WO2006100973A1 - Constant flow rate valve - Google Patents

Constant flow rate valve Download PDF

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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
Application number
PCT/JP2006/305088
Other languages
French (fr)
Japanese (ja)
Inventor
Eiji Fukuzawa
Yukinori Kubozono
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/en
Publication of WO2006100973A1 publication Critical patent/WO2006100973A1/en

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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

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Abstract

A constant flow rate valve having a small size and a simple structure. The valve regulates, independent of variation in pressure of water supplied, the flow rate of the water to be discharged from the valve to a predetermined rate. A constant flow rate valve (1) has a casing (2) having formed in it an inflow opening (12a) and an outflow opening (2a); an outer valve member (6) slidably provided inside the casing and varying a cross-sectional area of an outer variable flow path (14) formed between a valve body section (6b) and an inner peripheral section (2c) of the casing; an inner valve member (10) slidably provided inside the outer valve member and varying a cross sectional-area of an inner variable flow path (16) formed between an outer peripheral section (10b) and an inner peripheral section (6e) of the outer valve member; an outer coil spring (4) provided between the casing and the outer valve member and causing, when water pressure acts on the outer valve member, the outer valve member to slide to reduce the cross-sectional area of the outer variable flow path; and an inner coil spring (8) provided between the outer valve member and the inner valve member and causing, when water pressure acts on the inner valve member, the inner valve member to slide to reduce the cross-sectional area of the inner variable flow path.

Description

明 細 書  Specification
定流量弁  Constant flow valve
技術分野  Technical field
[0001] 本発明は、定流量弁に係わり、特に、供給される水の圧力の変動によらず流出させ る水の流量を所定量に調整する定流量弁に関する。  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.
背景技術  Background art
[0002] 従来から、水道直圧方式の大便器における洗浄水の供給経路等には、給水源から の給水圧の変動によらず洗浄水の流量を所定量に調整する定流量弁が用いられて いる。  Conventionally, a constant flow valve that adjusts the flow rate of cleaning water to a predetermined amount regardless of fluctuations in the supply water pressure from a water supply source has been used in the supply route of cleaning water in a direct water pressure toilet. ing.
このような従来の定流量弁としては、例えば、特許文献 1に記載されているように、 円筒状に延びる定流量弁本体内に固定された固定弁体に対し、複数の可動弁体が 直列に配置され、各可動弁体の開閉については、各可動弁体に取り付けられたばね 定数が異なるコイルばねの弾性力によって調整されるようになって!/、るものが知られ ている。  As such 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. As for the opening and closing of each movable valve body, the spring constant attached to each movable valve body is adjusted by the elastic force of different coil springs.
し力しながら、特許文献 1に記載されている従来の定流量弁においては、複数の可 動弁体が定流量弁本体内の長手方向に沿って直列に配置されているため、作動ス ペースを要し、狭く限られたスペースで使用することが難しぐ定流量弁の小型化を 妨げる要因となっている。したがって、定流量弁の小型化が従来力も課題となってい る。  However, in the conventional constant flow valve described in Patent Document 1, since a plurality of movable valve bodies are arranged in series along the longitudinal direction in the constant flow valve body, the working space is This is a factor that hinders the downsizing of constant flow valves that are difficult to use in narrow and limited spaces. Therefore, downsizing of the constant flow valve has been an issue with conventional power.
また、特許文献 2に記載されているように、円すいコイルばねを用い、このばねの非 線形ばね特性を利用した定流量弁も知られて 、るが、この定流量弁に用いられて ヽ る円すいコイルばねは、製造上、高い寸法精度と形状精度が要求されるため、歩留り が悪ぐ製造コストが高くなつてしまう。したがって、低コストで簡易な構造を有する定 流量弁が従来から要請されて 、る。  Further, as described in Patent Document 2, a constant flow valve using a conical coil spring and utilizing the non-linear spring characteristic of this spring is also known, but it can be used for this constant flow valve. Conical coil springs require high dimensional accuracy and shape accuracy in production, resulting in poor yield and high manufacturing cost. Therefore, there has been a demand for a constant flow valve having a simple structure at a low cost.
[0003] 特許文献 1 :実開昭 61— 40569号公報 [0003] Patent Document 1: Japanese Utility Model Publication No. 61-40569
特許文献 2 :特開平 6— 331051号公報  Patent Document 2: JP-A-6-31051
発明の開示 発明が解決しょうとする課題 Disclosure of the invention Problems to be solved by the invention
[0004] そこで、本発明は、上述した従来技術の課題を解決するためになされたものであり 、供給される水の圧力の変動によらず流出させる水の流量を所定量に調整する小型 でかつ簡易な構造を備えた定流量弁を提供することを目的として!ヽる。  [0004] Therefore, 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.
課題を解決するための手段  Means for solving the problem
[0005] 上記の目的を達成するために、本発明は、供給される水の圧力の変動によらず流 出させる水の流量を所定量に調整する定流量弁であって、流入口と流出口が形成さ れた定流量弁本体と、この流量弁本体の内側に上記定流量弁本体に対して摺動可 能に配置され、この摺動により、外周部と上記定流量弁本体の内周部との間に形成 される第 1流路の断面積を変化させる外側弁部材と、上記外側弁部材の内側に上記 外側弁部材に対して摺動可能に配置され、この摺動により、外周部と上記外側弁部 材の内周部との間に形成される第 2流路の断面積を変化させる内側弁部材と、上記 定流量弁本体と上記外側弁部材との間に配置され、上記外側弁部材を軸方向に付 勢し、上記外側弁部材に水圧が作用すると上記外側弁部材を摺動させ、上記第 1流 路の断面積を減少させるように縮む外側コイルばねと、上記外側弁部材と上記内側 弁部材との間に配置され、上記内側弁部材を軸方向に付勢し、上記内側弁部材に 水圧が作用すると上記内側弁部材を摺動させ、上記第 2流路の断面積を減少させる ように縮むコイルばねと、を有することを特徴として 、る。  In order to achieve the above object, 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. A constant flow valve body with an outlet formed therein and slidably disposed inside the flow valve body with respect to the constant flow valve body. 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. And 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.
このように構成された本発明の定流量弁にお！ヽては、外側弁部材が定流量弁本体 の内側に上記定流量弁本体に対して摺動可能に配置され、この摺動により、外周部 と上記定流量弁本体の内周部との間に形成される第 1流路の断面積が変化し、上記 外側弁部材の内側に上記外側弁部材に対して摺動可能に配置され、この摺動により 、外周部と上記外側弁部材の内周部との間に形成される第 2流路の断面積が変化し 、外側コイルばねが定流量弁本体と外側弁部材との間に配置され、内側コイルばね が外側弁部材と内側弁部材との間に配置されているため、供給される水の圧力の変 動によらず流出させる水の流量を所定量に調整する小型でかつ簡易な構造を備え た定流量弁を実現することができる。  In the constant flow valve of the present invention configured as described above! On the other hand, 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.
[0006] 本発明において、内側コイルばねのばね定数は、外側コイルばねのばね定数よりも 大きいことが好ましい。これにより、流路面積を大きくできる第 1流路を低水圧時に大 流量を流すことのできる流路とて使用できるように、上記外側弁部材及び上記内側弁 部材を軸方向に付勢して摺動させることができる。 In the present invention, 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.
[0007] 本発明にお 、て、外側弁部材は、外側弁部材を横断するように延びるアーチ部と、 このアーチ部に形成され内側弁部材を軸方向に摺動可能に支持する支持突起と、 を備え、内側弁部材には、支持突起を摺動可能に受け入れる凹部が形成されている ことが好ましい。これにより、内側弁部材が外側弁部材に対して正確に軸方向に摺動 することができる。  [0007] In the present invention, 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.
[0008] 本発明において、アーチ部は、上記外側弁部材の下流側を整流するように翼状に 形成されていることが好ましい。これにより、定流量弁後方の流れが整流されて、外 側弁部材の横方向の振動を防止することができる。  [0008] In the present invention, 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.
