WO2003004914A1 - Clapet - Google Patents

Clapet Download PDF

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Publication number
WO2003004914A1
WO2003004914A1 PCT/JP2002/006282 JP0206282W WO03004914A1 WO 2003004914 A1 WO2003004914 A1 WO 2003004914A1 JP 0206282 W JP0206282 W JP 0206282W WO 03004914 A1 WO03004914 A1 WO 03004914A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pipe
pressure
fluid
check
Prior art date
Application number
PCT/JP2002/006282
Other languages
English (en)
Japanese (ja)
Inventor
Yukihiko Karasawa
Original Assignee
Karasawa Fine., Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Karasawa Fine., Ltd filed Critical Karasawa Fine., Ltd
Publication of WO2003004914A1 publication Critical patent/WO2003004914A1/fr

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
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/04—Check valves with guided rigid valve members shaped as balls
    • 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
    • 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
    • F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
    • F16K11/105—Three-way check or safety valves with two or more closure members

Definitions

  • the fluid under pressure is automatically selected and discharged, or the pressurized fluid is discharged from one path.
  • the present invention relates to a check valve capable of supplying fluid to a path having a pressure lower than the supply pressure of two paths in which the fluid pressure changes.
  • FIG. 5 is a simplified diagram of the overall composition of such a particle refining system.
  • A is the low-pressure side fluid
  • B is the high-pressure side fluid.
  • the pipeline through which the low-pressure side fluid A flows is shown by a solid line
  • the pipeline through which the high-pressure side fluid B flows is shown by a dotted line.
  • Oil is used as the low-pressure fluid A.
  • the other high-pressure fluid B is a mixture of a plurality of immiscible liquids such as water and oil, and various slurries.
  • Tank 1 stores fluid A on the low pressure side. This low-pressure side fluid A is pumped by the pressure pump 2. The low-pressure fluid A discharged from the pressure pump 2 is adjusted to a predetermined pressure in the regulator 3 and reaches the two switching valves 4 and 4 ′.
  • Two discharge pipes are connected to each of the switching valves 4 and 5 .
  • Discharge conduit connected to the switching valve 4 is connected to the intensifier 5, a discharge conduit connected switching valve 4, the is connected to the intensifier 5 3.
  • the pressure booster 5 Discharges the high-pressure fluid B, which has been increased to a high pressure.
  • the pressure intensifiers 5 and 5 ′ use the forward and backward movements of the piston, and pressurize the high-pressure side fluid B during reciprocation, but cannot pressurize the other movement ′. Therefore, if Assure pressurized alternately by two intensifier 5, 5 5, it is possible to obtain a high pressure side fluid B under pressure from the stomach deviation or the other intensifier 5, 5 'at all times. This switching is performed by the switching valve 4, 4 5.
  • the high-pressure fluid B discharged from the pressure intensifier 5 is connected to an intermediate point between the two check valves 6 and 6.
  • the check valve 6 is configured to flow the fluid in the direction of the arrow in the figure but not in the reverse direction.
  • the high-pressure side fluid B discharged from the other pressure intensifier 5 ' is connected to an intermediate point between the two check valves 6,, 6'.
  • the check valve 6 ′ is configured such that the fluid flows in the direction of the arrow in the figure, but does not flow in the reverse direction.
  • the high pressure side fluid B is stored in the tank 7.
  • the high-pressure side fluid B in the tank 7 reaches the air pump 8 through a pipe extending from below the tank 7, is sent out by the air pump 8, is divided into two pipes, and is divided into two check valves 6 or check valves. Reach stop valve 6 '. If the pistons of the intensifiers 5 and 5 ′ are descending and pressurizing, the high-pressure fluid B from the air pump 8 cannot pass through the check valves 6, 6, but the pistons rise and the intensifier If 5, 5 'is depressurizing, the pressure of the high-pressure fluid B on the air pump 8 side will be higher, and the high-pressure fluid B will enter the cylinders of the pressure intensifiers 5, 5'.
