WO2022209964A1 - 弁 - Google Patents

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Publication number
WO2022209964A1
WO2022209964A1 PCT/JP2022/012340 JP2022012340W WO2022209964A1 WO 2022209964 A1 WO2022209964 A1 WO 2022209964A1 JP 2022012340 W JP2022012340 W JP 2022012340W WO 2022209964 A1 WO2022209964 A1 WO 2022209964A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
bellows
space
valve body
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2022/012340
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
英樹 東堂園
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Eagle Industry Co Ltd
Original Assignee
Eagle Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Eagle Industry Co Ltd filed Critical Eagle Industry Co Ltd
Priority to CN202280024743.5A priority Critical patent/CN117098943A/zh
Priority to JP2023510941A priority patent/JP7780506B2/ja
Priority to EP22780183.4A priority patent/EP4317755A4/en
Priority to US18/284,478 priority patent/US12510168B2/en
Publication of WO2022209964A1 publication Critical patent/WO2022209964A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/08—Details
    • F16K5/14—Special arrangements for separating the sealing faces or for pressing them together
    • F16K5/20—Special arrangements for separating the sealing faces or for pressing them together for plugs with spherical surfaces
    • F16K5/205—Sealing effected by the flowing medium
    • F16K5/207—Sealing effected by the flowing medium using bellows
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0655—Lift valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/36—Valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K41/00—Spindle sealings
    • F16K41/10—Spindle sealings with diaphragm, e.g. shaped as bellows or tube

Definitions

  • the present invention relates to a valve that controls working fluid.
  • Valves used to control working fluid in various industrial fields have a valve seat and a valve element that can be separated from and attached to the valve seat. Pressure and flow rate can be controlled.
  • Such valves include a spool valve in which a spool, which is a valve body, moves parallel to an opening, which is a valve seat, a butterfly valve, in which a valve body has a pivot shaft, and a
  • a typical valve form is a lift valve that moves perpendicularly to the valve.
  • lift valves are the most suitable for flow rate and pressure control.
  • Patent Document 1 As a lift valve, for example, as shown in Patent Document 1, there is a pressure control valve that adjusts the pressure of hydrogen gas supplied to the fuel cell.
  • the pressure control valve of Patent Document 1 includes a primary pressure space to which hydrogen gas is supplied from a gas supply source, a secondary pressure space to supply hydrogen gas whose pressure is adjusted to the nozzle portion of the fuel cell, a primary pressure space, and A valve housing having a valve hole that communicates with the secondary pressure space, a valve seat provided on the side of the secondary pressure space of the valve hole, and a solenoid that can be moved in the axial direction, and the tip of which is connected to the primary pressure space and the valve hole. and a valve body arranged in the secondary pressure space and seated or separated from the valve seat by movement of the rod.
  • the primary pressure chamber and the back space where the solenoid is disposed are hermetically separated by a bellows having one axial end fixed to a rod and the other axial end fixed to the inner peripheral surface of the valve housing. of hydrogen is prevented from leaking to the solenoid side.
  • the effective pressure receiving area of this bellows is equal to the opening area of the valve hole.
  • the force acting on the valve body is canceled by the fluid pressure in the primary pressure space, so the pressure of the upstream gas supplied to the primary pressure space fluctuates. Also, the influence on the movement of the valve body can be suppressed.
  • the fluid pressure in the secondary pressure space which fluctuates according to the manner in which the valve is used, always acts in the direction of moving the valve body closer to the valve seat, when the valve body is moved in the direction of moving away from the valve seat, the secondary The stroke distance of the valve body changes according to the fluid pressure in the pressure space, and there is a possibility that the valve body cannot be accurately moved in the direction away from the valve seat.
  • the present invention has been made in view of such problems, and an object of the present invention is to provide a valve capable of moving the valve disc in a direction away from the valve seat with high precision.