[0009] 本発明において、第 1流路又は第 2流路は、それらの流路断面積が最も減少した 場合においても通水状態に維持されることが好ましい。第 1流路又は第 2流路自体を 外側及び内側弁部材が水圧によって最も移動した状態における逃がし流路として利 用できるため、別途逃がし流路を構成する必要がなくコンパクトに構成でき、し力も、 この逃がし流路力 の流れが円筒状の第 1流路又は第 2流路力 分散して噴出する ことができ、振動の原因となる渦の発生を抑えることができる。  [0009] In the present invention, it is preferable that 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.
[0010] 本発明において、外側弁部材の支持突起の下流側端部は、上流側から下流側に 向かって広がり形状に形成され、第 2流路からの噴流を分散させる噴流分散部を備 えていることが好ましい。これにより、第 2流路からの噴流によるキヤビテーシヨンの発 生を低減することができる。  [0010] In the present invention, 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. Preferably it is. As a result, the occurrence of cavitation due to the jet flow from the second flow path can be reduced.
[0011] 本発明において、内側弁部材の下流側端部には、常に一定の流路断面積を有す る第 3流路が形成され、この第 3流路は噴流を分散させるように構成されて!、てもよ!/ヽ 。これにより、定流量弁に供給される水の圧力の変動によらず流出させる水の流量を 所定量に調整することができると共に、第 3流路からの噴流によるキヤビテーシヨンの 発生を低減することができる。  [0011] In the present invention, 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.
[0012] 本発明において、内側コイルばねの座卷部のコイルばね素線には、振動による騒 音を防止する騒音防止手段が設けられて 、ることが好ま 、。 [0013] 本発明にお 、て、騒音防止手段は、内側コイルばね又は外側コイルばねの座卷部 のコイルばね素線とその隣り合うコイルばね素線とを連結するように両コイルばね素 線に一体的に取り付けられているばね素線連結弾性部材によって構成されているこ とが好ましい。このばね素線連結弾性部材により、内側コイルばね又は外側コイルば ねの振動時にコイルばねの座卷部の隣り合うコイルばね素線同士が接触するのを完 全に防ぐことができるため、これらの接触によって発生する騒音を防ぐことができる。 また、ばね素線連結弾性部材により、内側コイルばね又は外側コイルばねの固有振 動数を変化させることができると共にばねの振動も吸収されるため、共振現象を抑制 することができる。 [0012] In the present invention, it is preferable that 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. [0013] In the present invention, 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.
[0014] 本発明において、外側弁部材の支持突起と内側弁部材の凹部には、内側弁部材 の軸方向の共振を抑制する共振抑制手段が設けられていることが好ましい。  [0014] In the present invention, it is preferable that 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.
[0015] 本発明において、内側コイルばね又は外側コイルばねの端部には、弾性部材が配 置されていることが好ましい。これにより、内側コイルばね又は外側コイルばねの端部 力 生ずる衝突音を抑えることができる。  In the present invention, it is preferable that 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.
[0016] 本発明において、外側弁部材又は内側弁部材の下流側部分には、円周方向に突 出する板状の複数の弁体脚部が形成され、この弁体脚部は、定流量弁本体に対す る外側弁部材の摺動又は外側弁部材に対する内側弁部材の摺動を案内するように 構成されて ヽることが好ま ヽ。  [0016] In the present invention, 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.
[0017] 本発明において、外側弁部材又は内側弁部材の弁体脚部には、径方向に突出す る突部が形成され、この突部は、外側弁部材を定流量弁本体に係止又は内側弁部 材を外側弁部材に係止するように構成されていることが好ましい。  [0017] In the present invention, 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. Alternatively, the inner valve member is preferably configured to be locked to the outer valve member.
発明の効果  The invention's effect
[0018] 本発明によれば、供給される水の圧力の変動によらず流出させる水の流量を所定 量に調整する小型でかつ簡易な構造を備えた定流量弁を提供することができる。 発明を実施するための最良の形態  [0018] According to the present invention, it is possible to provide a constant flow valve having a small and simple structure that adjusts the flow rate of water to be discharged to a predetermined amount regardless of fluctuations in the pressure of supplied water. BEST MODE FOR CARRYING OUT THE INVENTION
[0019] 以下、添付図面を参照して本発明の定流量弁の実施形態について説明する。 Hereinafter, embodiments of a constant flow valve of the present invention will be described with reference to the accompanying drawings.
図 1は、本発明の第 1実施形態による定流量弁を示す分解斜視図であり、図 2は、 本発明の第 1実施形態による定流量弁を示す斜視図である。 図 1及び図 2に示すように、本実施形態の定流量弁 1は、ほぼ円筒状の定流量弁本 体を形成するケーシング 2、このケーシング 2内に収容された外側圧縮コイルばね 4、 外側弁部材 6、内側圧縮コイルばね 8、内側弁部材 10、ケーシング 2の上流側端部 に取り付けられた蓋 12によって構成されている。 FIG. 1 is an exploded perspective view showing a constant flow valve according to the first embodiment of the present invention, and FIG. 2 is a perspective view showing the constant flow valve according to the first embodiment of the present invention. As shown in FIGS. 1 and 2, 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.
ケーシング 2の上流側端部に取り付けられた蓋 12には、定流量弁 1の流入口 12a が形成され、ケーシング 2の下流側端部には、定流量弁 1の流出口 2aが形成され、こ の流出口 2aの周囲には、ケーシング 2の製造上におけるヒケ防止のための肉盗み部 2bが形成されている。  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. Around the outlet 2a, a meat stealing portion 2b for preventing sink marks in the production of the casing 2 is formed.
[0020] 図 3は、図 2に示す本発明の第 1実施形態による定流量弁の I I断面図であり、図 4は、図 2に示す本発明の第 1実施形態による定流量弁の II II断面図である。ここで 、図 3では、定流量弁 1内の水の流れを矢印で示している。  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. Here, in FIG. 3, the flow of water in the constant flow valve 1 is indicated by arrows.
図 1〜図 4に示すように、外側弁部材 6は、ケーシング 2内に軸方向に摺動可能に 配置されており、内側弁部材 10は、外側弁部材 6の内側に軸方向に摺動可能に配 置されている。  As shown in FIGS. 1 to 4, 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.
外側弁部材 6は、流入口 12aからケーシング 2内に流入した水の圧力を外側弁部 材 6の上流側端部の受圧部 6aと内側弁部材 10の上流側端部の受圧部 10cで受圧 し、この受圧部 6aで受圧した水圧に応じて軸方向下流側に摺動するようになつてい る。  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.
また、図 1に示すように、外側弁部材 6の主要部である弁体部 6bは、上流側から下 流側に向力つて相対的に絞られた形状に形成されている。  Further, as shown in FIG. 1, the 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.
さらに、図 4に示すように、弁体部 6bの外周部とケーシング 2の流出口 2aとの間に は、第 1流路として外側可変流路 14が形成されており、外側弁部材 6が軸方向に摺 動することにより、弁体部 6bが外側可変流路 14の開度又は流路断面積を可変に調 整するようになっている。なお、図 3及び図 4では、初動低水圧時において、定流量 弁 1の流入口 12aからケーシング 2内に水が流入するものの、外側弁部材 6が軸方向 に摺動せずに、外側可変流路 14が最大に開放されている状態を示している。  Further, as shown in FIG. 4, 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. In FIGS. 3 and 4, water flows from the inlet 12a of the constant flow valve 1 into the casing 2 at the initial low water pressure, but the outer valve member 6 does not slide in the axial direction and can be changed outside. The flow path 14 is shown in a fully open state.
[0021] さらに、ケーシング 2の内周部 2cと外側弁部材 6の外周部 6cとの間には、外側圧縮 コイルばね 4が外側弁部材 6とほぼ同軸に配置されている。 この外側圧縮コイルばね 4は、ばね荷重とばねの縮みが比例する線形ばね特性を 有し、外側弁部材 6が作動しない状態では、ケーシング 2の内周部 2cと外側弁部材 6 の外周部 6cとの間に、外側弁部材 6を軸方向に付勢するように収容されている。定 流量弁 1の流入口 12aからケーシング 2内に水が流入すると、この水の圧力によって 外側弁部材 6の上流側端部の受圧部 6aと内側弁部材 10の上流側端部の受圧部 10 cとが下流側軸方向に押圧されるようになつている。さらに、この外側弁部材 6の押圧 と内側弁部材 10の押圧が内側圧縮コイルばね 8を介して外側弁部材 6を押圧するこ とにより、外側圧縮コイルばね 4の上流側端部 4aが下流側軸方向に押圧されるように なっている。 Furthermore, 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. When the outer valve member 6 is not operated, the outer peripheral portion 6c of the casing 2 and the outer peripheral portion 6c of the outer valve member 6 are provided. The outer valve member 6 is accommodated so as to be biased in the axial direction. When water flows into the casing 2 from the inlet 12a of the constant flow valve 1, the pressure of this water causes a pressure receiving portion 6a at the upstream end of the outer valve member 6 and a pressure receiving portion 10 at the upstream end of the inner valve member 10. c is pressed in the downstream axial direction. Further, the pressing of the outer valve member 6 and the pressing of the inner valve member 10 press the outer valve member 6 via the inner compression coil spring 8, so that the upstream end 4a of the outer compression coil spring 4 is on the downstream side. It is pressed in the axial direction.
