WO2006100973A1 - Vanne a debit constant - Google Patents

Vanne a debit constant Download PDF

Info

Publication number
WO2006100973A1
WO2006100973A1 PCT/JP2006/305088 JP2006305088W WO2006100973A1 WO 2006100973 A1 WO2006100973 A1 WO 2006100973A1 JP 2006305088 W JP2006305088 W JP 2006305088W WO 2006100973 A1 WO2006100973 A1 WO 2006100973A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve member
constant flow
valve
coil spring
flow path
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2006/305088
Other languages
English (en)
Japanese (ja)
Inventor
Eiji Fukuzawa
Yukinori Kubozono
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toto Ltd
Original Assignee
Toto 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 Toto Ltd filed Critical Toto Ltd
Priority to JP2007509213A priority Critical patent/JP4775769B2/ja
Publication of WO2006100973A1 publication Critical patent/WO2006100973A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D7/00—Control of flow
    • G05D7/01—Control of flow without auxiliary power
    • G05D7/0126—Control of flow without auxiliary power the sensing element being a piston or plunger associated with one or more springs
    • G05D7/0133—Control of flow without auxiliary power the sensing element being a piston or plunger associated with one or more springs within the flow-path
    • G05D7/014—Control of flow without auxiliary power the sensing element being a piston or plunger associated with one or more springs within the flow-path using sliding elements

