WO2015166628A1 - Pilot-type flow control valve - Google Patents

Pilot-type flow control valve Download PDF

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Publication number
WO2015166628A1
WO2015166628A1 PCT/JP2015/001871 JP2015001871W WO2015166628A1 WO 2015166628 A1 WO2015166628 A1 WO 2015166628A1 JP 2015001871 W JP2015001871 W JP 2015001871W WO 2015166628 A1 WO2015166628 A1 WO 2015166628A1
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WO
WIPO (PCT)
Prior art keywords
pilot
flow path
valve body
chamber
main
Prior art date
Application number
PCT/JP2015/001871
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French (fr)
Japanese (ja)
Inventor
博明 清水
田中　良和
Original Assignee
川崎重工業株式会社
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Filing date
Publication date
Application filed by 川崎重工業株式会社 filed Critical 川崎重工業株式会社
Publication of WO2015166628A1 publication Critical patent/WO2015166628A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/42—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor

Definitions

  • the present invention relates to a pilot type flow control valve.
  • Non-Patent Document 1 a pilot type valve device configured to operate a pilot valve body by electromagnetic force or the like and open and close the main valve body by a pressure difference of a fluid acting on the main valve body.
  • a pilot type valve device there is a pilot type flow rate control valve capable of controlling the flow rate in proportion to a control signal as shown in Non-Patent Document 1.
  • FIG. 5 is a diagram showing a schematic configuration of the pilot flow control valve 102 according to the aspect described in Non-Patent Document 1.
  • the pilot-type flow control valve 102 includes a main valve body 3 that can be seated on a valve seat 23 provided in a main flow path 25 through which a working fluid flows from an inlet port 21 to an outlet port 22, and the main valve body 3 to the valve seat 23. And a spring 42 that is biased in the approaching direction.
  • the main channel 25 is divided into a primary channel 11 on the inlet port 21 side and a secondary channel 12 on the outlet port 22 side by the main valve body 3 seated on the valve seat 23. Further, the main valve body 3 partitions the pilot chamber 43 that applies pilot pressure to the main valve body 3 and the main flow path 25.
  • a notch 38 is formed around the main valve body 3, and a pilot supply flow path 31 that connects the inside of the notch 38 and the main flow path 25 is formed inside the main valve body 3.
  • a variable throttle 32 is provided between the pilot supply passage 31 and the pilot chamber 43 by the cooperation of the inner peripheral surface of the body 2 in which the main valve body 3 is inserted, the main valve body 3 and the notch 38. Yes.
  • the pilot chamber 43 and the secondary side flow path 12 are connected by a pilot discharge flow path 60.
  • a pilot valve seat 57 is provided between the pilot chamber 43 and the pilot discharge passage 60.
  • the pilot flow control valve 102 includes a pilot valve body 5 that can be seated on the pilot valve seat 57, a spring 41 that biases the pilot valve body 5 toward the pilot valve seat 57, and the pilot valve body 5 as a pilot valve. And a solenoid 50 that applies a driving force in accordance with the amount of energization in the direction away from the seat 57.
  • the main valve body 3 is seated on the valve seat 23 when the pilot valve body 5 is seated on the pilot valve seat 57. At this time, the opening area of the variable throttle 32 is narrowed, but the pressure of the working fluid in the pilot chamber 43 and the pressure of the working fluid in the primary channel 11 are equal due to slight leakage.
  • the main valve body 3 remains seated on the valve seat 23 because the area on which the pilot pressure acts is larger than the area on the main valve body 3 on which the primary pressure acts.
  • the object of the present invention is to improve the performance of a pilot flow control valve.
  • the pilot flow control valve according to the present invention as seen from the first aspect is: An inlet port, an outlet port, a main flow path connecting the inlet port and the outlet port, a valve seat provided between a primary flow path and a secondary flow path of the main flow path, a pilot chamber, and the pilot A body having a pilot discharge channel connecting the chamber and the outlet port;
  • the first closing direction approaching the valve seat and the first opening direction away from the valve seat are movable, partitioning the main flow path and the pilot chamber, and moving in the first opening direction
  • the body is configured to increase an opening area of a first variable throttle formed between the main flow path and the pilot chamber and move in the first closing direction to reduce the opening area of the first variable throttle.
  • An inserted main valve body having a pilot supply flow path connecting the pilot chamber and the inlet port therein; A first spring that applies an urging force in the first closing direction to the main valve body; A second opening direction and the second variable throttle for partitioning the pilot chamber and the pilot discharge flow path and increasing an opening area of a second variable throttle formed between the pilot chamber and the pilot discharge flow path.
  • a pilot valve body inserted into the body so as to be movable in a second closing direction for reducing an opening area of the pilot valve body, and having an internal flow path connecting the pilot chamber and the pilot discharge flow path; , Driving force adding means for applying a driving force in the second opening direction to the pilot valve body; A second spring for applying a biasing force in the second closing direction to the pilot valve body; A check valve that allows passage of only a one-way flow from the inlet port to the pilot chamber in the pilot supply flow path.
  • open direction refers to “opening direction”
  • closed direction refers to “closing direction”.
  • the pilot flow control valve when the pressure of the working fluid at the outlet port becomes high even when the pilot valve is in the closed position, the working fluid flows from the gap between the main valve body and the body. Leak into the pilot room from the exit port. Furthermore, the working fluid in the pilot chamber leaks from the gap between the main valve body and the body to the pilot supply passage, but the working fluid flows from the pilot supply passage to the inlet port by the check valve provided in the pilot supply passage. I can't.
  • the pilot type flow control valve when the pilot type flow control valve is closed, the working fluid passes through the pilot chamber (from the inlet port to the outlet port) from the secondary side channel of the main channel to the primary channel. Leakage can be suppressed. Therefore, the performance of the pilot flow control valve can be improved.
  • the pilot-type flow control valve has a secondary pilot supply passage formed in the main valve body so as to connect the pilot chamber and the outlet port, and the pilot pilot flow passage from the outlet port to the pilot in the secondary pilot supply passage.
  • a check valve that allows only the flow toward the chamber to pass therethrough may be further provided.
  • the body further includes a balance chamber that applies a pressure in the second opening direction to the pilot valve body, and the internal flow path of the pilot valve body includes the balance chamber.
  • the internal channel may be provided with a throttle on the pilot chamber side of the branch path of the branch path.
  • the pilot flow control valve according to the present invention as seen from the second aspect is: An inlet port, an outlet port, a main flow path connecting the inlet port and the outlet port, a valve seat provided between a primary flow path and a secondary flow path of the main flow path, a pilot chamber, and the pilot A body having a pilot discharge channel connecting the chamber and the outlet port;
  • the first closing direction approaching the valve seat and the first opening direction away from the valve seat are movable, partitioning the main flow path and the pilot chamber, and moving in the first opening direction
  • the body is configured to increase an opening area of a first variable throttle formed between the main flow path and the pilot chamber and move in the first closing direction to reduce the opening area of the first variable throttle.
  • An inserted main valve body having a pilot supply channel connecting the pilot chamber and the inlet port and a sub pilot supply channel connecting the pilot chamber and the outlet port therein
  • a first spring that applies an urging force in the first closing direction to the main valve body
  • a second opening direction and the second variable throttle for partitioning the pilot chamber and the pilot discharge flow path and increasing an opening area of a second variable throttle formed between the pilot chamber and the pilot discharge flow path.
  • a pilot valve body inserted into the body so as to be movable in a second closing direction for reducing an opening area of the pilot valve body, and having an internal flow path connecting the pilot chamber and the pilot discharge flow path; , Driving force adding means for applying a variable driving force in the second opening direction to the pilot valve body; A second spring for applying a biasing force in the second closing direction to the pilot valve body; And a check valve that allows passage of only one-way flow from the outlet port toward the pilot chamber in the sub-pilot supply flow path.
  • the pilot flow control valve when the pressure of the primary flow path becomes smaller than the pressure of the secondary flow path with the main flow path open, the secondary pilot supply flow path The working fluid in the secondary channel flows through the pilot chamber.
  • the pressure in the pilot chamber is increased more quickly than in the case where the working fluid in the secondary side channel flows into the pilot chamber through the pilot discharge channel and the second variable throttle, and the main valve body is The main flow path can be closed by moving in the closing direction. Therefore, the performance of the pilot flow control valve can be improved.
  • the pilot flow control valve according to the present invention as seen from the third aspect is An inlet port, an outlet port, a main channel connecting the inlet port and the outlet port, a valve seat provided between a primary channel and a secondary channel of the main channel, a pilot chamber, and the pilot chamber And a pilot discharge passage connecting the outlet port and a body having a balance chamber;
  • the first closing direction approaching the valve seat and the first opening direction away from the valve seat are movable, partitioning the main flow path and the pilot chamber, and moving in the first opening direction
  • the body is configured to increase an opening area of a first variable throttle formed between the main flow path and the pilot chamber and move in the first closing direction to reduce the opening area of the first variable throttle.
  • An inserted main valve body having a pilot supply flow path connecting the pilot chamber and the inlet port therein; A first spring that applies an urging force in the first closing direction to the main valve body; An opening area of a second variable throttle formed between the pilot chamber and the pilot discharge channel is divided between the pilot chamber and the pilot discharge channel and between the pilot chamber and the balance chamber, respectively.
  • a pilot valve element inserted into the body so as to be movable in a second opening direction to be increased and a second closing direction in which an opening area of the second variable throttle is decreased, the pilot chamber, the pilot discharge flow path,
  • a spool-shaped pilot valve body having an internal flow path for connecting Driving force adding means for applying a variable driving force in the second opening direction to the pilot valve body;
  • a second spring that applies an urging force in the second closing direction to the pilot valve body,
  • the internal flow path of the pilot valve body has a branch path connected to the balance chamber, and a throttle is provided on the pilot chamber side of the branch path of the branch path in the internal flow path. is there.
  • the pilot valve body moves so that the pressure difference before and after the second variable throttle is constant and the balance is maintained with the main flow path open.
  • the flow rate of the pilot discharge passage can be controlled to be constant without depending on the pressure difference before and after the second variable throttle.
  • the flow rate of the main flow channel depends on the flow rate of the pilot discharge flow channel. Therefore, even if the pressure of the primary flow channel of the main flow channel fluctuates, The flow rate of the working fluid passing through the flow path can be kept constant. Therefore, the performance of the pilot flow control valve can be improved.
  • the performance of the pilot type flow control valve can be improved.
  • FIG. 1 is a diagram showing a schematic configuration of a pilot flow control valve according to an embodiment of the present invention.
  • FIG. 2 is a hydraulic circuit diagram of the pilot flow control valve shown in FIG.
  • FIG. 3 is a diagram showing a schematic configuration of a pilot flow control valve according to a reference example of the present invention.
  • FIG. 4 is a hydraulic circuit diagram of the pilot flow control valve according to the reference example shown in FIG.
  • FIG. 5 is a diagram showing a schematic configuration of a pilot flow control valve according to the aspect described in Non-Patent Document 1.
  • FIG. 3 is a diagram showing a schematic configuration of a pilot flow control valve according to a reference example of the present invention
  • FIG. 4 is a hydraulic circuit diagram of the pilot flow control valve according to the reference example shown in FIG.
  • a pilot flow control valve 101 includes a body 2, a main valve body 3 inserted into the body 2, a pilot valve body 5 inserted into the body 2, and a solenoid 50 that moves the pilot valve body 5. It has.
  • the body 2 includes an inlet port 21, an outlet port 22, a main passage 25 through which a working fluid flows from the inlet port 21 to the outlet port 22, a valve seat 23 formed in the main passage 25, a pilot chamber 43, a pilot discharge passage 60 etc. are provided.
  • the main valve body 3 is inserted into the body 2 so as to partition the main flow path 25 and the pilot chamber 43, and moves in a first closing direction approaching the valve seat 23 and a first opening direction separating from the valve seat 23. can do.
  • the main valve body 3 is urged in the first closing direction by a spring 42.
  • the main valve body 3 When the main valve body 3 is seated on the valve seat 23, the main flow path 25 is closed, and the opening degree of the main flow path 25 changes according to the distance between the main valve body 3 and the valve seat 23.
  • the main valve body 3 has a stepped cylindrical shape with a stepped surface in which the outer diameter at the sliding portion with the body 2 and the outer diameter at the seating portion with the valve seat 23 are different. However, it may be a cylindrical shape having the same outer diameter without a stepped surface.
  • a notch 38 is provided on the outer peripheral surface of the main valve body 3, and the primary flow path 11 in the notch 38 and the primary flow path 25 are connected by a pilot supply flow path 31.
  • a variable throttle 32 is formed between the pilot supply channel 31 and the pilot chamber 43 by the cooperation of the outer peripheral surface of the main valve body 3, the notch 38 and the inner peripheral surface of the body 2. The opening area of the variable throttle 32 increases as the main valve element 3 moves in the first opening direction, and decreases as the main valve element 3 moves in the first closing direction.
  • the pilot valve body 5 is inserted into the body 2 so as to partition the pilot chamber 43 and the pilot discharge flow path 60.
  • the pilot valve body 5 can move in a second opening direction that is the direction of the driving force F applied from the solenoid 50 and in a second closing direction that is opposite to the second opening direction.
  • the surface of the pilot valve body 5 in the second opening direction is exposed to the pilot chamber 43.
  • a notch 68 is formed on the outer peripheral surface of the pilot valve body 5.
  • An internal passage 64 that opens into the notch 68 and the pilot chamber 43 is formed in the pilot valve body 5.
  • a variable throttle 63 is formed between the internal passage 64 and the pilot discharge passage 60 by cooperation of the outer peripheral surface of the pilot valve body 5, the notch 68 and the inner peripheral surface of the body 2. The opening area of the variable throttle 63 increases as the pilot valve body 5 moves in the second opening direction, and decreases as the pilot valve body 5 moves in the second closing direction.
  • the variable throttle 63 has a reduced opening area, and the main valve body 3 is seated on the valve seat 23.
