command to the electromagnetic on-off valve 6 and supplies a current to the electromagnetic pressure regulating valve 7 to generate the secondary pressure p. ₂ is adjusted.

  More specifically, when the pressure difference between the detected pressure of the pressure sensor 8 and the target pressure is equal to or greater than a specified value, the control device 9 opens the first flow path 11 with respect to the electromagnetic on-off valve 6. When the differential pressure between the target pressure and the detected pressure is less than the specified value, a closing command for closing the first flow path 11 is transmitted to the electromagnetic on-off valve 6. Further, the control device 9 adjusts the current flowing through the electromagnetic pressure regulating valve 7 based on the differential pressure between the target pressure and the detected pressure so that the supply pressure becomes the target pressure, that is, the current flowing through the electromagnetic pressure regulating valve 7. Feedback control is provided.

<Electromagnetic pressure regulating valve>
The electromagnetic pressure regulating valve 7 is a valve that can depressurize the high-pressure fuel gas stored in the high-pressure tank 3 to a low pressure, and the configuration thereof will be described in detail below. In addition, the concept of directions such as up and down, left and right, and front and rear in the following description is used for convenience of explanation, and the arrangement and direction of the configuration of the electromagnetic pressure regulating valve 7 are limited to that direction. It does not suggest that. Further, the electromagnetic pressure regulating valve 7 described below is only one embodiment of the electromagnetic pressure regulating valve, and is not limited to the form described later, and can be added, deleted, and changed without departing from the spirit of the invention. .

  The electromagnetic pressure regulating valve 7 includes a housing 21 as shown in FIG. In the housing 21, a primary port 21a, a valve body hole 21b, and a secondary port 21c are formed. The primary port 21a is connected to the high-pressure tank 3 (see FIG. 1), and is connected to the valve body hole 21b via a primary side passage 21d formed in the housing 21.

  The valve body hole 21b extends along the axis L1 extending vertically, and has a circular cross section. The valve body hole 21b has a valve space 21e having a diameter larger than that of the remaining portion at an intermediate portion thereof, and the primary side passage 21d is connected to the valve space 21e. Further, the valve element hole 21b is connected to the secondary passage 21f in the secondary region 21g above the valve space 21e. The secondary side passage 21f is formed in the housing 21, and the valve element hole 21b is connected to the secondary port 21c through the secondary side passage 21f. The secondary port 21 c is connected to the fuel gas consumer 2 via the second flow path 12 and the merge flow path 14. Thus, the primary port 21a and the secondary port 21c are connected via the primary side passage 21d, the valve space 21e, the secondary side region 21g, and the secondary side passage 21f, and the primary side passage 21d, the valve space 21e, The secondary side region 21g and the secondary side passage 21f constitute a valve passage 22 that connects the primary port 21a and the secondary port 21c.

  The housing 21 has a seat portion 23. The seat portion 23 is formed so as to surround an opening connecting the secondary side region 21g and the valve space 21e. A valve body 24 is inserted into the valve body hole 21 b of the housing 21 so as to be seated on the seat portion 23. The valve body 24 is disposed along the axis L1 of the valve body hole 21b, and the tip end portion (that is, the upper end portion) 24a is located in the secondary region 21g. The valve body 24 is substantially cylindrical, and has a tapered portion 24b on the distal end portion 24a side. The tapered portion 24b has a tapered shape that tapers upward, and when the valve body 24 is located at the closed position as shown in FIG. 2, the seat 24 is seated and the valve passage 22 is closed. Yes.

  Furthermore, the housing 21 has a seal mounting portion 25 below the valve space 21e. The seal attachment portion 25 is formed on the inner peripheral surface of the housing 21 over the entire circumference in the circumferential direction, and is formed so as to protrude from the valve body hole 21b on the inner peripheral surface. The inner diameter of the seal mounting portion 25 is substantially the same as the hole diameter of the secondary side region 21g and the outer diameter of the valve body 24 (the outer diameter of the portion on the lower end 24d side from the tapered portion 24b). Further, the inner diameter of the housing 21 below the seal mounting portion 25 is slightly larger than the inner diameter of the seal mounting portion 25. Thus, a substantially annular bearing member accommodation space 26 is formed around the lower end side of the valve body 24 between the valve body 24 and the housing 21. A bearing member 27 is accommodated in the bearing member accommodation space 26.