  • the valve of the present invention is a valve housing in which a primary pressure space, a secondary pressure space, and a valve hole communicating with these spaces are formed; a valve seat provided closer to the secondary pressure space than the valve hole in the valve housing; a rod disposed within the valve housing axially movable by a drive source; a valve body arranged in the secondary pressure space and seated or separated from the valve seat by movement of the rod; A valve provided with a pressure-receiving surface that exerts a force directed to the side opposite to the secondary pressure space on the rod by the pressure in the primary pressure space, An axially expandable bellows is arranged across the valve body and the valve housing on the opposite side of the valve body from the valve seat in the axial direction.
  • the axially expandable bellows is arranged on the opposite side of the valve body to the valve seat in the axial direction, the pressure receiving area where the fluid pressure in the secondary pressure space acts on the valve body can be reduced. It is possible to reduce the influence of the force exerted on the valve body by the fluid pressure in the secondary pressure space, and to move the valve body in a direction away from the valve seat with high accuracy.
  • the bellows may have an enclosed interior space. According to this, the degree of freedom in arranging the valve is high regardless of the surrounding environment where the bellows is installed.
  • the internal space may be in a vacuum state. According to this, since the internal space is in a vacuum state, it is possible to reduce the change in the force acting on the valve body from the bellows due to the volume change of the internal space accompanying expansion and contraction of the bellows.
  • An effective pressure receiving area of the bellows may be equal to an effective pressure area of the valve. According to this, the force due to the fluid pressure in the secondary pressure space acting on the valve body is canceled, so the valve body can be moved with high accuracy regardless of the fluid pressure in the secondary pressure space.
  • a biasing means may be provided for biasing the valve body to one side in the axial direction, and the biasing means may be arranged in parallel with the bellows. According to this, since the biasing means and the bellows are arranged in parallel at a position close to the axial direction, the axial expansion and contraction of the bellows can be stabilized by the biasing force of the biasing means.
  • the valve housing may have a movable member to which one end of the bellows is hermetically fixed and whose axial position can be adjusted. According to this, by moving the movable member, it is possible to simultaneously adjust the degree of expansion and contraction of the bellows and the biasing force of the biasing means.
  • the biasing means may be located within the bellows. According to this, since the fluid pressure in the secondary pressure space does not act on the urging means, the urging force of the urging means can be appropriately applied to the valve body.
  • the bellows may be rotatably arranged with respect to the valve housing. According to this, it is possible to suppress the twisting of the bellows due to the operation of the valve.
  • the vacuum state in the present invention is defined by the Japanese Industrial Standards (JIS Z 8126) as "the state of a space filled with a gas having a pressure lower than the normal atmospheric pressure".
  • FIG. 4 is an enlarged cross-sectional view of a main part showing a state in which the pressure control valve is closed;
  • FIG. 4 is an enlarged cross-sectional view of a main part showing a state in which the pressure control valve is opened;
  • FIG. 5 is a cross-sectional view showing a pressure control valve according to Embodiment 2 of the present invention;
  • FIG. 7 is an enlarged cross-sectional view of a main part showing a pressure control valve in Example 3 according to the present invention;
  • a form for implementing the valve according to the present invention will be described below based on an embodiment. Although the embodiment will be described with a pressure control valve as an example, it can also be applied to other uses.
  • FIG. 1 A pressure control valve according to Embodiment 1 will be described with reference to FIGS. 1 to 3.
  • FIG. In the following description, left and right sides of the pressure control valve are defined as viewed from the front side of FIG. Specifically, the left side of the paper where the valve housing 10 is arranged is the left side of the pressure control valve, and the right side of the paper where the solenoid 80 is arranged is the right side of the pressure control valve.
  • the pressure control valve of the present invention adjusts the pressure of hydrogen gas (hereinafter simply referred to as "fluid”), which is a working fluid supplied from a gas supply source, and supplies the adjusted hydrogen gas to the outside. is.
  • fluid hydrogen gas
  • the pressure control valve V1 of the first embodiment includes a primary pressure space S1 into which fluid flows from a gas supply source, a secondary pressure space S2 into which fluid is supplied to the outside, and a primary pressure space S2.
  • a valve housing 10 having a valve hole 10d communicating the pressure space S1 and the secondary pressure space S2 is provided.