  • the pilot valve body 5 is moved in the second opening direction by energization of the solenoid 50 and the opening area of the variable throttle 63 is increased, the working fluid flows from the pilot chamber 43 to the pilot discharge passage 60, and the pilot chamber The pressure of the working fluid 43 decreases. Thereby, the main valve body 3 moves in the first opening direction, and the main flow path 25 is opened.
  • the pilot valve body 5 is not limited to the poppet type or the spool type, but the main valve body 3 is seated on the valve seat 23 and the pilot valve body 5 is in the closed position.
  • the pressure of the working fluid at the outlet port 22 becomes high, the working fluid leaks from the outlet port 22 to the pilot chamber 43 through the gap between the main valve body 3 and the body 2. Further, the working fluid flows out from the pilot chamber 43 to the primary side flow path 11 through the pilot supply flow path 31 through the gap between the body 2 and the main valve body 3. Therefore, when the fluid pressure actuator 100 is stopped and the above-described working fluid leaks, the stopped state cannot be maintained.
  • the pilot valve body 5 is not limited to the poppet type or the spool type, and the pilot discharge flow is in a state where the main flow path 25 is opened.
  • the main valve body 3 is closed first due to the relationship between the pressure P 1 of the primary flow path 11 acting on the main valve body 3, the pressure P 3 of the pilot chamber 43, and the spring force of the spring 42. Move in the direction.
  • the path through which the high-pressure working fluid is supplied to the pilot chamber 43 is the pilot supply flow path 31, but since the variable throttle 32 is provided therebetween, the high-pressure working fluid is supplied to the pilot chamber 43, It takes time for the pressure in the pilot chamber 43 to rise.
  • FIG. 1 is a diagram showing a schematic configuration of a pilot flow control valve 1 according to an embodiment of the present invention
  • FIG. 2 is a hydraulic circuit diagram of the pilot flow control valve 1 shown in FIG.
  • the pilot flow control valve 1 is used as a main control valve for controlling the flow rate of oil from a hydraulic pump for a work machine, for turning, and for traveling in a work machine.
  • the usage pattern of the pilot type flow control valve 1 is not limited to the above.
  • power machines hereinavy machinery
  • work machines such as hydraulic excavators, cranes, wheel loaders, and bulldozers are collectively referred to as “work machines”.
  • a pilot flow control valve 1 includes a body 2, a poppet-shaped main valve body 3 inserted into the body 2, and a spool type inserted into the body 2 so as to be coaxial with the main valve body 3.
  • the pilot valve body 5 and a solenoid 50 which is a driving force adding means for providing a driving force for operating the pilot valve body 5 are provided.
  • the body 2 may be formed as a separate body divided into a plurality of parts, and each body 2 may store the main valve body 3 and the pilot valve body 5 separately.
  • the body 2 is provided with an inlet port 21, an outlet port 22, and a main flow path 25 through which a working fluid flows from the inlet port 21 to the outlet port 22.
  • a valve seat 23 is formed in the main flow path 25.
  • the inlet port 21 is connected to a hydraulic pressure source such as a hydraulic pump, and the outlet port 22 is connected to the fluid pressure actuator 100.
  • the body 2 is provided with a pilot chamber 43, a balance chamber 45, and a pilot discharge channel 60.
  • the main valve body 3 is a columnar body inscribed in a cylindrical sliding surface formed in the body 2.
  • the main valve body 3 is inserted into the body 2 so as to partition the main flow path 25 and the pilot chamber 43.
  • the main valve body 3 can be seated on the valve seat 23 and can move in a first closing direction approaching the valve seat 23 and a first opening direction moving away from the valve seat 23.
  • the main flow path 25 is closed, and when the main valve body 3 moves in the first opening direction and moves away from the valve seat 23, the main flow path 25 is closed. Is released.
  • the main valve body 3 is biased by the spring 42 in the first closing direction.
  • the main flow path 25 is divided into the primary side flow path 11 and the secondary side flow path 12 by the main valve body 3 seated on the valve seat 23.
  • a notch 38 is formed on the outer peripheral surface of the main valve body 3.
  • a pilot supply flow path 31 that connects the notch 38 and a surface in the first closing direction of the main valve body 3 (hereinafter also referred to as “front surface”) is formed in the main valve body 3.
  • the pilot supply flow path 31 is a flow path that connects the primary flow path 11 and the pilot chamber 43 and supplies the working fluid from the primary flow path 11 to the pilot chamber 43.
  • the pilot supply flow path 31 is provided with a check valve 33 that allows a unidirectional flow from the primary flow path 11 to the pilot chamber 43 to pass through the main flow path 25 but does not allow the reverse flow to pass therethrough.
  • a variable throttle 32 is provided between the pilot supply flow path 31 and the pilot chamber 43.
  • the variable throttle 32 is formed by the cooperation of the outer peripheral surface of the main valve body 3 and the notch 38 and the inner peripheral surface of the body 2.
  • the opening area of the variable throttle 32 is throttled (closed) while the main valve body 3 is seated on the valve seat 23.
  • the opening area of the variable throttle 32 increases as the main valve element 3 moves in the first opening direction, and decreases as the main valve element 3 moves in the first closing direction.
  • a sub pilot supply flow path 35 that connects the secondary side flow path 12 and the pilot chamber 43 is formed in the main valve body 3.
  • the sub-pilot supply channel 35 includes a surface exposed to the first opening direction side of the main valve body 3 (hereinafter also referred to as “rear surface”) and a portion exposed to the main channel 25 on the outer peripheral surface of the main valve body 3. Is connected.
  • the sub pilot supply flow path 35 is provided with a check valve 36 that allows a one-way flow from the secondary side flow path 12 to the pilot chamber 43 to pass therethrough but does not allow the reverse flow to pass therethrough.
  • the pilot valve body 5 is a cylindrical body having an open end that is inscribed in a cylindrical sliding surface formed in the body 2.
  • the pilot valve body 5 is inserted into the body 2 so as to partition between the pilot chamber 43 and the pilot discharge channel 60 and between the pilot discharge channel 60 and the balance chamber 45.
  • the pilot valve body 5 is formed with a notch 68 provided on the outer peripheral surface and an internal passage 64.
  • the internal passage 64 connects the pilot chamber 43 and the pilot discharge channel 60 by connecting the notch 68 and the pilot chamber 43.
  • a variable throttle 63 is formed between the internal passage 64 and the pilot discharge passage 60 by the cooperation of the outer peripheral surface of the pilot valve body 5, the notch 68 and the inner peripheral surface of the body 2.
  • the pilot valve body 5 has a direction to increase the opening area of the variable throttle 63 (hereinafter referred to as “second opening direction”) and a direction to decrease the opening area of the variable throttle 63 (hereinafter referred to as “second closing direction”). It is possible to move to.
  • the internal passage 64 has a branch path 64 a connected to the balance chamber 45.
  • the branch path 64a is branched from the internal passage 64 on the pilot chamber 43 side with respect to the variable throttle 63, that is, on the pilot chamber 43 side with respect to the notch 68, and in the internal passage 64, on the pilot chamber 43 side with respect to the branch path 64a.
  • a fixed diaphragm 66 is formed. That is, the fixed throttle 66 is formed on the internal passage 64 that connects the pilot chamber 43 and the pilot discharge channel 60. Therefore, the balance chamber 45 and the pilot chamber 43 are communicated with each other via the internal passage 64 (including the branch path 64a, the same applies hereinafter), and a fixed throttle 66 exists between them.
  • the balance chamber 45 and the pilot discharge channel 60 are connected via an internal passage 64, and a variable throttle 63 exists between them.
  • the pilot valve body 5 is given a driving force F in the second opening direction by the solenoid 50.
  • the driving force F is variable according to a control signal applied to the solenoid 50.
  • the pilot valve body 5 is given a biasing force in the second closing direction opposite to the second opening direction by the spring 41.
  • the opening area of the variable aperture 63 is reduced (closed) when the solenoid 50 is off.
  • the opening area of the variable throttle 63 increases in proportion to the movement of the pilot valve body 5 in the second opening direction in proportion to the control signal given to the solenoid 50, and the pilot valve body 5 in the second closing direction. Decreases with movement.
  • the solenoid 50 includes a plunger 51 (movable iron core) connected to the pilot valve body 5 and a coil 52 provided around the plunger 51.
  • the plunger 51 and the spring 41 are disposed in the balance chamber 45.
  • the solenoid 50 is employed as the driving force adding means for applying the driving force to the pilot valve body 5, but the driving force adding means is not limited to this, and is a hydraulic pilot type (hydraulic driving type). May be.
  • the pilot valve body 5 When the solenoid 50 is off, the pilot valve body 5 is in a state where the opening area of the variable restrictor 63 is restricted, and the pilot discharge passage 60 is closed. At this time, the main valve body 3 is seated on the valve seat 23 and the main flow path 25 is closed. Furthermore, the opening area of the variable throttle 32 is reduced, and the pilot supply flow path 31 is closed.
  • the pressure of the working fluid in the primary channel 11 of the main channel 25 is the primary pressure P 1
  • the pressure of the working fluid in the secondary channel 12 is the secondary pressure P 2
  • the working fluid of the pilot chamber 43 the working fluid of the pilot chamber 43.
  • the check valve 33 is provided in the pilot supply flow path 31, the working fluid cannot flow from the pilot supply flow path 31 to the primary flow path 11 of the main flow path 25.
  • the working fluid leakage from the secondary side flow path 12 to the primary side flow path 11 through the pilot chamber 43 when the main flow path 25 is closed is suppressed, and the pilot flow control valve 1 Has been compensated for.
  • the fluid pressure actuator 100 is held in a stopped state by closing the main flow path 25, the working fluid leakage from the secondary side flow path 12 to the primary side flow path 11 is suppressed.
  • the stop state of the fluid pressure actuator 100 is maintained well.
  • the opening area of the variable throttle 32 increases, and the flow rate of the working fluid flowing through the variable throttle 32 increases. Since the flow rate of the working fluid passing through the variable throttle 32 and the flow rate of the working fluid passing through the variable throttle 63 are always equal, the movement amount of the main valve body 3 depends on the movement amount of the pilot valve body 5.
  • variable throttle 63 exists between the primary flow path 11 of the main flow path 25 and the pilot chamber 43, and a variable throttle 63 and a fixed throttle 66 exist between the pilot chamber 43 and the pilot discharge flow path 60. Therefore, the pressure decreases in the order of “primary side pressure P 1 > pilot pressure P 3 > balance pressure P 4 > secondary side pressure P 2 ”, and the main valve body 3 and the pilot valve body 5 remain in a fixed position.
  • the pilot pressure P 3 acts on the pilot valve body front surface of the pilot valve body 5 facing the pilot chamber 43, and the balance chamber.
  • the balance pressure P 4 acts on the back surface of the pilot valve body 5 facing the 45.
  • the spring force by the spring 41 and the driving force F by the solenoid 50 also act on the back surface of the pilot valve body.
  • the pilot valve body 5 is in a position where the force acting on the front surface of the pilot valve body (pilot pressure P 3 ) and the force acting on the rear surface of the pilot valve body (balance pressure P 4 , spring force, driving force F) are balanced. Will move.
  • the pressure difference generated before and after the fixed throttle 66 (pressure difference between the pilot pressure P 3 and the balance pressure P 4 ) is a predetermined value determined based on the spring force by the spring 41 and the driving force F by the solenoid 50. For this reason, the flow rate of the working fluid passing through the fixed throttle 66 becomes a predetermined value without being affected by pressure fluctuations such as the primary pressure P 1 . Further, since the flow rate passing through the fixed restrictor 66 and the flow rate passing through the variable restrictor 63 are equal, the pilot flow rate passing through the pilot discharge passage 60 downstream of the variable restrictor 63 also becomes a predetermined value.
  • the flow rate passing through the fixed restrictor 66, the flow rate passing through the variable restrictor 63, and the flow rate passing through the variable restrictor 32 are equal, and these flow rates are hereinafter referred to as pilot flow rates. Since the flow rate of the main flow path 25 depends on the pilot flow rate of the pilot discharge flow path 60, the flow rate of the pilot discharge flow path 60 is kept constant even if the pressure of the primary flow path 11 of the main flow path 25 fluctuates. By maintaining the flow rate at a constant value, the flow rate of the working fluid passing through the main flow path 25 can be maintained at a constant value. Therefore, the performance of the pilot flow control valve can be improved.
  • the pilot valve body 5 moves so that the pressure difference generated before and after the fixed throttle 66 is constant.
  • the pilot valve body 5 that operates as a pressure compensation spool can provide the pilot flow control valve 1 with a pressure compensation function.
  • the pilot flow rate that passes through the fixed throttle 66 is applied to the pilot valve body 5 by the spring force applied to the pilot valve body 5 by the spring 41 and the solenoid 50 regardless of changes in the primary side pressure P 1 or the secondary side pressure P 2. This corresponds to the driving force F to be applied.
  • the pilot flow rate that passes through the fixed throttle and the pilot discharge flow path 60 downstream thereof is in accordance with the operation amount of the pilot valve body 5 by the solenoid 50, and the flow rate of the main flow path 25 depends on the pilot flow rate.
  • the flow rate of the flow path 25 can be maintained at a value corresponding to the pilot flow rate.
  • the primary side pressure P 1 may be lower than the secondary side pressure P 2 .
  • the pilot pressure P 3 is lower than the secondary side pressure P 2 , the working fluid flows from the secondary side passage 12 into the pilot chamber 43 through the sub pilot supply passage 35.
  • the pilot pressure P 3 is quickly increased and the main valve body 3 is moved in the first closing direction as compared with the case where the working fluid flows into the pilot chamber 43 through the pilot discharge flow path 60 and the variable throttle 63.
  • the main flow path 25 can be closed.
  • the working fluid is piloted through both the pilot discharge flow path 60 and the sub pilot supply flow path 35.