Definitions

  • the present invention relates to a constant flow valve, and more particularly to a constant flow valve that adjusts the flow rate of water to flow out to a predetermined amount regardless of fluctuations in the pressure of supplied water.
  • a conventional constant flow valve for example, as described in Patent Document 1, a plurality of movable valve bodies are connected in series to a fixed valve body fixed in a constant flow valve body extending in a cylindrical shape.
  • the spring constant attached to each movable valve body is adjusted by the elastic force of different coil springs.
  • Patent Document 1 Japanese Utility Model Publication No. 61-40569
  • Patent Document 2 JP-A-6-31051
  • the present invention has been made to solve the above-described problems of the prior art, and is a small-sized device that adjusts the flow rate of water to flow out regardless of fluctuations in the pressure of the supplied water.
  • the purpose is to provide a constant flow valve with a simple structure.
  • the present invention is a constant flow valve that adjusts the flow rate of water to be discharged to a predetermined amount regardless of fluctuations in the pressure of supplied water.
  • An outer valve member that changes the cross-sectional area of the first flow path formed between the outer periphery and the outer valve member is disposed inside the outer valve member so as to be slidable with respect to the outer valve member.
  • An inner valve member that changes a cross-sectional area of the second flow path formed between the outer peripheral portion and the inner peripheral portion of the outer valve member, and is disposed between the constant flow valve main body and the outer valve member.
  • the outer valve member is urged in the axial direction, and when the water pressure acts on the outer valve member, the outer valve member is slid,
  • An outer coil spring that shrinks to reduce the cross-sectional area of the path, and is disposed between the outer valve member and the inner valve member, urges the inner valve member in the axial direction, and water pressure is applied to the inner valve member.
  • a coil spring that slides to cause the inner valve member to slide and to reduce the cross-sectional area of the second flow path.
  • the outer valve member is disposed inside the constant flow valve main body so as to be slidable with respect to the constant flow valve main body, and this sliding causes a gap between the outer peripheral portion and the inner peripheral portion of the constant flow valve main body.
  • the cross-sectional area of the first flow path formed on the inner side of the outer valve member is changed and is slidably disposed with respect to the outer valve member inside the outer valve member.
  • the cross-sectional area of the second flow path formed between the peripheral portion changes, the outer coil spring is disposed between the constant flow valve body and the outer valve member, and the inner coil spring is disposed between the outer valve member and the inner valve member. Therefore, it is possible to realize a constant flow valve with a small and simple structure that adjusts the flow rate of the discharged water to a predetermined amount regardless of the change in the pressure of the supplied water. it can.
  • the spring constant of the inner coil spring is greater than the spring constant of the outer coil spring. Larger is preferred. This allows the outer valve member and the inner valve member to be urged in the axial direction so that the first flow channel that can increase the flow channel area can be used as a flow channel that can flow a large flow rate at low water pressure. Can be slid.
  • the outer valve member includes an arch portion extending so as to cross the outer valve member, and a support protrusion formed on the arch portion and slidably supporting the inner valve member in the axial direction. It is preferable that the inner valve member is formed with a recess for slidably receiving the support protrusion. Thus, the inner valve member can slide accurately in the axial direction with respect to the outer valve member.
  • the arch portion is preferably formed in a wing shape so as to rectify the downstream side of the outer valve member. As a result, the flow behind the constant flow valve is rectified, and the lateral vibration of the outer valve member can be prevented.
  • the first flow path or the second flow path is maintained in a water-permeable state even when the cross-sectional area of the flow paths is the smallest. Since the first flow path or the second flow path itself can be used as an escape flow path in a state where the outer and inner valve members are moved most due to water pressure, it is not necessary to configure a separate escape flow path, and it can be configured compactly and has a strong force. The flow of the escape flow path force can be dispersed and ejected by the cylindrical first flow path or the second flow path force, and the generation of vortices causing vibrations can be suppressed.
  • the downstream end portion of the support protrusion of the outer valve member is formed in a shape that expands from the upstream side to the downstream side, and includes a jet dispersion portion that disperses the jet flow from the second flow path.
  • a jet dispersion portion that disperses the jet flow from the second flow path.
  • a third channel having a constant channel cross-sectional area is always formed at the downstream end of the inner valve member, and the third channel is configured to disperse the jet flow. Be it! As a result, it is possible to adjust the flow rate of water to flow out to a predetermined amount regardless of fluctuations in the pressure of the water supplied to the constant flow valve, and to reduce the occurrence of cavitation due to the jet flow from the third flow path. it can.
  • the coil spring element wire of the seat portion of the inner coil spring is provided with noise preventing means for preventing noise caused by vibration.
  • the noise preventing means is configured to connect the coil spring element wires of the inner coil spring or the outer coil spring and the coil spring element wires adjacent to the coil spring element wires. It is preferable that it is constituted by a spring wire connecting elastic member that is integrally attached to. This spring element connecting elastic member can completely prevent the adjacent coil spring elements of the coil spring contact portion from contacting each other when the inner coil spring or the outer coil spring vibrates. Noise generated by contact can be prevented. Further, the natural vibration frequency of the inner coil spring or the outer coil spring can be changed and the vibration of the spring can be absorbed by the spring element coupling elastic member, so that the resonance phenomenon can be suppressed.
  • resonance suppressing means for suppressing axial resonance of the inner valve member is provided in the support protrusion of the outer valve member and the recess of the inner valve member.
  • an elastic member is disposed at the end of the inner coil spring or the outer coil spring. As a result, it is possible to suppress the collision noise generated by the end force of the inner coil spring or the outer coil spring.
  • a plurality of plate-like valve body legs protruding in the circumferential direction are formed on the downstream side portion of the outer valve member or the inner valve member. It is preferable to be configured to guide the sliding of the outer valve member relative to the valve body or the sliding of the inner valve member relative to the outer valve member.
  • a radially projecting protrusion is formed on the valve body leg of the outer valve member or the inner valve member, and this protrusion locks the outer valve member to the constant flow valve body.
  • the inner valve member is preferably configured to be locked to the outer valve member.
  • FIG. 1 is an exploded perspective view showing a constant flow valve according to the first embodiment of the present invention
  • FIG. 2 is a perspective view showing the constant flow valve according to the first embodiment of the present invention.
  • the constant flow valve 1 of the present embodiment includes a casing 2 forming a substantially cylindrical constant flow valve main body, an outer compression coil spring 4 accommodated in the casing 2, an outer side
  • the valve member 6, the inner compression coil spring 8, the inner valve member 10, and the lid 12 attached to the upstream end of the casing 2 are configured.
  • the lid 12 attached to the upstream end of the casing 2 is formed with an inlet 12a of the constant flow valve 1, and the outlet 2a of the constant flow valve 1 is formed at the downstream end of the casing 2.
  • a meat stealing portion 2b for preventing sink marks in the production of the casing 2 is formed.
  • FIG. 3 is a sectional view of II of the constant flow valve according to the first embodiment of the present invention shown in FIG. 2, and FIG. 4 is II of the constant flow valve according to the first embodiment of the present invention shown in FIG. It is II sectional drawing.
  • FIG. 3 the flow of water in the constant flow valve 1 is indicated by arrows.
  • the outer valve member 6 is slidably disposed in the casing 2 in the axial direction, and the inner valve member 10 is slid in the axial direction inside the outer valve member 6. Arranged as possible.
  • the outer valve member 6 receives the pressure of water flowing into the casing 2 from the inlet 12a by the pressure receiving portion 6a at the upstream end of the outer valve member 6 and the pressure receiving portion 10c at the upstream end of the inner valve member 10. However, it slides axially downstream in accordance with the water pressure received by the pressure receiving portion 6a.
