JP6056645B2 - Pressure control valve - Google Patents

Description

  The present invention relates to a pressure control valve.

  A pressure control valve for compressed natural gas that reduces the pressure of gaseous fuel, for example, compressed natural gas, supplied to an internal combustion engine (hereinafter referred to as “engine”) from a high pressure in the fuel tank to a low pressure that can be injected by the injector for the gaseous fuel. It has been known. Patent Document 1 describes a regulator for compressed natural gas having a valve seat made of rubber.

Japanese Patent No. 3594507

  However, in the compressed natural gas regulator described in Patent Document 1, the valve seat is fixed at a predetermined position by a screw member that is screwed to the valve housing while being in contact with the valve seat. Since the fixed axial force between the valve housing and the screw member acts on the valve seat, the valve seat formed of rubber may be plastically deformed due to long-term use, and the fixed axial force of the screw member may be lost. For this reason, the position of the valve seat with respect to the valve housing becomes unstable, and the airtightness is lowered.

  An object of the present invention is to provide a pressure control valve that prevents a decrease in hermeticity.

The present invention provides a first chamber formed of an elastic material, a valve housing having a first chamber into which fluid from the outside flows in, a second chamber formed so as to be able to communicate with the first chamber and through which the fluid in the first chamber flows. Between the first chamber and the second chamber, and a valve seat having an outer diameter larger than the inner diameter of the first chamber and a valve seat that is formed of metal and supports the valve seat on the first chamber side. A pressure control valve comprising: a valve seat support member provided; and a valve body provided so as to be reciprocally movable with respect to the valve seat and shutting off or communicating with the first chamber and the second chamber when contacting or separating from the valve seat. The end surface of the valve seat support member on the first chamber side and the inner wall surface of the valve housing on the valve seat support member side are in contact with each other while the end surface of the valve seat on the first chamber side and the inner surface of the valve housing on the valve seat side are in contact with each other. A gap is formed between the wall surfaces.

  In the pressure control valve of the present invention, the valve seat support member that supports the valve seat formed of an elastic material is formed of metal. The valve seat support member is provided in the valve housing such that the end surface on the first chamber side contacts the inner wall surface of the valve housing on the valve seat support member side. At this time, the valve seat supported on the first chamber side of the valve seat support member forms a gap with the inner wall surface on the valve seat side of the valve housing. As a result, the acting force acting between the valve seat support member and the valve housing so that the valve seat support member is fixed at a predetermined position causes the end face of the valve seat support member on the first chamber side and the valve seat of the valve housing. While acting between the inner wall surface on the support member side, it does not act between the end surface on the first chamber side of the valve seat and the inner wall surface on the valve seat side of the valve housing. Thereby, the valve seat formed of the elastic material is positioned between the first chamber and the second chamber without being plastically deformed by the acting force, and between the first chamber and the second chamber over a long period of time. Airtightness can be reliably maintained.

It is a schematic diagram which shows schematic structure of the compressed natural gas supply system using the pressure control valve by 1st Embodiment of this invention. It is sectional drawing of the pressure control valve by 1st Embodiment of this invention. It is the III section enlarged view of FIG.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(One embodiment)
First, a schematic configuration of a compressed natural gas supply system using a “pressure control valve” according to an embodiment will be described with reference to FIG. The compressed natural gas supply system 5 is mounted on a vehicle including an engine that uses compressed natural gas as fuel. The compressed natural gas supply system 5 includes a gas filling port 10, a fuel tank 12, a gas fuel pressure control valve 1 as a “pressure control valve”, a gas fuel injector 17, an ECU 9, and the like.

  High-pressure gaseous fuel supplied from the outside through the gas filling port 10 is stored in the fuel tank 12 through the supply pipe 6. The gas filling port 10 has a backflow prevention function, and functions so that the gaseous fuel supplied from the gas filling port 10 does not flow back to the outside. The supply pipe 6 is provided with a gas filling valve 11.

The fuel tank 12 is provided with a fuel tank valve 13. The fuel tank valve 13 has a backflow prevention function from the fuel tank 12 to the gas filling port 10, an overflow prevention function that blocks the flow of the gaseous fuel from the fuel tank 12 when a specified amount or more of gaseous fuel flows through the supply pipe 7, In addition, a pressure-preventing safety function that prevents the fuel tank 12 from bursting by releasing the pressure in the fuel tank 12 to the outside when the pressure in the fuel tank 12 rises is provided.
The fuel tank valve 13 is connected to the gaseous fuel pressure control valve 1 via the supply pipe 7. The supply pipe 7 is provided with a main valve 14 that can manually shut off the supply pipe 7 and a main stop valve 15 that can electrically shut off the supply pipe 7.