  The bearing member 27 is generally formed in a cylindrical shape, and is configured by, for example, a ball guide, a ball bearing, or a slide bearing. The bearing member 27 is externally mounted on the valve body 24 and interposed between the valve body 24 and the housing 21 to support the valve body 24. Thereby, the valve body 24 can move smoothly in the vertical direction along the axis L1 in the housing 21.

  A high-pressure seal member 28 is provided on the upper side of the bearing member housing space 26 in which the bearing member 27 is arranged in this manner so as to close the space. The high-pressure seal member 28 is attached so as to be fitted into the inner peripheral portion of the seal attachment portion 25, and is disposed so as to contact the outer periphery of the valve body 24. The high-pressure seal member 28 arranged in this way seals the gap between the valve body 24 and the seal attachment portion 25.

  Further, a diaphragm seal 29 is provided below the bearing member accommodating space 26 so as to close the space. The diaphragm seal 29 is a diaphragm formed in a generally annular shape, and is disposed on the outer periphery of the valve body 24. The inner edge portion of the diaphragm seal 29 is attached to the valve body 24, and the outer edge portion is attached to the housing 21. More specifically, the inner edge portion of the diaphragm seal 29 is attached to the valve body 24 by being sandwiched between the lower end 24d of the valve body 24 and the mounting member 24c attached thereto. On the other hand, the outer edge portion of the diaphragm seal 29 is configured so that the housing 21 can be divided into two parts up and down, and is attached to the housing 21 by being sandwiched between these two parts.

Thus, the upper and lower sides of the bearing member 27 are sealed by the two seal members 28 and 29. That is, the bearing member accommodation space 26 is isolated from and separated from other spaces formed in the housing 21 (for example, the valve space 21e and the secondary region 21g). Thereby, since the bearing member 27 is not exposed to the fuel gas, a material that does not have corrosion resistance to the fuel gas can be used for the bearing member, and the choice of the material of the bearing member increases. Further, the bearing member 27 can be grease-lubricated to further smooth the movement of the valve body 24 and improve durability.
The bearing member accommodation space 26 is open to the atmosphere via an atmosphere communication passage 30 formed in the housing 21.

A pressure feedback chamber 31 is formed below the diaphragm seal 29 in the valve body hole 21b. The pressure return chamber 31 is a substantially disk-shaped space surrounded by the bottom of the housing 21 and the diaphragm seal 29. The pressure return chamber 31 faces the lower end 24d side of the valve body 24 (specifically, the attachment member 24c). The pressure feedback chamber 31 is isolated from the bearing member accommodating space 26 by a diaphragm seal 29 and is connected to the secondary side passage 21 f by a pressure equalizing passage 32 formed in the valve body 24. The pressure feedback chamber 31 is connected at all times and the secondary port 21c by pressure equalizing path 32, so that the secondary pressure p ₂ to be guided to the secondary port 21c is guided to the pressure feedback chamber 31 by pressure equalizing path 32 Yes.

  The valve body 24 has a flange 24e. The flange 24e is located on the lower side of the tapered portion 24b, and is formed over the entire circumference in the outer circumferential portion of the valve body 24. The flange 24e protrudes further outward in the radial direction from the tapered portion 24b, and is positioned so as to face the upper end of the seal mounting portion 25. A return spring 33 is arranged between the flange 24e and the upper end of the seal mounting portion 25. The return spring 33 is a so-called compression coil spring, and is externally attached to the valve body 24 in a compressed state, and urges the valve body 24 in the closed position direction (the direction in which the valve body 24 moves toward the closed position). The urged valve body 24 is seated on the seat portion 23 and closes the valve passage 22. An electromagnetic proportional solenoid 34 is provided at the opening end portion (that is, the upper end portion) of the housing 21 so as to apply a force against the urging force of the return spring 33 to the valve body 24.