  • valve body 6b which is the main part of the outer valve member 6, is formed in a shape that is relatively narrowed by directing the force from the upstream side to the downstream side.
  • an outer variable flow path 14 is formed as a first flow path between the outer peripheral portion of the valve body 6b and the outlet 2a of the casing 2, and the outer valve member 6 is By sliding in the axial direction, the valve body portion 6b variably adjusts the opening degree or the cross-sectional area of the outer variable flow path 14.
  • the flow path 14 is shown in a fully open state.
  • an outer compression coil spring 4 is disposed substantially coaxially with the outer valve member 6 between the inner peripheral portion 2c of the casing 2 and the outer peripheral portion 6c of the outer valve member 6.
  • the outer compression coil spring 4 has a linear spring characteristic in which the spring load and the spring contraction are proportional to each other.
  • downstream end portion of the valve body portion 6 b of the outer valve member 6 includes an arch portion 18 that extends so as to cross the outer valve member 6.
  • the outer valve member 6 moves downstream and moves outward from the outer valve member 6.
  • the step 6d formed on the outer periphery of the valve body 6b of the outer valve member 6 approaches the outlet 2a of the casing 2, and finally And the outer variable flow path 14 is completely closed.
  • a thin plate-like outer valve body leg portion 6f is formed at a position away from the arch portion 18 in the circumferential direction by 90 degrees.
  • the outer valve body leg 6f abuts on the inner periphery of the outlet 2 of the casing 2, thereby functioning as a guide for the movement of the outer valve member 6 and for rectifying the water ejected from the outer variable flow path 14. Also fulfills.
  • the valve body 10a which is the main part of the inner valve member 10, is formed in a shape that is relatively narrowed from the upstream side toward the downstream side.
  • an inner variable flow path 16 is formed as a second flow path between the inner peripheral portion 6e of the outer valve member 6 and the valve body portion 10a of the inner valve member 10, and the inner valve member 10 is the outer valve.
  • the valve body 10 a variably adjusts the opening degree or the cross-sectional area of the inner variable flow path 16.
  • An inner compression coil spring 8 is disposed substantially coaxially with the inner valve member 10 between the inner peripheral portion 6 e of the outer valve member 6 and the outer peripheral portion 10 b of the inner valve member 10.
  • the inner compression coil spring 8 has a smaller average diameter than the coil average diameter of the outer compression coil spring 4, and is arranged coaxially and nested with respect to the outer compression coil spring 4. Further, the inner compression coil spring 8 has a linear spring characteristic like the outer compression coil spring 4, but has a spring constant larger than the spring constant of the outer compression coil spring 4. That is, the constant flow valve 1 of the present embodiment is configured to be used in combination by arranging two linear compression coil springs 4 and 8 having different coil average diameters and spring constants in a coaxial and nested manner. ing.
  • the inner compression coil spring 8 has an inner valve member 10 between the inner peripheral portion 6e of the outer valve member 6 and the outer peripheral portion 10b of the inner valve member 10 when the inner valve member 10 is not operated. Is accommodated so as to urge the shaft in the axial direction.
  • the pressure receiving portion 10c at the upstream end of the inner valve member 10 is pressed in the downstream axial direction by the pressure of the water, and the inner valve
  • the downstream end 8b of the inner compression coil spring 8 is pressed against the outer valve member 6 in the downstream axial direction.
  • the inner valve member 10 moves downstream in response to an increase in water pressure received by the pressure receiving portion 10c of the inner valve member 10.
  • the stepped portion 10d formed on the outer peripheral portion 10b of the inner valve member 10 contacts the inner peripheral portion 6e of the outer valve member 6, and the inner variable flow path 16 Is closed to a predetermined opening degree or flow path cross-sectional area.
  • the dimensions and shape of the member 10 and the specifications of the outer compression coil spring 4 and the inner compression coil spring 8 are determined.
  • the outer compression coil spring 4 has a spring constant of 1.573 [N / mm], an average coil diameter of 20.7 mm, and a free height of 14 mm.
  • the inner compression coil spring 8 has a spring constant of 3.557 [NZmm], an average coil diameter of 11.4 mm, and a free height of 13.35 mm.
  • a support protrusion 22 is formed at the center of the arch portion 18 of the outer valve member 6 to support the inner valve member 10 so as to be slidable in the axial direction.
  • the inner valve member 10 is formed with a recess 20 that slidably receives the support protrusion 22 of the outer valve member 6.
  • the support protrusion 22 of the outer valve member 6 When the support protrusion 22 of the outer valve member 6 is received in the recess 20 of the inner valve member 10, the support protrusion 22 causes the inner valve member 10 to slide accurately in the axial direction with respect to the outer valve member 6. Therefore, it functions as a damper that prevents lateral vibration and prevents sudden movement of the inner valve member 10 due to water flow.
  • the arch portion 18 of the outer valve member 6 includes a wing portion 24 formed in a wing shape, and the wing portion 24 rectifies the downstream side of the outer valve member 6, so that the outer valve portion due to the turbulence of water flow. This prevents the material 6 from vibrating in the lateral direction.
  • FIG. 1 to FIG. 3 it is the central portion of the arch portion 18 of the outer valve member 6, and the downstream end portion of the support protrusion 22 of the outer valve member 6 is a jet dispersion portion 26.
  • the jet dispersion portion 26 is formed in a substantially truncated cone shape that expands from the upstream side toward the downstream side.
  • the jet dispersion part 26 is closed to the minimum opening or the cross-sectional area of the inner variable flow path 16 with the outer variable flow path 14 of the constant flow valve 1 kept closed.
  • a pair of inner valve body leg portions 10f are formed on the valve body portion 10a of the inner valve body portion 10 so as to come into contact with the inner peripheral portion 6e of the outer valve member 6, and this inner valve body leg portion 10f.
  • a hook portion 10g which is a projecting portion projecting in the radial direction, is formed at the tip on the downstream side.
  • This inner valve leg The part lOf abuts on the inner peripheral part 6e of the outer valve member 6, thereby functioning as a guide for the movement of the inner valve member 10, and also serves to rectify water ejected from the inner variable flow path 16.
  • the hook portion 10g is engaged with the outer valve member 6 on the downstream end side of the inner variable flow path 16, whereby the movement of the inner valve member 10 to the upstream side can be restricted, and the outer valve member 6 is retained. Therefore, the lid for holding the inner stool member 10 corresponding to the lid 12 for carrying out can be omitted.
  • FIG. 5 is a characteristic diagram qualitatively showing the relationship between the water pressure and the flow rate and the relationship between the water pressure and the total flow cross-sectional area in the constant flow valve 1 of the present embodiment.
  • the horizontal axis represents the difference in water pressure at the inlet 12a and the outlet 2a (differential pressure) P
  • the left vertical axis represents the flow rate Q
  • the right vertical axis represents the total flow at the outlet 2a of the constant flow valve 1.
  • the channel cross-sectional area S is shown
  • the flow rate diagram is shown by a solid line
  • the characteristic diagram of the total channel cross-sectional area is shown by a broken line.
  • each operating state of the constant flow valve in operation is represented by 0, A, B, C, and D in ascending order of the pressure of water flowing into the constant flow valve.
  • FIGS. 6 to 9 are sectional views showing the constant flow valves in the operating states A to D of FIG.
  • FIG. 10 is a cross-sectional view showing an operating state D along the III-II I cross section of FIG. 2 in the constant flow valve 1 according to the first embodiment of the present invention.
  • FIG. 11 is a cross-sectional view showing an operating state D according to the II-II cross section of FIG. 2 in the constant flow valve 1 according to the first embodiment of the present invention.
  • the constant flow valve 1 in the operating state O which is the initial state is the force that water is flowing into the casing 2 from the inlet 12a of the constant flow valve 1. There is almost no differential pressure P.
  • the outer valve member 6 and the inner valve member 10 are located on the most upstream side, and the outer variable channel 14 and the inner variable channel 16 are opened to the maximum!
  • the flow path cross-sectional area S is 140 mm 2 and the flow rate Q has almost no differential pressure P.
  • the outer valve member 6 and the inner valve member 10 of the constant flow valve 1 increase the differential pressure P of the inflowing water.
  • the operation state O the operation state A (see FIGS. 5 and 6), the operation state B (see FIGS. 5 and 7), the operation state C (see FIGS. 5 and 8), and the operation state D (FIG. 5). And see Fig. 9 to Fig. 11).
  • the water pressure applied to each of the pressure receiving part 6a of the outer valve member 6 and the pressure receiving part 10c of the inner valve member 10 is higher than that in the operating state O. Will also rise.