  • the working fluid may be supplied to the chamber 43, or the working fluid may be supplied to the pilot chamber 43 only from the auxiliary pilot supply channel 35.
  • the primary pressure P 1 becomes lower than the secondary pressure P 2
  • the main flow path 25 is quickly closed.
  • the fluid pressure actuator 100 connected to the secondary flow path 12 Is a cylinder that operates the arm of the work machine, it is possible to prevent a situation in which the arm drops momentarily due to a decrease in the pressure of the working fluid during the arm raising operation.
  • the pilot flow control valve 1 according to the present embodiment, the second problem described above can be solved.
  • the pilot flow control valve 1 may not include the sub pilot supply flow path 35 and the check valve 36 provided in the main valve body 3. Similarly, the pilot flow control valve 1 may not include the fixed throttle 66 provided in the internal passage 64 of the pilot valve body 5. Further, in the pilot type flow control valve 1, the pilot valve body 5 may be a poppet type.
  • the pilot flow control valve 1 may not include the check valve 33 in the pilot supply flow path 31 provided in the main valve body 3. Similarly, the pilot flow control valve 1 may not include the fixed throttle 66 provided in the internal passage 64 of the pilot valve body 5. Further, in the pilot type flow control valve 1, the pilot valve body 5 may be a poppet type.
  • the pilot flow control valve 1 does not have to include the check valve 33 in the pilot supply flow path 31 provided in the main valve body 3.
  • the pilot flow control valve 1 may not include the auxiliary pilot supply flow path 35 and the check valve 36 provided in the main valve body 3.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

A pilot-type flow control valve (1) is provided with: a body (2) provided with a main channel (25) in which a valve seat (23) is formed, a pilot chamber (43), and a pilot discharge channel (60); a main valve body (3) for partitioning the main channel (25) and the pilot chamber (43), the main valve body (3) being capable of being seated on the valve seat (23); a spring (42) for urging the main valve body (3) so as to seat the main valve body (3); a pilot valve body (5) for partitioning the pilot discharge channel (60) from the pilot chamber (43); a solenoid (50) for activating the pilot valve body (5); and a spring (41) for urging the pilot valve body (5). Inside the main valve body (3), a pilot supply channel (31) is formed for connecting the pilot chamber (43) and a primary-side channel (11) of the main channel (25), the pilot supply channel (31) being provided with a check valve (33) for allowing passage of only a flow from the primary-side channel (11) toward the pilot chamber (43).

Description

パイロット式流量制御弁Pilot flow control valve
　本発明は、パイロット式流量制御弁に関する。 The present invention relates to a pilot type flow control valve.
　従来、電磁力などによってパイロット弁体を作動し、主弁体に作用する流体の圧力差で主弁体を開閉するように構成されたパイロット式弁装置が知られている。このようなパイロット式弁装置の一例として、非特許文献１に示されるような、制御信号に比例した流量制御が可能なパイロット式流量制御弁がある。 Conventionally, there has been known a pilot type valve device configured to operate a pilot valve body by electromagnetic force or the like and open and close the main valve body by a pressure difference of a fluid acting on the main valve body. As an example of such a pilot type valve device, there is a pilot type flow rate control valve capable of controlling the flow rate in proportion to a control signal as shown in Non-Patent Document 1.
　図５は、非特許文献１に記載された態様のパイロット式流量制御弁１０２の概略構成を示した図である。パイロット式流量制御弁１０２は、入口ポート２１から出口ポート２２へ作動流体が流れるメイン流路２５に設けられたバルブシート２３に着座可能な主弁体３と、主弁体３をバルブシート２３へ近づく向きに付勢するスプリング４２とを備えている。メイン流路２５は、バルブシート２３に着座した主弁体３によって、入口ポート２１側の一次側流路１１と、出口ポート２２側の二次側流路１２とに分けられている。また、主弁体３は、主弁体３へパイロット圧を付与するパイロット室４３とメイン流路２５との間を仕切っている。主弁体３の周囲にはノッチ３８が形成され、主弁体３の内部にはノッチ３８内とメイン流路２５とを接続するパイロット供給流路３１が形成されている。パイロット供給流路３１とパイロット室４３との間には、主弁体３が挿入されたボディ２の内周面と主弁体３とノッチ３８との協働により、可変絞り３２が設けられている。 FIG. 5 is a diagram showing a schematic configuration of the pilot flow control valve 102 according to the aspect described in Non-Patent Document 1. The pilot-type flow control valve 102 includes a main valve body 3 that can be seated on a valve seat 23 provided in a main flow path 25 through which a working fluid flows from an inlet port 21 to an outlet port 22, and the main valve body 3 to the valve seat 23. And a spring 42 that is biased in the approaching direction. The main channel 25 is divided into a primary channel 11 on the inlet port 21 side and a secondary channel 12 on the outlet port 22 side by the main valve body 3 seated on the valve seat 23. Further, the main valve body 3 partitions the pilot chamber 43 that applies pilot pressure to the main valve body 3 and the main flow path 25. A notch 38 is formed around the main valve body 3, and a pilot supply flow path 31 that connects the inside of the notch 38 and the main flow path 25 is formed inside the main valve body 3. A variable throttle 32 is provided between the pilot supply passage 31 and the pilot chamber 43 by the cooperation of the inner peripheral surface of the body 2 in which the main valve body 3 is inserted, the main valve body 3 and the notch 38. Yes.
　パイロット室４３と二次側流路１２とは、パイロット排出流路６０で接続されている。パイロット室４３とパイロット排出流路６０との間にはパイロットバルブシート５７が設けられている。パイロット式流量制御弁１０２は、このパイロットバルブシート５７に着座可能なパイロット弁体５と、パイロット弁体５をパイロットバルブシート５７へ近づく向きへ付勢するスプリング４１と、パイロット弁体５をパイロットバルブシート５７から離れる向きへの通電量に応じた駆動力を付与するソレノイド５０とを、更に備えている。 The pilot chamber 43 and the secondary side flow path 12 are connected by a pilot discharge flow path 60. A pilot valve seat 57 is provided between the pilot chamber 43 and the pilot discharge passage 60. The pilot flow control valve 102 includes a pilot valve body 5 that can be seated on the pilot valve seat 57, a spring 41 that biases the pilot valve body 5 toward the pilot valve seat 57, and the pilot valve body 5 as a pilot valve. And a solenoid 50 that applies a driving force in accordance with the amount of energization in the direction away from the seat 57.
　上記構成のパイロット式流量制御弁１０２において、パイロット弁体５がパイロットバルブシート５７に着座している状態では、主弁体３がバルブシート２３に着座している。このとき、可変絞り３２の開口面積は絞られているが僅かな漏れにより、パイロット室４３の作動流体の圧力と一次側流路１１の作動流体の圧力とが等しい。そして、主弁体３における一次側圧力が作用している面積よりもパイロット圧力が作用している面積が大きいことにより、主弁体３はバルブシート２３に着座した状態で留まっている。 In the pilot flow control valve 102 configured as described above, the main valve body 3 is seated on the valve seat 23 when the pilot valve body 5 is seated on the pilot valve seat 57. At this time, the opening area of the variable throttle 32 is narrowed, but the pressure of the working fluid in the pilot chamber 43 and the pressure of the working fluid in the primary channel 11 are equal due to slight leakage. The main valve body 3 remains seated on the valve seat 23 because the area on which the pilot pressure acts is larger than the area on the main valve body 3 on which the primary pressure acts.
　そして、ソレノイド５０への通電によりパイロット弁体５がパイロットバルブシート５７から離れると、パイロット室４３からパイロット排出流路６０へ作動流体の流れが生じ、パイロット室４３の作動流体の圧力が低下する。これにより、主弁体３がバルブシート２３から離れる向きに移動し、メイン流路２５が開放される。 When the pilot valve body 5 is separated from the pilot valve seat 57 by energization of the solenoid 50, the working fluid flows from the pilot chamber 43 to the pilot discharge passage 60, and the pressure of the working fluid in the pilot chamber 43 decreases. Thereby, the main valve body 3 moves in a direction away from the valve seat 23, and the main flow path 25 is opened.
　本発明は、パイロット式流量制御弁の性能を向上することを目的とする。 The object of the present invention is to improve the performance of a pilot flow control valve.
　第１の側面から見た本発明に係るパイロット式流量制御弁は、
入口ポート、出口ポート、前記入口ポートと前記出口ポートを繋ぐメイン流路、前記メイン流路の一次側流路と二次側流路との間に設けられたバルブシート、パイロット室、及び前記パイロット室と前記出口ポートとを接続するパイロット排出流路を有するボディと、
前記バルブシートに近づく第１閉方向と前記バルブシートから離れる第１開方向とへ移動可能であって、前記メイン流路と前記パイロット室との間を仕切り、前記第１開方向へ移動して前記メイン流路と前記パイロット室の間に形成された第１可変絞りの開口面積を増大させ、前記第１閉方向へ移動して前記第１可変絞りの開口面積を減少させるように前記ボディに挿入された主弁体であって、前記パイロット室と前記入口ポートとを接続するパイロット供給流路を内部に有する主弁体と、
前記主弁体に前記第１閉方向の付勢力を与える第１スプリングと、
前記パイロット室と前記パイロット排出流路との間を仕切り、前記パイロット室と前記パイロット排出流路の間に形成された第２可変絞りの開口面積を増大させる第２開方向と前記第２可変絞りの開口面積を減少させる第２閉方向とへ移動可能に前記ボディに挿入されたパイロット弁体であって、前記パイロット室と前記パイロット排出流路とを接続する内部流路を有するパイロット弁体と、
前記パイロット弁体に前記第２開方向の駆動力を与える駆動力付加手段と、
前記パイロット弁体に前記第２閉方向の付勢力を与える第２スプリングと、
前記パイロット供給流路において前記入口ポートから前記パイロット室へ向かう一方向の流れのみを通過させる逆止弁と、を備えているものである。なお、この明細書及び特許請求の範囲において、「開方向」とあるのは「開く向き」を言い、「閉方向」とは「閉じる向き」を言うこととする。 The pilot flow control valve according to the present invention as seen from the first aspect is:
An inlet port, an outlet port, a main flow path connecting the inlet port and the outlet port, a valve seat provided between a primary flow path and a secondary flow path of the main flow path, a pilot chamber, and the pilot A body having a pilot discharge channel connecting the chamber and the outlet port;
The first closing direction approaching the valve seat and the first opening direction away from the valve seat are movable, partitioning the main flow path and the pilot chamber, and moving in the first opening direction The body is configured to increase an opening area of a first variable throttle formed between the main flow path and the pilot chamber and move in the first closing direction to reduce the opening area of the first variable throttle. An inserted main valve body having a pilot supply flow path connecting the pilot chamber and the inlet port therein;
A first spring that applies an urging force in the first closing direction to the main valve body;
A second opening direction and the second variable throttle for partitioning the pilot chamber and the pilot discharge flow path and increasing an opening area of a second variable throttle formed between the pilot chamber and the pilot discharge flow path. A pilot valve body inserted into the body so as to be movable in a second closing direction for reducing an opening area of the pilot valve body, and having an internal flow path connecting the pilot chamber and the pilot discharge flow path; ,
Driving force adding means for applying a driving force in the second opening direction to the pilot valve body;
A second spring for applying a biasing force in the second closing direction to the pilot valve body;
A check valve that allows passage of only a one-way flow from the inlet port to the pilot chamber in the pilot supply flow path. In this specification and claims, “open direction” refers to “opening direction”, and “closed direction” refers to “closing direction”.
　上記本発明に係るパイロット式流量制御弁では、パイロット弁体が閉位置にあっても、出口ポートの作動流体の圧力が高圧となった場合には、主弁体とボディの隙間から作動流体が出口ポートからパイロット室へ漏れ出る。さらに、パイロット室の作動流体は主弁体とボディの隙間からパイロット供給流路へ漏れ出るが、パイロット供給流路に設けられた逆止弁により、パイロット供給流路から入口ポートへ作動流体が流れることができない。このようにして、パイロット式流量制御弁が閉弁時の場合に、メイン流路の二次側流路から一次側流路への（入口ポートから出口ポートへの）パイロット室を介した作動流体の漏出を抑制することができる。よって、パイロット式流量制御弁の性能を向上させることができる。 In the pilot flow control valve according to the present invention, when the pressure of the working fluid at the outlet port becomes high even when the pilot valve is in the closed position, the working fluid flows from the gap between the main valve body and the body. Leak into the pilot room from the exit port. Furthermore, the working fluid in the pilot chamber leaks from the gap between the main valve body and the body to the pilot supply passage, but the working fluid flows from the pilot supply passage to the inlet port by the check valve provided in the pilot supply passage. I can't. Thus, when the pilot type flow control valve is closed, the working fluid passes through the pilot chamber (from the inlet port to the outlet port) from the secondary side channel of the main channel to the primary channel. Leakage can be suppressed. Therefore, the performance of the pilot flow control valve can be improved.
　上記パイロット式流量制御弁が、前記パイロット室と前記出口ポートとを接続するように前記主弁体内に形成された副パイロット供給流路と、前記副パイロット供給流路において、前記出口ポートから前記パイロット室へ向かう流れのみを通過させる逆止弁とを、更に備えていてもよい。 The pilot-type flow control valve has a secondary pilot supply passage formed in the main valve body so as to connect the pilot chamber and the outlet port, and the pilot pilot flow passage from the outlet port to the pilot in the secondary pilot supply passage. A check valve that allows only the flow toward the chamber to pass therethrough may be further provided.
　また、上記パイロット式流量制御弁において、前記ボディが、前記パイロット弁体に前記第２開方向の圧力を作用させるバランス室を更に有し、前記パイロット弁体の前記内部流路が、前記バランス室と接続された分岐路を有し、前記内部流路において前記分岐路の分岐箇所よりも前記パイロット室側に絞りが設けられていてもよい。 In the pilot flow control valve, the body further includes a balance chamber that applies a pressure in the second opening direction to the pilot valve body, and the internal flow path of the pilot valve body includes the balance chamber. The internal channel may be provided with a throttle on the pilot chamber side of the branch path of the branch path.