  The electromagnetic proportional solenoid 34 is screwed and fixed to the outer periphery of the opening end portion of the housing 21. The electromagnetic proportional solenoid 34 has a solenoid coil 35. The solenoid coil 35 is generally formed in a cylindrical shape, and the housing 21 is screwed to the lower end side thereof. The solenoid coil 35 has a substantially cylindrical case 35a in which a bobbin 35b and a coil wire 35c are provided. The bobbin 35b is also formed in a substantially cylindrical shape, and the solenoid coil 35 is configured by winding a coil wire 35c around the bobbin 35b. The coil wire 35 c is electrically connected to the control device 9. A yoke 36 is provided at the lower end side in the solenoid coil 35, and the upper end portion is closed by a cover 37. A movable member 38 is provided between the yoke 36 and the cover 37.

  The movable member 38 is made of a magnetic material, is formed in a substantially cylindrical shape, and is disposed along the axis L1. The outer diameter of the movable member 38 is smaller than the inner diameter of the solenoid coil 35. An annular guide member 39 is interposed between the movable member 38 and the solenoid coil 35. The guide member 39 is made of a nonmagnetic material, and supports the movable member 38 so as to be slidable in the vertical direction along the axis L1. The yoke 36 faces the lower end portion of the movable member 38 in the vertical direction and is positioned in a state of being spaced apart from each other. The yoke 36 is made of a magnetic material and is formed in a generally annular shape. The yoke 36 and the movable member 38 are magnetized by passing a current through the solenoid coil 35, and the yoke 36 attracts the movable member 38.

  A compression coil spring 40 is provided between the upper end portion of the movable member 38 and the cover 37, and the movable member 38 is urged toward the valve body 24 by the compression coil spring 40. A pressing member 41 is provided at the lower end of the movable member 38. The pressing member 41 extends along the axis L <b> 1 and is inserted into the yoke 36. A proximal end portion of the pressing member 41 is fixed to the movable member 38. The distal end of the pressing member 41 is formed in a partial spherical shape, and is in contact with the distal end portion 24 a of the valve body 24. The pressing member 41 is urged by the compression coil spring 40 via the movable member 38, and the tip thereof is pressed against the tip portion 24 a of the valve body 24. Therefore, the pressing member 41 causes the current to flow through the solenoid coil 35 to attract the movable member 38 toward the yoke 36, thereby pressing the valve body 24 in the open position direction with a force corresponding to the current so as to open the valve passage 22. It has become.

The electromagnetic pressure regulating valve 7 configured as described above is guided from the high pressure tank 3 to the valve space 21e by the taper portion 24b of the valve body 24 and the upper surface of the flange 24e (pressure receiving surface P1 corresponding to the first pressure receiving surface). The primary pressure p1 is received in the open position direction, and the primary pressure p1 is received in the closed position direction on the lower surface of the flange 24e (the pressure receiving surface P2 corresponding to the second pressure receiving surface). The pressure-receiving surface P1 is a partial region of the tapered surface, and is a region on the outer side in the radial direction from the secondary region 21g in plan view. In each of the pressure receiving surfaces P1 and P2, the primary pressure p1 acts in a direction opposite to each other and cancels each other. Receiving area of the pressure receiving surface P1, P2 has an inner diameter of the outer diameter _{r 2} of the lower end 24d side of the flange 24e of the valve body 24 and the secondary-side region 21g (i.e., seat diameter _{r 1)} and is substantially have the same diameter So they are almost identical. Therefore, the acting force due to the primary pressure p1 received at the pressure receiving surface P1 and the acting force due to the primary pressure p1 received at the pressure receiving surface P2 cancel each other, and the influence due to the fluctuation of the primary pressure p1 in the valve body 24 is made substantially zero. Can do. The pressure receiving area of the pressure receiving surface P2 may be larger than the pressure receiving area of the pressure receiving surface P1.

Further, electromagnetic pressure regulating valve 7, by receiving the secondary pressure p ₂ flowing secondary side area 21g in the tapered surface of the distal end and the tapered portion 24b of the valve element 24 (pressure receiving surface P3) in the open position direction, the diaphragm seal 29 and secondary pressure p ₂ guided to the pressure feedback chamber 31 at the lower end 24d (pressure receiving surface P4) of the valve body 24 receives the pressure in the closed position. The pressure receiving surface P3 is a region that overlaps the secondary region 21g in plan view. Secondary pressure p ₂ to the pressure receiving in pressure receiving surface P3, P4 is acting in a direction against each other.