  • the outer compression coil spring 4 is pressed in the downstream axial direction by the pressure receiving portion 6a of the outer valve member 6 and the pressure receiving portion 10c at the upstream end of the inner valve member 10, and the inner compression coil spring 8 is moved to the inner valve.
  • the member 10 is pressed in the downstream axial direction by the pressure receiving part 10c.
  • the outer compression coil spring 4 has a small spring constant and the outer compression coil spring 4 contracts more in the axial direction than the inner compression coil spring 8
  • the outer valve member 6 is larger in the casing 2 than the inner valve member 10 in the downstream axial direction.
  • the outer variable flow path 14 and the inner variable flow path 16 are both open, and the flow rate Q increases as the water pressure increases.
  • the total cross-sectional area S is decreasing, although increasing toward zero.
  • the water pressure applied to each of the pressure receiving part 6a of the outer valve member 6 and the pressure receiving part 10c of the inner valve member 10 is in the operating state. It is in a state where it has risen further than A.
  • the outer compression coil spring 4 is further pressed in the downstream axial direction by the pressure receiving portion 6a of the outer valve member 6 and the pressure receiving portion 10c at the upstream end of the inner valve member 10, and the inner compression coil spring 8 is The pressure is further pressed in the downstream axial direction by the pressure receiving portion 10c of the inner valve member 10.
  • step portion 6d of the arch portion 18 of the outer valve member 6 contacts the outlet 2a of the casing 2, and the outer variable flow path 14 is completely closed, but the inner variable flow path 16 is opened in the operating state A. Slightly closed than the state.
  • the differential pressure P is 0.15 MPa
  • the channel cross-sectional area S is 30 mm 2.
  • the flow rate Q is 20LZmin.
  • the total channel cross-sectional area S decreases from the operating state A to B as the water pressure increases.
  • the constant flow valve 1 in the operating state C is received by the outer valve member 6.
  • the water pressure applied to each of the pressure portion 6a and the pressure receiving portion 10c of the inner valve member 10 is further increased from the operating state B.
  • the outer compression coil spring 4 is not further compressed, and the step portion 6d of the arch portion 18 of the outer valve member 6 is in contact with the outlet 2a of the casing 2 so that the outer variable flow path 14 is completely closed.
  • the inner compression coil spring 8 is further pressed in the downstream axial direction by the pressure receiving portion 10c of the inner valve member 10. At this time, the inner variable flow path 16 is further closed than in the opened state of the operating state B.
  • the flow rate Q increases slightly as the water pressure increases and temporarily reaches the maximum, but after that, in the operating state C, the flow rate is minimum. It tends to decrease toward the target flow rate value Q.
  • the operating state B force also decreases as the water pressure increases toward C.
  • the constant flow valve 1 in the operating state D has a hydraulic pressure applied to each of the pressure receiving portion 6a of the outer valve member 6 and the pressure receiving portion 10c of the inner valve member 10. It is in a state where it is further raised than the operating state C. In this state, both the outer compression coil spring 4 and the inner compression coil spring 8 are not further compressed, and the step 6d of the arch portion 18 of the outer valve member 6 is in contact with the outlet 2a of the casing 2 and can be changed outside. The flow path 14 remains closed.
  • the inner variable flow path 16 without sliding the inner valve member 10 further in the downstream axial direction is slightly closed from the open state of the operating state C and closed to the minimum opening or the cross-sectional area of the flow path. It will be in the state. That is, the outer valve member 6 and the inner valve member 10 are located on the most downstream side with respect to the casing 2, the outer variable flow channel 14 remains closed, and only the inner variable flow channel 16 is minimized. It is opened and the water flow is maintained (see Fig. 11).
  • the differential pressure P is 1.0 MPa
  • the channel cross-sectional area S is 10 mm 2 .
  • the flow rate Q is 20LZmin.
  • the outer valve member 6, the inner valve member 10, and the outer compression coil spring 4 corresponding to the differential pressure of the water flowing in from the inlet 12a.
  • the lower limit target flow rate value Q is the upper limit target flow rate value Q.
  • the outer valve member 6 is slidably disposed in the casing 2 forming the constant flow valve main body in the axial direction.
  • the inner valve member 10 is slidably disposed in the axial direction.
  • the outer compression coil spring 4 is disposed between the inner peripheral portion 2c of the casing 2 and the outer peripheral portion 6c of the outer valve member 6 so as to be substantially coaxial with the outer valve member 6.
  • the inner valve member 10 is disposed substantially coaxially with the inner valve member 10 between the inner peripheral member 6e 6 and the outer peripheral member 10b of the inner valve member 10. Therefore, since these multiple members 4, 6, 8, and 10 are concentrated in a limited space in the casing 2 by using each other's space, the entire constant flow valve 1 is made compact. It is possible to become
  • two linear coil springs 4 and 8 having different coil average diameters and spring constants are arranged substantially coaxially and nested, and used in combination. Therefore, a constant flow valve with a small and simple structure can be realized.
  • the outer valve member 6 includes the arch portion 18 that supports the inner valve member 10 so as to be slidable in the axial direction. Since the protrusion 22 is inserted into the recess 20 of the inner valve member 10, the inner valve member 10 can accurately slide in the axial direction with respect to the outer valve member 6. In addition, when the inner valve member 10 slides in the axial direction, it is possible to prevent lateral vibration and to prevent the inner valve member 10 from rapidly moving due to water flow.
  • the wing portion 24 rectifies the downstream side of the outer valve member 6.
  • the lateral vibration of the outer valve member 6 due to the turbulence of the water flow can be reduced.
  • the downstream end of the support protrusion 22 of the outer valve member 6 is provided with the jet dispersion part 26 formed in a truncated cone shape.
  • the inner variable flow path 16 is closed to the minimum opening or flow cross-sectional area, i.e., the inner variable flow path. 1
  • the flow passage cross-sectional area of 6 is the smallest, the water flow state is maintained, and the jet flow from the inner variable flow passage 16 can be dispersed along the outer surface of the dispersion member 26 using the Coanda effect. Therefore, the occurrence of cavitation due to the jet can be reduced.
  • FIG. 12 is a cross-sectional view similar to FIG. 8, showing a constant flow valve according to a second embodiment of the present invention.
  • the same parts as those in the constant flow valve 1 of the first embodiment shown in FIG. 8 are denoted by the same reference numerals, and the description thereof is omitted.
  • the constant flow valve 30 according to the second embodiment of the present invention has different structures at both ends 8a, 8b of the inner compression coil spring 8 of the constant flow valve 1 according to the first embodiment described above. It was made.
  • One of the upstream end 8a and the downstream end 8b of the inner compression coil spring 8 of the constant flow valve 30 according to the present embodiment corresponds to the seating portion of the winding start portion of the coil spring element wire 32.
  • the other side corresponds to the saddle part which is the end of winding.
  • the inner compression coil spring 8 has a so-called closed-end type saddle shape in which the spring element wires 32 of the coil of the seat portion are in contact with each other.
  • the inner compression coil spring 8 when the inner compression coil spring 8 is expanded or contracted, in order to prevent noise caused by the strong contact between the spring elements 32 of the adjacent coil of the seat flange portion of the inner compression coil spring 8, The coil spring element wire 32 of the buttocks is covered with a rubber tube 34 as noise prevention means.
  • a groove 36 that holds the downstream end portion 8 b of the inner compression coil spring 8 is formed in a contact portion where the downstream end portion 8 b of the inner compression coil spring 8 contacts.
  • a flat ring 38 made of vibration-proof rubber, which is an elastic member, is disposed between this groove 36 and the downstream end 8b of the inner compression coil spring 8.
  • a load is repeatedly applied to the inner compression coil spring 8 in a state where the inner compression coil spring 8 is compressed due to a high feed water pressure of water flowing in from the inlet 12a.
  • the inner compression coil spring 8 vibrates vigorously as the frequency of the inner compression coil spring 8 approaches the natural frequency. Since the flat ring 38 is disposed between the downstream end 8b of the inner valve 8 and the groove 36 of the outer valve member 6, the downstream end 8b of the inner compression coil spring 8 and the groove 36 of the outer valve member 6 are It is possible to suppress the collision sound caused by the collision.
