WO2006082703A1 - 流体制御弁 - Google Patents
流体制御弁 Download PDFInfo
- Publication number
- WO2006082703A1 WO2006082703A1 PCT/JP2006/300473 JP2006300473W WO2006082703A1 WO 2006082703 A1 WO2006082703 A1 WO 2006082703A1 JP 2006300473 W JP2006300473 W JP 2006300473W WO 2006082703 A1 WO2006082703 A1 WO 2006082703A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- control valve
- pair
- fluid control
- flapper assembly
- flapper
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K7/00—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves
- F16K7/12—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves with flat, dished, or bowl-shaped diaphragm
- F16K7/14—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves with flat, dished, or bowl-shaped diaphragm arranged to be deformed against a flat seat
- F16K7/17—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves with flat, dished, or bowl-shaped diaphragm arranged to be deformed against a flat seat the diaphragm being actuated by fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
- F16K31/0679—Electromagnet aspects, e.g. electric supply therefor with more than one energising coil
-
- 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
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/04—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only lift valves
- F16K11/044—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only lift valves with movable valve members positioned between valve seats
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0686—Braking, pressure equilibration, shock absorbing
- F16K31/0693—Pressure equilibration of the armature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/08—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid using a permanent magnet
- F16K31/082—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid using a permanent magnet using a electromagnet and a permanent magnet
-
- 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
- F16K31/126—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a diaphragm, bellows, or the like
-
- 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 fluid control valve that selectively exerts the pressure of an air supply port on a control port.
- This fluid control valve is required to have a quick response.
- Conventional products do not always have a sufficient response.
- it is essential to increase the air flow velocity.
- increasing the flow velocity causes problems such as indefinite eddy, shock wave, boundary layer separation point fluctuation, and so on, and stable performance is obtained. There was a problem that it was not possible.
- An object of the present invention is to obtain a fluid control valve having a quick response. It is another object of the present invention to obtain a fluid control valve having stable performance free from problems such as shock waves.
- a fluid control valve includes a pressure chamber having an output port; an air supply nozzle and an exhaust air nozzle located on the same straight line that communicate with the pressure chamber; A flapper assembly having a pair of opening and closing control surfaces facing each other and movable between the supply nozzle and the exhaust nozzle; and moving the flapper assembly so that the opening ends of the supply nozzle and the exhaust nozzle and the flapper assembly A flapper assembly moving mechanism that increases the distance between the pair of open / close control surfaces on one side and decreases the other side.
- the flapper assembly can be urged to move in a direction in which one of the pair of opening / closing control surfaces is in close contact with the supply air nozzle by the spring means.
- a diameter-expanding taper surface that gradually increases the diameter toward the flapper assembly is formed, and the opening / closing control surface corresponding to the air supply nozzle A conical opening / closing control surface corresponding to the taper surface is preferable.
- the exhaust nozzle can have a constant diameter, and the opening / closing control surface corresponding to the exhaust nozzle preferably has a needle shape whose diameter decreases as the distance from the flapper assembly increases.
- the pair of opening / closing control surfaces of the flapper assembly can be provided, for example, on both surfaces of the flapper with a fixed peripheral edge.
- a pair of flappers can be provided, and the pair of flappers can be integrally provided with an open / close control surface facing the open ends of the supply nozzle and the exhaust nozzle.
- the flapper assembly moving mechanism can be manually operated, pneumatically driven, hydraulically driven, or driven by a piezoelectric element. However, in consideration of controllability, the flapper assembly moving mechanism is preferably electromagnetically controlled as an electromagnetic drive mechanism.
- the electromagnetic drive mechanism can be composed of, for example, a permanent magnet fixed to a flapper assembly and a fixed coil that generates an electromagnetic action between the permanent magnet and moves the flapper assembly.
- the present invention also proposes a more preferable aspect of the electromagnetic drive mechanism.