  • the discharge fluid of the discharge pressure Pd of the gas supply source is always supplied to the primary pressure space S1, and the control pressure Pc in the secondary pressure space S2 is controlled by reducing the valve opening degree of the valve 50 in the pressure control valve V1. is decreased and the valve opening of the valve 50 is opened to increase the control pressure Pc in the secondary pressure space S2.
  • the valve 50 is composed of a valve body 51 and a valve seat 10f formed on the left surface of a partition wall portion 10e extending radially inward of the valve housing 10.
  • the valve body The valve 50 is opened and closed by the seal member 15 disposed on the right side of the valve 51 moving axially toward and away from the valve seat 10f.
  • the valve 50 of this embodiment is a normally closed valve that closes in a non-energized state.
  • the pressure control valve V1 is used by being attached to a manifold member (not shown) having passages communicating with the gas supply source and the outside.
  • the pressure control valve V1 comprises a valve housing 10 made of a metal material, a valve element 51 arranged in the valve housing 10 so as to be able to reciprocate in the axial direction, and a rod arranged on the right side of the valve element 51 in the axial direction.
  • a member 20 a solenoid 80 connected to the valve housing 10 and exerting a driving force on the rod member 20 and the valve body 51, a first bellows 30 sealed between the valve housing 10 and the rod member 20, and a valve and a second bellows 60 as a bellows that is hermetically fixed to the left of the body 51 in the axial direction and defines an independent internal space S4.
  • the valve housing 10 includes a valve housing main body portion 10A (hereinafter simply referred to as the main body portion 10A) and a movable member that can adjust the axial position with respect to the main body portion 10A.
  • a lid member 13 and a shaft member 16 are provided.
  • a primary pressure space S1 communicating with a gas supply source through a plurality of radially penetrating inlet ports 11 is formed on the axially right side of the body portion 10A.
  • a secondary pressure space S2 is formed that communicates with the outside through a plurality of outlet ports 12 penetrating through.
  • the main body portion 10A is formed with a recess 10a that is recessed axially rightward from the left end in the axial direction and that is open at the left end in the axial direction.
  • the left end of the main body 10A in the axial direction is closed by a lid member 13 and a shaft member 16, and the space surrounded by the inner peripheral surface, the right end surface, and the lid member 13 and the shaft member 16 forming the recess 10a is secondary. It is a pressure space S2.
  • the cover member 13 is screwed and fixed to the left end portion of the main body portion 10A so that the fixing position in the axial direction can be adjusted with respect to the main body portion 10A.
  • a through hole 13a is formed in the central portion of the lid member 13 so as to penetrate in the left-right direction.
  • the large-diameter flange portion 16 d of the shaft member 16 is in contact with the right end face of the lid member 13 .
  • the shaft member 16 has a left end shaft portion 16c, a large diameter flange portion 16d, a flange portion 16a, and a right end shaft portion 16b in order from the left side in the axial direction.
  • the large-diameter flange portion 16d and the flange portion 16a are arranged apart from each other in the axial direction. It is formed to have a small diameter and a larger diameter than the left end shaft portion 16c and the right end shaft portion 16b.
  • a body part 61 of a second bellows 60 that can be expanded and contracted in the axial direction and a biasing member that urges the valve body 51 to the right in the axial direction, which is the closing direction of the valve 50, are provided.
  • a coil spring 14 as a force means is arranged in parallel.
  • the second bellows 60 includes a body portion 61 as a metal accordion-shaped bellows main body, a shaft member 16 that closes the opening at the left end of the body portion 61 in the axial direction, and the opening at the right end of the body portion 61 in the axial direction. and a valve body 51.
  • the body portion 61 is located between the flange portion 16a of the shaft member 16 and a flange portion 54 (see FIG. 2) which is provided at substantially the center in the axial direction of the valve body 51 and faces the flange portion 16a in the axial direction. and fixed by any fixing means such as welding.
  • the internal space S4 of the second bellows 60 is hermetically separated from the secondary pressure space S2.
  • This internal space S4 is in a vacuum state filled with a gas with a pressure lower than the atmospheric pressure.
  • the body portion 61 of the second bellows 60 may be made of a material other than metal.