  The gaseous fuel pressure control valve 1 reduces the pressure of the gaseous fuel supplied via the supply pipe 7 to a pressure that can be supplied to the gaseous fuel injector 17. For example, the pressure control valve 1 for gaseous fuel reduces the pressure of 0.2 MPa to 0.65 MPa, which is a pressure capable of supplying the gaseous fuel of 20 MPa in the fuel tank 12 to the injector 17 for gaseous fuel. The pressure control valve 1 for gaseous fuel can change the pressure of the gaseous fuel supplied to the injector 17 for gaseous fuel in advance within a desired pressure range. The detailed structure of the gas fuel pressure control valve 1 will be described later.

  The gaseous fuel decompressed by the gaseous fuel pressure control valve 1 has its oil removed by the oil filter 16 and is supplied to the gaseous fuel injector 17 through the supply pipe 8. The gaseous fuel injector 17 injects gaseous fuel into the intake pipe 18 in accordance with an instruction from the electrically connected ECU 9. The gaseous fuel injector 17 is provided with a temperature sensor and a pressure sensor (not shown). Information on the temperature and pressure of the gaseous fuel detected by the temperature sensor and the pressure sensor is output to the ECU 9. The ECU 9 outputs a signal for shutting off the supply pipe 7 to the main stop valve 15 when the pressure of the gaseous fuel supplied to the gaseous fuel injector 17 exceeds a specified value.

The gaseous fuel injected into the intake pipe 18 is mixed with air introduced from the atmosphere and introduced into the cylinder 191 from the intake port of the engine 19 to which the intake pipe 18 is connected. In the engine 19, rotational torque is generated by compression of the gaseous fuel and air mixed gas due to the rise of the piston 192 and explosion of the mixed gas. 1 indicates the flow of air introduced into the engine 19 and exhausted exhaust gas after combustion.
In this way, the compressed natural gas supply system 5 depressurizes the high-pressure gaseous fuel to a low pressure that can be supplied to the gaseous fuel injector 17 by the gaseous fuel pressure control valve 1, and the decompressed gaseous fuel is injected into the gaseous fuel injector. 17 is supplied to the engine 19.

  Next, the detailed structure of the pressure control valve 1 for gaseous fuel is demonstrated based on FIG. 2 and 3 indicate the direction in which the gaseous fuel flows in the gaseous fuel pressure control valve 1.

  The pressure control valve 1 for gaseous fuel includes a first valve housing 31, a second valve housing 32, a lead-out passage forming member 34, a valve body 36, a valve seat 38, a pressure receiving member 42, and the like.

  The first valve housing 31 includes a cylindrical portion 311 and a flange portion 312. The cylinder part 311 and the flange part 312 are integrally formed from metal. The first valve housing 31 corresponds to a “valve housing” described in the claims.

The cylindrical portion 311 is formed in a substantially cylindrical shape, and includes an introduction passage 313, a high pressure chamber 314, and a storage chamber 315.
The introduction passage 313 is formed substantially perpendicular to the central axis of the gaseous fuel pressure control valve 1 at the side of the cylindrical portion 311. The introduction passage 313 communicates the inside of the supply pipe 7 with the high pressure chamber 314.
The high-pressure chamber 314 is formed in a substantially cylindrical shape at the approximate center of the cylindrical portion 311. The high-pressure chamber 314 as the “first chamber” is located downstream of the introduction passage 313 with respect to the fuel tank 12, and high-pressure gaseous fuel flowing through the introduction passage 313 flows into the high-pressure chamber 314.
The accommodation chamber 315 is formed at one end of the cylindrical portion 311 and accommodates a shaft support member 371 and a lid member 372 described later. The storage chamber 315 communicates with the high pressure chamber 314. In addition, the storage chamber 315 communicates with the inside of the flange portion 312 via a communication path 316 formed in the radially outward direction of the high-pressure chamber 314.