Receiving area of the pressure receiving surface P3 is determined in accordance with the sheet size r _1, pressure receiving area of the pressure receiving surface P4 is dependent on the effective diameter r ₃ of the diaphragm seal 29. While the seat diameter r ₁ is substantially the same as the outer diameter r _{2 of the} valve body 24, the effective diameter r ₃ of the diaphragm seal 29 is larger than the seat diameter r ₁ and the outer diameter r _{2 of the} valve body 24. ing. Therefore, the pressure receiving surface P4 has a larger pressure receiving area than the pressure receiving surface P3. Thus, the valve element 24, the action force due to the secondary pressure p ₂ received by the pressure receiving surface P3, P4 is not completely canceled, the action force corresponding to the difference between the pressure receiving areas of each pressure receiving surface P3, P4 is closed Acts in the direction of the position.

  Further, the valve body 24 is not only receiving such an acting force but also urged by the return spring 33 in the closed position direction. Therefore, the electromagnetic pressure regulating valve 7 is configured as a normally closed valve in which the valve body 24 is seated on the seat portion 23 in a state where the current to the solenoid coil 35 is interrupted. The electromagnetic pressure regulating valve 7 configured as described above is used as a shut-off valve. When the detected pressure of the pressure sensor 8 exceeds the allowable pressure, the control device 9 cuts off the current flowing through the solenoid coil 35 and The valve passage 22 is urgently shut off by the pressure regulating valve 7. By such an emergency shutoff, for example, even if unintended high-pressure fuel gas is supplied to the fuel gas consumer 2, the second flow path 12 can be shut off immediately, and the fuel gas consumer 2 is damaged. Can be prevented.

<Operation of electromagnetic pressure regulator>
Hereinafter, the operation of the electromagnetic pressure regulating valve 7 will be described with reference to FIG. First, a current is passed through the solenoid coil 35 in accordance with the differential pressure between the target pressure and the supply pressure received from the ECU (not shown) by the control device 9. Then, an exciting force acts on the movable member 38 and the movable member 38 is attracted toward the yoke 36. Accordingly, the valve body 24 is pushed in the open position direction by the pressing member 41 and is separated from the seat portion 23. Then, the valve passage 22 is opened, and the fuel gas in the valve space 21e led from the high-pressure tank 3 flows to the secondary side region 21g. At this time, the fuel gas flowing from the valve space 21e to the secondary side area 21g is reduced to the secondary pressure p ₂ by the orifice (not shown) formed between the valve body 24 and the seat 23.

The fuel gas of the secondary pressure p ₂ thus reduced in pressure is output from the secondary port 21c through the secondary side passage 21f, and a part of the fuel gas passes through the pressure equalizing passage 32 to the pressure feedback chamber 31. Led. The diaphragm seal 29 receives the secondary pressure p ₂ of the fuel gas guided to the pressure feedback chamber 31. The valve element 24, an excitation force which the movable member 38 is subjected, move with the pressure receiving surface P3, P4 acting force by each receiving secondary pressure p _2, and to a position where the spring forces are balanced in the return spring 33, so that the force is balanced The opening of the valve passage 22 (that is, the opening of the orifice) is adjusted. Therefore, even if the secondary pressure p ₂ fluctuates, the opening degree of the valve passage 22 is adjusted and the secondary pressure p ₂ is maintained at a constant pressure corresponding to the current. That is held at a constant pressure secondary pressure p ₂ is corresponding to the current.

More specifically, for example, when the secondary pressure p ₂ is lower than the constant pressure, the force in the open position direction due to the excitation force is larger than the acting force due to the secondary pressure p ₂ and the force in the closed position direction due to the spring force. The valve body 24 moves in the open position direction so as to be separated from the seat portion 23. Therefore, opening the secondary pressure p ₂ rises spread of the valve passage 22, the action by the secondary pressure p ₂ power, excitation force, and the spring force of the return spring 33 are balanced position, i.e. secondary pressure p ₂ the valve body 24 position to be constant pressure to move the secondary pressure p ₂ is returned to the constant pressure. Thus, electromagnetic pressure regulating valve 7 may be secondary pressure p ₂ controls the opening degree of the valve passage 22 accordingly be varied, pressure regulates the secondary pressure p ₂ to the target pressure. Therefore, the electromagnetic pressure regulating valve 7 has high pressure controllability, and can modulate the high-pressure fuel gas to a lower pressure more accurately. In the case the secondary pressure p ₂ is higher than the predetermined pressure, as opposed to the movement to above, the valve body 24 as the secondary pressure p ₂ is returned to the predetermined pressure is moved in the closing direction.