  • the coil spring 14 is a compression spring and is arranged inside the second bellows 60, that is, inside the internal space S4. Specifically, the tip shaft portion 52 of the valve body 51 and the right end shaft portion 16b of the shaft member 16 are inserted inside the coil spring 14 . As a result, axial vibration of the coil spring 14 is suppressed (see FIG. 2). That is, the coil spring 14 and the trunk portion 61 of the second bellows 60 overlap in the radial direction.
  • the biasing force of the coil spring 14 keeps the large-diameter flange portion 16 d of the shaft member 16 in contact with the right end surface of the lid member 13 . Further, since the internal space S4 is in a vacuum state, it is easy to adjust the biasing force of the coil spring 14 with the vacuum as a reference.
  • the body portion 10A is formed with a recess 10c in which the inner diameter side of the axial right end is recessed to the left in the axial direction. 10b are formed.
  • the communication hole portion 10b has a smaller diameter than the recesses 10a and 10c.
  • the main body portion 10A is provided with a partition wall portion 10e that partitions the recess portion 10a and the communication hole portion 10b so as to extend in the inner diameter direction.
  • a valve hole 10d is formed.
  • the valve hole 10d communicates with the axial left side of the communication hole portion 10b.
  • a first bellows 30 is hermetically fixed to the recess 10c.
  • a space surrounded by the first bellows 30 and the communication hole portion 10b is a primary pressure space S1.
  • the first bellows 30 includes a cylindrical body portion 31 having a bellows that can be expanded and contracted in the axial direction, a fixed plate portion 32 that closes the opening at the left end of the body portion 31 in the axial direction, and the right end of the body portion 31 in the axial direction. and a ring portion 33 that is press-fitted and fixed to the concave portion 10c.
  • the body portion 31, the fixing plate portion 32 and the ring portion 33 are made of metal.
  • the fixed plate portion 32 and the ring portion 33 are formed thicker than the body portion 31 and have more rigidity than the body portion 31 .
  • the body portion 31 , the fixed plate portion 32 and the ring portion 33 may be made of different materials, but the fixed plate portion 32 and the ring portion 33 preferably have higher rigidity than the body portion 31 .
  • the body portion 31, the fixing plate portion 32 and the ring portion 33 may be made of a material other than metal.
  • the left surface of the fixed plate portion 32 in the axial direction is a tapered surface 32d extending so as to decrease in diameter toward the left.
  • a portion of the tapered surface 32 d on the inner diameter side functions as a pressure receiving surface facing the pressure receiving surface of the axially right end surface of the large diameter portion 53 of the valve body 51 .
  • a protruding shaft portion 32a extending to the left in the axial direction is formed at the radial center portion at the left end of the tapered surface 32d of the fixed plate portion 32.
  • the left end portion in the axial direction of the protruding shaft portion 32a i. It is press-fitted and fixed to a concave portion 53a of a valve body 51, which will be described later, through the valve hole 10d.
  • the protruding shaft portion 32 a and the rod member 20 function as a rod that transmits a moving force to the valve body 51 .
  • a fitting recess 33a recessed to the left in the axial direction is formed on the inner diameter side of the right end of the ring portion 33 in the axial direction.
  • the valve body 51 is formed with a tip shaft portion 52, a flange portion 54, and a large diameter portion 53 in order from the left end in the axial direction.
  • the distal shaft portion 52 has a smaller diameter than the flange portion 54 and the large diameter portion 53
  • the flange portion 54 has a smaller diameter than the large diameter portion 53
  • the large diameter portion 53 has a larger diameter than the valve hole 10 d of the valve housing 10 .
  • recessed portion 53a On the end face on the axial right side of the large-diameter portion 53, there is a recessed portion 53a recessed axially leftward in the radially central portion, and an annular groove portion 53b formed to surround the outer diameter side of the recessed portion 53a open axially rightward. , and an annular seal member 15 made of a rubber material is press-fitted into the annular groove portion 53b.