  • the intensifiers 5, 5 5 alternately lower the piston to supply the pressurized high-pressure fluid B, the conversely, the intensifiers 5, 5, 5 alternately raise the piston to increase the high-pressure fluid.
  • B is decompressed, and new high-pressure fluid B is supplied from the tank 7.
  • the high-pressure side fluid B that has passed through the check valves 6, 6 reaches the jet impingement section 9, is divided into two flow paths, and is provided with nozzles 91, provided at the ends of the flow paths. 9 Injected from 1.
  • the fluid ejected from one nozzle 91 collides with the fluid ejected from the other nozzle 91, the particles contained in the slurry are crushed or the water and oil particles are finely emulsified. Will be.
  • the high-pressure side fluid B that has collided in the jet impingement section 9 returns to the tank 7 again, circulates, and is repeatedly collided until the desired emulsification degree and particle size are reached.
  • the check valve 6, 6 5 in the above configuration usually of the type which presses the ball valve on the valve seat by a coil spring has been used. If the pressure of the fluid on the valve seat side is high, Fluid flows as body pressure overcomes the coil spring and pushes up the valve body. If the pressure of the fluid on the coil spring side is high, the valve body will be pressed against the valve seat and will not flow. That is. Subject of the Invention.
  • the fluid to be handled is a solid-liquid multi-phase fluid (slurry)
  • the solid particles in the fluid flow as if rubbing the coil spring.
  • the coil spring wears and weakens the elasticity of the spring. If the elasticity of the spring is weak, the movement of the valve body will be poor and the check cannot be made.
  • both the ball valve element and the coil spring are in the flow path, there has been a problem that the flow path area is reduced and the flow rate is reduced.
  • the present invention provides a valve chamber, a first pipe and a second pipe which are opened at opposing positions of the valve chamber, and a valve chamber of the first pipe and the second pipe.
  • a valve seat formed at the side end, a discharge pipe opening between the two valve seats, and the two valve seats in the valve chamber And a valve body movably provided between the two.
  • valve chamber a valve chamber, a first pipe and a second pipe which open at positions opposite to the valve chamber, a valve seat formed at a valve chamber side opening of the first pipe, and the first pipe inside the valve chamber.
  • a partition wall provided between the pipe and the second pipe, a main flow path formed through the partition wall, and an auxiliary flow path formed through the partition wall at a position distant from the main flow path;
  • a valve body passage formed between the partition wall and the inner wall of the valve chamber on the valve seat side; and a position in the valve body passage that abuts on the valve seat and closes, and is separated from the valve seat.
  • a valve body that is movable between a position where the valve is opened to approach the auxiliary flow path, and a direction in which the valve body passage is closer to the second pipe in the valve position than in the valve closed position. It is characterized by being inclined.
  • An opening of the main flow passage facing the first conduit is located at a position shifted from the first conduit, or the check valve is arranged symmetrically with the first conduits connected to each other.
  • a configuration may be adopted in which a suction pipe communicating with the coupled first pipe is provided.
  • FIG. 1 is a view showing a first embodiment of a check valve of the present invention
  • FIG. 2 is a cross-sectional view showing a configuration of a check valve of a second embodiment of the present invention
  • FIG. 3 is a reverse view shown in FIG. Fig. 4 shows a check valve with stop valves arranged symmetrically.
  • Fig. 4 is a simplified view of the overall configuration of a system for refining particles.
  • Fig. 5 is an overall configuration of a conventional system for refining particles.
  • FIG. 1 is a view showing a first embodiment of the check valve of the present invention.