In the electromagnetic pressure regulating valve 7 operating in this way, the valve body 24 is supported by the bearing member 27 and can move smoothly. Therefore, even if the secondary pressure p ₂ fluctuates, the valve body 24 moves quickly to return the secondary pressure p ₂ to the constant pressure, so that the followability of the electromagnetic pressure regulating valve 7 to the constant pressure can be improved. it can. Thus, it is possible to reduce the variation range of the secondary pressure p _2.

<Fuel gas supply method>
Hereinafter, a fuel gas supply method in the fuel gas supply system 1 will be described with reference to the flowchart of FIG. 3 and the graph of FIG. 4. In the fuel gas supply system 1, as shown at time t1 in FIG. 4A, when the target pressure is input to the control device 9, the fuel gas supply process is started, and the process proceeds to step S1. In step S1, which is a differential pressure calculation step, the differential pressure between the supply pressure detected by the pressure sensor 8 and the target pressure is calculated. When the differential pressure is calculated, the process proceeds to step S2.

  In step S2, which is a target pressure determination step, the control device 9 determines whether or not the differential pressure calculated in step S1 is equal to or greater than a predetermined value. If it is determined that the value is equal to or greater than the specified value, the process proceeds to step S3. In step S3, which is a step-up process, the control device 9 causes the current to flow through the electromagnetic on-off valve 6 to open the first flow path 11 (see time t1 in FIG. 4C). As a result, the fuel gas decompressed by the decompression valve 5 is guided to the fuel gas consumer 2 through the electromagnetic on-off valve 6. Since the Cv value of the electromagnetic on-off valve 6 is larger than that of the electromagnetic pressure regulating valve 7, a large flow rate of fuel gas is led to the fuel gas consumer 2 and the supply pressure rises quickly. When a voltage is applied to the electromagnetic on-off valve 6 in step S3 to open the first flow path 11, the process proceeds to step S4.

In step S4, which is a pressure regulating process, the controller 9 applies the voltage to the electromagnetic on-off valve 6 and simultaneously causes a current to flow through the electromagnetic pressure regulating valve 7 to operate the electromagnetic pressure regulating valve 7 (FIG. 4B). Time t1). As a result, a small flow amount of fuel gas is guided from the second flow path 12 to the fuel gas consumer 2. At this time, the control device 9 adjusts the opening of the valve passage 22 by controlling the current flowing through the electromagnetic pressure regulating valve 7 in accordance with the differential pressure between the supply pressure detected by the pressure sensor 8 and the target pressure. pressure regulates the secondary pressure _{p 2} so as to make the pressure to the target pressure (see time t2~t3 in Figure 4 (b)). That is, the control device 9 performs feedback control of the electromagnetic pressure regulating valve 7 so that the supply pressure becomes the target pressure.

  In this way, by performing feedback control of the supply pressure based on the detection result of the pressure sensor 8, the supply pressure can be more accurately controlled to the target pressure. When the control device 9 starts the feedback control, the process returns to step S1, and the control device 9 calculates the differential pressure again. If it is determined that the differential pressure calculated in step S2 is greater than or equal to the specified value, the above control is repeated (see times t2 to t3 in FIGS. 4B to 4E), and the differential pressure is the specified value. If it is determined that the value is less than the value, the process proceeds to step S5.

  In step S5, which is a valve closing process, the control device 9 stops applying the voltage to the electromagnetic on-off valve 6, closes the electromagnetic on-off valve 6, and closes the first flow path 11 (FIG. 4C). (See time t3). When the first flow path 11 is closed, the process proceeds to step S4. In step S4, the control device 9 performs feedback control on the current flowing through the electromagnetic pressure regulating valve 7 in accordance with the differential pressure between the supply pressure detected by the pressure sensor 8 and the target pressure (FIG. 4 (a), ( b) and (e) times t3 to t4). Then, the process returns to step S1.