  • the constant flow valve 30 of the present embodiment described above has a configuration in which the coil spring element wire 32 of the collar portion which is the both end portions 8a and 8b of the inner compression coil spring 8 is covered with the rubber tube 34.
  • 1S described above is not limited to such a configuration, and even if it is connected to the coiled wire of both ends 4a and 4b of the outer compression coil spring 4, it may be configured to be covered with a rubber tube. .
  • the force described for the configuration in which the flat ring 38 is disposed between the downstream end 8b of the inner compression coil spring 8 and the groove 36 of the outer valve member 6 is as described above.
  • the form is not limited, and the upstream end 8a of the inner compression coil spring 8 and both ends 4a, 4b of the outer compression coil spring 4 may be arranged in a flat ring.
  • the inner compression coil spring 8 having the closed end type of the countersunk shape is used, and although the embodiment has been described in which the coil spring element wire 32 is covered with the rubber tube 34 to prevent the contact sound between the coil elements 32 adjacent to each other in the washer portion, the present invention is limited to such an embodiment. However, other forms are also applicable.
  • FIG. 13 is a perspective view showing an inner compression coil spring used in the constant flow valve according to the first modification of the second embodiment of the present invention.
  • an inner compression coil spring 40 having a so-called open-end type saddle shape in which the spring wires are not in contact with each other may be used.
  • the spring wires of the adjacent coils 42a and 42b of the spring seat 42 or the springs 44a and 44b of the spring seat 44 Eliminate unpleasant contact noise between the coil spring wires because the wires do not touch at all be able to.
  • FIG. 14 is a perspective view showing an inner compression coil spring used in the constant flow valve according to the second modification of the second embodiment of the present invention.
  • an inner compression coil spring 45 having an open-end type saddle shape is used, similar to the inner compression coil spring 40 shown in FIG. And then.
  • a spring wire connecting elastic member 47 is attached so as to connect the portions 46a and 46b.
  • the spring element connecting elastic member 47 is formed of hard rubber or the like, and is formed in a curved shape in an arc shape inside thereof and matches the diameter of the inner diameter force coil spring element 46 to be a coil spring. Two elongated holes 47a and 47b that allow the strand 46 to pass therethrough are provided.
  • the spring wire connecting elastic member 47 may be formed of an elastic adhesive portion obtained by bonding and solidifying the portions 46 a and 46 b of the coil spring wire 46 using an elastic adhesive. .
  • the inner compression coil spring 45 shown in FIG. 14 shows a form in which the spring element wire connecting elastic member 47 is attached to both ends thereof, but the inner compression coil spring 45 is not limited to such a form.
  • the spring element wire connecting elastic member 47 is attached to at least one end portion (seat portion) of the.
  • the start end portion of the coil spring wire 46 at both ends (the flange portions) of the inner compression coil spring 45 ( (Or end portion) 46a and the adjacent portion 46b corresponding to the first turn from that portion are attached to the spring wire connecting elastic member 47, so that when the inner coil spring 45 vibrates, the starting end portion of the coil spring wire 46 (or Since it is possible to completely prevent direct contact between the terminal portion 46a and the adjacent portion 46b, noise generated by these contacts can be prevented.
  • the natural frequency of the inner compression coil spring 45 can be changed by the spring element connecting elastic member 47. Therefore, even when the inner compression coil spring 45 is used such that surging occurs at a hydraulic pressure within the practical water pressure range (0.5 MPa to 0.8 MPa) when the spring wire connecting elastic member 47 is not attached.
  • the spring element connecting elastic member 47 is If surging is supposed to occur due to the installation, the water pressure can be set outside the practical water pressure range (0.5 MPa to 0.8 MPa) to avoid surges in the practical water pressure range. Can do.
  • the spring wire connecting elastic member 47 is adjacent to the start end portion (or the end portion) 46a of the spring wire connecting elastic member 47 by an elastic portion or the like which is solidified by bonding with hard rubber or an elastic adhesive.
  • 46b is integrally formed and produces the same effect as that with dampers attached to both ends (cushion collars) of the inner compression coil spring 45. Therefore, even if surging occurs, The vibration can be absorbed and suppressed.
  • the start end portion (or end portion) of the coil spring element wire 46 at the end portion (cushion portion) of the inner compression coil spring 45 is provided.
  • 46a and the adjacent portion 46b corresponding to the first turn from that portion have been described in the form in which the spring element connecting elastic member 47 is attached.
  • the present invention is not limited to such a form, and both ends of the outer compression coil spring 4 are provided.
  • the spring element connecting elastic member 47 may be attached to the starting end part (or the terminal end part) of the coil spring element wire and the adjacent part thereof.
  • FIG. 15 is a sectional view similar to FIG. 8, showing a constant flow valve according to a third embodiment of the present invention.
  • the same parts as those of the constant flow valve 1 of the first embodiment shown in FIG. 8 are denoted by the same reference numerals, and description thereof is omitted.
  • the constant flow valve 50 includes a recess 20 of the inner valve member 10 of the constant flow valve 1 of the first embodiment described above and an outer side inserted into the recess 20.
  • the structure differs from that of the first embodiment in that oil 52, which is a viscous material, is sealed in a space between the upstream end of the support protrusion 22 of the valve member 6.
  • the upstream side of the support protrusion 22 of the outer valve member 6 is composed of a small diameter portion 53 and a piston portion 54, and a plurality of slit grooves 54 a are formed on the peripheral surface of the piston portion 54.
  • An O-ring 56 is provided in the middle, and even if the support protrusion 22 of the outer valve member 6 slides violently in the axial direction within the recess 20 of the inner valve member 10, the oil 52 in the recess 20 leaks to the outside. It is not so.
  • FIG. 16 is a perspective view showing a constant flow valve according to a fourth embodiment of the present invention
  • FIG. 17 is a cross-sectional view of the constant flow valve according to the fourth embodiment of the present invention shown in FIG.
  • FIG. 18 is a V-V sectional view of the constant flow valve according to the fourth embodiment of the present invention shown in FIG.
  • FIGS. 16 to 18 the same parts as those of the constant flow valve 1 of the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
  • the flow of water in the constant flow valve is indicated by arrows.
  • the constant flow valve 60 has an inlet 62a and an outlet 62b formed in the same manner as the components of the constant flow valve 1 of the first embodiment.
  • the casing 62 is a constant flow valve body, the outer compression coil spring 4 accommodated in the casing 62, the outer valve member 66, the inner compression coil spring 8, and the inner valve member 70.
  • the configurations of the outer variable channel 74 and the inner variable channel 74 included in the configuration are different from the configurations of the outer variable channel 14 and the inner variable channel 16 of the first embodiment.
  • the arrangement of the outer compression coil spring 4, the outer valve member 66, the inner compression coil spring 8, and the inner valve member 70 in the casing 62 of the constant flow valve 60 is the same as that in the casing 2 of the constant flow valve 1 of the first embodiment.
  • the outer valve member 66 is slidably arranged in the casing 62 in the axial direction, and the inner valve member 70 is slidable in the inner side of the outer valve member 66 in the same manner as the arrangement of each component in FIG. Is arranged.
  • the outer compression coil spring 4 is disposed substantially coaxially with the outer valve member 66 between the inner peripheral portion 62c of the casing 62 and the outer peripheral portion 66a of the outer valve member 66.
  • the inner compression coil spring 8 is disposed substantially coaxially with the inner valve member 70 between the peripheral portion 66b and the outer peripheral portion 70b of the inner valve member 70.
  • An outer variable flow path 74 is formed as a first flow path between the outer peripheral portion 66a of the outer valve member 66 and the outlet 62b, as in the outer variable flow path 14 of the constant flow valve 1 of the first embodiment. ing.
  • the outer variable flow path 74 is configured such that the opening degree or the flow path cross-sectional area is variable when the outer valve member 66 slides in the axial direction with respect to the casing 62.
  • the outer valve member 66 is slid to the most downstream position with respect to the casing 62. In other words, the outer valve member 66 is closed to the minimum opening or the cross-sectional area of the flow path, that is, the water passage state is maintained even if the flow cross-sectional area of the outer variable flow path 74 is the smallest. (See Figure 17 and Figure 18).
  • the second An inner variable flow path 76 is formed as a flow path.