　第２の側面から見た本発明に係るパイロット式流量制御弁は、
入口ポート、出口ポート、前記入口ポートと前記出口ポートを繋ぐメイン流路、前記メイン流路の一次側流路と二次側流路との間に設けられたバルブシート、パイロット室、及び前記パイロット室と前記出口ポートとを接続するパイロット排出流路を有するボディと、
前記バルブシートに近づく第１閉方向と前記バルブシートから離れる第１開方向とへ移動可能であって、前記メイン流路と前記パイロット室との間を仕切り、前記第１開方向へ移動して前記メイン流路と前記パイロット室の間に形成された第１可変絞りの開口面積を増大させ、前記第１閉方向へ移動して前記第１可変絞りの開口面積を減少させるように前記ボディに挿入された主弁体であって、前記パイロット室と前記入口ポートとを接続するパイロット供給流路と前記パイロット室と前記出口ポートとを接続する副パイロット供給流路とを内部に有する主弁体と、
前記主弁体に前記第１閉方向の付勢力を与える第１スプリングと、
前記パイロット室と前記パイロット排出流路との間を仕切り、前記パイロット室と前記パイロット排出流路の間に形成された第２可変絞りの開口面積を増大させる第２開方向と前記第２可変絞りの開口面積を減少させる第２閉方向とへ移動可能に前記ボディに挿入されたパイロット弁体であって、前記パイロット室と前記パイロット排出流路とを接続する内部流路を有するパイロット弁体と、
前記パイロット弁体に可変な前記第２開方向の駆動力を与える駆動力付加手段と、
前記パイロット弁体に前記第２閉方向の付勢力を与える第２スプリングと、
前記副パイロット供給流路において前記出口ポートから前記パイロット室へ向かう一方向の流れのみを通過させる逆止弁とを備えているものである。 The pilot flow control valve according to the present invention as seen from the second aspect is:
An inlet port, an outlet port, a main flow path connecting the inlet port and the outlet port, a valve seat provided between a primary flow path and a secondary flow path of the main flow path, a pilot chamber, and the pilot A body having a pilot discharge channel connecting the chamber and the outlet port;
The first closing direction approaching the valve seat and the first opening direction away from the valve seat are movable, partitioning the main flow path and the pilot chamber, and moving in the first opening direction The body is configured to increase an opening area of a first variable throttle formed between the main flow path and the pilot chamber and move in the first closing direction to reduce the opening area of the first variable throttle. An inserted main valve body having a pilot supply channel connecting the pilot chamber and the inlet port and a sub pilot supply channel connecting the pilot chamber and the outlet port therein When,
A first spring that applies an urging force in the first closing direction to the main valve body;
A second opening direction and the second variable throttle for partitioning the pilot chamber and the pilot discharge flow path and increasing an opening area of a second variable throttle formed between the pilot chamber and the pilot discharge flow path. A pilot valve body inserted into the body so as to be movable in a second closing direction for reducing an opening area of the pilot valve body, and having an internal flow path connecting the pilot chamber and the pilot discharge flow path; ,
Driving force adding means for applying a variable driving force in the second opening direction to the pilot valve body;
A second spring for applying a biasing force in the second closing direction to the pilot valve body;
And a check valve that allows passage of only one-way flow from the outlet port toward the pilot chamber in the sub-pilot supply flow path.
　上記本発明に係るパイロット式流量制御弁によれば、メイン流路が開放されている状態で一次側流路の圧力が二次側流路の圧力より小さくなったときに、副パイロット供給流路を通じて二次側流路の作動流体がパイロット室へ流入する。これにより、パイロット排出流路と第２可変絞りとを通じて二次側流路の作動流体をパイロット室へ流入させる場合と比較して速やかに、パイロット室の圧力を高めて、主弁体を第１閉方向へ移動させて、メイン流路を閉止することができる。よって、パイロット式流量制御弁の性能を向上させることができる。 According to the pilot flow control valve according to the present invention, when the pressure of the primary flow path becomes smaller than the pressure of the secondary flow path with the main flow path open, the secondary pilot supply flow path The working fluid in the secondary channel flows through the pilot chamber. As a result, the pressure in the pilot chamber is increased more quickly than in the case where the working fluid in the secondary side channel flows into the pilot chamber through the pilot discharge channel and the second variable throttle, and the main valve body is The main flow path can be closed by moving in the closing direction. Therefore, the performance of the pilot flow control valve can be improved.
　第３の側面から見た本発明に係るパイロット式流量制御弁は、
入口ポート、出口ポート、前記入口ポートと前記出口ポートを繋ぐメイン流路、前記メイン流路の一次側流路と二次側流路との間に設けられたバルブシート、パイロット室、前記パイロット室と前記出口ポートとを接続するパイロット排出流路、及びバランス室を有するボディと、
前記バルブシートに近づく第１閉方向と前記バルブシートから離れる第１開方向とへ移動可能であって、前記メイン流路と前記パイロット室との間を仕切り、前記第１開方向へ移動して前記メイン流路と前記パイロット室の間に形成された第１可変絞りの開口面積を増大させ、前記第１閉方向へ移動して前記第１可変絞りの開口面積を減少させるように前記ボディに挿入された主弁体であって、前記パイロット室と前記入口ポートとを接続するパイロット供給流路を内部に有する主弁体と、
前記主弁体に前記第１閉方向の付勢力を与える第１スプリングと、
前記パイロット室と前記パイロット排出流路との間及び前記パイロット室と前記バランス室との間をそれぞれ仕切り、前記パイロット室と前記パイロット排出流路の間に形成された第２可変絞りの開口面積を増大させる第２開方向と前記第２可変絞りの開口面積を減少させる第２閉方向とへ移動可能に前記ボディに挿入されたパイロット弁体であって、前記パイロット室と前記パイロット排出流路とを接続する内部流路を有するスプール形のパイロット弁体と、
前記パイロット弁体に可変な前記第２開方向の駆動力を与える駆動力付加手段と、
前記パイロット弁体に前記第２閉方向の付勢力を与える第２スプリングと、を備え、
前記パイロット弁体の前記内部流路が、前記バランス室と接続された分岐路を有し、前記内部流路において前記分岐路の分岐箇所よりも前記パイロット室側に絞りが設けられているものである。 The pilot flow control valve according to the present invention as seen from the third aspect is
An inlet port, an outlet port, a main channel connecting the inlet port and the outlet port, a valve seat provided between a primary channel and a secondary channel of the main channel, a pilot chamber, and the pilot chamber And a pilot discharge passage connecting the outlet port and a body having a balance chamber;
The first closing direction approaching the valve seat and the first opening direction away from the valve seat are movable, partitioning the main flow path and the pilot chamber, and moving in the first opening direction The body is configured to increase an opening area of a first variable throttle formed between the main flow path and the pilot chamber and move in the first closing direction to reduce the opening area of the first variable throttle. An inserted main valve body having a pilot supply flow path connecting the pilot chamber and the inlet port therein;
A first spring that applies an urging force in the first closing direction to the main valve body;
An opening area of a second variable throttle formed between the pilot chamber and the pilot discharge channel is divided between the pilot chamber and the pilot discharge channel and between the pilot chamber and the balance chamber, respectively. A pilot valve element inserted into the body so as to be movable in a second opening direction to be increased and a second closing direction in which an opening area of the second variable throttle is decreased, the pilot chamber, the pilot discharge flow path, A spool-shaped pilot valve body having an internal flow path for connecting
Driving force adding means for applying a variable driving force in the second opening direction to the pilot valve body;
A second spring that applies an urging force in the second closing direction to the pilot valve body,
The internal flow path of the pilot valve body has a branch path connected to the balance chamber, and a throttle is provided on the pilot chamber side of the branch path of the branch path in the internal flow path. is there.
　上記本発明に係るパイロット式流量制御弁によれば、メイン流路が開放されている状態で、第２可変絞り前後の圧力差が一定となるようにパイロット弁体が移動し、バランスを保つ。このパイロット弁体の圧力補償機能によって、第２可変絞り前後の圧力差に依存せず、パイロット排出流路の流量を一定に制御することができる。この結果、メイン流路の流量はパイロット排出流路の流量に依存するため、メイン流路の一次側流路の圧力が変動しても、パイロット排出流路の流量を一定に保つことで、メイン流路を通過する作動流体の流量を一定に保持することができる。よって、パイロット式流量制御弁の性能を向上させることができる。 According to the pilot flow control valve according to the present invention, the pilot valve body moves so that the pressure difference before and after the second variable throttle is constant and the balance is maintained with the main flow path open. By this pressure compensation function of the pilot valve body, the flow rate of the pilot discharge passage can be controlled to be constant without depending on the pressure difference before and after the second variable throttle. As a result, the flow rate of the main flow channel depends on the flow rate of the pilot discharge flow channel. Therefore, even if the pressure of the primary flow channel of the main flow channel fluctuates, The flow rate of the working fluid passing through the flow path can be kept constant. Therefore, the performance of the pilot flow control valve can be improved.
　本発明によれば、パイロット式流量制御弁の性能を向上させることができる。 According to the present invention, the performance of the pilot type flow control valve can be improved.
図１は本発明の一実施形態に係るパイロット式流量制御弁の概略構成を示す図である。FIG. 1 is a diagram showing a schematic configuration of a pilot flow control valve according to an embodiment of the present invention. 図２は図１に示すパイロット式流量制御弁の油圧回路図である。FIG. 2 is a hydraulic circuit diagram of the pilot flow control valve shown in FIG. 図３は本発明の参考例に係るパイロット式流量制御弁の概略構成を示した図である。FIG. 3 is a diagram showing a schematic configuration of a pilot flow control valve according to a reference example of the present invention. 図４は図３に示す参考例に係るパイロット式流量制御弁の油圧回路図である。FIG. 4 is a hydraulic circuit diagram of the pilot flow control valve according to the reference example shown in FIG. 図５は非特許文献１に記載された態様のパイロット式流量制御弁の概略構成を示した図である。FIG. 5 is a diagram showing a schematic configuration of a pilot flow control valve according to the aspect described in Non-Patent Document 1.
　非特許文献１に記載のパイロット式流量制御弁１０２では、パイロット弁体５はポペット弁である。前述の従来のパイロット式流量制御弁１０２において、ポペット形のパイロット弁体５に代えてスプール形のパイロット弁体５を採用すると、例えば、図３及び図４に示すパイロット式流量制御弁１０１のようになる。図３は本発明の参考例に係るパイロット式流量制御弁の概略構成を示した図であり、図４は図３に示す参考例に係るパイロット式流量制御弁の油圧回路図である。 In the pilot-type flow control valve 102 described in Non-Patent Document 1, the pilot valve body 5 is a poppet valve. In the above-described conventional pilot type flow control valve 102, when the spool type pilot valve body 5 is employed instead of the poppet type pilot valve body 5, for example, a pilot type flow control valve 101 shown in FIGS. become. FIG. 3 is a diagram showing a schematic configuration of a pilot flow control valve according to a reference example of the present invention, and FIG. 4 is a hydraulic circuit diagram of the pilot flow control valve according to the reference example shown in FIG.
　参考例に係るパイロット式流量制御弁１０１は、ボディ２と、ボディ２に挿入された主弁体３と、ボディ２に挿入されたパイロット弁体５と、パイロット弁体５を移動させるソレノイド５０とを備えている。 A pilot flow control valve 101 according to the reference example includes a body 2, a main valve body 3 inserted into the body 2, a pilot valve body 5 inserted into the body 2, and a solenoid 50 that moves the pilot valve body 5. It has.
　ボディ２には、入口ポート２１、出口ポート２２、入口ポート２１から出口ポート２２へ作動流体が流れるメイン流路２５、メイン流路２５に形成されたバルブシート２３、パイロット室４３、パイロット排出流路６０などが設けられている。 The body 2 includes an inlet port 21, an outlet port 22, a main passage 25 through which a working fluid flows from the inlet port 21 to the outlet port 22, a valve seat 23 formed in the main passage 25, a pilot chamber 43, a pilot discharge passage 60 etc. are provided.
　主弁体３は、メイン流路２５とパイロット室４３とを仕切るようにボディ２に挿入されており、バルブシート２３に近づく第１閉方向と、バルブシート２３から離れる第１開方向とへ移動することができる。主弁体３はスプリング４２によって第１閉方向に付勢されている。主弁体３がバルブシート２３に着座することによってメイン流路２５が閉止され、主弁体３とバルブシート２３との離間距離に応じてメイン流路２５の開度が変化する。なお、図１では、主弁体３は、ボディ２との摺動部における外径とバルブシート２３との着座部における外径とが異なる、段差面のある段付きの円柱形状となっているが、段差面のない同一外径の円柱形状であっても良い。 The main valve body 3 is inserted into the body 2 so as to partition the main flow path 25 and the pilot chamber 43, and moves in a first closing direction approaching the valve seat 23 and a first opening direction separating from the valve seat 23. can do. The main valve body 3 is urged in the first closing direction by a spring 42. When the main valve body 3 is seated on the valve seat 23, the main flow path 25 is closed, and the opening degree of the main flow path 25 changes according to the distance between the main valve body 3 and the valve seat 23. In FIG. 1, the main valve body 3 has a stepped cylindrical shape with a stepped surface in which the outer diameter at the sliding portion with the body 2 and the outer diameter at the seating portion with the valve seat 23 are different. However, it may be a cylindrical shape having the same outer diameter without a stepped surface.