The flange portion 312 is provided at an end portion of the cylindrical portion 311 opposite to the end portion where the accommodation chamber 315 is formed. The flange portion 312 is formed so that the outer diameter is larger than the outer diameter of the cylindrical portion 311. The flange portion 312 includes an intermediate chamber 317, a low pressure chamber 318, and a communication path 319.
The intermediate chamber 317 is located on the opposite side to the storage chamber 315 with respect to the high pressure chamber 314 and is formed to communicate with the high pressure chamber 314.
The low pressure chamber 318 is located on the opposite side of the intermediate chamber 317 from the high pressure chamber 314 and is formed to communicate with the intermediate chamber 317. The inner diameter of the low pressure chamber 318 as the “second chamber” is formed to be larger than the inner diameter of the intermediate chamber 317.
The communication path 319 is formed so as to extend outward from the low pressure chamber 318. The communication passage 319 communicates with the lead-out passage 341 formed by the lead-out passage forming member 34 provided on the radially outer side of the flange portion 312.

  The outlet passage forming member 34 is connected to the gaseous fuel injector 23 through the supply pipe 8. As a result, the low pressure chamber 318 of the flange portion 312 communicates with the inside of the gaseous fuel injector 23 via the communication passage 319 and the outlet passage 341.

  The second valve housing 32 includes a cylinder part 321 and a flange part 322. The cylinder part 321 and the flange part 322 are integrally formed from metal. The second valve housing 32 is connected to the flange portion 312 of the first valve housing 31. The second valve housing 32 corresponds to a “valve housing” recited in the claims.

  The cylindrical portion 321 is formed in a substantially bottomed cylindrical shape, and houses the first spring 44 therein. A through-hole 323 that communicates the inside and the outside of the cylinder part 321 is formed in the bottom wall of the cylinder part 321. A needle 441 described later is inserted through the through hole 323. Further, a through hole 324 that communicates the inside and the outside of the cylinder portion 321 is formed on the side wall of the cylinder portion 321. The through hole 324 communicates with the inside of the intake pipe 18 via a communication path 326 formed by the communication path forming member 325.

  The flange portion 322 is provided at the end of the cylindrical portion 321 on the opening side. The flange portion 322 is formed such that its outer diameter is larger than the outer diameter of the cylindrical portion 321.

  The valve body 36 is a substantially rod-shaped metal member accommodated in the first valve housing 31 so as to be reciprocally movable with respect to the first valve housing 31 and the second valve housing 32. The valve body 36 includes a first shaft portion 361, a contact portion 362, a second shaft portion 363, and a restriction portion 364. The first shaft portion 361, the contact portion 362, the second shaft portion 363, and the restriction portion 364 are integrally formed.

  The first shaft portion 361 is formed in a rod shape and is located in the high pressure chamber 314 and the storage chamber 315. The first shaft portion 361 is supported while sliding on a shaft support member 371 housed in the housing chamber 315. One end of the first shaft portion 361 protrudes from the shaft support member 371 to the outside of the first valve housing 31 and is positioned in an adjustment chamber 373 formed between the shaft support member 371 and the lid member 372. The adjustment chamber 373 communicates with the low pressure chamber 318 via the communication path 316 and the intermediate chamber 317. Between the first shaft portion 361 and the shaft support member 371, and between the shaft support member 371 and the first valve housing 31, a seal member 374 that maintains an airtightness between the adjustment chamber 373 and the high pressure chamber 314, 375 is provided.

  The contact portion 362 is provided so as to be connected to the other end portion of the first shaft portion 361. The contact portion 362 has a substantially trapezoidal cross-sectional shape in a plane including the central axis of the valve body 36, and is formed so that the maximum outer diameter is larger than the outer diameter of the first shaft portion 361. The contact portion 362 has a tapered surface 365 whose outer diameter decreases from the high pressure chamber 314 side toward the low pressure chamber 318 side. One end of the second spring 366 is locked to the end surface of the contact portion 362 opposite to the side where the tapered surface 365 is formed. The other end of the second spring 366 is in contact with the inner wall of the first valve housing 31 that forms the high-pressure chamber 314. The second spring 366 urges the valve body 36 in a direction in which the valve body 36 comes into contact with the valve seat 38.

  The second shaft portion 363 is formed in a rod shape, and is provided so as to connect one end portion to the end portion on the side where the outer diameter of the contact portion 362 is small. The second shaft portion 363 is mainly located in the intermediate chamber 317 and the low pressure chamber 318.