  • a valve chamber 12 is formed inside a work 11 of a check valve 10, and a first pipe 13 and a second pipe 1 are provided at opposing positions of the valve chamber 12. 4 and a discharge conduit 15 opening in the middle between them.
  • a ball-shaped valve element 16 is inserted into the valve chamber 12.
  • the valve body 13 abuts on a valve seat 13 a formed at the valve chamber side end of the first pipe line 13, and this first pipe line 13 is formed. Close.
  • it is at the position 16 'shown by the dotted line, it abuts on the valve seat 14a of the second conduit 14 and closes the second conduit 14.
  • Discharge line 15 has multiple small holes 15a, 15b, 15c This allows the valve 16 to freely move back and forth between the positions indicated by the solid line and the dotted line, and prevents all three from being simultaneously closed by the valve 16. Further, even if one of the three small-diameter holes 15 a, 15 b, and 15 c is closed, the remaining two cross-sectional areas are made equal to the cross-sectional area of the discharge pipe 15.
  • valve body 16 When the fluid pressure in the second pipe 14 becomes higher than the fluid pressure in the first pipe 13, the valve body 16 is moved by the pressure from the second pipe 14 as shown by a solid line to the valve seat 13. a, and closes the first pipe 13. Fluid flows from the second conduit 14 to the third conduit, the discharge conduit 15.
  • valve element 16 is pushed by the higher pressure of the fluid in the first pipe 13 and the second pipe 14 and presses against the lower valve seat.
  • the flow from the pipe 13 to the second pipe 14 and, conversely, the flow from the second pipe 14 to the first pipe 13 can be reliably prevented.
  • the check valve 10 of this embodiment since there is no coil spring in the valve chamber 12, the problem of wear of the coil spring is eliminated, the flow path is widened, and a large flow rate can be secured. Also, when the valve element 16 presses against one of the two valve seats 13a and 14a and closes the valve, it goes from the pipe 13 or 14 with the other valve seat to the discharge pipe 15 Since the valve element 16 does not exist in the flow path, the flow path can be made large from this surface, and a large flow rate can be secured.
  • valve seat 13a or the valve body 16 in contact with the valve seat 14a almost completely closed one of the small-diameter holes 15a or 15c.
  • the valve 16 since the remaining two can secure an area approximately equal to the area of the discharge pipe 15, as a result, the valve 16 does not obstruct the flow.
  • the check valve 10 includes one check valve composed of a first conduit 13 and a discharge conduit 15 and one check valve composed of a second conduit 14 and a discharge conduit 15. It has a configuration that combines two check valves. At the same time, the high-pressure fluid in either the first pipe 13 or the second pipe 14 can flow to the discharge pipe 15 and has the function of a switching valve. It has something.
  • FIG. 2 is a cross-sectional view illustrating a configuration of a check valve 20 according to a second embodiment of the present invention.
  • a check valve 20 has a configuration in which blocks 21 and 22 are connected by sealing them with a packing (not shown) or the like.
  • a valve chamber 23 is formed between these two blocks 21 and 22.
  • a first pipe 24 and a second pipe 25 are formed at opposing positions in the valve chamber 23, and a middle part thereof is partitioned by a partition wall 26.
  • the partition wall 26 has two through holes. One is a main channel 27 having substantially the same diameter as the first channel 24 and the second channel 25, and the other is an auxiliary channel 28 having a smaller diameter than the main channel 27.
  • the ball-shaped valve element 29 is disposed in a valve element passage 23b formed between the wall 23a on the valve seat 24a side of the valve chamber 23 and the wall 26a of the partition wall 26.
  • the wall 26 a of the partition wall 26 forming the valve body passage 23 b and the wall 23 a of the valve chamber 23 are formed by a second pipe extending from the main flow path 27 to the auxiliary flow path 28. The slope is such that it approaches the path 25, whereby the valve element passage 23b is similarly inclined.