　主弁体３の外周面にはノッチ３８が設けられており、このノッチ３８内とメイン流路２５の一次側流路１１とがパイロット供給流路３１で接続されている。このパイロット供給流路３１とパイロット室４３との間には、主弁体３の外周面とノッチ３８とボディ２の内周面との協働により可変絞り３２が形成されている。可変絞り３２の開口面積は、主弁体３の第１開方向への移動に伴い増大し、主弁体３の第１閉方向への移動に伴い減少する。 A notch 38 is provided on the outer peripheral surface of the main valve body 3, and the primary flow path 11 in the notch 38 and the primary flow path 25 are connected by a pilot supply flow path 31. A variable throttle 32 is formed between the pilot supply channel 31 and the pilot chamber 43 by the cooperation of the outer peripheral surface of the main valve body 3, the notch 38 and the inner peripheral surface of the body 2. The opening area of the variable throttle 32 increases as the main valve element 3 moves in the first opening direction, and decreases as the main valve element 3 moves in the first closing direction.
　パイロット弁体５は、パイロット室４３とパイロット排出流路６０とを仕切るようにボディ２に挿入されている。パイロット弁体５は、ソレノイド５０から与えられる駆動力Ｆの向きである第２開方向と、この第２開方向と反対向きの第２閉方向とへ移動することができる。パイロット弁体５の第２開方向の面はパイロット室４３に露出している。パイロット弁体５の外周面にはノッチ６８が形成されている。そして、このノッチ６８内とパイロット室４３内とに開口する内部通路６４が、パイロット弁体５内に形成されている。内部通路６４とパイロット排出流路６０の間において、パイロット弁体５の外周面とノッチ６８とボディ２の内周面との協働により可変絞り６３が形成されている。可変絞り６３の開口面積は、パイロット弁体５の第２開方向への移動に伴い増大し、パイロット弁体５の第２閉方向への移動に伴い減少する。 The pilot valve body 5 is inserted into the body 2 so as to partition the pilot chamber 43 and the pilot discharge flow path 60. The pilot valve body 5 can move in a second opening direction that is the direction of the driving force F applied from the solenoid 50 and in a second closing direction that is opposite to the second opening direction. The surface of the pilot valve body 5 in the second opening direction is exposed to the pilot chamber 43. A notch 68 is formed on the outer peripheral surface of the pilot valve body 5. An internal passage 64 that opens into the notch 68 and the pilot chamber 43 is formed in the pilot valve body 5. A variable throttle 63 is formed between the internal passage 64 and the pilot discharge passage 60 by cooperation of the outer peripheral surface of the pilot valve body 5, the notch 68 and the inner peripheral surface of the body 2. The opening area of the variable throttle 63 increases as the pilot valve body 5 moves in the second opening direction, and decreases as the pilot valve body 5 moves in the second closing direction.
　上記構成のパイロット式流量制御弁１０１において、ソレノイド５０の非通電時には、可変絞り６３は開口面積が絞られており、主弁体３がバルブシート２３に着座している。そして、ソレノイド５０への通電によりパイロット弁体５が第２開方向に移動し、可変絞り６３の開口面積が増大すると、パイロット室４３からパイロット排出流路６０へ作動流体の流れが生じ、パイロット室４３の作動流体の圧力が低下する。これにより、主弁体３が第１開方向に移動し、メイン流路２５が開放される。 In the pilot flow control valve 101 configured as described above, when the solenoid 50 is not energized, the variable throttle 63 has a reduced opening area, and the main valve body 3 is seated on the valve seat 23. When the pilot valve body 5 is moved in the second opening direction by energization of the solenoid 50 and the opening area of the variable throttle 63 is increased, the working fluid flows from the pilot chamber 43 to the pilot discharge passage 60, and the pilot chamber The pressure of the working fluid 43 decreases. Thereby, the main valve body 3 moves in the first opening direction, and the main flow path 25 is opened.
（第１の課題）
　上記参考例に係るパイロット式流量制御弁１０１において、パイロット弁体５がポペット形やスプール形の形式に限らず、主弁体３がバルブシート２３に着座し且つパイロット弁体５が閉位置にあっても、出口ポート２２の作動流体の圧力が高圧となった場合には、主弁体３とボディ２の隙間から作動流体が出口ポート２２からパイロット室４３へ漏れ出る。さらに、ボディ２と主弁体３の隙間を通じてパイロット室４３から一次側流路１１へパイロット供給流路３１を介して作動流体が流出する。そのため、流体圧アクチュエータ１００が停止しているときに、上記のような作動流体漏れが生じると、その停止状態を維持することができない。 (First issue)
In the pilot flow control valve 101 according to the above reference example, the pilot valve body 5 is not limited to the poppet type or the spool type, but the main valve body 3 is seated on the valve seat 23 and the pilot valve body 5 is in the closed position. However, when the pressure of the working fluid at the outlet port 22 becomes high, the working fluid leaks from the outlet port 22 to the pilot chamber 43 through the gap between the main valve body 3 and the body 2. Further, the working fluid flows out from the pilot chamber 43 to the primary side flow path 11 through the pilot supply flow path 31 through the gap between the body 2 and the main valve body 3. Therefore, when the fluid pressure actuator 100 is stopped and the above-described working fluid leaks, the stopped state cannot be maintained.
（第２の課題）
　また、上記参考例に係るパイロット式流量制御弁１０１において、メイン流路２５が開放されて主弁体３の第１開方向への移動が停止した後で、流体圧アクチュエータ１００への作動流体の供給を停止するために、ソレノイド５０をオフにする。ソレノイド５０がオフとなると、パイロット弁体５に作用している駆動力Ｆが解放され、可変絞り６３が閉じられる。このように、メイン流路２５が開放され且つパイロット排出流路６０が閉止されている状態において、二次側流路１２から一次側流路１１へ作動流体の逆流を防止するために、早急にメイン流路２５が閉じられねばならない。 (Second problem)
Further, in the pilot flow control valve 101 according to the above reference example, after the main flow path 25 is opened and the movement of the main valve body 3 in the first opening direction is stopped, the working fluid is supplied to the fluid pressure actuator 100. To stop the supply, the solenoid 50 is turned off. When the solenoid 50 is turned off, the driving force F acting on the pilot valve body 5 is released, and the variable throttle 63 is closed. As described above, in order to prevent the backflow of the working fluid from the secondary side flow path 12 to the primary side flow path 11 in a state where the main flow path 25 is opened and the pilot discharge flow path 60 is closed, immediately. The main flow path 25 must be closed.
　ところが、図３，４に示される参考例に係るパイロット式流量制御弁１０１では、パイロット弁体５がポペット形やスプール形の形式に限らず、メイン流路２５が開放された状態でパイロット排出流路６０が閉止されると、主弁体３に作用する一次側流路１１の圧力Ｐ1とパイロット室４３の圧力Ｐ3とスプリング４２のばね力との関係により主弁体３が第１閉方向へ移動する。ここで、パイロット室４３へ高圧の作動流体が供給される経路はパイロット供給流路３１であるが、その間に可変絞り３２が設けられているため、パイロット室４３に高圧の作動流体が供給され、パイロット室４３の圧力が上昇するには時間を要する。その結果、主弁体３がメイン流路２５を閉止することに時間を要する。そのため、出口ポート２２に接続された流体圧アクチュエータ１００が作業機械のアームを動作させるシリンダである場合には、アームを停止させるためにソレノイド５０をオフにしたときに、アームを所望の位置で停止できないような不都合が懸念される。 However, in the pilot flow control valve 101 according to the reference example shown in FIGS. 3 and 4, the pilot valve body 5 is not limited to the poppet type or the spool type, and the pilot discharge flow is in a state where the main flow path 25 is opened. When the passage 60 is closed, the main valve body 3 is closed first due to the relationship between the pressure P 1 of the primary flow path 11 acting on the main valve body 3, the pressure P 3 of the pilot chamber 43, and the spring force of the spring 42. Move in the direction. Here, the path through which the high-pressure working fluid is supplied to the pilot chamber 43 is the pilot supply flow path 31, but since the variable throttle 32 is provided therebetween, the high-pressure working fluid is supplied to the pilot chamber 43, It takes time for the pressure in the pilot chamber 43 to rise. As a result, it takes time for the main valve body 3 to close the main flow path 25. Therefore, when the fluid pressure actuator 100 connected to the outlet port 22 is a cylinder for operating the arm of the work machine, the arm is stopped at a desired position when the solenoid 50 is turned off to stop the arm. There are concerns about inconveniences that cannot be made.
（第３の課題）
　また、上記参考例に係るパイロット式流量制御弁１０１において、メイン流路２５及びパイロット排出流路６０が開放された状態で、可変絞り６３を通過する作動流体が一定流量である場合、パイロット室４３と二次側流路１２とを繋ぐ流路に存在する可変絞り６３によって、パイロット圧力Ｐ3は二次側圧力Ｐ2よりも高く、パイロット弁体５は一定の位置に留まっている。ここで、一次側圧力Ｐ1が増大すると、パイロット圧力Ｐ3と二次側圧力Ｐ2との圧力差が大きくなって、パイロット排出流路６０を通過するパイロット流量が増大することになる。このとき、メイン流路２５のメイン流量はパイロット排出流路６０のパイロット流量に依存するため、メイン流量も増大してしまう。このように、一次側圧力Ｐ1の変動により、メイン流量が変動してしまうという不都合がある。 (Third issue)
Further, in the pilot flow control valve 101 according to the above reference example, when the working fluid passing through the variable throttle 63 is a constant flow rate with the main flow path 25 and the pilot discharge flow path 60 being opened, the pilot chamber 43 The pilot pressure P 3 is higher than the secondary pressure P 2 , and the pilot valve body 5 remains at a fixed position by the variable throttle 63 existing in the flow path connecting the secondary side flow path 12 and the secondary side flow path 12. Here, when the primary pressure P 1 increases, the pressure difference between the pilot pressure P 3 and the secondary pressure P 2 increases, and the pilot flow rate passing through the pilot discharge flow path 60 increases. At this time, since the main flow rate of the main flow path 25 depends on the pilot flow rate of the pilot discharge flow path 60, the main flow rate also increases. Thus, there is a disadvantage that the main flow rate fluctuates due to fluctuations in the primary pressure P 1 .
〔本発明の実施形態〕
　以下、上記第１～３の課題を解決し得る本発明の実施形態について、図面を参照して説明する。図１は本発明の一実施形態に係るパイロット式流量制御弁１の概略構成を示す図、図２は図１に示すパイロット式流量制御弁１の油圧回路図である。本実施形態では、パイロット式流量制御弁１を、作業機械において油圧ポンプからの油を作業機用、旋回用、走行用に流量制御するメインコントロールバルブに用いている。但し、パイロット式流量制御弁１の使用形態は上記に限定されない。なお、この明細書では、油圧ショベル、クレーン、ホイールローダ、ブルドーザ等の動力機械類（重機）を総称して「作業機械」という。 Embodiment of the present invention
Hereinafter, embodiments of the present invention capable of solving the first to third problems will be described with reference to the drawings. FIG. 1 is a diagram showing a schematic configuration of a pilot flow control valve 1 according to an embodiment of the present invention, and FIG. 2 is a hydraulic circuit diagram of the pilot flow control valve 1 shown in FIG. In the present embodiment, the pilot flow control valve 1 is used as a main control valve for controlling the flow rate of oil from a hydraulic pump for a work machine, for turning, and for traveling in a work machine. However, the usage pattern of the pilot type flow control valve 1 is not limited to the above. In this specification, power machines (heavy machinery) such as hydraulic excavators, cranes, wheel loaders, and bulldozers are collectively referred to as “work machines”.
　先ず、図１及び図２を参照しながら、本実施形態に係るパイロット式流量制御弁１の概略構成について説明する。本実施形態に係るパイロット式流量制御弁１は、ボディ２と、ボディ２に挿入されたポペット形の主弁体３と、主弁体３と同軸となるようにボディ２に挿入されたスプール形のパイロット弁体５と、パイロット弁体５を動作させるための駆動力を与える駆動力付加手段であるソレノイド５０とを備えている。なお、ボディ２を複数個に分割された別体として形成し、それぞれのボディ２が主弁体３とパイロット弁体５とを別々に収納するようにしてもよい。 First, a schematic configuration of the pilot flow control valve 1 according to the present embodiment will be described with reference to FIGS. 1 and 2. A pilot flow control valve 1 according to this embodiment includes a body 2, a poppet-shaped main valve body 3 inserted into the body 2, and a spool type inserted into the body 2 so as to be coaxial with the main valve body 3. The pilot valve body 5 and a solenoid 50 which is a driving force adding means for providing a driving force for operating the pilot valve body 5 are provided. The body 2 may be formed as a separate body divided into a plurality of parts, and each body 2 may store the main valve body 3 and the pilot valve body 5 separately.
　ボディ２には、入口ポート２１、出口ポート２２、入口ポート２１から出口ポート２２へ作動流体が流れるメイン流路２５が設けられている。このメイン流路２５には、バルブシート２３が形成されている。入口ポート２１は油圧ポンプなどの油圧源と接続されており、出口ポート２２は流体圧アクチュエータ１００と接続されている。さらに、ボディ２には、パイロット室４３と、バランス室４５と、パイロット排出流路６０が設けられている。 The body 2 is provided with an inlet port 21, an outlet port 22, and a main flow path 25 through which a working fluid flows from the inlet port 21 to the outlet port 22. A valve seat 23 is formed in the main flow path 25. The inlet port 21 is connected to a hydraulic pressure source such as a hydraulic pump, and the outlet port 22 is connected to the fluid pressure actuator 100. Further, the body 2 is provided with a pilot chamber 43, a balance chamber 45, and a pilot discharge channel 60.
　主弁体３は、ボディ２に形成された円筒形滑り面に内接している円柱形状体である。主弁体３は、メイン流路２５とパイロット室４３とを仕切るように、ボディ２に挿入されている。 The main valve body 3 is a columnar body inscribed in a cylindrical sliding surface formed in the body 2. The main valve body 3 is inserted into the body 2 so as to partition the main flow path 25 and the pilot chamber 43.