  • the sealing member 15 can contact a valve seat 10f provided on the periphery of the valve hole 10d on the axially left end surface of the partition wall portion 10e of the valve housing 10, and is in contact with the valve seat 10f. , the amount of fluid leakage between the valve seat 10f and the valve body 51 is substantially zero.
  • the sealing member 15 is not limited to the rubber material, and may be made of synthetic resin, metal, or the like.
  • the valve seat 10f may be composed of a member different from the valve housing 10 press-fitted into the valve hole 10d.
  • a solenoid 80 is inserted into a casing 81 having an opening 81a that opens axially leftward, and is inserted into the opening 81a of the casing 81 between the inner diameter side of the casing 81 and the inner diameter side of the valve housing 10.
  • a substantially cylindrical center post 82 disposed in the center post 82; a rod member 20 inserted through the center post 82 and reciprocating in the axial direction;
  • a movable iron core 84 whose axial right end is inserted and fixed, an excitation coil 86 wound around a center post 82 via a bobbin, a portion of the center post 82, the movable iron core 84, and a rod member. 20, and a cylindrical sleeve 87 with a bottom in which a part of the device 20 is housed.
  • the center post 82 is formed of a rigid body that is a magnetic material such as iron or silicon steel. and a cylindrical convex portion 82d extending axially leftward from the inner diameter side.
  • a portion on the right side of the insertion hole 82c in the axial direction is a small diameter hole portion 82e having a diameter slightly larger than that of the rod member 20, and a portion on the left side of the insertion hole 82c in the axial direction is a portion with a diameter larger than that of the small diameter hole portion 82e. It is a large diameter hole portion 82f.
  • An annular bearing 17 is arranged in the large-diameter hole 82f to guide the movement of the rod member 20 in the axial direction and to restrict the inclination of the rod member 20. As shown in FIG.
  • the tubular projection 82d is inserted so as to fit into the fitting recess 33a of the first bellows 30. As shown in FIG.
  • the center post 82 is formed with a notch portion 82g which is notched from the left end portion of the cylindrical convex portion 82d to the left end portion of the cylindrical portion 82b so as to open in the outer diameter direction.
  • the bottom portion of the notch portion 82g is formed so that the left end thereof is axially leftward of the bearing 17 and axially rightward of the left end surface of the tubular convex portion 82d so as to protrude radially inward in a cross-sectional view. It extends in an arc shape in the outer diameter direction. That is, the left end portion of the notch portion 82g communicates with the large diameter hole portion 82f of the insertion hole 82c.
  • the notch portion 82g is located at the axially left side of the back space S3 inside the solenoid 80 and the pressure control valve.
  • a passage communicating with the space outside V1 is formed. That is, the left portion of the rear space S3 in the axial direction is at atmospheric pressure.
  • the axially left portion of the back space S3 referred to here includes the space in the first bellows 30 and the axially leftward space of the bearing 17 in the large-diameter hole portion 82f.
  • the sleeve 87 includes a tubular member 87a into which a part of the center post 82 and a part of the movable iron core 84 are inserted, and a U-shaped cross-sectional view that opens axially to the left and is connected to the axially right end of the tubular member 87a. and a cap member 87b having a shape.
  • a radially penetrating port 87c is formed in the cap member 87b, and the port 87c communicates between the axially right portion of the back space S3 in the solenoid 80 and the space outside the pressure control valve V1. That is, the portion on the right side in the axial direction of the rear space S3 is at atmospheric pressure.
  • the axially left portion of the rear space S3 referred to here is the space axially rightward of the bearing 17 in the large-diameter hole portion 82f, the space in the small-diameter hole portion 82e of the insertion hole 82c, and the movable space in the sleeve 87. It includes the left and right spaces of the iron core 84 .
  • the back space S3 inside the solenoid 80 is mainly the space inside the sleeve 87 on the back side of the valve element 51 that is separated from the primary pressure space S1.
  • the rod member 20 is inserted through the insertion hole 82 c of the center post 82 , the axial right end of the rod member 20 is fitted and fixed to the movable core 84 , and the axial left end of the rod member 20 is connected to the first bellows 30 . is inserted into the body portion 31 of the The axial left end portion of the rod member 20 is fitted and fixed in a concave portion 32c recessed axially leftward in the right end surface of a shaft portion 32b extending axially rightward from the right surface of the fixed plate portion 32 .