また、外側弁部材 6の弁体部 6bの下流側端部は、外側弁部材 6を横断するよう〖こ 延びるアーチ部 18を備えている。外側弁部材 6の受圧部 6aと内側弁部材 10の上流 側端部の受圧部 10cとが受圧する水圧の上昇に応じて、外側弁部材 6が下流側へ 移動し、外側弁部材 6から外側圧縮コイルばね 4の上流側端部 4aに加わるばね荷重 が増すにつれて、外側弁部材 6の弁体部 6bの外周部に形成された段部 6dがケーシ ング 2の流出口 2aに近づき、最終的には当接して外側可変流路 14が完全に閉鎖さ れるようになっている。  Further, the 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. As the water pressure received 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 rises, the outer valve member 6 moves downstream and moves outward from the outer valve member 6. As the spring load applied to the upstream end 4a of the compression coil spring 4 increases, 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.
また、弁体部 6bにおいて、アーチ部 18から 90度円周方向に離れた位置には薄板 状態の外側弁体脚部 6fが形成されている。この外側弁体脚部 6fは、ケーシング 2の 流出口 2の内周に当接することにより、外側弁部材 6の移動におけるガイドとして機構 すると共に、外側可変流路 14から噴出する水を整流する役目も果たす。  Further, in the valve body portion 6b, 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.
内側弁部材 10の主要部である弁体部 10aは、上流側から下流側に向かって相対 的に絞られた形状に形成されている。  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.
また、外側弁部材 6の内周部 6eと内側弁部材 10の弁体部 10aとの間には、第 2流 路として内側可変流路 16が形成されており、内側弁部材 10が外側弁部材 6に対して 軸方向に摺動することにより、弁体部 10aが内側可変流路 16の開度又は流路断面 積を可変に調整するようになっている。なお、図 3及び図 4では、定流量弁 1の流入 口 12aからケーシング 2内に水が流入するものの、内側弁部材 10が外側弁部材 6に 対して軸方向に摺動せずに、内側可変流路 16が最大に開放されている状態を示し ている。 Further, 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. By sliding in the axial direction with respect to the member 6, the valve body 10 a variably adjusts the opening degree or the cross-sectional area of the inner variable flow path 16. In FIGS. 3 and 4, water flows into the casing 2 from the inlet 12a of the constant flow valve 1, but the inner valve member 10 does not slide axially with respect to the outer valve member 6, and the inner valve member 10 Indicates that the variable flow path 16 is fully open. ing.
[0023] 外側弁部材 6の内周部 6eと内側弁部材 10の外周部 10bとの間には、内側圧縮コィ ルばね 8が内側弁部材 10とほぼ同軸に配置されている。  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.
この内側圧縮コイルばね 8は、外側圧縮コイルばね 4のコイル平均径よりも小さ ヽ平 均径を有し、外側圧縮コイルばね 4に対して同軸かつ入れ子状に配置されている。さ らに、内側圧縮コイルばね 8は、外側圧縮コイルばね 4と同様に線形ばね特性を有し ているが、外側圧縮コイルばね 4のばね定数よりも大きいばね定数を有している。す なわち、本実施形態の定流量弁 1は、コイル平均径とばね定数の異なる 2つの線形 圧縮コイルばね 4, 8を同軸かつ入れ子状に配置することにより、組み合わせて使用 するように構成されている。  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.
[0024] また、内側圧縮コイルばね 8は、内側弁部材 10が作動しない状態では、外側弁部 材 6の内周部 6eと内側弁部材 10の外周部 10bとの間に、内側弁部材 10を軸方向に 付勢するように収容されている。定流量弁 1の流入口 12aからケーシング 2内に水が 流入すると、この水の圧力によって内側弁部材 10の上流側端部の受圧部 10cが下 流側軸方向に押圧されて、この内側弁部材 10の押圧により内側圧縮コイルばね 8の 下流側端部 8bが外側弁部材 6を下流側軸方向に押圧されるようになって ヽる。 さらに、外側弁部材 6が外側可変流路 14を完全に閉鎖した後に内側弁部材 10の 受圧部 10cが受圧する水圧の上昇に応じて、内側弁部材 10が下流側へ移動し、内 側弁部材 10から内側圧縮コイルばね 8に加わるばね荷重が増すにつれて、内側弁 部材 10の外周部 10bに形成された段部 10dが外側弁部材 6の内周部 6eに当接し、 内側可変流路 16が所定の開度または流路断面積まで閉鎖されるようになっている。  In addition, 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. When water flows into the casing 2 from the inlet 12a of the constant flow valve 1, 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 By the pressing of the member 10, the downstream end 8b of the inner compression coil spring 8 is pressed against the outer valve member 6 in the downstream axial direction. Furthermore, after the outer valve member 6 completely closes the outer variable flow path 14, 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. As the spring load applied to the inner compression coil spring 8 from the member 10 increases, 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.
[0025] なお、上述した実施形態の定流量弁 1においては、一例として、流入口 12aと流出 口 2aにおける水圧の差 (差圧) Pがほぼ 0. 15MPaの場合に、まず外側弁部材 6が 最も下流側に摺動して外側可変流路 14を完全に閉鎖し、差圧 Pがほぼ 1. OMPaの 場合に、外側弁部材 6が外側可変流路 14を完全に閉鎖した状態で、内側弁部材 10 が最も下流側に摺動して内側可変流路 16を最小限度に開放し、それぞれの場合の 流出口 2aにおける流量 Qが下限目標流量値 Q力も上限目標流量値 Qまでの目標  [0025] In the constant flow valve 1 of the above-described embodiment, as an example, when the water pressure difference (differential pressure) P between the inlet 12a and the outlet 2a is approximately 0.15 MPa, first the outer valve member 6 Slides to the most downstream side and completely closes the outer variable flow path 14, and when the differential pressure P is approximately 1. OMPa, the outer valve member 6 fully closes the outer variable flow path 14, The inner valve member 10 slides to the most downstream side to open the inner variable flow path 16 to the minimum.In each case, the flow rate Q at the outlet 2a is the lower limit target flow rate value Q, and the force is the target up to the upper limit target flow rate value Q.
0 1  0 1
定流量域となる 20LZmin〜25LZminの範囲となるように、外側弁部材 6と内側弁 部材 10の寸法及び形状と外側圧縮コイルばね 4及び内側圧縮コイルばね 8の仕様 が定められている。 Outer valve member 6 and inner valve so that the constant flow rate range is 20LZmin to 25LZmin. 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.
これらのばね仕様の一例として、外側圧縮コイルばね 4については、ばね定数が 1. 573 [N/mm] ,コイル平均径が 20. 7mm、自由高さが 14mmである。また、内側圧 縮コイルばね 8については、ばね定数が 3. 557 [NZmm]、コイル平均径が 11. 4m m、自由高さが 13. 35mmである。  As an example of these spring specifications, 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.