  • the inner variable flow path 76 is configured such that the opening degree or the flow path cross-sectional area is variable by sliding the inner valve member 70 in the axial direction with respect to the outer valve member 66.
  • the flow rate of water flowing in from the front opening 79 formed upstream is adjustable.
  • the inner valve member 70 is slid to the most downstream position with respect to the casing 62 or the outer valve member 66.
  • the variable flow path 76 is in a state where the downstream inner peripheral portion 66c of the outer valve member 66 and the outer peripheral protrusion 70b of the inner valve member 70 are in contact with each other and are completely closed.
  • the outer valve member 66 and the inner valve member 70 increase as the pressure of the water flowing into the casing 62 from the inlet 62a increases.
  • the outer variable flow path 74 has a minimum opening degree.
  • the outer variable flow path 74 can effectively disperse the jet flowing out downstream of the constant flow valve 60.
  • the jet flow from the outlet 62b can be dispersed over a wide range. Can be prevented.
  • FIG. 19 is a perspective view showing a constant flow valve according to a fifth embodiment of the present invention
  • FIG. 20 is a sectional view taken along line VI-VI of the constant flow valve according to the fifth embodiment of the present invention shown in FIG. FIG.
  • the same parts as those of the constant flow valve 1 of the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.
  • the flow of water in the constant flow valve is indicated by arrows.
  • the constant flow valve 80 is formed with an inlet 82a and an outlet 82b, similar to the components of the constant flow valve 1 of the first embodiment.
  • the casing 82 is a constant flow valve main body, the outer compression coil spring 4, the outer valve member 86, the inner compression coil spring 8, and the inner valve member 90 accommodated in the casing 82.
  • the downstream end 90c of the axial center of the inner valve member 90 of the constant flow valve 80 has a nozzle shape that tapers toward the upstream side and downstream side, and the axial center of this nozzle shape is the center.
  • the configuration differs from that of the first embodiment in that a plurality of constant channels 92, which are third channels, are formed.
  • the arrangement of the outer compression coil spring 4, the outer valve member 86, the inner compression coil spring 8, and the inner valve member 90 in the casing 82 of the constant flow valve 80 is the same as that in the casing 2 of the constant flow valve 1 of the first embodiment.
  • the outer valve member 86 is slidably arranged in the casing 82 in the axial direction, and the inner valve member 90 is slidable in the axial direction on the inner side of the outer valve member 86. Is arranged.
  • outer compression coil spring 4 is disposed substantially coaxially with the outer valve member 86 between the inner peripheral portion 82c of the casing 82 and the outer peripheral portion 86a of the outer valve member 86.
  • the inner compression coil spring 8 is disposed substantially coaxially with the inner valve member 90 between the inner peripheral portion 86b and the outer peripheral portion 90b of the inner valve member 90.
  • the outer valve member 86 and the inner valve are arranged in the same manner as the operation state D of the constant flow valve 1 of the first embodiment shown in Figs.
  • the member 90 is slid to the most downstream position with respect to the casing 82.
  • the outer variable flow path 84 is used as the first flow path, similarly to the outer variable flow path 14 of the constant flow valve 1 of the first embodiment. Is formed.
  • the outer variable flow path 84 is configured such that the opening degree or the flow path cross-sectional area is variable when the outer valve member 86 slides in the axial direction with respect to the casing 82.
  • the outer valve member 86 is slid to the most downstream position with respect to the casing 82.
  • the outer peripheral portion 86a of the outer valve member 86 and the outflow port 82b are in contact with each other and are completely closed.
  • the second An inner variable flow path 88 is formed as a flow path.
  • the inner variable flow path 88 is configured such that the opening degree or the flow path cross-sectional area is variable when the inner valve member 90 slides in the axial direction with respect to the outer valve member 86.
  • the inner valve member 90 is slid to the most downstream position with respect to the casing 82 or the outer valve member 86.
  • the inner variable flow path 88 is in a state of being completely closed by the contact between the downstream inner peripheral portion 86c of the outer valve member 86 and the outer peripheral protrusion 90b of the inner valve member 90.
  • the constant flow path 92 is configured so that each of the outer valve member 86 and the inner valve member 90 slides to the position on the most downstream side with respect to the casing 82. Even when 84 and the inner variable flow path 88 are completely closed, they are always opened with a constant flow passage area. Further, in the constant flow valve 80 of the present embodiment, the jet flow that has passed through the constant flow path 92 is dispersed, so that the generation of cavitation due to the jet flow is reduced. In the constant flow valve 80 according to the fifth embodiment of the present invention described above, the outer valve member 86 and the inner valve member 90 in which the water pressure in the casing 82 is high are the outer variable flow channel 84 and the inner variable flow channel, respectively.
  • either the outer variable flow path or the inner variable flow path is the maximum even when the water pressure in the casing becomes a high pressure region higher than a predetermined value.
  • the constant flow valve 80 of the present embodiment is configured to be opened with a small opening degree or a cross-sectional area of the flow path, but the constant flow valve 80 of the present embodiment is a constant flow formed at the axial center downstream end 90c of the inner valve member 90. Since the path 92 is always a simple structure with a constant channel cross-sectional area, the flow rate can be more accurately compared to the constant flow valves of the first to fourth embodiments, especially at high pressures. Can be managed.
  • the outlet formed at the downstream end of the inner valve member 90 has a protruding shape.
  • These force disturbing elements may be provided, or notches may be provided at intervals along the periphery of the outlet.
  • the outlet formed at the downstream end of the inner valve member 90 may be a non-circular shape such as a flat shape.
  • FIG. 1 is an exploded perspective view showing a constant flow valve according to a first embodiment of the present invention.
  • FIG. 2 is a perspective view showing the constant flow valve according to the first embodiment of the present invention.
  • FIG. 3 is a cross-sectional view taken along line II of the constant flow valve according to the first embodiment of the present invention shown in FIG.
  • FIG. 4 is a II-II cross-sectional view of the constant flow valve according to the first embodiment of the present invention shown in FIG.
  • FIG. 5 shows the relationship between the water pressure and the flow rate in the constant flow valve according to the first embodiment of the present invention
  • the water pressure FIG. 5 is a characteristic diagram qualitatively showing the relationship with the entire channel cross-sectional area.
  • FIG. 6 is a sectional view showing an operating state A of the constant flow valve according to the first embodiment of the present invention.
  • FIG. 7 is a sectional view showing an operating state B of the constant flow valve according to the first embodiment of the present invention.
  • FIG. 8 is a sectional view showing an operating state C of the constant flow valve according to the first embodiment of the present invention.
  • FIG. 9 is a sectional view showing an operating state D of the constant flow valve according to the first embodiment of the present invention.
  • FIG. 10 is a cross-sectional view showing an operation state D along the III-III cross section of FIG. 2 in the constant flow valve according to the first embodiment of the present invention.
  • FIG. 11 is a cross-sectional view showing an operating state D by the II-II cross section of FIG. 2 in the constant flow valve according to the first embodiment of the present invention.
  • FIG. 12 is a sectional view similar to FIG. 8, showing a constant flow valve according to a second embodiment of the present invention.
  • FIG. 13 is a perspective view showing an inner compression coil spring used in the constant flow valve according to the first modification of the second embodiment of the present invention.
  • FIG. 14 A perspective view showing an inner compression coil spring used in a constant flow valve according to a second modification of the second embodiment of the present invention.
  • FIG. 15 is a sectional view similar to FIG. 8, showing a constant flow valve according to a third embodiment of the present invention.
  • FIG. 16 is a perspective view showing a constant flow valve according to a fourth embodiment of the present invention.
  • FIG. 17 is a sectional view taken along line IV-IV of the constant flow valve according to the fourth embodiment of the present invention shown in FIG.
  • FIG. 18 is a cross-sectional view taken along the line V-V of the constant flow valve according to the fourth embodiment of the present invention shown in FIG. [19]
  • FIG. 19 is a perspective view showing a constant flow valve according to a fifth embodiment of the present invention.
  • FIG. 20 is a cross-sectional view of the constant flow valve VI-VI according to the fifth embodiment of the present invention shown in FIG. Explanation of symbols