- a permanent magnet is formed in a cylindrical shape, and a pair of flappers having an opening / closing control surface is provided in the flapper assembly, and the cylindrical permanent magnet and the cylindrical permanent magnet are disposed between the center portions of the pair of flappers. They are connected by connecting members including magnet yokes located at both ends of the magnet.
- a pair of fixed coils arranged symmetrically from the middle position of the pair of flappers on the outer periphery of the cylindrical permanent magnet and the pair of magnet yokes, and coils positioned on both sides and the outer periphery of the fixed coil
- the flap yoke side end surface of the coil yoke is positioned outside the outer end surfaces of the pair of magnet yokes in a non-energized state and a neutral position (flapper non-deformation position) with respect to the fixed coil.
- the fixed coils are controlled so that currents flow in opposite directions.
- the flapper assembly of the fluid control valve of the present invention opens the supply nozzle and the exhaust nozzle.
- FIG. 1 is a longitudinal sectional view of a fluid control valve according to the present invention in a non-energized state.
- FIG. 2 is a longitudinal sectional view of a fluid control valve in FIG.
- FIG. 3 is a longitudinal sectional view showing a more general embodiment of a fluid control valve according to the present invention.
- FIG. 4 is a block diagram showing an example in which the fluid control valve according to the present invention is combined with a control device. It is.
- FIG. 5 is a block diagram showing another example in which the fluid control valve according to the present invention is combined with a control device.
- FIG. 1 and FIG. 2 show a first embodiment of a fluid control valve CV according to the present invention.
- the fluid control valve CV has a rotationally symmetric columnar shape centered on the axis O as a whole, and has left and right flow path blocks 10L and 10R and a central control block 20.
- an air supply port chamber 12 and a control port chamber 13 partitioned by a partition wall 11 are formed, and the force between the air supply port chamber 12 and the control port chamber 13 is on the axial line O. It communicates with an air supply nozzle 14 that is positioned and drilled in the partition wall 11.
- a diameter-expanded taper surface 14a that gradually increases in diameter toward the control block 20 is formed.
- a control port chamber 16 and an exhaust port chamber 17 partitioned by a partition wall 15 are formed.
- the exhaust chambers 17 communicate with each other through an exhaust nozzle 18 having a fixed diameter that is located on the axis 0 and is formed in the partition wall 15. Therefore, the supply nozzle 14 and the exhaust nozzle 18 are located on the same straight line (on the axis 0).
- the supply port chamber 12 communicates with the pressurized air source P through the supply port 12a, and the control port chamber 13 and the control port chamber 16 are controlled through the control port 13a and the control port 16a, respectively.
- the exhaust port chamber 17 communicates with the device C, and the exhaust port chamber 17 communicates with the atmosphere via the exhaust port 17a.
- the control port chamber 13 and the control port chamber 16 are in communication with each other.
- the control block 20 positioned between the flow path block 10L and the flow path block 10R includes a flapper assembly 30 and a flapper assembly movement mechanism (electromagnetic drive mechanism) 22 that moves the flapper assembly 30 in the direction of the axis O. ing.
- the flapper assembly 30 has a circular elastically deformable flapper 31L located on the flow path block 10L side and an identical flapper 31R located on the flow path block 10R side.
- the shafts of the left and right flapper 31L (31R) The parts are coupled to each other through a central cylindrical permanent magnet 25, left and right magnet yokes 26, and a flapper connection piece 27 (a symmetrical connection member).
- the peripheral edge of the flapper 31L is clamped and fixed between the flow path block 10L and the control block 20, and the peripheral edge of the flapper 31R is controlled with the flow path block 10R. It is clamped between the blocks 20.
- the cylindrical permanent magnet 25 is positioned in a floating state in the center of the control block 20. Flapper 31L (31R) can of course be perforated.
- Opening / closing control bodies 32L and 32R facing the supply nozzle 14 and the exhaust nozzle 18 are fixed to the flapper 31L and the flapper 31R, respectively.
- the open / close control body 32L is formed with a conical open / close control surface (conical protrusion) 33 corresponding to the diameter-expanded tapered surface 14a.