[0026] さらに、図 1〜図 3に示すように、外側弁部材 6のアーチ部 18の中心部には、内側 弁部材 10を軸方向に摺動可能に支持する支持突起 22が形成されて 、る。 Furthermore, as shown in FIGS. 1 to 3, 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. RU
一方、内側弁部材 10には、外側弁部材 6の支持突起 22を摺動可能に受け入れる 凹部 20が形成されている。外側弁部材 6の支持突起 22が内側弁部材 10の凹部 20 に受け入れられている状態では、この支持突起 22が、内側弁部材 10を外側弁部材 6に対して軸方向に正確に摺動させて横方向への振動を防止し、水の流動による内 側弁部材 10の急激な移動を防止するダンパー機能を果たすようになって 、る。 また、外側弁部材 6のアーチ部 18は、翼状に形成された翼部 24を備えており、この 翼部 24が外側弁部材 6の下流側を整流することにより、水流の乱れによる外側弁部 材 6の横方向の振動を防止するようになって 、る。  On the other hand, the inner valve member 10 is formed with a recess 20 that slidably receives 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. Further, 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.
[0027] さらに、図 1〜図 3に示すように、外側弁部材 6のアーチ部 18の中心部であり、外側 弁部材 6の支持突起 22の下流側端部は噴流分散部 26となっており、この噴流分散 部 26は、上流側から下流側に向力つて広がり形状となるほぼ円錐台形状に形成され ている。 また、噴流分散部 26は、特に、定流量弁 1の外側可変流路 14が閉鎖され たままの状態のもとに、内側可変流路 16が最小限の開度または流路断面積まで閉 鎖された状態、すなわち、内側可変流路 16の流路断面積が最も減少しても通水状 態に維持された状態となっている場合に、コアンダ効果により内側可変流路 16から の噴流を噴流分散部 26の外面に沿わせて分散させ、噴流によるキヤビテーシヨンの 発生を低減するようになって 、る。 Further, as shown in 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. In addition, 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. In the chained state, that is, when the flow passage cross-sectional area of the inner variable flow passage 16 is the smallest, the water flow state is maintained, and the jet flow from the inner variable flow passage 16 is caused by the Coanda effect. Is distributed along the outer surface of the jet dispersion part 26 to reduce the generation of the cavity due to the jet.
なお、内側弁体部 10の弁体部 10aには、外側弁部材 6の内周部 6eと当接するよう に一対の内側弁体脚部 10fが形成されており、この内側弁体脚部 10fの下流側先端 には径方向に突出した突部であるフック部 10gが形成されている。この内側弁体脚 部 lOfは、外側弁部材 6の内周部 6eと当接することにより、内側弁部材 10の移動に おけるガイドとして機構すると共に、内側可変流路 16から噴出する水を整流する役 目も果たす。また、フック部 10gが内側可変流路 16の下流端側の外側弁部材 6に係 止されることによって内側弁部材 10の上流側への移動を規制することができ、外側 弁部材 6を保持するための蓋体 12に対応する内側便部材 10を保持するための蓋体 を省略することができる。 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. Further, 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.
[0028] つぎに、上述した本発明の第 1実施形態による定流量弁 1の動作 (作用）について 説明する。 [0028] Next, the operation (action) of the constant flow valve 1 according to the first embodiment of the present invention will be described.
図 5は、本実施形態の定流量弁 1における水圧と流量との関係、及び、水圧と全流 路断面積との関係をそれぞれ定性的に示した特性線図である。ここで、図 5において 、横軸に流入口 12aと流出口 2aにおける水圧の差 (差圧) P、左側縦軸に流量 Q、右 側縦軸に定流量弁 1の流出口 2aにおける全流路断面積 Sをそれぞれ示し、流量線 図につ ヽては実線で示し、全流路断面積の特性線図につ ヽては破線で示して 、る。 また、図 5の線図では、作動中の定流量弁の各作動状態について、定流量弁に流 入する水の圧力の小さい順に 0、 A、 B、 C、 Dで表している。  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. Here, in FIG. 5, 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, and the characteristic diagram of the total channel cross-sectional area is shown by a broken line. Further, in the diagram of FIG. 5, 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.
さらに、図 6〜図 9は、図 5の作動状態 A〜Dにおける各定流量弁を示す断面図で ある。また、図 10は、本発明の第 1実施形態による定流量弁 1において、図 2の III— II I断面による作動状態 Dを示す断面図である。さらに、図 11は、本発明の第 1実施形 態による定流量弁 1において、図 2の II II断面による作動状態 Dを示す断面図であ る。  Further, 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. Further, 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.
[0029] まず、図 3〜図 5に示すように、初期状態である作動状態 Oの定流量弁 1は、定流 量弁 1の流入口 12aからケーシング 2内に水が流入している力 差圧 Pがほとんど生 じていない状態である。この状態では、外側弁部材 6と内側弁部材 10は、最も上流 側に位置しており、外側可変流路 14と内側可変流路 16は最大に開放されて!、る。 ここで、これら外側可変流路 14と内側可変流路 16が最大に開放された作動状態 O において、流路断面積 Sは 140mm2であり、流量 Qは差圧 Pがほとんど生じていない [0029] First, as shown in FIGS. 3 to 5, 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. In this state, 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! Here, in the operating state O in which the outer variable flow path 14 and the inner variable flow path 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.
0  0
なめ、ほぼ 0となる。  It ’s almost zero.
さらに、定流量弁 1の外側弁部材 6と内側弁部材 10は、流入する水の差圧 Pが上昇 するにつれて、作動状態 Oから、作動状態 A (図 5及び図 6参照）、作動状態 B (図 5 及び図 7参照)、作動状態 C (図 5及び図 8参照)、作動状態 D (図 5及び図 9〜図 11 参照)の順で作動する。 In addition, 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. As a result, from 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).
[0030] 図 5及び図 6に示すように、作動状態 Aの定流量弁 1は、外側弁部材 6の受圧部 6a と内側弁部材 10の受圧部 10cのそれぞれに加わる水圧が作動状態 Oよりも上昇した 状態となる。この状態では、外側圧縮コイルばね 4が外側弁部材 6の受圧部 6aと内側 弁部材 10の上流側端部の受圧部 10cとにより下流側軸方向に押圧され、内側圧縮 コイルばね 8が内側弁部材 10の受圧部 10cにより下流側軸方向に押圧されている。 このとき、ばね定数の小さ 、外側圧縮コイルばね 4が内側圧縮コイルばね 8よりも軸 方向に大きく縮むため、ケーシング 2内では、外側弁部材 6が内側弁部材 10よりも大 きく下流側軸方向に摺動する。また、外側可変流路 14と内側可変流路 16は共に開 放されており、流量 Qは水圧の上昇と共に下限目標の流量値 Q  As shown in FIGS. 5 and 6, in the constant flow valve 1 in the operating state A, 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. In this state, 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. At this time, since 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. To slide. 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.
0に向力つて増加して いるが、全流路断面積 Sは減少している。  The total cross-sectional area S is decreasing, although increasing toward zero.
[0031] また、図 5及び図 7に示すように、作動状態 Bの定流量弁 1は、外側弁部材 6の受圧 部 6aと内側弁部材 10の受圧部 10cのそれぞれに加わる水圧が作動状態 Aよりもさら に上昇した状態となる。この状態では、外側圧縮コイルばね 4が外側弁部材 6の受圧 部 6aと内側弁部材 10の上流側端部の受圧部 10cとにより下流側軸方向にさらに押 圧され、内側圧縮コイルばね 8が内側弁部材 10の受圧部 10cにより下流側軸方向に さらに押圧される。このとき、外側弁部材 6のアーチ部 18の段部 6dがケーシング 2の 流出口 2aに当接し、外側可変流路 14が完全に閉鎖されるが、内側可変流路 16は 作動状態 Aの開放状態よりもわずかに閉鎖されている。 Further, as shown in FIGS. 5 and 7, in the constant flow valve 1 in the operating state B, 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. In this state, 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. At this time, the 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.
ここで、作動状態 Bにおいて、差圧 Pは 0. 15MPa、流路断面積 Sは 30mm2であ Here, in the operating state B, the differential pressure P is 0.15 MPa, and the channel cross-sectional area S is 30 mm 2.
B B  B B
り、流量 Qは 20LZminとなる。  Therefore, the flow rate Q is 20LZmin.
B  B
また、作動状態 A力 Bへの途中の状態において、流量 Qは水圧の上昇と共に増 加して下限目標の流量値 Qを超えて一旦最大となるが、その後作動状態 Bでは、流  In the middle of the operating state A force B, the flow rate Q increases as the water pressure increases and exceeds the lower limit target flow rate value Q.