Landscapes

  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Safety Valves (AREA)

Abstract

L'invention concerne une vanne à débit constant de petite taille et de structure simple. La vanne concernée règle le volume d'eau qu'elle doit décharger à un débit constant indépendamment des variations de pression d'alimentation. Une vanne à débit constant (1) se compose d'un logement (2) comportant une ouverture d'admission (12a) et une ouverture de sortie (2a), un élément de vanne extérieur (6) réalisé pour être coulissant à l'intérieur du logement et adaptant une section d'écoulement d'une voie de passage variable extérieure (14) formée entre une partie corps de vanne (6b) et une partie périphérique intérieure (2c) du logement, d'un élément de vanne intérieur (10) réalisé pour être coulissant à l'intérieur de l'élément de vanne extérieur et adaptant une section d'écoulement d'une voie de passage variable intérieure (16) formée entre une partie périphérique extérieure (10b) et une partie périphérique intérieure (6c) de l'élément de vanne extérieur, d'un ressort à enroulement extérieur (4) placé entre le logement et l'élément de vanne extérieur et faisant glisser l'élément de vanne extérieur sous l'effet de la pression de l'eau sur ce dernier, pour réduire la section d'écoulement de la voie de passage variable extérieure, d'un ressort à enroulement intérieur (8) placé entre l'élément de vanne extérieur et l'élément de vanne intérieur et faisant glisser l'élément de vanne intérieur, sous l'effet de la pression de l'eau sur ce dernier, pour réduire la section d'écoulement de la voie de passage variable intérieure.
PCT/JP2006/305088 2005-03-18 2006-03-15 Vanne a debit constant Ceased WO2006100973A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2007509213A JP4775769B2 (ja) 2005-03-18 2006-03-15 定流量弁