  • the axial left end portion of the rod member 20 may be fixed to the right surface of the fixed plate portion 32 by an adhesive, welding, or the like.
  • the effective pressure receiving area B of the valve body 51 is the same size as the opening area of the valve hole 10d.
  • the non-energized state of the pressure control valve V1 will be described. As shown in FIGS. 1 and 2, in the non-energized state of the pressure control valve V1, the valve body 51 is pressed axially rightward by the biasing force of the coil spring 14, that is, in the valve closing direction. The seal member 15 of the valve body 51 is seated on the valve seat 10f, and the valve 50 is closed.
  • the valve body 51 is subjected to the biasing force (F sp ) of the coil spring 14, the force (F P1 ) due to the pressure P1 of the working fluid in the primary pressure space S1, and the secondary pressure space S1.
  • the interior space S4 is in a vacuum state, and the force FP4 due to the pressure in the interior space S4 acting on the valve body 51 is substantially zero, so the description is omitted here.
  • valve body 51 is designed not to be affected by the working fluid in the primary pressure space S1 and the secondary pressure space S2.
  • the force F rod F sp -F P3 substantially acts on the valve body 51, and the biasing force (F sp ) of the coil spring 14 is the force (F P3 ) (F sp >F p3 ), the valve 50 is closed by being pressed in the valve closing direction.
  • an electromagnetic force (F sol ) generated by applying a current to the solenoid 80 is a force F rod (F sol >F rod )
  • the movable iron core 84 is drawn toward the center post 82, that is, toward the left in the axial direction, and the rod member 20 and the valve body 51 fixed to the movable iron core 84 move toward the left in the axial direction, that is, By moving together in the valve opening direction, the seal member 15 of the valve body 51 is separated from the valve seat 10f, and the valve 50 is opened.
  • the distal end shaft portion 52 of the valve body 51 contacts the right end shaft portion 16b of the shaft member 16, thereby restricting the further separation of the valve body 51 from the valve seat 10f. .
  • an electromagnetic force acts on the valve body 51 to the left in the axial direction, and a force F rod acts to the right in the axial direction (that is, when the right direction is positive, the force F rod- F sol is acting).
  • the pressure control valve V1 has the difference (F sp -F p3 ) between the electromagnetic force (F sol ) of the solenoid 80, the biasing force (F sp ) of the coil spring 14, and the force (F P3 ) due to the pressure P3.
  • the pressure P2 of the working fluid in the secondary pressure space S2 can be appropriately controlled by the valve opening degree of the valve 50 adjusted by the balance between and.
  • the urging force of the first bellows 30 itself and the urging force of the second bellows 60 are exemplified in a form in which the valve body 51 is hardly acted upon.
  • the biasing force of 60 itself may act.
  • the axially expandable second bellows 60 is positioned between the valve body 51 and the shaft member 16 at the position on the opposite side of the valve body 51 from the valve seat 10f in the axial direction. Therefore, the second bellows 60 can reduce the substantial pressure receiving area where the fluid pressure in the secondary pressure space S2 acts on the valve body 51, and the fluid pressure in the secondary pressure space S2 can be reduced. Therefore, the influence of the force on the valve body 51 can be reduced.
  • valve body 51 can be accurately moved in the direction away from the valve seat 10f. Further, since the valve body 51 can be moved in the direction away from the valve seat 10f with a small electromagnetic force, the construction of the solenoid 80 can be reduced. In particular, it is useful when the opening area of the valve hole 10d is formed to be large to control a large flow rate of the control fluid.
  • a primary pressure space S1 acting on the valve body 51 is formed by the pressure receiving surface of the valve body 51 (that is, the axially right end surface of the large diameter portion 53) and the pressure receiving surface of the first bellows 30 facing the pressure receiving surface. Since the influence of the force due to the pressure P1 of the working fluid inside can be reduced, the valve element 51 can be moved in a direction away from the valve seat 10f with high accuracy.