0  0
量 Qは減少して目標の流量値 Q  Quantity Q decreases and target flow value Q
0に近づいて目標定流領域に収まる。一方、全流路 断面積 Sについては、作動状態 Aから Bにかけて水圧の上昇と共に減少する。  It approaches 0 and falls within the target constant flow region. On the other hand, the total channel cross-sectional area S decreases from the operating state A to B as the water pressure increases.
[0032] さらに、図 5及び図 8に示すように、作動状態 Cの定流量弁 1は、外側弁部材 6の受 圧部 6aと内側弁部材 10の受圧部 10cのそれぞれに加わる水圧が作動状態 Bよりもさ らに上昇した状態となる。この状態では、外側圧縮コイルばね 4はこれ以上縮まず、 外側弁部材 6のアーチ部 18の段部 6dがケーシング 2の流出口 2aに当接して外側可 変流路 14が完全閉鎖された状態まま、内側圧縮コイルばね 8が内側弁部材 10の受 圧部 10cにより下流側軸方向にさらに押圧される。このとき、内側可変流路 16は作動 状態 Bの開放状態よりもさらに閉鎖される。 Furthermore, as shown in FIGS. 5 and 8, 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. In this state, 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.
また、作動状態 B力 Cへの途中の状態において、流量 Qは水圧の上昇と共に作 動状態 Bの流量よりもわずかに増カロして一旦最大となるが、その後作動状態 Cでは、 流量は最小目標の流量値 Qに向力つて減少傾向となる。一方、全流路断面積 Sに  In addition, in the middle of the operating state B force C, 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. On the other hand, the total cross-sectional area S
0  0
ついては、作動状態 B力も Cにかけて水圧の上昇と共にさらに減少する。 As a result, the operating state B force also decreases as the water pressure increases toward C.
つぎに、図 5及び図 9〜図 11に示すように、作動状態 Dの定流量弁 1は、外側弁部 材 6の受圧部 6aと内側弁部材 10の受圧部 10cのそれぞれに加わる水圧が作動状態 Cよりもさらに上昇した状態となる。この状態では、外側圧縮コイルばね 4と内側圧縮 コイルばね 8は共にこれ以上縮まず、また外側弁部材 6のアーチ部 18の段部 6dがケ 一シング 2の流出口 2aに当接して外側可変流路 14が閉鎖された状態のままである。 さらに、内側弁部材 10も下流側軸方向へこれ以上摺動することなぐ内側可変流 路 16は作動状態 Cの開放状態よりもわずかに閉鎖されて最小限の開度または流路 断面積まで閉鎖された状態となる。すなわち、外側弁部材 6と内側弁部材 10がケー シング 2に対して最も下流側に位置し、外側可変流路 14が閉鎖されたままの状態で 、かつ内側可変流路 16のみが最小限度に開放されて通水状態が維持された状態と なる（図 11参照)。  Next, as shown in FIG. 5 and FIGS. 9 to 11, 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. Furthermore, 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).
ここで、作動状態 Dにおいて、差圧 Pは 1. 0MPa、流路断面積 Sは 10mm2であり Here, in the operating state D, the differential pressure P is 1.0 MPa, and the channel cross-sectional area S is 10 mm 2 .
D D  D D
、流量 Qは 20LZminとなる。  The flow rate Q is 20LZmin.
D  D
また、作動状態 C力 Dへの途中の状態において、流量 Qは水圧の上昇と共に減 少して作動状態 Dで下限目標流量値 Qに近づく。一方、全流路断面積 Sについては  In the middle of the operating state C force D, the flow rate Q decreases as the water pressure increases and approaches the lower limit target flow rate value Q in the operating state D. On the other hand, the total cross-sectional area S
0  0
、作動状態 C力 Dにかけて水圧の上昇と共にさらに減少し、 Dにおいて全流路面積 は最小となる。その後作動状態 Dよりも水圧が上昇しても、断面積 Sは変わらずにほ ぼ一定となり、さらに水圧が上昇するとともに流量は増加する。 [0034] 上述した本発明の第 1実施形態による定流量弁 1によれば、流入口 12aから流入し た水の差圧に応じた外側弁部材 6、内側弁部材 10、外側圧縮コイルばね 4、内側圧 縮コイルばね 8の一連の作動により、定流量弁 1に供給される水の圧力の変動によら ず流出口 2aから流出させる水の流量を下限目標流量値 Q力 上限目標流量値 Q In the operating state C force D, it further decreases as the water pressure increases, and in D, the total channel area is minimized. After that, even if the water pressure increases from the operating state D, the cross-sectional area S remains unchanged and the flow rate increases as the water pressure increases. [0034] According to the constant flow valve 1 according to the first embodiment of the present invention described above, 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. By the series of operations of the inner compression coil spring 8, the lower limit target flow rate value Q is the upper limit target flow rate value Q.
0 1 の範囲である目標定流量域内となるように調整することができる。  It can be adjusted so that it falls within the target constant flow rate range which is the range of 0 1.
[0035] また、本実施形態の定流量弁 1によれば、定流量弁本体を形成するケーシング 2内 に外側弁部材 6が軸方向に摺動可能に配置され、この外側弁部材 6の内側に内側 弁部材 10が軸方向に摺動可能に配置されている。さらに、外側圧縮コイルばね 4が ケーシング 2の内周部 2cと外側弁部材 6の外周部 6cとの間に外側弁部材 6とほぼ同 軸に配置されて、内側圧縮コイルばね 8が外側弁部材 6の内周部 6eと内側弁部材 1 0の外周部 10bとの間に内側弁部材 10とほぼ同軸に配置されている。したがって、こ れらの複数の部材 4, 6, 8, 10が互いのスペースを利用して、ケーシング 2内の限ら れたスペースにコンパクトに集約されているため、定流量弁 1の全体を小型化するこ とがでさる。  In addition, according to the constant flow valve 1 of the present embodiment, 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. Further, 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
[0036] さらに、本実施形態の定流量弁 1によれば、コイル平均径とばね定数が異なる 2つ の線形コイルばね 4, 8をほぼ同軸かつ入れ子状に配置して、組み合わせて使用す るため、小型でかつ簡易な構造を備えた定流量弁を実現することができる。  Furthermore, according to the constant flow valve 1 of the present embodiment, 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.
[0037] また、本実施形態の定流量弁 1によれば、外側弁部材 6が内側弁部材 10を軸方向 に摺動可能に支持するアーチ部 18を備えており、このアーチ部 18の支持突起 22が 内側弁部材 10の凹部 20に挿入されて 、るため、内側弁部材 10が外側弁部材 6に 対して正確に軸方向に摺動することができる。また、内側弁部材 10が軸方向に摺動 する際、横方向への振動を防止すると共に、水の流動による内側弁部材 10の急激な 移動を防止することができる。  Further, according to the constant flow valve 1 of the present embodiment, 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.
[0038] さらに、本実施形態の定流量弁 1によれば、外側弁部材 6のアーチ部 18が翼部 24 を備えているため、この翼部 24が外側弁部材 6の下流側を整流して、水流の乱れに よる外側弁部材 6の横方向の振動を低減することができる。  Furthermore, according to the constant flow valve 1 of the present embodiment, since the arch portion 18 of the outer valve member 6 includes the wing portion 24, the wing portion 24 rectifies the downstream side of the outer valve member 6. Thus, the lateral vibration of the outer valve member 6 due to the turbulence of the water flow can be reduced.
[0039] また、本実施形態の定流量弁 1によれば、外側弁部材 6の支持突起 22の下流側端 部が円錐台形状に形成された噴流分散部 26を備えている。このため、特に、定流量 弁 1の外側可変流路 14が完全に閉鎖されたままの状態のもとに、内側可変流路 16 が最小限の開度または流路断面積まで閉鎖された状態、すなわち、内側可変流路 1 6の流路断面積が最も減少しても通水状態に維持された状態では、コアンダ効果を 利用して内側可変流路 16からの噴流を分散部材 26の外面に沿わせて分散させるこ とができるため、噴流によるキヤビテーシヨンの発生を低減することができる。 [0039] Further, according to the constant flow valve 1 of the present embodiment, 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. For this reason, in particular, constant flow With the outer variable flow path 14 of the valve 1 fully closed, 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 When 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.