　主弁体３はバルブシート２３に着座可能であって、バルブシート２３へ近づく第１閉方向と、バルブシート２３から離れる第１開方向とに移動可能である。主弁体３が第１閉方向に移動してバルブシート２３に着座するとメイン流路２５が閉止され、主弁体３が第１開方向に移動してバルブシート２３から離れるとメイン流路２５が開放される。主弁体３は、スプリング４２により第１閉方向に付勢されている。バルブシート２３に着座した主弁体３によって、メイン流路２５は一次側流路１１と二次側流路１２とに分けられている。 The main valve body 3 can be seated on the valve seat 23 and can move in a first closing direction approaching the valve seat 23 and a first opening direction moving away from the valve seat 23. When the main valve body 3 moves in the first closing direction and sits on the valve seat 23, the main flow path 25 is closed, and when the main valve body 3 moves in the first opening direction and moves away from the valve seat 23, the main flow path 25 is closed. Is released. The main valve body 3 is biased by the spring 42 in the first closing direction. The main flow path 25 is divided into the primary side flow path 11 and the secondary side flow path 12 by the main valve body 3 seated on the valve seat 23.
　主弁体３の外周面には、ノッチ３８が形成されている。このノッチ３８と、主弁体３の第１閉方向側の面（以下、「前面」ともいう）とを接続するパイロット供給流路３１が、主弁体３内に形成されている。パイロット供給流路３１は、一次側流路１１とパイロット室４３とを接続し、一次側流路１１からパイロット室４３へ作動流体を供給する流路である。パイロット供給流路３１には、メイン流路２５の一次側流路１１からパイロット室４３へ向かう一方向の流れは通過するが、その逆流は通過させない、逆止弁３３が設けられている。 A notch 38 is formed on the outer peripheral surface of the main valve body 3. A pilot supply flow path 31 that connects the notch 38 and a surface in the first closing direction of the main valve body 3 (hereinafter also referred to as “front surface”) is formed in the main valve body 3. The pilot supply flow path 31 is a flow path that connects the primary flow path 11 and the pilot chamber 43 and supplies the working fluid from the primary flow path 11 to the pilot chamber 43. The pilot supply flow path 31 is provided with a check valve 33 that allows a unidirectional flow from the primary flow path 11 to the pilot chamber 43 to pass through the main flow path 25 but does not allow the reverse flow to pass therethrough.
　パイロット供給流路３１とパイロット室４３との間には、可変絞り３２が設けられている。可変絞り３２は、主弁体３の外周面及びノッチ３８とボディ２の内周面との協働により形成されている。可変絞り３２の開口面積は、主弁体３がバルブシート２３に着座している状態で絞られている（閉じられている）。そして、可変絞り３２の開口面積は、主弁体３の第１開方向の移動に伴って増大し、主弁体３の第１閉方向の移動に伴って減少する。 A variable throttle 32 is provided between the pilot supply flow path 31 and the pilot chamber 43. The variable throttle 32 is formed by the cooperation of the outer peripheral surface of the main valve body 3 and the notch 38 and the inner peripheral surface of the body 2. The opening area of the variable throttle 32 is throttled (closed) while the main valve body 3 is seated on the valve seat 23. The opening area of the variable throttle 32 increases as the main valve element 3 moves in the first opening direction, and decreases as the main valve element 3 moves in the first closing direction.
　さらに、主弁体３には、パイロット供給流路３１とは別に、二次側流路１２とパイロット室４３とを接続する副パイロット供給流路３５が形成されている。副パイロット供給流路３５は、主弁体３の第１開方向側の面（以下、「背面」ともいう）と、主弁体３の外周面のメイン流路２５に露出している部分とを接続している。この副パイロット供給流路３５には、二次側流路１２からパイロット室４３への一方向の流れは通過させるが、その逆流は通過させない逆止弁３６が設けられている。 Furthermore, in addition to the pilot supply flow path 31, a sub pilot supply flow path 35 that connects the secondary side flow path 12 and the pilot chamber 43 is formed in the main valve body 3. The sub-pilot supply channel 35 includes a surface exposed to the first opening direction side of the main valve body 3 (hereinafter also referred to as “rear surface”) and a portion exposed to the main channel 25 on the outer peripheral surface of the main valve body 3. Is connected. The sub pilot supply flow path 35 is provided with a check valve 36 that allows a one-way flow from the secondary side flow path 12 to the pilot chamber 43 to pass therethrough but does not allow the reverse flow to pass therethrough.
　パイロット弁体５は、ボディ２に形成された円筒形滑り面に内接している一端開放の円筒形状体である。パイロット弁体５は、パイロット室４３とパイロット排出流路６０との間、及び、パイロット排出流路６０とバランス室４５との間を仕切るように、ボディ２に挿入されている。 The pilot valve body 5 is a cylindrical body having an open end that is inscribed in a cylindrical sliding surface formed in the body 2. The pilot valve body 5 is inserted into the body 2 so as to partition between the pilot chamber 43 and the pilot discharge channel 60 and between the pilot discharge channel 60 and the balance chamber 45.
　パイロット弁体５には、外周面に設けられたノッチ６８と、内部通路６４とが形成されている。内部通路６４は、ノッチ６８とパイロット室４３とを接続することにより、パイロット室４３とパイロット排出流路６０とを接続している。内部通路６４とパイロット排出流路６０との間には、パイロット弁体５の外周面とノッチ６８とボディ２の内周面との協働により、可変絞り６３が形成されている。パイロット弁体５は、可変絞り６３の開口面積を増大せる向き（以下、「第２開方向」という）と、可変絞り６３の開口面積を減少させる向き（以下、「第２閉方向」という）とへ移動可能である。 The pilot valve body 5 is formed with a notch 68 provided on the outer peripheral surface and an internal passage 64. The internal passage 64 connects the pilot chamber 43 and the pilot discharge channel 60 by connecting the notch 68 and the pilot chamber 43. A variable throttle 63 is formed between the internal passage 64 and the pilot discharge passage 60 by the cooperation of the outer peripheral surface of the pilot valve body 5, the notch 68 and the inner peripheral surface of the body 2. The pilot valve body 5 has a direction to increase the opening area of the variable throttle 63 (hereinafter referred to as “second opening direction”) and a direction to decrease the opening area of the variable throttle 63 (hereinafter referred to as “second closing direction”). It is possible to move to.
　内部通路６４は、バランス室４５と接続された分岐路６４ａを有している。分岐路６４ａは、可変絞り６３よりもパイロット室４３側、即ち、ノッチ６８よりもパイロット室４３側で内部通路６４から分岐しているそして、内部通路６４において分岐路６４ａよりもパイロット室４３側に固定絞り６６が形成されている。つまり、パイロット室４３とパイロット排出流路６０とを接続する内部通路６４上に固定絞り６６が形成されている。したがって、内部通路６４（分岐路６４ａを含む、以下同じ。）を介してバランス室４５とパイロット室４３とが連通されており、これらの間に固定絞り６６が存在している。また、内部通路６４を介してバランス室４５とパイロット排出流路６０とが接続されており、これらの間に可変絞り６３が存在している。 The internal passage 64 has a branch path 64 a connected to the balance chamber 45. The branch path 64a is branched from the internal passage 64 on the pilot chamber 43 side with respect to the variable throttle 63, that is, on the pilot chamber 43 side with respect to the notch 68, and in the internal passage 64, on the pilot chamber 43 side with respect to the branch path 64a. A fixed diaphragm 66 is formed. That is, the fixed throttle 66 is formed on the internal passage 64 that connects the pilot chamber 43 and the pilot discharge channel 60. Therefore, the balance chamber 45 and the pilot chamber 43 are communicated with each other via the internal passage 64 (including the branch path 64a, the same applies hereinafter), and a fixed throttle 66 exists between them. In addition, the balance chamber 45 and the pilot discharge channel 60 are connected via an internal passage 64, and a variable throttle 63 exists between them.
　パイロット弁体５には、ソレノイド５０により第２開方向の駆動力Ｆが与えられる。駆動力Ｆは、ソレノイド５０に付与される制御信号に応じて可変である。一方、パイロット弁体５は、スプリング４１により、第２開方向と反対の第２閉方向への付勢力が与えられている。可変絞り６３の開口面積は、ソレノイド５０がオフの時に絞られている（閉じられている）。そして、可変絞り６３の開口面積は、ソレノイド５０に与えられた制御信号に比例して、パイロット弁体５の第２開方向への移動に伴い増大し、パイロット弁体５の第２閉方向の移動に伴い減少する。 The pilot valve body 5 is given a driving force F in the second opening direction by the solenoid 50. The driving force F is variable according to a control signal applied to the solenoid 50. On the other hand, the pilot valve body 5 is given a biasing force in the second closing direction opposite to the second opening direction by the spring 41. The opening area of the variable aperture 63 is reduced (closed) when the solenoid 50 is off. The opening area of the variable throttle 63 increases in proportion to the movement of the pilot valve body 5 in the second opening direction in proportion to the control signal given to the solenoid 50, and the pilot valve body 5 in the second closing direction. Decreases with movement.
　ソレノイド５０は、パイロット弁体５と接続されたプランジャ５１（可動鉄心）と、プランジャ５１の周囲に設けられたコイル５２とを備えている。プランジャ５１やスプリング４１は、バランス室４５に配置されている。なお、本実施形態ではパイロット弁体５に駆動力を与える駆動力付加手段としてソレノイド５０を採用しているが、駆動力付加手段はこれに限定されず、油圧パイロット式（油圧駆動式）であってもよい。 The solenoid 50 includes a plunger 51 (movable iron core) connected to the pilot valve body 5 and a coil 52 provided around the plunger 51. The plunger 51 and the spring 41 are disposed in the balance chamber 45. In this embodiment, the solenoid 50 is employed as the driving force adding means for applying the driving force to the pilot valve body 5, but the driving force adding means is not limited to this, and is a hydraulic pilot type (hydraulic driving type). May be.
　次に、上記構成のパイロット式流量制御弁１の動作を説明する。ソレノイド５０がオフのとき、パイロット弁体５は可変絞り６３の開口面積が絞られた状態にあり、パイロット排出流路６０が閉止されている。このとき、主弁体３はバルブシート２３に着座しており、メイン流路２５が閉止されている。さらに、可変絞り３２の開口面積が絞られた状態にあり、パイロット供給流路３１が閉止されている。ここで、メイン流路２５の一次側流路１１の作動流体の圧力を一次側圧力Ｐ1、二次側流路１２の作動流体の圧力を二次側圧力Ｐ2、パイロット室４３の作動流体の圧力をパイロット圧力Ｐ3、バランス室４５の作動流体の圧力をバランス圧力Ｐ4とする。可変絞り３２の開口面積は絞られているが僅かな漏れがあり、一次側圧力Ｐ1とパイロット圧力Ｐ3とが等しい。そして、主弁体３の前面より背面の面積が大きいことにより、主弁体３はバルブシート２３に着座した状態で留まっている。また、パイロット弁体５の内部通路６４に流れがないので、パイロット圧力Ｐ3とバランス圧力Ｐ4とが等しい。したがって、「一次側圧力Ｐ1＝パイロット圧力Ｐ3＝バランス圧力Ｐ4＞二次側圧力Ｐ2」の関係が成立している。 Next, the operation of the pilot flow control valve 1 configured as described above will be described. When the solenoid 50 is off, the pilot valve body 5 is in a state where the opening area of the variable restrictor 63 is restricted, and the pilot discharge passage 60 is closed. At this time, the main valve body 3 is seated on the valve seat 23 and the main flow path 25 is closed. Furthermore, the opening area of the variable throttle 32 is reduced, and the pilot supply flow path 31 is closed. Here, the pressure of the working fluid in the primary channel 11 of the main channel 25 is the primary pressure P 1 , the pressure of the working fluid in the secondary channel 12 is the secondary pressure P 2 , and the working fluid of the pilot chamber 43. Is the pilot pressure P 3 , and the pressure of the working fluid in the balance chamber 45 is the balance pressure P 4 . Although the opening area of the variable throttle 32 is throttled, there is a slight leak, and the primary pressure P 1 and the pilot pressure P 3 are equal. The main valve body 3 remains seated on the valve seat 23 because the area of the back surface is larger than the front surface of the main valve body 3. Further, since there is no flow in the internal passage 64 of the pilot valve body 5, it is equal to the pilot pressure P 3 and the balance pressure P 4. Therefore, the relationship of “primary pressure P 1 = pilot pressure P 3 = balance pressure P 4 > secondary pressure P 2 ” is established.
　一方、ソレノイド５０がオフで、且つ、メイン流路２５及びパイロット排出流路６０が閉止されている状態において、流体圧アクチュエータ１００に外部から負荷が掛かり、二次側流路１２の圧力が上昇した場合を以下に検討する。このとき、可変絞り６３の開口面積は絞られているが、パイロット弁体５の形式に限らず、ボディ２と主弁体３との隙間を通じて二次側流路１２の作動流体がパイロット室４３へ漏れ出る。さらに、主弁体３とボディ２との隙間（可変絞り３２の隙間）を通じて、パイロット室４３の作動流体がパイロット供給流路３１へ漏れ出る。しかし、パイロット供給流路３１に逆止弁３３が設けられていることから、作動流体がパイロット供給流路３１からメイン流路２５の一次側流路１１へ流れることはできない。このようにして、メイン流路２５が閉止されているときの、二次側流路１２から一次側流路１１へのパイロット室４３を介した作動流体漏れが抑制され、パイロット式流量制御弁１の動作が補償されている。例えば、メイン流路２５が閉止されることにより流体圧アクチュエータ１００が停止状態で保持されている場合に、二次側流路１２から一次側流路１１への作動流体漏れが抑制されることにより、流体圧アクチュエータ１００の停止状態が良好に維持される。以上の通り、本実施形態に係るパイロット式流量制御弁１によれば、前述の第１の課題を解決することができる。 On the other hand, when the solenoid 50 is off and the main flow path 25 and the pilot discharge flow path 60 are closed, a load is applied to the fluid pressure actuator 100 from the outside, and the pressure of the secondary side flow path 12 increases. The case is considered below. At this time, the opening area of the variable throttle 63 is reduced, but not limited to the type of the pilot valve body 5, the working fluid in the secondary side flow path 12 flows through the gap between the body 2 and the main valve body 3. Leak into. Further, the working fluid in the pilot chamber 43 leaks into the pilot supply flow path 31 through the gap between the main valve body 3 and the body 2 (the gap between the variable throttles 32). However, since the check valve 33 is provided in the pilot supply flow path 31, the working fluid cannot flow from the pilot supply flow path 31 to the primary flow path 11 of the main flow path 25. Thus, the working fluid leakage from the secondary side flow path 12 to the primary side flow path 11 through the pilot chamber 43 when the main flow path 25 is closed is suppressed, and the pilot flow control valve 1 Has been compensated for. For example, when the fluid pressure actuator 100 is held in a stopped state by closing the main flow path 25, the working fluid leakage from the secondary side flow path 12 to the primary side flow path 11 is suppressed. The stop state of the fluid pressure actuator 100 is maintained well. As described above, according to the pilot flow control valve 1 according to the present embodiment, the first problem described above can be solved.