  The restricting portion 364 is formed in a columnar shape having an outer diameter larger than that of the second shaft portion 363. The restricting portion 364 is engaged with the pressure receiving member 42. The restricting portion 364 is formed such that the cross-sectional area of the restricting portion 364 in the direction perpendicular to the central axis of the first valve housing 31 is the same as the cross-sectional area of the end portion of the first shaft portion 361 protruding into the adjustment chamber 373. Is done. Thereby, the pressure of the gaseous fuel in the low pressure chamber 318 and the adjustment chamber 373 acting on the valve body 36 is canceled.

  The valve seat 38 is formed in an approximately annular shape from an elastic material. The valve seat 38 has a through-hole 383 through which the second shaft portion 363 of the valve body 36 is inserted substantially at the center. The valve seat 38 is supported by a valve seat support member 39. A valve seat surface 381 that contacts or separates from the tapered surface 365 of the contact portion 362 is formed at the edge portion that forms the opening of the through hole 383 on the high pressure chamber 314 side. As shown in FIG. 3, the valve seat 38 is formed such that its outer diameter R <b> 1 is larger than the inner diameter R <b> 2 of the high-pressure chamber 314.

  The valve seat support member 39 is formed in a substantially annular shape from metal. The valve seat support member 39 is accommodated in the intermediate chamber 317 of the first valve housing 31 while supporting the valve seat 38. The valve seat support member 39 has a through hole 391 and a valve seat housing chamber 392 communicating with the through hole 391 at substantially the center. The through hole 391 communicates with the through hole 383 of the valve seat 38 when the valve seat 38 is accommodated in the valve seat accommodating chamber 392. The valve seat accommodating chamber 392 is formed in a concave shape at the end portion on the high pressure chamber 314 side, and has an inner diameter larger than the inner diameter R2 of the high pressure chamber 314. A valve seat 38 having an outer diameter R1 is press-fitted and fixed in the valve seat accommodating chamber 392. Thereby, the movement of the valve seat 38 of the valve seat housing chamber 392 in the radial direction is restricted by the inner wall of the valve seat housing chamber 392.

An end surface 393 on the high-pressure chamber 314 side of the valve seat support member 39 accommodated in the intermediate chamber 317 is in contact with the inner wall surface 310 of the first valve housing 31. A seal member 394 is provided between the end surface 393 of the valve seat support member 39 and the inner wall surface 310 of the first valve housing 31.
When the end surface 393 of the valve seat support member 39 and the inner wall surface 310 of the first valve housing 31 are in contact, the end surface 382 of the valve seat 38 on the high pressure chamber 314 side and the inner wall surface 310 of the first valve housing 31 are A gap is formed between them. The valve seat 38 is provided so that the gap is as small as possible. A seal member 384 is provided between the valve seat 38 and the valve seat support member 39. The end surface 393 corresponds to the “end surface on the first chamber side of the valve seat support member” recited in the claims. The end surface 382 corresponds to “the end surface of the valve seat on the first chamber side” recited in the claims. The inner wall surface 310 corresponds to “an inner wall surface of the valve housing on the valve seat support member side” and “an inner wall surface of the valve housing on the valve seat side” recited in the claims.

  The retainer 395 is provided in the intermediate chamber 317 on the low pressure chamber 318 side of the valve seat support member 39. The retainer 395 is screwed into a thread groove formed on the inner wall of the first valve housing 31 that forms the intermediate chamber 317. As a result, an axial force is generated between the retainer 395 and the first valve housing 31 so that the end surface 393 of the valve seat support member 39 is in contact with the inner wall surface 310 of the first valve housing 31. The retainer 395 corresponds to a “regulating member” described in the claims.

  The retainer 395 has a through hole 396 and a communication path 397. The through hole 396 is formed substantially at the center of the retainer 395, communicates with the through hole 383 of the valve seat 38 and the through hole 391 of the valve seat support member 39, and allows the high pressure chamber 314 and the low pressure chamber 318 to communicate with each other. A communication passage 397 formed in the radially outward direction of the through hole 396 communicates the adjustment chamber 373 and the low pressure chamber 318 via the intermediate chamber 317 and the communication passage 316.

  The pressure receiving member 42 is provided between the first valve housing 31 and the second valve housing 32. The pressure receiving member 42 includes a diaphragm 421, a first connecting member 422, a second connecting member 423, a spring holder 424, and the like. The pressure receiving member 42 divides the low pressure chamber 318 of the flange portion 312 of the first housing 31 and the inside of the second housing 32, and the pressure between the low pressure chamber 318 and the second valve housing 32 in which the first spring 44 is accommodated. Is displaced toward the first valve housing 31 side or the second valve housing 32 side.