[0040] つぎに、図 12は、本発明の第 2実施形態による定流量弁を示す図 8と同様な断面 図である。ここで、図 12において、図 8に示す第 1実施形態の定流量弁 1と同一の部 分については同一の符号を付し、それらの説明は省略する。 Next, 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. Here, in FIG. 12, 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.
図 12に示すように、本発明の第 2実施形態による定流量弁 30は、上述した第 1実 施形態による定流量弁 1の内側圧縮コイルばね 8の両端部 8a, 8bの部分を異なる構 成にしたものである。  As shown in FIG. 12, 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.
[0041] 本実施形態による定流量弁 30の内側圧縮コイルばね 8の上流側端部 8aと下流側 端部 8bは、いずれか一方がコイルばね素線 32の巻き始め部分の座卷部に相当し、 他方が巻き終わり部分となる座卷部に相当して 、る。  [0041] 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.
また、内側圧縮コイルばね 8は、この座卷部のコイルのばね素線 32同士が接触す る、いわゆる、クローズトエンドタイプの座卷形状を有するものである。本実施形態で は、内側圧縮コイルばね 8の伸縮時に、内側圧縮コイルばね 8の座卷部の隣り合うコ ィルのばね素線 32同士が強く接触することによって生じる騒音を防止するため、座 卷部のコイルばね素線 32は、騒音防止手段であるゴム管 34で覆われている。  Further, 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. In the present embodiment, 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.
さらに、外側弁部材 6において、内側圧縮コイルばね 8の下流側端部 8bが接触する 接触部には、内側圧縮コイルばね 8の下流側端部 8bを保持する溝 36が形成されて いる。この溝 36と内側圧縮コイルばね 8の下流側端部 8bとの間には、弾性部材であ る防振ゴムで作られた平リング 38が配置されている。  Further, in the outer valve member 6, 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. Between this groove 36 and the downstream end 8b of the inner compression coil spring 8, a flat ring 38 made of vibration-proof rubber, which is an elastic member, is disposed.
[0042] 上述した本実施形態の定流量弁 30によれば、内側圧縮コイルばね 8がその付近を 通過する水流によるカルマン渦の影響を受けて高周波で振動した場合でも、内側圧 縮コイルばね 8の上流側端部 8a及び下流側端部 8bである座卷部のコイルばね素線 32はゴム管 34で覆われているため、座卷部の隣り合うコイルのばね素線 32同士が 接触することによって生ずる「キーン」という高音の不快な接触音を防ぐことができる。 また、本実施形態の定流量弁 30によれば、流入口 12aから流入される水の給水圧 が高ぐ内側圧縮コイルばね 8が縮んだ状態で、内側圧縮コイルばね 8に繰り返し荷 重が加わると、この内側圧縮コイルばね 8の振動数が固有振動数に近づいて内側圧 縮コイルばね 8が激しく振動する、いわゆる「サージング」と呼ばれる一種の共振現象 が生じた場合でも、内側圧縮コイルばね 8の下流側端部 8bと外側弁部材 6の溝 36と の間には平リング 38が配置されているため、内側圧縮コイルばね 8の下流側端部 8b と外側弁部材 6の溝 36との衝突によって生ずる衝突音を抑えることができる。 [0042] According to the constant flow valve 30 of the present embodiment described above, even when the inner compression coil spring 8 vibrates at a high frequency due to the influence of Karman vortex caused by the water flow passing therearound, the inner compression coil spring 8 Since the coil spring wire 32 of the washer portion, which is the upstream end portion 8a and the downstream end portion 8b, is covered with the rubber tube 34, the spring wire wires 32 of the adjacent coils of the washer portion come into contact with each other. It is possible to prevent an unpleasant high-pitched contact sound such as “Keen”. In addition, according to the constant flow valve 30 of the present embodiment, 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. Even when a kind of resonance phenomenon called “surging” occurs, 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.
[0043] なお、上述した本実施形態の定流量弁 30では、内側圧縮コイルばね 8の両端部 8a , 8bである座卷部のコイルばね素線 32をゴム管 34で覆った形態にっ 、て説明した 1S このような形態に限定されず、外側圧縮コイルばね 4の両端部 4a, 4bのコイルば ね素線にっ ヽても同様に、ゴム管で覆うような形態にしてもょ 、。 Note that 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. .
また、本実施形態の定流量弁 30では、内側圧縮コイルばね 8の下流側端部 8bと外 側弁部材 6の溝 36との間に平リング 38を配置した形態について説明した力 このよう な形態に限定されず、内側圧縮コイルばね 8の上流側端部 8aや外側圧縮コイルば ね 4の両端部 4a, 4bについても平リングを配置した形態にしてもよい。  In the constant flow valve 30 of the present embodiment, 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.
[0044] さら〖こ、上述した本発明の第 2実施形態による定流量弁 30では、一例として、クロ ーズトエンドタイプの座卷形状を有する内側圧縮コイルばね 8を用い、この座卷部の コイルばね素線 32をゴム管 34で覆うことによって、座卷部の隣り合うコイルのばね素 線 32同士が接触する接触音を防止するような形態について説明したが、このような 形態に限定されず、他の形態についても適用可能である。 [0044] Further, in the constant flow valve 30 according to the second embodiment of the present invention described above, as an example, 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.
図 13は、本発明の第 2実施形態の第 1変形例による定流量弁に使用される内側圧 縮コイルばねを示す斜視図である。第 2実施形態の定流量弁の第 1変形例として、ク ローズトエンドタイプの座卷形状を有する内側圧縮コイルばね 8を用いる代わりに、図 13に示すような、座卷部の隣り合うコイルのばね素線同士が接触しない、いわゆる、 オープンエンドタイプの座卷形状を有する内側圧縮コイルばね 40を使用してもよい。 これにより、内側圧縮コイルばね 40の振動にかかわらず、ばねの座卷部 42の隣り合 うコイル 42a, 42bのばね素線同士、またはばねの座卷部 44のコイル 44a, 44bのば ね素線同士が全く接触しないため、コイルばねの素線間の不快な接触音を排除する ことができる。 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. As a first modified example of the constant flow valve of the second embodiment, instead of using the inner compression coil spring 8 having a closed end type buckle shape, as shown in FIG. Alternatively, 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. As a result, regardless of the vibration of the inner compression coil spring 40, 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.
[0045] また、図 14は、本発明の第 2実施形態の第 2変形例による定流量弁に使用される 内側圧縮コイルばねを示す斜視図である。図 14に示すように、第 2実施形態の定流 量弁の第 2変形として、図 13に示す内側圧縮コイルばね 40と同様に、オープンェン ドタイプの座卷形状を有する内側圧縮コイルばね 45を使用して 、る。  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. As shown in FIG. 14, as a second modification of the constant flow valve of the second embodiment, 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.
さらに、この内側圧縮コイルばね 45の両端部 (座卷部）におけるコイルばね素線 46 の始端部分 (又は終端部分) 46aとその部分力 ほぼ一巻き目に相当する隣接部分 46b〖こは、両部分 46a, 46bを連結するように、ばね素線連結弾性部材 47が取り付 けられている。このばね素線連結弾性部材 47は、硬質ゴム等で形成されており、そ の内部には、円弧状に湾曲して形成され且つその内径力コイルばね素線 46の直径 に一致してコイルばね素線 46を揷通可能とする 2つの長孔 47a, 47bを備えて 、る。 なお、このばね素線連結弾性部材 47については、コイルばね素線 46の両部分 46 a, 46bを弾性接着剤を用いて接着して固化した弾性接着剤の部分によって構成さ れていてもよい。  Further, the adjacent end portion 46b of the coil spring element wire 46a and the adjacent portion 46b corresponding to the first turn of both ends of the inner compression coil spring 45 (the end flange portion) are substantially equal to each other. 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. .
また、図 14に示す内側圧縮コイルばね 45においてはその両端部にばね素線連結 弾性部材 47が取り付けられた形態を示しているが、このような形態に限定ざれず、内 側圧縮コイルばね 45の少なくとも一方の端部 (座卷部）にばね素線連結弾性部材 47 が取り付けられて 、ればよ 、。  In addition, 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.