　ソレノイド５０が通電されると、パイロット弁体５に駆動力Ｆが付与され、パイロット弁体５が第２開方向に移動する。すると、可変絞り６３の開口面積が増加し、パイロット排出流路６０を通じてパイロット室４３から二次側流路１２へ作動流体が流れ出し、パイロット圧力Ｐ3が低下する。これにより、主弁体３が第１開方向に移動してバルブシート２３から離れ、メイン流路２５が開放される。メイン流路２５の開放に伴い、可変絞り３２が開かれてパイロット供給流路３１も開放される。 When the solenoid 50 is energized, a driving force F is applied to the pilot valve body 5 and the pilot valve body 5 moves in the second opening direction. Then, the variable throttle opening area 63 is increased, the pilot chamber working fluid flows 43 from the secondary flow path 12 through the pilot discharge flow path 60, decreases the pilot pressure P 3. As a result, the main valve body 3 moves in the first opening direction to leave the valve seat 23, and the main flow path 25 is opened. As the main channel 25 is opened, the variable throttle 32 is opened and the pilot supply channel 31 is also opened.
　主弁体３の第１開方向の移動に伴って可変絞り３２の開口面積が増大し、可変絞り３２を流れる作動流体の流量が増大する。可変絞り３２を通過する作動流体の流量と可変絞り６３を通過する作動流体の流量は常に等しいため、主弁体３の移動量はパイロット弁体５の移動量に依存する。 As the main valve body 3 moves in the first opening direction, the opening area of the variable throttle 32 increases, and the flow rate of the working fluid flowing through the variable throttle 32 increases. Since the flow rate of the working fluid passing through the variable throttle 32 and the flow rate of the working fluid passing through the variable throttle 63 are always equal, the movement amount of the main valve body 3 depends on the movement amount of the pilot valve body 5.
　上記のようにメイン流路２５及びパイロット排出流路６０が開放された状態において、可変絞り６３を通過する作動流体が一定流量である場合を以下に検討する。メイン流路２５の一次側流路１１とパイロット室４３との間には可変絞り３２が存在し、パイロット室４３とパイロット排出流路６０との間には可変絞り６３及び固定絞り６６が存在するため、「一次側圧力Ｐ1＞パイロット圧力Ｐ3＞バランス圧力Ｐ4＞二次側圧力Ｐ2」の順に低くなり、主弁体３とパイロット弁体５は一定の位置に留まっている。 The case where the working fluid passing through the variable throttle 63 is a constant flow rate in the state where the main flow path 25 and the pilot discharge flow path 60 are opened as described above will be considered below. A variable throttle 32 exists between the primary flow path 11 of the main flow path 25 and the pilot chamber 43, and a variable throttle 63 and a fixed throttle 66 exist between the pilot chamber 43 and the pilot discharge flow path 60. Therefore, the pressure decreases in the order of “primary side pressure P 1 > pilot pressure P 3 > balance pressure P 4 > secondary side pressure P 2 ”, and the main valve body 3 and the pilot valve body 5 remain in a fixed position.
　ここで、パイロット弁体５の内部通路６４上に固定絞り６６が形成されているため、パイロット室４３に面したパイロット弁体５のパイロット弁体前面にはパイロット圧力Ｐ3が作用し、バランス室４５に面したパイロット弁体５のパイロット弁体背面にはバランス圧力Ｐ4が作用する。また、パイロット弁体背面には、スプリング４１によるバネ力、及び、ソレノイド５０による駆動力Ｆも作用する。これにより、パイロット弁体５は、パイロット弁体前面に作用する力（パイロット圧力Ｐ3）とパイロット弁体背面に作用する力（バランス圧力Ｐ4、バネ力、駆動力Ｆ）とが釣り合う位置に移動することになる。つまり、固定絞り６６の前後に生じる圧力差（パイロット圧力Ｐ3とバランス圧力Ｐ4との圧力差）は、スプリング４１によるバネ力及びソレノイド５０による駆動力Ｆに基づいて定まる所定値となる。そのため、固定絞り６６を通過する作動流体の流量は、一次側圧力Ｐ1等の圧力変動の影響を受けることなく、所定値となる。また、固定絞り６６を通過する流量と可変絞り６３を通過する流量とは等しいので、可変絞り６３の後流のパイロット排出流路６０を通過するパイロット流量も所定値となる。更に言えば、固定絞り６６を通過する流量と可変絞り６３を通過する流量と可変絞り３２を通過する流量は等しく、以下では、これらの流量をパイロット流量と呼ぶ。なお、メイン流路２５の流量はパイロット排出流路６０のパイロット流量に依存するため、メイン流路２５の一次側流路１１の圧力が変動しても、パイロット排出流路６０の流量を一定値に保つことで、メイン流路２５を通過する作動流体の流量を一定値に保持することができる。よって、パイロット式流量制御弁の性能を向上させることができる。 Here, since the fixed throttle 66 is formed on the internal passage 64 of the pilot valve body 5, the pilot pressure P 3 acts on the pilot valve body front surface of the pilot valve body 5 facing the pilot chamber 43, and the balance chamber. The balance pressure P 4 acts on the back surface of the pilot valve body 5 facing the 45. Further, the spring force by the spring 41 and the driving force F by the solenoid 50 also act on the back surface of the pilot valve body. As a result, the pilot valve body 5 is in a position where the force acting on the front surface of the pilot valve body (pilot pressure P 3 ) and the force acting on the rear surface of the pilot valve body (balance pressure P 4 , spring force, driving force F) are balanced. Will move. That is, the pressure difference generated before and after the fixed throttle 66 (pressure difference between the pilot pressure P 3 and the balance pressure P 4 ) is a predetermined value determined based on the spring force by the spring 41 and the driving force F by the solenoid 50. For this reason, the flow rate of the working fluid passing through the fixed throttle 66 becomes a predetermined value without being affected by pressure fluctuations such as the primary pressure P 1 . Further, since the flow rate passing through the fixed restrictor 66 and the flow rate passing through the variable restrictor 63 are equal, the pilot flow rate passing through the pilot discharge passage 60 downstream of the variable restrictor 63 also becomes a predetermined value. Further, the flow rate passing through the fixed restrictor 66, the flow rate passing through the variable restrictor 63, and the flow rate passing through the variable restrictor 32 are equal, and these flow rates are hereinafter referred to as pilot flow rates. Since the flow rate of the main flow path 25 depends on the pilot flow rate of the pilot discharge flow path 60, the flow rate of the pilot discharge flow path 60 is kept constant even if the pressure of the primary flow path 11 of the main flow path 25 fluctuates. By maintaining the flow rate at a constant value, the flow rate of the working fluid passing through the main flow path 25 can be maintained at a constant value. Therefore, the performance of the pilot flow control valve can be improved.
　上記の通り、パイロット弁体５の内部通路６４に固定絞り６６が設けられることによって、固定絞り６６の前後に生じる圧力差が一定となるようにパイロット弁体５が移動する。このように、圧力補償スプールとして動作するパイロット弁体５によって、パイロット式流量制御弁１に圧力補償機能を備えることができる。固定絞り６６を通過するパイロット流量は、一次側圧力Ｐ1又は二次側圧力Ｐ2の変化に関わらず、スプリング４１によりパイロット弁体５へ与えられるバネ力及びソレノイド５０によりパイロット弁体５へ与えられる駆動力Ｆに応じたものとなる。即ち、固定絞りやその下流のパイロット排出流路６０を通過するパイロット流量はソレノイド５０によるパイロット弁体５の操作量に応じたものとなり、メイン流路２５の流量はパイロット流量に依存するため、メイン流路２５の流量をパイロット流量に対応した値に保持することができる。以上の通り、本実施形態に係るパイロット式流量制御弁１によれば、前述の第３の課題を解決することができる。 As described above, by providing the fixed throttle 66 in the internal passage 64 of the pilot valve body 5, the pilot valve body 5 moves so that the pressure difference generated before and after the fixed throttle 66 is constant. Thus, the pilot valve body 5 that operates as a pressure compensation spool can provide the pilot flow control valve 1 with a pressure compensation function. The pilot flow rate that passes through the fixed throttle 66 is applied to the pilot valve body 5 by the spring force applied to the pilot valve body 5 by the spring 41 and the solenoid 50 regardless of changes in the primary side pressure P 1 or the secondary side pressure P 2. This corresponds to the driving force F to be applied. That is, the pilot flow rate that passes through the fixed throttle and the pilot discharge flow path 60 downstream thereof is in accordance with the operation amount of the pilot valve body 5 by the solenoid 50, and the flow rate of the main flow path 25 depends on the pilot flow rate. The flow rate of the flow path 25 can be maintained at a value corresponding to the pilot flow rate. As described above, according to the pilot flow control valve 1 according to the present embodiment, the third problem described above can be solved.
　また、メイン流路２５が開放されている状態において、二次側圧力Ｐ2より一次側圧力Ｐ1が低くなることがある。このとき、二次側圧力Ｐ2よりもパイロット圧力Ｐ3が低いために、副パイロット供給流路３５を通じて二次側流路１２からパイロット室４３へ作動流体が流れ込む。これにより、パイロット排出流路６０及び可変絞り６３を通ってパイロット室４３へ作動流体を流入させる場合と比較して速やかに、パイロット圧力Ｐ3を増大させて、主弁体３を第１閉方向へ移動させて、メイン流路２５を閉止することができる。なお、メイン流路２５を閉止するために、二次側流路１２からパイロット室４３へ高圧が導入される際に、パイロット排出流路６０と副パイロット供給流路３５の両方を通じて作動流体がパイロット室４３へ供給されてもよいし、副パイロット供給流路３５のみから作動流体がパイロット室４３へ供給されてもよい。上記の通り、二次側圧力Ｐ2より一次側圧力Ｐ1が低くなったときにメイン流路２５が速やかに閉止されるので、例えば、二次側流路１２に接続された流体圧アクチュエータ１００が作業機械のアームを動作させるシリンダである場合には、アーム上昇動作時に作動流体の圧力が低下することによってアームが一瞬降下するような事態を防ぐことができる。以上の通り、本実施形態に係るパイロット式流量制御弁１によれば、前述の第２の課題を解決することができる。 Moreover, in the state where the main flow path 25 is opened, the primary side pressure P 1 may be lower than the secondary side pressure P 2 . At this time, since the pilot pressure P 3 is lower than the secondary side pressure P 2 , the working fluid flows from the secondary side passage 12 into the pilot chamber 43 through the sub pilot supply passage 35. As a result, the pilot pressure P 3 is quickly increased and the main valve body 3 is moved in the first closing direction as compared with the case where the working fluid flows into the pilot chamber 43 through the pilot discharge flow path 60 and the variable throttle 63. The main flow path 25 can be closed. In order to close the main flow path 25, when high pressure is introduced from the secondary side flow path 12 to the pilot chamber 43, the working fluid is piloted through both the pilot discharge flow path 60 and the sub pilot supply flow path 35. The working fluid may be supplied to the chamber 43, or the working fluid may be supplied to the pilot chamber 43 only from the auxiliary pilot supply channel 35. As described above, when the primary pressure P 1 becomes lower than the secondary pressure P 2 , the main flow path 25 is quickly closed. For example, the fluid pressure actuator 100 connected to the secondary flow path 12 Is a cylinder that operates the arm of the work machine, it is possible to prevent a situation in which the arm drops momentarily due to a decrease in the pressure of the working fluid during the arm raising operation. As described above, according to the pilot flow control valve 1 according to the present embodiment, the second problem described above can be solved.
　以上に本発明の好適な実施の形態を説明したが、上記パイロット式流量制御弁１の構成は例えば以下のように変更することができる。 Although the preferred embodiment of the present invention has been described above, the configuration of the pilot flow control valve 1 can be changed as follows, for example.
　例えば、第１の課題を解決する観点では、パイロット式流量制御弁１は、主弁体３に設けられた副パイロット供給流路３５及び逆止弁３６を備えていなくてもよい。同様に、パイロット式流量制御弁１は、パイロット弁体５の内部通路６４に設けられた固定絞り６６を備えていなくてもよい。更に、パイロット式流量制御弁１は、パイロット弁体５がポペット式であっても良い。 For example, from the viewpoint of solving the first problem, the pilot flow control valve 1 may not include the sub pilot supply flow path 35 and the check valve 36 provided in the main valve body 3. Similarly, the pilot flow control valve 1 may not include the fixed throttle 66 provided in the internal passage 64 of the pilot valve body 5. Further, in the pilot type flow control valve 1, the pilot valve body 5 may be a poppet type.
　また、例えば、第２の課題を解決する観点では、パイロット式流量制御弁１は、主弁体３に設けられたパイロット供給流路３１に逆止弁３３を備えていなくてもよい。同様に、パイロット式流量制御弁１は、パイロット弁体５の内部通路６４に設けられた固定絞り６６を備えていなくてもよい。更に、パイロット式流量制御弁１は、パイロット弁体５がポペット式であっても良い。 For example, from the viewpoint of solving the second problem, the pilot flow control valve 1 may not include the check valve 33 in the pilot supply flow path 31 provided in the main valve body 3. Similarly, the pilot flow control valve 1 may not include the fixed throttle 66 provided in the internal passage 64 of the pilot valve body 5. Further, in the pilot type flow control valve 1, the pilot valve body 5 may be a poppet type.