  Next, a case where the target pressure is changed will be described. When the target pressure is changed and becomes lower (see time t4 in FIG. 4A), the target pressure becomes lower than the supply pressure, so that the control device 9 determines in step S2 that the differential pressure is less than the specified value. The process proceeds to S5. In step S5, the control device 9 maintains the closed state of the electromagnetic on-off valve 6 and proceeds to step 4. In step S4, the control device 9 feedback-controls the current flowing through the electromagnetic pressure regulating valve 7 based on the differential pressure between the supply pressure detected by the pressure sensor 8 and the target pressure, thereby reducing the supply pressure (FIG. 4B). ) And (c) (see time t4).

  When the target pressure is changed and becomes higher (see time t5), the control device 9 determines whether or not the differential pressure is equal to or higher than a specified value in step S2. Here, the control device 9 determines that the differential pressure is less than the specified value, and proceeds to step S5. In step S5, the control device 9 maintains the closed state of the electromagnetic on-off valve 6 in the same manner as when the target pressure is low, and the control device 9 is electromagnetic in step 4 so that the supply pressure becomes the target pressure. The current flowing through the pressure regulating valve 7 is feedback controlled (see time t5 in FIGS. 4B and 4C).

  On the other hand, when the target pressure is changed significantly and the control device 9 determines in step S2 that the differential pressure is equal to or greater than the specified value, the process proceeds to step S3 (see time t6 in FIGS. 4A to 4E). . In step S <b> 3, the control device 9 applies a voltage to the electromagnetic on-off valve 6 to open the first flow path 11. As a result, a large amount of fuel gas is supplied from the first dew 11 to the fuel gas consumer 2, and the supply pressure increases. On the other hand, the control device 9 performs feedback control of the electromagnetic pressure regulating valve 7 again so that the supply pressure becomes the target pressure in step S4. Then, returning to step S1, the differential pressure is calculated, and if it is determined in step S2 that the differential pressure is less than the specified value, the control device 9 closes the electromagnetic on-off valve 6 in step S5. The first flow path 11 is closed, and the supply pressure is adjusted to the target pressure by the electromagnetic pressure regulating valve 7 (see time t7 in FIGS. 4A and 4C).

  As described above, in the fuel gas supply system 1, the electromagnetic pressure control valve 7 and the electromagnetic on-off valve 6 are operated to control the supply pressure with high accuracy according to the target pressure that fluctuates in a wide range from a small flow rate to a large flow rate. can do. Therefore, the pressure control in the control device 9 is easy even when the target pressure fluctuates. In addition, by reducing the Cv value of the electromagnetic pressure regulating valve 7 relative to the electromagnetic on / off valve 6, the configuration of the electromagnetic pressure regulating valve 7 is more complicated and has a larger number of parts than the electromagnetic pressure regulating valve 6. Can be planned. Thereby, the manufacturing cost of the electromagnetic pressure regulating valve 7 can be reduced, and as a result, the manufacturing cost of the fuel gas supply system 1 can be reduced.

  Furthermore, in the fuel gas supply system 1, the pressure reducing valve 5 is provided on the upstream side of the electromagnetic on-off valve 6, so that a predetermined pressure is supplied from the electromagnetic on-off valve 6 regardless of the remaining amount of fuel gas in the high-pressure tank 3. Fuel gas can be supplied. Thereby, the high-pressure tank 3 can also be applied to the low-pressure fuel gas consumer 2. Further, since the pressure of the fuel gas supplied from the electromagnetic on-off valve 6 to the fuel gas consumer 2 is stabilized by using the pressure reducing valve 5, the pressure regulation operation of the supply pressure by the electromagnetic pressure regulating valve 7 is stabilized. Moreover, since the electromagnetic pressure regulating valve 7 can depressurize the high-pressure fuel gas to a low pressure, it is not necessary to provide a pressure reducing valve in the second flow path 12. Therefore, the number of valves interposed in the second flow path 12 can be reduced, and the pressure loss of the second flow path 12 can be reduced. Thereby, the pressure loss of the fuel gas supply system 1 can be reduced, and the use limit pressure in the high-pressure tank 3 can be lowered.