[0046] 上述した本発明の第 2実施形態の第 2変形例による定流量弁によれば、内側圧縮コ ィルばね 45の両端部 (座卷部）におけるコイルばね素線 46の始端部分 (又は終端部 分) 46aとその部分からほぼ一巻き目に相当する隣接部分 46bにばね素線連結弾性 部材 47を取り付けることにより、内側コイルばね 45の振動時にコイルばね素線 46の 始端部分 (又は終端部分) 46aと隣接部分 46b同士が直接接触するのを完全に防ぐ ことができるため、これらの接触によって発生する騒音を防ぐことができる。 [0046] According to the constant flow valve according to the second modified example of the second embodiment of the present invention described above, 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.
また、ばね素線連結弾性部材 47により、内側圧縮コイルばね 45の固有振動数を変 えることができる。したがって、ばね素線連結弾性部材 47が取り付けられていない場 合に実用水圧帯域範囲（0. 5MPa〜0. 8MPa)内の水圧においてサージングが発 生するような内側圧縮コイルばね 45の使用状態でも、ばね素線連結弾性部材 47が 取り付けたことにより、サージングが発生するとされていると水圧を実用水圧帯域範囲 (0. 5MPa〜0. 8MPa)外に設定することができ、実用上の水圧域においるサージ ングを回避することができる。 Further, 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.
さら〖こ、ばね素線連結弾性部材 47は、硬質ゴム又は弾性接着剤を用いて接着して 固化した弾性部分等によってばね素線連結弾性部材 47の始端部分 (又は終端部分 ) 46aと隣接部分 46b同士を一体的に形成しており、内側圧縮コイルばね 45の両端 部 (座卷部）にダンパーが装着されたことと同様の効果を生じるため、サージングが発 生したとしてもその直後にすぐにその振動を吸収して抑制することができる。  Further, 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.
なお、上述した本発明の第 2実施形態の第 2変形例による定流量弁では、内側圧 縮コイルばね 45の端部 (座卷部）のコイルばね素線 46の始端部分 (又は終端部分） 46aとその部分からほぼ一巻き目に相当する隣接部分 46bにばね素線連結弾性部 材 47が取り付けられた形態について説明したが、このような形態に限定されず、外側 圧縮コイルばね 4の両端部又は一端部についても、内側圧縮コイルばね 45と同様に 、コイルばね素線の始端部分 (又は終端部分)とその隣接部分にばね素線連結弾性 部材 47を取り付けてもよい。  In the constant flow valve according to the second modified example of the second embodiment of the present invention described above, 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. However, the present invention is not limited to such a form, and both ends of the outer compression coil spring 4 are provided. Similarly to the inner compression coil spring 45, 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.
つぎに、図 15は、本発明の第 3実施形態による定流量弁を示す図 8と同様な断面 図である。ここで、図 15において、図 8に示す第 1実施形態の定流量弁 1と同一の部 分については同一の符号を付し、それらの説明は省略する。  Next, FIG. 15 is a sectional view similar to FIG. 8, showing a constant flow valve according to a third embodiment of the present invention. Here, in FIG. 15, 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.
図 15に示すように、本発明の第 3実施形態による定流量弁 50は、上述した第 1実 施形態の定流量弁 1の内側弁部材 10の凹部 20とこの凹部 20に挿入される外側弁 部材 6の支持突起 22の上流側端部との間のスペースに、粘性体であるオイル 52が 封入された構成となっている点で第 1実施形態とは異なった構成となっている。 また、外側弁部材 6の支持突起 22の上流側は、小径部 53とピストン部 54とから構 成されており、このピストン部 54の周面には複数のスリット溝 54aが形成されている。 外側弁部材 6の支持突起 22が内側弁部材 10の凹部 20内で軸方向に移動する際に は、このスリット溝 54aを通じて、オイル 52が小径部 53の周囲の空間部 53aへ向けて 移動可能に構成されている。  As shown in FIG. 15, the constant flow valve 50 according to the third embodiment of the present invention 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. Further, 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. When the support protrusion 22 of the outer valve member 6 moves in the axial direction in the recess 20 of the inner valve member 10, the oil 52 can move toward the space portion 53a around the small diameter portion 53 through the slit groove 54a. It is configured.
さらに、外側弁部材 6の支持突起 22が軸方向に摺動する内側弁部材 10の凹部 20 の途中には Oリング 56が設けられており、外側弁部材 6の支持突起 22が内側弁部材 10の凹部 20内で軸方向に激しく摺動しても凹部 20内のオイル 52が外部へ漏れな いようになっている。 Further, the recess 20 of the inner valve member 10 in which the support protrusion 22 of the outer valve member 6 slides in the axial direction. 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.
上述した本実施形態の定流量弁 50によれば、内側弁部材 10がサージング等によ つて激しく振動して外側弁部材 6の支持突起 22が内側弁部材 10の凹部 20内で軸 方向に激しく振動しょうとする場合でも、凹部 20内に封入されたオイル 52の粘性によ り、これらの振動が抑制されるため、サージングの発生を防止することができる。 つぎに、図 16は、本発明の第 4実施形態による定流量弁を示す斜視図であり、図 1 7は、図 16に示す本発明の第 4実施形態による定流量弁の IV— IV断面図であり、図 18は、図 16に示す本発明の第 4実施形態による定流量弁の V— V断面図である。こ こで、図 16〜図 18において、第 1実施形態の定流量弁 1と同一の部分については同 一の符号を付し、それらの説明は省略する。なお、図 17では、定流量弁内の水の流 れを矢印で示している。  According to the constant flow valve 50 of the present embodiment described above, the inner valve member 10 vibrates vigorously due to surging or the like, and the support protrusion 22 of the outer valve member 6 vibrates in the axial direction within the recess 20 of the inner valve member 10. Even in the case of vibration, since the vibration of the oil 52 enclosed in the recess 20 is suppressed, the occurrence of surging can be prevented. Next, FIG. 16 is a perspective view showing a constant flow valve according to a fourth embodiment of the present invention, and 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. Here, in 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. In FIG. 17, the flow of water in the constant flow valve is indicated by arrows.
図 16〜図 18に示すように、本発明の第 4実施形態による定流量弁 60は、第 1実施 形態の定流量弁 1の構成要素と同様に、流入口 62aと流出口 62bが形成された定流 量弁本体であるケーシング 62、このケーシング 62内に収容された外側圧縮コイルば ね 4、外側弁部材 66、内側圧縮コイルばね 8、内側弁部材 70によって構成されてい るが、これらの構成に含まれる外側可変流路 74及び内側可変流路 74の構成が第 1 実施形態の外側可変流路 14及び内側可変流路 16の構成と異なっている。  As shown in FIGS. 16 to 18, the constant flow valve 60 according to the fourth embodiment of the present invention 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.
また、定流量弁 60のケーシング 62内における外側圧縮コイルばね 4、外側弁部材 66、内側圧縮コイルばね 8、内側弁部材 70の各配置は、第 1実施形態の定流量弁 1 のケーシング 2内における各構成要素の配置と同様に、外側弁部材 66がケーシング 62内に軸方向に摺動可能に配置されており、内側弁部材 70が外側弁部材 66の内 側に軸方向に摺動可能に配置されている。  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.
さらに、ケーシング 62の内周部 62cと外側弁部材 66の外周部 66aとの間には、外 側圧縮コイルばね 4が外側弁部材 66とほぼ同軸に配置されており、外側弁部材 66 の内周部 66bと内側弁部材 70の外周部 70bとの間には、内側圧縮コイルばね 8が内 側弁部材 70とほぼ同軸に配置されている。 [0049] また、図 16〜図 18に示す定流量弁 60においては、図 9〜図 11に示す第 1実施形 態の定流量弁 1の作動状態 Dと同様に、外側弁部材 66と内側弁部材 70がケーシン グ 62に対して最も下流側の位置に摺動した状態となっている。 Further, 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. [0049] In addition, in the constant flow valve 60 shown in Figs. 16 to 18, the outer valve member 66 and the inner side in the same manner as the operation state D of the constant flow valve 1 of the first embodiment shown in Figs. The valve member 70 is slid to the most downstream position with respect to the casing 62.
外側弁部材 66の外周部 66aと流出口 62bとの間には、第 1実施形態の定流量弁 1 の外側可変流路 14と同様に、第 1流路として外側可変流路 74が形成されている。こ の外側可変流路 74は、外側弁部材 66がケーシング 62に対して軸方向に摺動するこ とによって開度または流路断面積が可変するようになっている。  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.