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005-079813 2005-03-18
JP2005079813 2005-03-18

Publications (1)

Publication Number Publication Date
WO2006100973A1 true WO2006100973A1 (fr) 2006-09-28

Family

ID=37023637

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2006/305088 Ceased WO2006100973A1 (fr) 2005-03-18 2006-03-15 Vanne a debit constant

Country Status (2)

Country Link
JP (1) JP4775769B2 (fr)
WO (1) WO2006100973A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008103365A1 (fr) * 2007-02-21 2008-08-28 Victaulic Company Soupape à débit constant
CN103383015A (zh) * 2012-05-03 2013-11-06 李耀强 气液两用恒流器
CN103527829A (zh) * 2013-10-18 2014-01-22 项大利 一种流体稳压阀
CN105135017A (zh) * 2012-05-03 2015-12-09 晋江市东亨工业设计有限公司 一种节流设备
WO2020210651A1 (fr) 2019-04-10 2020-10-15 PAVmed Inc. Systèmes et procédés pour une résistance à l'écoulement variable
CN112253828A (zh) * 2020-09-29 2021-01-22 宁波方太厨具有限公司 一种水流量稳流阀及应用该阀的燃气热水器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4838975Y1 (fr) * 1970-02-07 1973-11-17
JPS5786668A (en) * 1980-11-15 1982-05-29 Toupure Kk Airflow equalizing unit in air conditioning
JPS6140569U (ja) * 1984-08-16 1986-03-14 パロマ工業株式会社 多段式定流量弁
JPS63303281A (ja) * 1987-06-03 1988-12-09 Paloma Ind Ltd 水温補正付き定流量弁
JPH0336567U (fr) * 1989-08-22 1991-04-09

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4838975Y1 (fr) * 1970-02-07 1973-11-17
JPS5786668A (en) * 1980-11-15 1982-05-29 Toupure Kk Airflow equalizing unit in air conditioning
JPS6140569U (ja) * 1984-08-16 1986-03-14 パロマ工業株式会社 多段式定流量弁
JPS63303281A (ja) * 1987-06-03 1988-12-09 Paloma Ind Ltd 水温補正付き定流量弁
JPH0336567U (fr) * 1989-08-22 1991-04-09

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7647942B2 (en) 2007-02-21 2010-01-19 Victaulic Company Constant flow rate valve
WO2008103365A1 (fr) * 2007-02-21 2008-08-28 Victaulic Company Soupape à débit constant
CN105202238A (zh) * 2012-05-03 2015-12-30 晋江市东亨工业设计有限公司 一种恒流器
CN103383015A (zh) * 2012-05-03 2013-11-06 李耀强 气液两用恒流器
CN105135017A (zh) * 2012-05-03 2015-12-09 晋江市东亨工业设计有限公司 一种节流设备
CN103383015B (zh) * 2012-05-03 2016-02-10 李耀强 气液两用恒流器
CN103527829A (zh) * 2013-10-18 2014-01-22 项大利 一种流体稳压阀
CN103527829B (zh) * 2013-10-18 2015-12-23 项大利 一种流体稳压阀
WO2020210651A1 (fr) 2019-04-10 2020-10-15 PAVmed Inc. Systèmes et procédés pour une résistance à l'écoulement variable
CN113811709A (zh) * 2019-04-10 2021-12-17 帕夫梅德有限公司 用于可变流阻滞器的系统和方法
EP3953625A4 (fr) * 2019-04-10 2023-04-26 PAVmed Inc. Systèmes et procédés pour une résistance à l'écoulement variable
CN112253828A (zh) * 2020-09-29 2021-01-22 宁波方太厨具有限公司 一种水流量稳流阀及应用该阀的燃气热水器
CN112253828B (zh) * 2020-09-29 2021-07-23 宁波方太厨具有限公司 一种水流量稳流阀及应用该阀的燃气热水器

Also Published As

Publication number Publication date
JPWO2006100973A1 (ja) 2008-09-04
JP4775769B2 (ja) 2011-09-21

Similar Documents

Publication Publication Date Title
JP6378618B2 (ja) 減衰バルブ及び緩衝器
CN105008780B (zh) 电磁阀
CN102102729B (zh) 缓冲器
JP6239921B2 (ja) 液圧緩衝器
JP5528447B2 (ja) ヘルムホルツ共鳴器の調節のための方法及び該方法の実施のためのヘルムホルツ共鳴器
JP6093587B2 (ja) ソレノイドバルブ
US20160369905A1 (en) Control valve
JP2010511814A (ja) 流量調整装器
KR20140122249A (ko) 포핏 밸브
US20160153583A1 (en) Control valve
WO2018036755A1 (fr) Commutateur haute pression réglable en pression et purificateur d'eau utilisant le commutateur haute pression
CN104487749A (zh) 常闭型电磁阀
JP4775769B2 (ja) 定流量弁
CN109424772A (zh) 减压阀
CN102639843B (zh) 可变性能阀
JP2008509365A (ja) 逆止弁
JP2010060000A (ja) 定流量弁
JP2014156886A (ja) ソレノイドバルブ
JP6018517B2 (ja) ソレノイドバルブ
KR102641641B1 (ko) 체크 밸브
CN103857949A (zh) 流量控制阀
EP2821683B1 (fr) Soupape de régulation de pression
JP6059549B2 (ja) ソレノイドバルブ
JP6997655B2 (ja) バルブ装置、及び緩衝器
CN111561594B (zh) 动态流量平衡阀

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 2007509213

Country of ref document: JP

NENP Non-entry into the national phase

Ref country code: DE

NENP Non-entry into the national phase

Ref country code: RU

122 Ep: pct application non-entry in european phase

Ref document number: 06729109

Country of ref document: EP

Kind code of ref document: A1