  • the differential pressure causes the ball-shaped valve body 29 to be pushed. Since the diameter of the main flow path 27 is smaller than the diameter of the valve element 29, the valve element 29 necessarily moves in the valve element passage 23b along the slope of the walls 23a and 26a. It reaches the inside of the valve body passage 23 b shown in FIG. 2 (b). Further, at this time, the fluid also flows through the auxiliary flow path 28, but since the area of the auxiliary flow path 28 is small, the flow velocity is increased and the pressure is reduced. Therefore, the static pressure in the auxiliary flow path 28 decreases, and the valve element 29 is attracted to the open end of the auxiliary flow path 28 by this pressure difference.
  • the fluid flows from the first conduit 24 to the main conduit 27 ⁇ the second conduit 25.
  • the valve element 29 also enters the valve element path 23 b and deviates from the flow path from the first pipe line 24 to the main flow path 27. A large flow area can be secured.
  • the fluid in the second conduit 25 will flow from both the main flow path 27 and the auxiliary flow path 28. Attempts to flow toward the first pipeline 24.
  • the cross-sectional area of the auxiliary flow path 28 is smaller than the cross-sectional area of the main flow path 27. Is smaller, the flow velocity passing through the auxiliary flow path 28 becomes faster than the flow velocity passing through the main flow path 27. Therefore, the valve element 29 is first pressed against the valve seat 24a by the pressure from the auxiliary flow path 28 as shown by the solid line in FIG. 2 (a).
  • FIG. 3 is a view showing a check valve 30 in which the check valves 20 shown in FIG. 2 are arranged symmetrically.
  • the check valve on the right side and 2 0 5, the check valve of the left and 2 0, also the configuration, the right of the check valve 2 0, are denoted by "the configuration towards.
  • the check valves 20, 20 ′ on both sides adjoin the first pipes 24, 24 ′, and these are connected to the suction pipe 31.
  • the fluid is supplied from the suction line 31.
  • the valve element 29 ′ is connected to the valve seat 24 a. 'Close the valve by pressing against.
  • the valve body 29 is moved to a position close to the auxiliary flow passage 28 and is opened.
  • the fluid flows from the first pipe 24 to the second pipe 25 via the main flow path 27. If the pressure in the second line 25 is higher than the pressure in the suction line 31, the fluid flows from the first line 24, via the main flow path 27, to the second line 25, Flows to
  • FIG. 4 is a diagram showing an example of a configuration in which the check valve of the present invention is used in the system for refining particles described in FIG.
  • the same components as those of the conventional example such as the pressure intensifiers 5 and 5 ', the air pump 8 and the jet impingement section 9 are denoted by the same reference numerals and description thereof is omitted.
  • the tank 40 and 40 5 the low-pressure side fluid A is filled.
  • Tank 40 has a pressure pump 41 and tank 40 'has a pressure pump 41', which is immersed in the liquid.
  • the discharge port of the pressure pump 41 is connected to the intensifier 5, the discharge port of the pressure pump 4 I 5 is connected to the intensifier 5 '.
  • the discharge pressure of the pressure pumps 41, 41 ' is monitored by pressure gauges 42, 42', and is controlled by a control device (not shown) so as to reach a predetermined pressure.
  • the pressure pump 41 To operate the pressure intensifier 5, the pressure pump 41 is rotated in the forward direction, and the low pressure side fluid A is sent to the pressure intensifier 5 while monitoring the discharge pressure with the pressure gauge 42. As a result, the piston of the intensifier 5 is pushed down, and the high-pressure fluid B is pressurized to a high pressure and sent out.
  • the pressure pump 41 When the pressure pump 41 is rotated in the reverse direction, the low-pressure fluid A supplied to the pressure intensifier 5 is recovered, whereby the pressure in the pressure intensifier 5 is reduced, and the high-pressure fluid B is supplied to the pressure intensifier 5. .
  • the fluid contained in the accumulator 43 is supplied to the pressure intensifier 5 by being pushed by the gas, and helps the piston of the pressure intensifier 5 to rise.
  • the pressure pumps 41, 41 'and the pressure intensifiers 5, 5 are connected by only one pipe, and the hydraulic pressure 0 path is simplified.