  The diaphragm 421 is an annular thin film, and its radially outer end is sandwiched between the end of the flange portion 312 of the first valve housing 31 and the end of the flange portion 322 of the second valve housing 32. Supported by A first connecting member 422, a second connecting member 423, and a spring holder 424 are connected to the radially inner end of the diaphragm 421.

  The first connecting member 422 is a metal member provided on the low pressure chamber 318 side with respect to the diaphragm 421. A regulating portion 364 of the valve body 36 is engaged with an end portion of the first connecting member 422 on the first valve housing 31 side. A convex portion 425 to which the second coupling member 423 is connected is provided at the end of the first coupling member 422 on the second valve housing 32 side. The first connecting member 422 and the second connecting member 423 are displaced together with the diaphragm 421 while sandwiching the radially inner end of the diaphragm 421.

  The spring holder 424 is a dish-shaped metal member supported by the first connecting member 422 and the second connecting member 423 together with the diaphragm 421. The spring holder 424 locks one end of the first spring 44.

  The other end of the first spring 44 opposite to the side locked by the spring holder 424 is in contact with the spring holder 442 accommodated in the second valve housing 32. The first spring 44 biases the valve body 36 in a direction away from the valve seat 38 via the pressure receiving member 42. The biasing force of the first spring 44 is set larger than the biasing force of the second spring 366. As a result, when the high pressure chamber 314 and the low pressure chamber 318 are not filled with gaseous fuel, the valve element 36 is separated from the valve seat 38.

  The needle 441 is inserted through the through hole 323 of the second valve housing 32 and is screw-coupled to the second valve housing 32. The needle 441 contacts substantially the center of the spring holder 442 and adjusts the position of the spring holder 442 relative to the second valve housing 32. Thereby, the needle 441 can adjust the urging force of the first spring 44. Specifically, when the needle 441 is screwed into the second valve housing 32, the urging force of the first spring 44 becomes relatively large.

  Next, the operation of the gaseous fuel pressure control valve 1 will be described with reference to FIGS.

  Since the gaseous fuel injector 17 does not consume gaseous fuel in the supply pipe 8 when the engine 19 is stopped, the pressure of the gaseous fuel in the low pressure chamber 318 of the gaseous fuel pressure control valve 1 connected to the supply pipe 8 is Relatively high. At this time, the pressure of the fuel in the low pressure chamber 318 acts on the pressure receiving member 42, so that the pressure receiving member 42 is displaced toward the second valve housing 32. The valve body 36 connected to the pressure receiving member 42 moves downward in FIG. 2 against the urging force of the first spring 44, and the tapered surface 365 of the contact portion 362 and the valve seat surface 381 of the valve seat 38 are moved. Abut. As a result, the high pressure chamber 314 and the low pressure chamber 318 are blocked.

  When the engine 19 is driven and the gaseous fuel injector 17 injects gaseous fuel into the intake pipe 18, the pressure in the low pressure chamber 318 decreases. The pressure receiving member 42 is displaced in the direction of the first valve housing 31 when the pressure in the low pressure chamber 318 becomes smaller than a predetermined value. The valve body 36 connected to the pressure receiving member 42 moves upward in FIG. 2, and the tapered surface 365 of the contact portion 362 and the valve seat surface 381 of the valve seat 38 are separated from each other. As a result, the gaseous fuel in the high pressure chamber 314 flows into the low pressure chamber 318 through the through holes 383, 391, and 396. At this time, the pressure of the gaseous fuel supplied to the gaseous fuel injector 17 is determined by the size of the opening area between the tapered surface 365 of the valve body 36 and the valve seat surface 381 of the valve seat 38.