- the opening / closing control body 32R is formed with a needle-like opening / closing control surface (needle-like protrusion) 34 for inserting the tip portion into the exhaust nozzle 18.
- the needle-like opening / closing control surface 34 has a diameter that decreases as the distance from the control block 20 increases.
- a coil spring 35 is inserted between the opening / closing control body 32R and the partition wall 15 so as to press and urge the flapper assembly 30 toward the air supply nozzle 14.
- the diameter of the conical opening / closing control surface 33 is normally increased.
- the communication between the supply port chamber 12 and the control port chamber 13 is cut off in close contact with the tapered surface 14a.
- the flapper assembly moving mechanism 22 includes a columnar permanent magnet 25 of the control block 20 and a fixed coil yoke portion 24 positioned in the outer periphery of the columnar permanent magnet 25.
- the fixed coil yoke portion 24 having a cylindrical shape as a whole includes a central coil yoke 28a, a pair of coils (fixed coils) 29 positioned on both sides thereof, and a pair of end coil yokes positioned outside the coil 29.
- the central coil yoke 28a, the coil 29, and the end coil yoke 28b are further provided with a peripheral coil yoke 28c.
- the pair of coils 29 are wound in the same direction and are connected to the control circuit 44 (see FIGS. 4 and 5) so that currents flow in opposite directions.
- the both end surfaces (outer end surfaces) of the left and right end coil yokes 28b of the fixed coil yoke portion 24 are slightly (distance) from the both end surfaces (outer end surfaces) of the left and right magnet yokes 26 of the cylindrical permanent magnet 25 at the neutral position. d ( Figure 2 only) Located outside.
- the fluid control valve having the above-described configuration operates as follows.
- the coil 29 of the flapper assembly moving mechanism 22 is not energized, as shown in FIG. 1, the flapper assembly 30 is moved to the supply nozzle 14 side by the force of the coil spring 35, and the conical opening / closing control surface 33 is expanded. Close communication between air supply port chamber 12 and control port chamber 13 (control port chamber 16) in close contact with tapered surface 14a It is. That is, the pressure of the pressurized air source P is not exerted on the control device C.
- the outer end surfaces of the pair of end coil yokes 28b are located outside the outer end surfaces of the pair of magnet yokes 26 by a distance d, so that one end coil
- a repulsive force attractive force
- an attractive force repulsive force
- a gap is formed between the diameter-expanded tapered surface 14a and the conical opening / closing control surface 33, and the distance between the opening end 18a and the needle-shaped opening / closing control surface 34 is reduced.
- the distance between the conical opening / closing control surface 33 of the flapper assembly 30 and the opening end (expanded taper surface 14a) of the air supply nozzle 14 increases, while the opening of the double dollar opening / closing control surface 34 and the exhaust nozzle 18 increases.
- the distance to edge 18a is reduced.
- the supply port chamber 12 and the control port chamber 13 (control port chamber 16) communicate with each other, and the pressure of the pressurized air source P is exerted on the control device C.
- control port chamber 16 and the exhaust port chamber 17 communicate with each other via the exhaust nozzle 18, and the air in the control port chamber 13 (control port chamber 16) passes through the exhaust port 17a. Therefore, the pressure in the control port chamber 13 (control port chamber 16) is kept lower than the pressure in the supply port chamber 12.
- the amount of movement of the flapper assembly 30 against the coil spring 35 can be controlled by the amount of current supplied to the coil 29.
- the flapper assembly 30 When the flapper assembly 30 is moved to the maximum and the needle-shaped opening / closing control surface 34 closes the opening end 18a of the exhaust nozzle 18, the air in the control port chamber 13 (control port chamber 16) is transferred to the outside air through the exhaust nozzle 18. Since it is not released, the pressure in the control port chamber 13 (control port chamber 16) rises, and eventually the control port chamber 13 (control port chamber 1) 6) The pressure inside the air supply port chamber 12 becomes equal. Therefore, by controlling the moving position of the flapper assembly 30 with the amount of current supplied to the coil 29, the take-out pressure of the control port chamber 13 (control port chamber 16) can be controlled.