  • Intensifier 5 line from 5 are connected to both ends of the check valve 10 and 30 arranged in parallel. That is, the pipeline from the pressure intensifier 5 is connected to the first pipeline 13 of the check valve 10 and the second pipeline 25 of the check valve 30. Further, the conduit from the intensifier 5 5 includes a second conduit 14 of the check valve 10 is connected to the second conduit 25 of the check valve 30 '. The discharge pipe 15 of the check valve 10 is connected to the jet impingement section 9, and the suction pipe 31 of the check valve 30 is connected to the tank 7 via the air pump 8.
  • the check valves 10 and 30 operate as follows.
  • the pressure intensifier 5 ′ is in the depressurization period.
  • the pressure in the first pipe 13 increases, so that the valve element 16 is pressed against the valve seat 14a by the pressure to close the second pipe 14 as shown by the dotted line.
  • the high-pressure side fluid B from the pressure intensifier 5 reaches the jet impingement section 9 from the first pipe 13 via the discharge pipe 15, and is jetted from the nozzles 91 and 91 to collide. Will be.
  • the valve body 29 ′ of the check valve 20 ′ approaches the auxiliary flow path 28 ′ and enters the valve state.
  • the pressure of the second pipe 25 connected to the pressure intensifier 5 increases, and the valve element 29 comes into pressure contact with the valve seat 24 a to be in a closed state. Therefore, the high-pressure side fluid B in the tank 7 is supplied to the intensifier 5 ′ by the air pump 8 through the suction pipe 31, the second pipe 25 ′.
  • the pressure intensifier 5 ′ when the pressure intensifier 5 ′ is in the pressurizing period and pressurizes the high-pressure fluid B, the pressure intensifier 5 enters the depressurizing period. Then, the high-pressure fluid B from the compressor 5 ′ reaches the jet impingement section 9 from the second pipe 14 via the discharge pipe 15, and is jetted from the nozzles 9 1 and 9 1 to collide. .
  • the high-pressure side fluid B in the tank 7 is supplied to the pressure intensifier 5 by the air pump 8 through the suction pipe 31, the second pipe 25, and the like.
  • the check valves 10 and 30 of the present invention shown in FIGS. 1 and 3 are used in the system for miniaturizing particles shown in FIG. 4 and include two pressure intensifiers 5 and 5 ′ whose fluid pressure changes periodically.
  • the fluid acts not only as a check valve but also as a switching valve.
  • the check valve of the present invention includes: a valve chamber; a first pipe and a second pipe that are opened at opposing positions of the valve chamber; a first pipe and a second pipe.
  • a valve seat formed at the end of the valve chamber on the side of the valve chamber, a discharge pipe opening at an intermediate position between the two valve seats, a valve body movably provided between the two valve seats in the valve chamber,
  • the coil spring could be eliminated, and the problem of coil spring wear could be solved.
  • the flow rate can be secured by increasing the flow path.
  • the first and second pipelines whose fluid pressure changes periodically and the discharge pipeline are connected, the higher pressure of the first and second pipelines is selected to discharge. It can automatically communicate with the pipe.
  • the two check valves can be integrated into one, and piping can be simplified.
  • valve chamber and a first pipe and a second pipe which are opened at opposing positions of the valve chamber, A valve seat formed at the valve chamber side opening of the first pipe, a partition wall provided between the first pipe and the second pipe in the valve chamber, and a main flow formed through the partition wall.
  • valve element passage is inclined such that the valve opening position is closer to the second conduit than the valve closing position, the coil spring can be eliminated from the check valve. There is no need to worry about abrasion, and the flow path becomes larger, ensuring a sufficient flow rate.
  • the two Fluid can be automatically supplied to the lower pressure one of the second lines of the two check valves. Also, since the two check valves are connected, piping can be simplified.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Check Valves (AREA)
  • Multiple-Way Valves (AREA)