  • the second bellows 60 has a sealed internal space S4, and the second bellows 60 can expand and contract in the axial direction in that state. According to this, when the second bellows 60 expands and contracts in the axial direction, the structure can be simplified because there is no need for a flow path for taking fluid into and out of the internal space S4. That is, regardless of the surrounding environment where the second bellows 60 is installed, the pressure control valve V1 can be arranged with a high degree of freedom.
  • the change in the force acting on the valve body 51 due to the change in the volume of the internal space S4 accompanying the expansion and contraction of the second bellows 60 can be reduced.
  • the second bellows 60 when the second bellows 60 is compressed in the axial direction, it is possible to suppress an increase in the fluid pressure in the internal space S4, thereby allowing the second bellows 60 to make a large stroke in the compression direction.
  • the force due to the pressure in the internal space S4 acting on the valve body 51 can be made substantially zero.
  • the effective pressure receiving area C of the second bellows 60 is equal to the opening area of the valve hole 10 d, that is, the effective pressure receiving area B of the valve body 51 .
  • the effective pressure-receiving area A of the first bellows 30 is equal to the effective pressure-receiving area B of the valve body 51 .
  • the force due to the fluid pressure in the primary pressure space S1 acting on the valve body 51 is canceled, so the valve body 51 can be moved with high precision regardless of the fluid pressure in the primary pressure space S1.
  • the coil spring 14 that urges the valve body 51 to the right in the axial direction is arranged in parallel with the second bellows 60 so as to overlap in the radial direction, the urging force of the coil spring 14 causes the second bellows 60 to move. Axial expansion and contraction can be stabilized.
  • the valve housing 10 also includes a cover member 13 and a shaft member 16 to which one end of the second bellows 60 is hermetically fixed and whose axial position relative to the body portion 10A can be adjusted. According to this, by moving the lid member 13 to change the distance from the valve body 51, the expansion/contraction degree of the second bellows 60 and the biasing force of the second bellows 60 can be adjusted at the same time.
  • the lid member 13 when changing the distance between the lid member 13 and the shaft member 16 and the valve body 51, the lid member 13 is moved with respect to the main body portion 10A while the rotation of the shaft member 16 is restricted.
  • the screwing depth of the cover member 13 can be changed to an arbitrary one by rotating the chisel. By doing so, it is possible to avoid twisting of the second bellows 60 and twisting of the first bellows 30 when changing the distance between the lid member 13 and the shaft member 16 and the valve body 51 .
  • the second bellows 60 is rotatable relative to the main body portion 10A of the valve housing 10 due to the above configuration, twisting of the second bellows 60 due to the operation of the valve 50 can be suppressed.
  • the internal space S4 is in a vacuum state, it is easy to adjust the biasing force of the coil spring 14 based on the vacuum.
  • the coil spring 14 is arranged inside the second bellows 60, the fluid pressure in the secondary pressure space S2 and the flow of the working fluid do not act on the coil spring 14, and the urging force of the coil spring 14 is applied to the valve body 51. can be properly acted on.
  • the pressure control valve V2 of the second embodiment has a coil spring 140 as a biasing means arranged in the back space S3.
  • the solenoid 800 has a center post 820 arranged on the axial right side inside the coil 86 and a movable iron core 840 arranged on the axial left side inside the coil 86 .
  • a recess 820a recessed to the right in the axial direction is formed in the radial center portion of the left end portion of the center post 820, and the coil spring 140 is arranged in the recess 820a.
  • the coil spring 140 has a diameter slightly smaller than the diameter of the recess 820a, and is formed axially longer than the axial length of the recess 820a in the compressed state. are placed in In other words, the coil spring 140 is axially spaced from the second bellows 60 and does not radially overlap.
  • the pressure control valve V2 when the pressure control valve V2 is in a non-energized state, the valve body 51 moves leftward in the axial direction due to the biasing force of the coil spring 140, and the seal member 15 is separated from the valve seat 10f. . That is, the pressure control valve V2 is a normally open type valve.