<Another supply method of fuel gas>
Hereinafter, another fuel gas supply method in the fuel gas supply system 1 will be described with reference to the flowchart of FIG. Another fuel gas supply method described below is similar in procedure to the above-described supply method. Therefore, only the points in which the procedure is different will be described, and the same points are denoted by the same reference numerals and the description thereof is omitted. In another supply method, when it is determined in step S2 that the differential pressure is less than a specified value, the process proceeds to step S11.

  In step S11 which is an open / close state determination step, the control device 9 determines the open / close state based on the voltage applied to the electromagnetic open / close valve 6. When the electromagnetic on-off valve 6 is in an open state, that is, when the differential pressure shifts from a specified value to a specified value, the process proceeds to step S12. In step S12 which is a target pressure achievement determination step, the control device 9 determines whether or not the supply pressure detected by the pressure sensor 8 has reached the target pressure, that is, whether or not the supply pressure is equal to or higher than the target pressure. When supply pressure is less than target pressure, it transfers to step S4 and the control apparatus 9 hold | maintains the open state of the electromagnetic on-off valve 6. FIG. When the control device 9 holds the open state of the electromagnetic on-off valve 6 and it is determined in step S12 that the supply pressure is equal to or higher than the target pressure, the process proceeds to step S5, and in step S5, the control device 9 The first flow path 11 is closed by the on-off valve 6. In addition, the valve opening holding process is comprised by three processes, the opening / closing state determination process, the target pressure achievement determination process, and the valve closing process.

  After the electromagnetic on-off valve 6 is closed in this way, if the control device 9 determines in step S11 that the electromagnetic on-off valve 6 is in the closed state, the process proceeds to step S4. And it returns to step S1 from step S4, and it adjusts so that supply pressure may turn into target pressure only with the electromagnetic pressure regulating valve 7 until it determines with the said differential pressure being more than a regulation value by step S2. If it is determined in step S2 that the differential pressure is greater than or equal to the specified value, the electromagnetic on-off valve 6 is opened again, and a large flow of fuel gas is supplied.

  According to such another fuel gas supply method, when the differential pressure exceeds a specified value and a large amount of fuel gas needs to be supplied, for example, at the start of operation, the supply pressure is increased and the differential pressure becomes the specified value. Even if it becomes less than this, the electromagnetic on-off valve 6 is held open until the supply pressure reaches the target pressure. Also, during high load operation, a large amount of fuel gas is consumed and the differential pressure between the supply pressure and the target pressure once exceeds the specified value.Then, the first flow path is opened by the electromagnetic on-off valve, and the differential pressure becomes the specified value. Even when recovering below, the electromagnetic on-off valve is held open until the supply pressure reaches the target pressure. As a result, rapid pressure-up support is possible, and the supply pressure can be quickly raised to the target pressure. Therefore, the responsiveness of the fuel gas supply system is improved.

  Other fuel gas supply methods have the same effects as the fuel gas supply method described above.

[Other embodiments]
In the fuel gas supply system 1 of the present embodiment, only one electromagnetic on-off valve 6 is provided, but two or more electromagnetic on-off valves 6 may be provided. For example, the supply passage 4 may be branched into three or more flow paths, an electromagnetic pressure regulating valve may be interposed in one flow path, and one electromagnetic open / close valve may be interposed in each of the other flow paths. In this case, it is preferable that the Cv values of all the electromagnetic on-off valves are configured to be different so that the electromagnetic on-off valves that are operated in accordance with the required flow rate in the fuel gas consumer 2 are changed. The pressure reducing valve 5 is provided in parallel with the electromagnetic pressure regulating valve 7, but may be provided in series with the electromagnetic pressure regulating valve 7. That is, the pressure reducing valve 5 may be provided on the high-pressure tank 3 side from the branch point where the supply passage 4 branches into the two flow paths 11 and 12.

  In addition, when the differential pressure exceeds a specified value, the control device 9 adjusts the supply pressure by the electromagnetic pressure regulating valve 7 while opening the first flow path 11 by the electromagnetic on-off valve 6. The electromagnetic pressure regulating valve 7 may be stopped and only a predetermined pressure may be supplied from the electromagnetic opening / closing valve 6. Further, the control device 9 feedback-controls the opening degree of the electromagnetic pressure regulating valve 7 based on the detection result of the pressure sensor 8, and the target pressure immediately before the control is assumed to be the supply pressure, and the supply pressure is received. The operation of the electromagnetic pressure regulating valve 7 may be controlled based on the differential pressure from the target pressure. In this embodiment, the Cv value is applied as the capacity coefficient. However, the capacity coefficient is a coefficient indicating the volume or weight of the fluid passing through the valve per unit time when the valve is fully opened. It may be an Av value.