　また、例えば、第３の課題を解決する観点では、パイロット式流量制御弁１は、主弁体３に設けられたパイロット供給流路３１に逆止弁３３を備えていなくてもよい。同様に、パイロット式流量制御弁１は、主弁体３に設けられた副パイロット供給流路３５及び逆止弁３６を備えていなくてもよい。 For example, from the viewpoint of solving the third problem, the pilot flow control valve 1 does not have to include the check valve 33 in the pilot supply flow path 31 provided in the main valve body 3. Similarly, the pilot flow control valve 1 may not include the auxiliary pilot supply flow path 35 and the check valve 36 provided in the main valve body 3.
　１　パイロット式流量制御弁
　２　ボディ
　　２１　入口ポート
　　２２　出口ポート
　　２３　バルブシート
　　２５　メイン流路
　　　１１　一次側流路
　　　１２　二次側流路
　３　主弁体
　　３１　パイロット流路
　　３２　可変絞り（第１可変絞り）
　　３３，３６　逆止弁
　　３５　副パイロット供給流路
　　３８　ノッチ
　５　パイロット弁体
　４１　スプリング（第２スプリング）
　４２　スプリング（第１スプリング）
　４３　パイロット室
　４５　バランス室
　５０　ソレノイド
　　５１　プランジャ
　　５２　コイル
　６０　パイロット排出流路
　６３　可変絞り（第２可変絞り）
　６４　内部通路
　　６４ａ　分岐路
　６６　固定絞り
　６８　ノッチ
　１００　流体圧アクチュエータ
  DESCRIPTION OF SYMBOLS 1 Pilot type flow control valve 2 Body 21 Inlet port 22 Outlet port 23 Valve seat 25 Main flow path 11 Primary side flow path 12 Secondary side flow path 3 Main valve body 31 Pilot flow path 32 Variable restrictor (first variable restrictor)
33, 36 Check valve 35 Sub pilot supply flow path 38 Notch 5 Pilot valve body 41 Spring (second spring)
42 Spring (first spring)
43 Pilot chamber 45 Balance chamber 50 Solenoid 51 Plunger 52 Coil 60 Pilot discharge flow path 63 Variable throttle (second variable throttle)
64 Internal passage 64a Branching passage 66 Fixed restriction 68 Notch 100 Fluid pressure actuator

Claims (5)

  1. 　入口ポート、出口ポート、前記入口ポートと前記出口ポートを繋ぐメイン流路、前記メイン流路の一次側流路と二次側流路との間に設けられたバルブシート、パイロット室、及び前記パイロット室と前記出口ポートとを接続するパイロット排出流路を有するボディと、
    　前記バルブシートに近づく第１閉方向と前記バルブシートから離れる第１開方向とへ移動可能であって、前記メイン流路と前記パイロット室との間を仕切り、前記第１開方向へ移動して前記メイン流路と前記パイロット室の間に形成された第１可変絞りの開口面積を増大させ、前記第１閉方向へ移動して前記第１可変絞りの開口面積を減少させるように前記ボディに挿入された主弁体であって、前記パイロット室と前記入口ポートとを接続するパイロット供給流路を内部に有する主弁体と、
    　前記主弁体に前記第１閉方向の付勢力を与える第１スプリングと、
    　前記パイロット室と前記パイロット排出流路との間を仕切り、前記パイロット室と前記パイロット排出流路の間に形成された第２可変絞りの開口面積を増大させる第２開方向と前記第２可変絞りの開口面積を減少させる第２閉方向とへ移動可能に前記ボディに挿入されたパイロット弁体であって、前記パイロット室と前記パイロット排出流路とを接続する内部流路を有するパイロット弁体と、
    　前記パイロット弁体に前記第２開方向の駆動力を与える駆動力付加手段と、
    　前記パイロット弁体に前記第２閉方向の付勢力を与える第２スプリングと、
    　前記パイロット供給流路において前記入口ポートから前記パイロット室へ向かう一方向の流れのみを通過させる逆止弁と、を備えているパイロット式流量制御弁。     An inlet port, an outlet port, a main flow path connecting the inlet port and the outlet port, a valve seat provided between a primary flow path and a secondary flow path of the main flow path, a pilot chamber, and the pilot A body having a pilot discharge channel connecting the chamber and the outlet port;
    The first closing direction approaching the valve seat and the first opening direction away from the valve seat are movable, partitioning the main flow path and the pilot chamber, and moving in the first opening direction The body is configured to increase an opening area of a first variable throttle formed between the main flow path and the pilot chamber and move in the first closing direction to reduce the opening area of the first variable throttle. An inserted main valve body having a pilot supply flow path connecting the pilot chamber and the inlet port therein;
    A first spring that applies an urging force in the first closing direction to the main valve body;
    A second opening direction and the second variable throttle for partitioning the pilot chamber and the pilot discharge flow path and increasing an opening area of a second variable throttle formed between the pilot chamber and the pilot discharge flow path. A pilot valve body inserted into the body so as to be movable in a second closing direction for reducing an opening area of the pilot valve body, and having an internal flow path connecting the pilot chamber and the pilot discharge flow path; ,
    Driving force adding means for applying a driving force in the second opening direction to the pilot valve body;
    A second spring for applying a biasing force in the second closing direction to the pilot valve body;
    A pilot-type flow control valve comprising: a check valve that allows only a one-way flow from the inlet port toward the pilot chamber to pass through the pilot supply flow path.
  2. 　前記パイロット室と前記出口ポートとを接続するように前記主弁体内に形成された副パイロット供給流路と、
    　前記副パイロット供給流路において、前記出口ポートから前記パイロット室へ向かう流れのみを通過させる逆止弁とを、更に備えている請求項１に記載のパイロット式流量制御弁。     A secondary pilot supply channel formed in the main valve body to connect the pilot chamber and the outlet port;
    The pilot-type flow control valve according to claim 1, further comprising a check valve that allows only a flow from the outlet port toward the pilot chamber to pass through the sub pilot supply flow path.
  3. 　前記ボディが、前記パイロット弁体に前記第２開方向の圧力を作用させるバランス室を更に有し、
    　前記パイロット弁体の前記内部流路が、前記バランス室と接続された分岐路を有し、
    　前記内部流路において前記分岐路の分岐箇所よりも前記パイロット室側に絞りが設けられている、請求項１又は２に記載のパイロット式流量制御弁。     The body further includes a balance chamber for applying a pressure in the second opening direction to the pilot valve body;
    The internal flow path of the pilot valve body has a branch path connected to the balance chamber;
    The pilot-type flow control valve according to claim 1 or 2, wherein a throttle is provided on the pilot chamber side of the internal flow path with respect to a branching point of the branch path.
  4. 　入口ポート、出口ポート、前記入口ポートと前記出口ポートを繋ぐメイン流路、前記メイン流路の一次側流路と二次側流路との間に設けられたバルブシート、パイロット室、及び前記パイロット室と前記出口ポートとを接続するパイロット排出流路を有するボディと、
    　前記バルブシートに近づく第１閉方向と前記バルブシートから離れる第１開方向とへ移動可能であって、前記メイン流路と前記パイロット室との間を仕切り、前記第１開方向へ移動して前記メイン流路と前記パイロット室の間に形成された第１可変絞りの開口面積を増大させ、前記第１閉方向へ移動して前記第１可変絞りの開口面積を減少させるように前記ボディに挿入された主弁体であって、前記パイロット室と前記入口ポートとを接続するパイロット供給流路と前記パイロット室と前記出口ポートとを接続する副パイロット供給流路とを内部に有する主弁体と、
    　前記主弁体に前記第１閉方向の付勢力を与える第１スプリングと、
    　前記パイロット室と前記パイロット排出流路との間を仕切り、前記パイロット室と前記パイロット排出流路の間に形成された第２可変絞りの開口面積を増大させる第２開方向と前記第２可変絞りの開口面積を減少させる第２閉方向とへ移動可能に前記ボディに挿入されたパイロット弁体であって、前記パイロット室と前記パイロット排出流路とを接続する内部流路を有するパイロット弁体と、
    　前記パイロット弁体に可変な前記第２開方向の駆動力を与える駆動力付加手段と、
    　前記パイロット弁体に前記第２閉方向の付勢力を与える第２スプリングと、
    　前記副パイロット供給流路において前記出口ポートから前記パイロット室へ向かう一方向の流れのみを通過させる逆止弁と、を備えているパイロット式流量制御弁。     An inlet port, an outlet port, a main flow path connecting the inlet port and the outlet port, a valve seat provided between a primary flow path and a secondary flow path of the main flow path, a pilot chamber, and the pilot A body having a pilot discharge channel connecting the chamber and the outlet port;
    The first closing direction approaching the valve seat and the first opening direction away from the valve seat are movable, partitioning the main flow path and the pilot chamber, and moving in the first opening direction The body is configured to increase an opening area of a first variable throttle formed between the main flow path and the pilot chamber and move in the first closing direction to reduce the opening area of the first variable throttle. An inserted main valve body having a pilot supply channel connecting the pilot chamber and the inlet port and a sub pilot supply channel connecting the pilot chamber and the outlet port therein When,
    A first spring that applies an urging force in the first closing direction to the main valve body;
    A second opening direction and the second variable throttle for partitioning the pilot chamber and the pilot discharge flow path and increasing an opening area of a second variable throttle formed between the pilot chamber and the pilot discharge flow path. A pilot valve body inserted into the body so as to be movable in a second closing direction for reducing an opening area of the pilot valve body, and having an internal flow path connecting the pilot chamber and the pilot discharge flow path; ,
    Driving force adding means for applying a variable driving force in the second opening direction to the pilot valve body;
    A second spring for applying a biasing force in the second closing direction to the pilot valve body;
    A pilot flow control valve comprising: a check valve that allows passage of only a one-way flow from the outlet port toward the pilot chamber in the sub-pilot supply flow path.
  5. 　入口ポート、出口ポート、前記入口ポートと前記出口ポートを繋ぐメイン流路、前記メイン流路の一次側流路と二次側流路との間に設けられたバルブシート、パイロット室、前記パイロット室と前記出口ポートとを接続するパイロット排出流路、及びバランス室を有するボディと、
    　前記バルブシートに近づく第１閉方向と前記バルブシートから離れる第１開方向とへ移動可能であって、前記メイン流路と前記パイロット室との間を仕切り、前記第１開方向へ移動して前記メイン流路と前記パイロット室の間に形成された第１可変絞りの開口面積を増大させ、前記第１閉方向へ移動して前記第１可変絞りの開口面積を減少させるように前記ボディに挿入された主弁体であって、前記パイロット室と前記入口ポートとを接続するパイロット供給流路を内部に有する主弁体と、
    　前記主弁体に前記第１閉方向の付勢力を与える第１スプリングと、
    　前記パイロット室と前記パイロット排出流路との間及び前記パイロット室と前記バランス室との間をそれぞれ仕切り、前記パイロット室と前記パイロット排出流路の間に形成された第２可変絞りの開口面積を増大させる第２開方向と前記第２可変絞りの開口面積を減少させる第２閉方向とへ移動可能に前記ボディに挿入されたパイロット弁体であって、前記パイロット室と前記パイロット排出流路とを接続する内部流路を有するスプール形のパイロット弁体と、
    　前記パイロット弁体に可変な前記第２開方向の駆動力を与える駆動力付加手段と、
    　前記パイロット弁体に前記第２閉方向の付勢力を与える第２スプリングと、を備え、
    　前記パイロット弁体の前記内部流路が、前記バランス室と接続された分岐路を有し、前記内部流路において前記分岐路の分岐箇所よりも前記パイロット室側に絞りが設けられている、
    パイロット式流量制御弁。
          An inlet port, an outlet port, a main channel connecting the inlet port and the outlet port, a valve seat provided between a primary channel and a secondary channel of the main channel, a pilot chamber, and the pilot chamber And a pilot discharge passage connecting the outlet port and a body having a balance chamber;
    The first closing direction approaching the valve seat and the first opening direction away from the valve seat are movable, partitioning the main flow path and the pilot chamber, and moving in the first opening direction The body is configured to increase an opening area of a first variable throttle formed between the main flow path and the pilot chamber and move in the first closing direction to reduce the opening area of the first variable throttle. An inserted main valve body having a pilot supply flow path connecting the pilot chamber and the inlet port therein;
    A first spring that applies an urging force in the first closing direction to the main valve body;
    An opening area of a second variable throttle formed between the pilot chamber and the pilot discharge channel is divided between the pilot chamber and the pilot discharge channel and between the pilot chamber and the balance chamber, respectively. A pilot valve element inserted into the body so as to be movable in a second opening direction to be increased and a second closing direction in which an opening area of the second variable throttle is decreased, the pilot chamber, the pilot discharge flow path, A spool-shaped pilot valve body having an internal flow path for connecting
    Driving force adding means for applying a variable driving force in the second opening direction to the pilot valve body;
    A second spring that applies an urging force in the second closing direction to the pilot valve body,
    The internal flow path of the pilot valve body has a branch path connected to the balance chamber, and the internal flow path is provided with a throttle on the pilot chamber side of the branch path of the branch path;
    Pilot type flow control valve.
PCT/JP2015/001871 2014-04-28 2015-03-31 Pilot-type flow control valve WO2015166628A1 (en)

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JP2010144928A (en) * 2008-12-22 2010-07-01 Incova Technologies Inc Poppet valve operated by electrohydraulic poppet pilot valve

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022201602B3 (en) 2022-02-16 2023-06-29 Vitesco Technologies GmbH Valve device for a heat pump system, heat pump system with such a valve device and building with such a valve device or such a heat pump system

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