  • the coil spring 140 is arranged in the back space S3, it is avoided that the fluid pressure of the primary pressure space S1 and the secondary pressure space S2, which are higher than the atmospheric pressure, acts on the coil spring 140. , the biasing force of the coil spring 140 can be appropriately applied to the valve body 51 .
  • the diameter of the coil spring 140 is slightly smaller than the diameter of the recess 820a. Inclination of the coil spring 140 is restricted by the inner peripheral surface of the .
  • a coil spring 240 as a biasing means is arranged in parallel in the secondary pressure space S2, that is, on the outer diameter side of the body portion 61 of the second bellows 60. According to this, the axial expansion and contraction of the second bellows 60 can be stabilized by the biasing force of the coil spring 240 .
  • the inner diameter of the coil spring 240 is larger than that of the large-diameter flange portion 16 d of the shaft member 16 , and the axial left end portion of the coil spring 240 abuts the right surface of the lid member 13 .
  • the coil spring 240 is axially inserted from the shaft member 16 side and arranged on the outer diameter side of the body portion 61.
  • the effective pressure-receiving area of the second bellows is formed equal to the effective pressure-receiving area of the valve body to cancel the force due to the fluid pressure in the secondary pressure space acting on the valve body.
  • the effective pressure-receiving area of the second bellows may be slightly smaller or larger than the effective pressure-receiving area of the valve body.
  • the effective pressure-receiving area of the second bellows is formed smaller than the effective pressure-receiving area of the valve body, and the valve body is in contact with the valve seat. preferably easy to maintain.
  • the effective pressure-receiving area of the first bellows is formed equal to the effective pressure-receiving area of the valve body to cancel the force due to the fluid pressure in the primary pressure space acting on the valve body.
  • the effective pressure-receiving area of the first bellows may be slightly smaller or larger than the effective pressure-receiving area of the valve body.
  • the primary pressure space and the back space are separated by the first bellows. and the back space may be partitioned. That is, the primary pressure space and the rear space may communicate with each other through a slight gap between the outer peripheral surface of the rod and the inner peripheral surface of the valve housing or solenoid case.
  • the first bellows is provided with a pressure receiving surface that applies a force in the valve closing direction to the rod due to the pressure in the primary pressure space.
  • a large-diameter portion may be provided on the solenoid side of the rod, and a step between the small-diameter portion and the large-diameter portion may be used as the pressure receiving surface.
  • valve body and the rod are configured as separate members, but the present invention is not limited to this, and the valve body and the rod may be integrated.
  • the internal space of the second bellows is sealed, but the internal space of the second bellows may communicate with the external space.
  • the fluid pressure in the external space should be lower than the fluid pressure in the secondary pressure space.
  • the sealed internal space of the second bellows is in a vacuum state, but the internal space of the second bellows has a lower fluid pressure than the secondary pressure space.
  • a fluid may be enclosed.
  • the biasing means is a push spring, but it may be a pull spring. Further, the biasing means is not limited to the coil spring, and may be a leaf spring or the like.
  • the urging means is arranged in the internal space
  • the urging means is arranged in the back space
  • the urging means is secondary.
  • the biasing means may be arranged in the primary pressure space.
  • the movable member constitutes the valve housing, but it does not have to constitute the valve housing.
  • the movable member and the valve housing do not have to form a secondary pressure space, and the movable member can move relative to the valve housing, and the relative position with the valve housing can be fixed. Just do it.
  • the effective pressure-receiving area B of the valve body is equal to the opening area of the valve hole 10d. It may be larger than the opening area of the hole.
  • the solenoid is used as the drive source for moving the valve body, but the valve body may be moved using a drive source other than the solenoid.
  • valve is a pressure control valve. It may be a capacity control valve or the like incorporated in the compressor.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Valves (AREA)
PCT/JP2022/012340 2021-03-29 2022-03-17 弁 Ceased WO2022209964A1 (ja)

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JP2023510941A JP7780506B2 (ja) 2021-03-29 2022-03-17 弁
EP22780183.4A EP4317755A4 (en) 2021-03-29 2022-03-17 VALVE
US18/284,478 US12510168B2 (en) 2021-03-29 2022-03-17 Valve

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