  In this embodiment, the push-type electromagnetic pressure regulating valve 7 is used, but a pull-type electromagnetic pressure regulating valve 7 may be used. Moreover, although the electromagnetic proportional solenoid 34 is used as a drive device, a force motor or a piezoelectric element may be used.

DESCRIPTION OF SYMBOLS 1 Fuel gas supply system 2 Fuel gas consumer 3 High pressure tank 4 Supply passage 5 Pressure reducing valve 6 Electromagnetic on-off valve 7 Electromagnetic pressure regulating valve 8 Pressure sensor 9 Control device 11 1st flow path 12 2nd flow path 14 Merge flow path

Claims (7)

A fuel gas supply system that supplies fuel gas stored in a tank to a fuel gas consumer via a supply passage that merges into one after branching into first and second flow paths,
An electromagnetic on-off valve provided in the first flow path for opening and closing between the tank and the fuel gas consumer;
An electromagnetic pressure regulating valve that is provided in the second flow path and regulates fuel gas led from the tank to the fuel gas consumer;
A control device for controlling the opening / closing operation of the electromagnetic on-off valve and the pressure adjusting operation of the electromagnetic pressure regulating valve ;
The electromagnetic pressure regulating valve has a smaller capacity coefficient than the electromagnetic on-off valve,
When the differential pressure between the fuel gas supply pressure of the fuel gas consumer and the target pressure is equal to or greater than a specified value, the control device opens the first flow path by the electromagnetic on-off valve to consume the fuel gas. If the pressure difference is less than a specified value, the first flow path is closed by the electromagnetic on-off valve, and the supply pressure of the fuel gas consumer is regulated by the electromagnetic pressure regulating valve. A fuel gas supply system. The fuel gas supply system according to claim 1, wherein the capacity coefficient is a Cv value, and the electromagnetic pressure regulating valve has a Cv value of 50% or less of a Cv value of the electromagnetic on-off valve. The control device, when the differential pressure is be more than a specified value to boost the supply pressure, even the differential pressure to said supply pressure reaches the target pressure becomes less than the specified value of the said electromagnetic on-off valve The fuel gas supply system according to claim 2 , wherein the fuel gas supply system is configured to maintain an open state. A supply pressure detector for detecting a supply pressure of the fuel gas consumer;
The fuel gas supply system according to any one of claims 1 to 3 , wherein the control device obtains a supply pressure of the fuel gas consumer from a detection result of the supply pressure detector. The fuel according to any one of claims 1 to 4 , further comprising a pressure reducing valve provided on the upstream side of the electromagnetic on-off valve in the first flow path to reduce the fuel gas supplied from the tank to a predetermined pressure. Gas supply system. A pressure control method for a fuel gas supply system that supplies fuel gas stored in a tank to a fuel gas consumer via a supply passage that merges into one after branching to a first and second flow path,
A differential pressure calculating step of calculating a differential pressure between a supply pressure of the fuel gas of the fuel gas consumer and a target pressure;
When the differential pressure is greater than or equal to a specified value, the first flow path is opened by an electromagnetic on-off valve provided in the first flow path, leading from the tank to the fuel gas consumer, and the supply pressure is increased. A boosting step to
When the differential pressure is less than a specified value, an electromagnetic pressure regulating valve that closes the first flow path by the electromagnetic open / close valve, is provided in the second flow path, and has a smaller capacity coefficient than the electromagnetic open / close valve. A pressure control method for a fuel gas supply system, comprising: a pressure adjusting step for adjusting the supply pressure. A valve opening holding step of holding the open state of the electromagnetic on-off valve even if the differential pressure becomes less than a specified value until the supply pressure increased in the pressure increasing step reaches the target pressure;
The pressure control method for a fuel gas supply system according to claim 6 , wherein the pressure adjusting step is executed after the valve opening holding step.

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