- the supply port chamber 12 and the control port chamber 13 can be disconnected from each other when the coil 29 is not energized.
- the coil spring 35 is omitted, and the coil 29 is not energized, and the diameter-increasing tapered surface 14a of the constant supply nozzle 14 and the conical opening / closing control surface 33 of the opening / closing control body 32L It is also possible to form a certain gap between them (maintain in a neutral position).
- the gap between the diameter-expanded tapered surface 14a and the conical opening / closing control surface 33 is changed to be larger or smaller by forward and reverse energization of the coil 29, and the pressure in the control port chamber 13 (control port chamber 16) is changed. Can be controlled.
- FIG. 3 shows an embodiment in which the fluid control valve of the present invention is more general.
- the conical opening / closing control surface 33 and the needle opening / closing control surface 34 of the above embodiment are eliminated, and the planar opening / closing control surfaces 34L and 34R are formed on the left and right opening / closing control bodies 32L and 32R, respectively.
- the coil spring 35 is omitted.
- the same operational effects as those of the first embodiment can be obtained except for the operational effects of the diameter-expanded tapered surface 14a (opening end 18a) and the conical opening / closing control surface 33 (needle-shaped opening / closing control surface 34). it can.
- the flapper assembly moving mechanism can be manually operated, pneumatically driven, hydraulically driven, piezoelectric element driven, or the like, which is preferably configured to move linearly on the axis 0.
- the electromagnetic drive mechanism is suitable, and the positional relationship between the permanent magnet and the coil is the permanent magnet on the flapper assembly side as in the electromagnetic drive mechanism of the above embodiment.
- positions a coil in the fixed side is good.
- the pair of coils may be arranged in such a manner that they are wound in opposite directions and are a composite coil composed of a series of conductive wires or two independent coils, and currents flow in opposite directions.
- the fluid control valve CV of the present invention can be used in various applications, and the application is not limited.
- FIG. 4 shows an example in which a rectifying throttle device 40 is interposed between the fluid control valve CV and the control device C of the present invention so that more accurate pressure can be taken out.
- a rectifying throttle device 40 is connected to the control ports 13a and 16a of the fluid control valve CV.
- the rectifier / throttle device 40 is configured to reduce pressure fluctuation on the input side and extract it to the output side, and the configuration thereof is not limited.
- the rectifying and throttle device 40 is provided with a differential pressure sensor 41 that detects a differential pressure between the input side and the output side, and an absolute pressure detection sensor 42 that detects an absolute pressure.
- the absolute pressure detection sensor 42 is arranged on either the input side or output side of the rectifier throttle device 40 or on both sides (input side and output side) in consideration of the flow rate or pressure passing through the rectifier throttle device 40. can do. 4 and 5 show the absolute pressure detection sensor 42 arranged on the output side of the rectifying and throttle device 40.
- FIG. The arithmetic circuit 43 integrates the differential pressure detected by the differential pressure sensor 41 and the absolute pressure detected by the absolute pressure detection sensor 42, and calculates the flow rate on the output side of the rectifier throttle device 40. The flow rate signal is fed back to the control circuit 44 of the fluid control valve CV, and a more accurate control pressure is taken out from the control ports 13a and 16a.
- a force S can be used by combining a gauge pressure sensor (not shown) and an atmospheric pressure sensor (not shown). If these are further connected to a temperature sensor (not shown), the fluid temperature can be stored as a correction factor for fluid calculation, so that more accurate detection can be performed.
- an isothermal pneumatic cylinder device having a pneumatic cylinder filled with a fiber material such as polyester can be used.
- the synthetic fiber material is preferably filled with several percent with respect to the inner volume of the pneumatic cylinder.
- isothermal pneumatic cylinder devices have been known to reduce the instantaneous temperature change that occurs when large air flows in and out of the pneumatic cylinder. Control is possible.