Abstract

Un premier objet est pourvu d'un clapet qui rend la présence des ressorts en spirale inutile et qui est capable d'augmenter le débit d'écoulement. Cet objet comprend une chambre de clapet (12), un premier pipeline (13) et un second pipeline (14) qui s'ouvrent au niveaux des positions opposées à la chambre de clapet, des sièges de clapet (13a, 14a) formés aux extrémités chambre-clapet du premier et du second pipeline, un pipeline (15) d'apport s'ouvrant à un niveau intermédiaire entre les deux sièges de clapet et un corps (16) de clapet mobile entre les deux sièges de clapet dans la chambre de clapet. Le premier et le second pipeline (13, 14) sont commutés automatiquement de façon que le pipeline qui possède la pression la plus élevée soit connecté au pipeline (15) d'apport afin de laisser un fluide s'écouler. Dans ce cas, l'absence de tout ressort en spirale dans le canal d'écoulement permet d'augmenter la taille de ce dernier et, on évite aussi les problèmes d'usure de ces ressorts. Par ailleurs, le corps (16) de clapet peut être placé en dehors du canal d'écoulement, et de ce point de vue également, le débit d'écoulement peut être augmenté.
PCT/JP2002/006282 2001-07-03 2002-06-24 Clapet WO2003004914A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001-202194 2001-07-03
JP2001202194A JP2003014146A (ja) 2001-07-03 2001-07-03 逆止弁

Publications (1)

Publication Number Publication Date
WO2003004914A1 true WO2003004914A1 (fr) 2003-01-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2002/006282 WO2003004914A1 (fr) 2001-07-03 2002-06-24 Clapet

Country Status (3)

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JP (1) JP2003014146A (fr)
TW (1) TW565667B (fr)
WO (1) WO2003004914A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008060168A1 (fr) * 2006-11-15 2008-05-22 William Steven Gillanders Soupape hydraulique et actionneur hydraulique double action
NL2014231A (en) * 2014-04-04 2016-01-20 Hamilton Sundstrand Space Sys Dual check valve and method of controlling flow through the same.
CN107869600A (zh) * 2016-09-27 2018-04-03 惠州科赛医疗有限公司 一种切换阀
CN111623147A (zh) * 2020-05-13 2020-09-04 温州东特科技有限公司 一种卫生级三通阀

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4759270B2 (ja) * 2005-01-11 2011-08-31 日本特殊陶業株式会社 微粒化装置の制御方法
CN103104718A (zh) * 2011-11-09 2013-05-15 江西福事特液压有限公司 扩口式高压梭阀
JP5904254B2 (ja) * 2013-12-17 2016-04-13 株式会社デンソー 油圧制御弁及びバルブタイミング調整装置
DE102014015628A1 (de) * 2014-10-22 2016-04-28 Webasto SE Wechselventil
KR101969014B1 (ko) * 2018-03-27 2019-04-15 현대강전(주) 유체의 흐름 방향을 제어할 수 있는 밸브 어셈블리
KR101994923B1 (ko) * 2018-03-27 2019-07-03 현대강전(주) 다수의 출입구를 가지는 밸브 어셈블리

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63193169U (fr) * 1987-05-30 1988-12-13
JPH11280579A (ja) * 1998-03-30 1999-10-12 Denso Corp 弁装置及びそれを用いた燃料タンク
JP2000074232A (ja) * 1998-06-19 2000-03-14 Yazaki Corp ガス集合設備用調整弁

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63193169U (fr) * 1987-05-30 1988-12-13
JPH11280579A (ja) * 1998-03-30 1999-10-12 Denso Corp 弁装置及びそれを用いた燃料タンク
JP2000074232A (ja) * 1998-06-19 2000-03-14 Yazaki Corp ガス集合設備用調整弁

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008060168A1 (fr) * 2006-11-15 2008-05-22 William Steven Gillanders Soupape hydraulique et actionneur hydraulique double action
NL2014231A (en) * 2014-04-04 2016-01-20 Hamilton Sundstrand Space Sys Dual check valve and method of controlling flow through the same.
US9388909B2 (en) 2014-04-04 2016-07-12 Hamilton Sundstrand Space Systems International, Inc. Dual check valve and method of controlling flow through the same
CN107869600A (zh) * 2016-09-27 2018-04-03 惠州科赛医疗有限公司 一种切换阀
CN111623147A (zh) * 2020-05-13 2020-09-04 温州东特科技有限公司 一种卫生级三通阀

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TW565667B (en) 2003-12-11

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