  In the pressure control valve 1 for gaseous fuel according to one embodiment, the end surface 393 of the valve seat support member 39 is in contact with the inner wall surface 310 of the first valve housing 31, while the end surface 382 of the valve seat 38 and the inner wall surface 310 are in contact with each other. A gap is formed between them. When an axial force in the screw connection of the retainer 395 acts on the valve seat support member 39, the axial force acts between the end surface 393 of the valve seat support member 39 and the inner wall surface 310. Since the valve seat support member 39 is formed of a metal material, even if the axial force of the retainer 395 is applied, the valve seat support member 39 is not easily plastically deformed, so that the axial force of the retainer 395 is maintained. That is, the valve seat support member 39 is held at a predetermined position. Further, since a gap is formed between the end surface 382 of the valve seat 38 and the inner wall surface 310, the axial force does not act on the valve seat 38 formed of an elastic material. Thereby, since the valve seat 38 is not plastically deformed by the axial force, the valve seat 38 is provided at a desired position, and the airtightness between the high pressure chamber 314 and the low pressure chamber 318 can be reliably maintained for a long time. .

  Further, the outer diameter R1 of the valve seat 38 and the inner diameter of the valve seat housing chamber 392 in which the valve seat 38 is press-fitted and fixed are formed to be larger than the inner diameter R2 of the high-pressure chamber 314. This prevents the valve seat 38 from dropping from the valve seat housing chamber 392 of the valve seat support member 39 even when the holding force in the radial direction of the valve seat 38 that is press-fitted into the valve seat housing chamber 392 is lost. Can do.

  Further, the valve seat 38 is provided so as to make the gap between the end surface 382 of the valve seat 38 and the inner wall surface 310 of the first valve housing 31 as small as possible. Thereby, it can prevent that the sealing performance of the valve seat 38 falls.

(Other embodiments)
(A) In the above-described embodiment, the “pressure control valve” of the present invention is used in a compressed natural gas supply system that depressurizes the high-pressure gaseous fuel to a low pressure that can be supplied to the gaseous fuel injector and supplies it to the gaseous fuel injector. It was. However, the system in which the “pressure control valve” of the present invention is used is not limited to this. What is necessary is just to be used for the system provided with the function which controls the pressure of the fluid.

  (A) In the above-described embodiment, the outer diameter of the valve seat and the inner diameter of the valve seat housing chamber are formed to be larger than the inner diameter of the high-pressure chamber. However, the outer diameter of the valve seat and the inner diameter of the valve seat housing chamber are not limited to this. It may be smaller than the inner diameter of the high pressure chamber.

  (C) In the above-described embodiment, the retainer holds the end surface of the valve seat support member so as to contact the inner wall surface of the first valve housing. However, the method of holding the valve seat support member so as to contact the inner wall surface of the first valve housing is not limited to this. A screw groove may be formed in the valve seat support member, and the valve seat support member may abut against the inner wall surface of the first valve housing by screwing with a screw groove formed in the first valve housing. That is, there is no need for a retainer.

  As mentioned above, this invention is not limited to such embodiment, It can implement with a various form in the range which does not deviate from the summary.

1 ... Pressure control valve for gas fuel (pressure control valve),
31 ... 1st valve housing (valve housing),
310 ・ ・ ・ Inner wall surface (inner wall surface on the valve seat support member side of the valve housing, inner wall surface on the valve seat side of the valve housing),
314 ・ ・ ・ High pressure chamber (first chamber),
318 ... low pressure chamber (second chamber),
32 ・ ・ ・ Second valve housing (valve housing),
36 ・ ・ ・ Valve,
38 ... valve seat,
382 ... End face (end face of the valve seat on the first chamber side),
39 ... Valve seat support member,
393... End face (end face on the first chamber side of the valve seat support member).

Claims (2)

A valve housing (31, 32) having a first chamber (314) into which fluid from the outside flows, and a second chamber (318) formed to be able to communicate with the first chamber and through which the fluid in the first chamber flows. ,
A valve seat (38) formed of an elastic material, located between the first chamber and the second chamber, and having an outer diameter (R1) larger than an inner diameter (R2) of the first chamber ;
A valve seat support member (39) formed of metal and provided between the first chamber and the second chamber while supporting the valve seat on the first chamber side;
A valve body (36) provided so as to be capable of reciprocating with respect to the valve seat, and shutting off or communicating with the first chamber and the second chamber when contacting or separating from the valve seat;
With
The end surface of the valve seat support member on the first chamber side and the inner wall surface (310) of the valve housing on the valve seat support member side are in contact with each other, while the end surface of the valve seat on the first chamber side is in contact. A pressure control valve characterized in that a gap is formed between (382) and the inner wall surface (310) on the valve seat side of the valve housing. The pressure control valve according to claim 1, further comprising a regulating member (395) for regulating a relative position of the valve seat support member with respect to the valve housing.

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