- FIG. 5 shows that a branch circuit of the rectifying and constricting device 40 connected to the air tank 45 is provided between the fluid control valve CV and the control device C of the present invention so that more accurate pressure can be taken out.
- Example It is.
- the configuration around the rectifying and restricting device 40 is the same as the configuration of FIG. 4, and the same elements are denoted by the same reference numerals.
- the rectifying throttle device 40 is not interposed between the fluid control valve CV and the isothermal pneumatic cylinder device (control device C), the flow resistance can be significantly reduced, and the isothermal air High-speed control of the pressure cylinder device is possible.
- a fluid control valve with quick response can be obtained. Further, according to the present invention, a fluid control valve having a stable performance without problems such as shock waves can be obtained, and can be applied to various pressure control devices.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fluid Mechanics (AREA)
- Magnetically Actuated Valves (AREA)
- Lift Valve (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/815,126 US7641171B2 (en) | 2005-02-02 | 2006-01-17 | Fluid control valve |
KR1020077017141A KR101272724B1 (ko) | 2005-02-02 | 2006-01-17 | 유체제어밸브 |
JP2007501522A JP4732433B2 (ja) | 2005-02-02 | 2006-01-17 | 流体制御弁 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005026587 | 2005-02-02 | ||
JP2005-026587 | 2005-02-02 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006082703A1 true WO2006082703A1 (ja) | 2006-08-10 |
Family
ID=36777093
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2006/300473 WO2006082703A1 (ja) | 2005-02-02 | 2006-01-17 | 流体制御弁 |
Country Status (6)
Country | Link |
---|---|
US (1) | US7641171B2 (ja) |
JP (1) | JP4732433B2 (ja) |
KR (1) | KR101272724B1 (ja) |
CN (1) | CN100559049C (ja) |
TW (1) | TWI347417B (ja) |
WO (1) | WO2006082703A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1970610A1 (de) * | 2007-03-14 | 2008-09-17 | Asco Joucomatic GmbH | Vorrichtung zur Regelung eines fluiden oder gasförmigen Mediums |
CN103028177A (zh) * | 2011-09-29 | 2013-04-10 | 北京航天长峰股份有限公司 | 麻醉蒸发器输出浓度控制装置 |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2013159067A1 (en) * | 2012-04-20 | 2013-10-24 | Martin Bryan A | Magnetic field switches |
CN103016783B (zh) * | 2012-12-08 | 2015-01-28 | 中国航天科技集团公司第六研究院第十一研究所 | 一种双线圈驱动气锁式双稳态电磁副阀 |
CN103075537B (zh) * | 2013-02-05 | 2015-04-01 | 中国第一汽车股份有限公司无锡油泵油嘴研究所 | 一种双向一体式对置阀、高压燃油进回联动控制系统及控制方法 |
DE102013108164B4 (de) * | 2013-07-30 | 2017-11-02 | Hartmuth Rausch | Ventil mit einem Linearantrieb für den Ventilkolben |
TWI480496B (zh) | 2013-11-20 | 2015-04-11 | Ind Tech Res Inst | 通電直熱再生式壓縮空氣乾燥裝置及除濕再生單元 |
TWM493020U (zh) | 2014-08-26 | 2015-01-01 | Ind Tech Res Inst | 除濕單體、分層溫控除濕元件及乾燥裝置 |
TWI526656B (zh) | 2014-08-26 | 2016-03-21 | 財團法人工業技術研究院 | 除濕單體、分層溫控除濕元件、乾燥裝置及其溫控方法 |
JP6628968B2 (ja) * | 2015-02-10 | 2020-01-15 | 特許機器株式会社 | 流体サーボバルブ及び流体サーボ装置 |
JP6587526B2 (ja) * | 2015-12-03 | 2019-10-09 | 本田技研工業株式会社 | 電磁弁 |
JP6587527B2 (ja) * | 2015-12-03 | 2019-10-09 | 本田技研工業株式会社 | 電磁弁 |
DE102016212950A1 (de) * | 2016-07-15 | 2018-01-18 | Festo Ag & Co. Kg | Elektromagnetischer Ventilantrieb, Verfahren zu seiner Herstellung und damit ausgestattetes Magnetventil |
WO2019079426A1 (en) | 2017-10-17 | 2019-04-25 | Automotive Technologies International, Inc. | HIGH SPEED VALVE |
IT201800005892A1 (it) * | 2018-05-31 | 2019-12-01 | Valvola per fluidi, preferibilmente per gas |
Citations (4)
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JPS52143592U (ja) * | 1977-04-13 | 1977-10-31 | ||
JPS60167279U (ja) * | 1984-04-16 | 1985-11-06 | 株式会社トキメック | 比例ソレノイド形電磁圧力制御弁 |
JPH06272784A (ja) * | 1993-03-16 | 1994-09-27 | Mitsubishi Electric Corp | ポペット式比例電磁液圧制御弁 |
JPH0755043A (ja) * | 1993-07-22 | 1995-03-03 | Robert Bosch Gmbh | 電磁的に作動可能な圧力制御弁 |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS52143592A (en) * | 1976-05-26 | 1977-11-30 | Inoue Japax Res Inc | Composite grinder |
JPS60167279A (ja) * | 1984-02-09 | 1985-08-30 | Matsushita Electric Ind Co Ltd | 再充電可能な電気化学装置 |
US4819682A (en) * | 1986-05-19 | 1989-04-11 | Marcke Karel C Van | Pneumatically operable valve |
JP3633166B2 (ja) * | 1996-12-28 | 2005-03-30 | アイシン・エィ・ダブリュ株式会社 | リニアソレノイド |
JP2001099016A (ja) | 1999-09-30 | 2001-04-10 | Denso Corp | 圧力制御弁 |
JP4275463B2 (ja) * | 2003-06-04 | 2009-06-10 | 藤倉ゴム工業株式会社 | 電空変換式空気レギュレータ |
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2006
- 2006-01-17 US US11/815,126 patent/US7641171B2/en not_active Expired - Fee Related
- 2006-01-17 JP JP2007501522A patent/JP4732433B2/ja active Active
- 2006-01-17 WO PCT/JP2006/300473 patent/WO2006082703A1/ja not_active Application Discontinuation
- 2006-01-17 CN CNB2006800037885A patent/CN100559049C/zh not_active Expired - Fee Related
- 2006-01-17 KR KR1020077017141A patent/KR101272724B1/ko active IP Right Grant
- 2006-01-24 TW TW095102703A patent/TWI347417B/zh active
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JPS52143592U (ja) * | 1977-04-13 | 1977-10-31 | ||
JPS60167279U (ja) * | 1984-04-16 | 1985-11-06 | 株式会社トキメック | 比例ソレノイド形電磁圧力制御弁 |
JPH06272784A (ja) * | 1993-03-16 | 1994-09-27 | Mitsubishi Electric Corp | ポペット式比例電磁液圧制御弁 |
JPH0755043A (ja) * | 1993-07-22 | 1995-03-03 | Robert Bosch Gmbh | 電磁的に作動可能な圧力制御弁 |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1970610A1 (de) * | 2007-03-14 | 2008-09-17 | Asco Joucomatic GmbH | Vorrichtung zur Regelung eines fluiden oder gasförmigen Mediums |
CN103028177A (zh) * | 2011-09-29 | 2013-04-10 | 北京航天长峰股份有限公司 | 麻醉蒸发器输出浓度控制装置 |
Also Published As
Publication number | Publication date |
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US7641171B2 (en) | 2010-01-05 |
KR20070103007A (ko) | 2007-10-22 |
JP4732433B2 (ja) | 2011-07-27 |
US20090032751A1 (en) | 2009-02-05 |
TWI347417B (en) | 2011-08-21 |
TW200628716A (en) | 2006-08-16 |
JPWO2006082703A1 (ja) | 2008-06-26 |
CN101111705A (zh) | 2008-01-23 |
KR101272724B1 (ko) | 2013-06-10 |
CN100559049C (zh) | 2009-11-11 |
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