なお、図 16〜図 18に示す定流量弁 60では、外側弁部材 66がケーシング 62に対 して最も下流側の位置まで摺動した状態となって 、るため、この外側可変流路 74は 、外側弁部材 66により最小限の開度または流路断面積まで閉鎖された状態、すなわ ち、外側可変流路 74の流路断面積が最も減少しても通水状態に維持された状態と なっている（図 17及び図 18参照)。  In the constant flow valve 60 shown in FIGS. 16 to 18, 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).
[0050] 一方、外側弁部材 66の内周部 66bと内側弁部材 70の外周部 70aとの間には、第 1 実施形態の定流量弁 1の内側可変流路 16と同様に、第 2流路として内側可変流路 7 6が形成されている。この内側可変流路 76は、内側弁部材 70が外側弁部材 66に対 して軸方向に摺動することによって開度または流路断面積が可変するようになってお り、内側弁部材 70の上流に形成された前方開口部 79から流入した水の流量を調整 可能となっている。  On the other hand, between the inner peripheral portion 66b of the outer valve member 66 and the outer peripheral portion 70a of the inner valve member 70, as in the inner variable flow path 16 of the constant flow valve 1 of the first embodiment, 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.
なお、図 16〜図 18に示す定流量弁 60では、内側弁部材 70がケーシング 62また は外側弁部材 66に対して最も下流側の位置まで摺動した状態となっており、このとき の内側可変流路 76は、外側弁部材 66の下流側内周部 66cと内側弁部材 70の外周 突起 70bが当接して完全に閉鎖された状態となっている。  In the constant flow valve 60 shown in FIGS. 16 to 18, 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.
[0051] 上述した本発明の第 4実施形態による定流量弁 60においては、流入口 62aからケ 一シング 62内に流入した水の圧力が高くなるにつれて、外側弁部材 66と内側弁部 材 70のそれぞれが下流側軸方向に摺動し、外側可変流路 74と内側可変流路 76の 開度または流路断面積を調整して、流出口 62bからの流量が所定量に調整される。 さらに水圧が上昇して所定以上の水圧になると、外側弁部材 66と内側弁部材 70が 最も下流側の位置まで摺動し、外側可変流路 74の流路断面積が最も減少しても通 水状態に維持された状態まま、内側可変流路 76が完全に閉鎖される。 [0051] In the above-described constant flow valve 60 according to the fourth embodiment of the present invention, 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. Each slides in the axial direction on the downstream side, and the flow rate from the outlet 62b is adjusted to a predetermined amount by adjusting the opening degree or the channel cross-sectional area of the outer variable channel 74 and the inner variable channel 76. When the water pressure further rises to a predetermined level or higher, the outer valve member 66 and the inner valve member 70 slide to the most downstream position, and even if the flow path cross-sectional area of the outer variable flow path 74 is reduced the most The inner variable flow path 76 is completely closed while maintaining the water state.
本実施形態の定流量弁 60によれば、ケーシング 62内の水圧が高ぐ内側弁部材 7 0が内側可変流路 76を完全に閉鎖した状態でも、外側可変流路 74が最小限の開度 または流路断面積で開放されているため、この外側可変流路 74により、定流量弁 60 の下流側へ流出される噴流を効果的に分散させることができる。  According to the constant flow valve 60 of the present embodiment, even when the inner valve member 70 having a high water pressure in the casing 62 completely closes the inner variable flow path 76, the outer variable flow path 74 has a minimum opening degree. Alternatively, since the cross-sectional area is open, the outer variable flow path 74 can effectively disperse the jet flowing out downstream of the constant flow valve 60.
また、外側可変流路 74を最小限の開度または流路断面積で開放することにより、 流出口 62bからの噴流を広範囲に分散させることができため、噴流によるキヤビテー シヨンの発生を効果的に防止することができる。  In addition, by opening the outer variable flow path 74 with a minimum opening or a cross-sectional area of the flow path, the jet flow from the outlet 62b can be dispersed over a wide range. Can be prevented.
つぎに、図 19は、本発明の第 5実施形態による定流量弁を示す斜視図であり、図 2 0は、図 19に示す本発明の第 5実施形態による定流量弁の VI— VI断面図である。こ こで、図 19及び図 20において、第 1実施形態の定流量弁 1と同一の部分については 同一の符号を付し、それらの説明は省略する。なお、図 20では、定流量弁内の水の 流れを矢印で示している。  Next, FIG. 19 is a perspective view showing a constant flow valve according to a fifth embodiment of the present invention, and 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. Here, in FIG. 19 and FIG. 20, 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. In FIG. 20, the flow of water in the constant flow valve is indicated by arrows.
図 19及び図 20に示すように、本発明の第 5実施形態による定流量弁 80は、第 1実 施形態の定流量弁 1の構成要素と同様に、流入口 82aと流出口 82bが形成された定 流量弁本体であるケーシング 82、このケーシング 82内に収容された外側圧縮コイル ばね 4、外側弁部材 86、内側圧縮コイルばね 8、内側弁部材 90によって構成されて いる。し力しながら、定流量弁 80の内側弁部材 90の軸心下流側端部 90cが、上流側 力 下流側にかけて先細りとなるノズル形状となっており、このノズル形状の軸心を中 心に第 3流路である複数の定流路 92が形成された構成となっている点が第 1実施形 態の構成と異なっている。  As shown in FIGS. 19 and 20, the constant flow valve 80 according to the fifth embodiment of the present invention 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. However, 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.
また、定流量弁 80のケーシング 82内における外側圧縮コイルばね 4、外側弁部材 86、内側圧縮コイルばね 8、内側弁部材 90の各配置は、第 1実施形態の定流量弁 1 のケーシング 2内における各構成要素の配置と同様に、外側弁部材 86がケーシング 82内に軸方向に摺動可能に配置されており、内側弁部材 90が外側弁部材 86の内 側に軸方向に摺動可能に配置されている。  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.
さらに、ケーシング 82の内周部 82cと外側弁部材 86の外周部 86aとの間には、外 側圧縮コイルばね 4が外側弁部材 86とほぼ同軸に配置されており、外側弁部材 86 の内周部 86bと内側弁部材 90の外周部 90bとの間には、内側圧縮コイルばね 8が内 側弁部材 90とほぼ同軸に配置されている。 Further, the 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.
[0053] なお、図 19及び図 20に示す定流量弁 80においては、図 9〜図 11に示す第 1実施 形態の定流量弁 1の作動状態 Dと同様に、外側弁部材 86と内側弁部材 90がケーシ ング 82に対して最も下流側の位置に摺動した状態となっている。 [0053] In the constant flow valve 80 shown in Figs. 19 and 20, 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.
また、外側弁部材 86の外周部 86aと流出口 82bとの間には、第 1実施形態の定流 量弁 1の外側可変流路 14と同様に、第 1流路として外側可変流路 84が形成されてい る。この外側可変流路 84は、外側弁部材 86がケーシング 82に対して軸方向に摺動 することによって開度または流路断面積が可変するようになっている。  Further, between the outer peripheral portion 86a of the outer valve member 86 and the outlet 82b, 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.
なお、図 19及び図 20に示す定流量弁 80では、外側弁部材 86がケーシング 82に 対して最も下流側の位置まで摺動した状態となっており、このときの外側可変流路 84 は、外側弁部材 86の外周部 86aと流出口 82bが当接して完全に閉鎖された状態とな つている。  In the constant flow valve 80 shown in FIGS. 19 and 20, 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.
[0054] さらに、外側弁部材 86の内周部 86bと内側弁部材 90の外周部 90aとの間には、第 1実施形態の定流量弁 1の内側可変流路 16と同様に、第 2流路として内側可変流路 88が形成されている。この内側可変流路 88は、内側弁部材 90が外側弁部材 86に 対して軸方向に摺動することによって開度または流路断面積が可変するようになって いる。  [0054] Further, between the inner peripheral portion 86b of the outer valve member 86 and the outer peripheral portion 90a of the inner valve member 90, as in the inner variable flow path 16 of the constant flow valve 1 of the first embodiment, 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.
なお、図 19及び図 20に示す定流量弁 80では、内側弁部材 90がケーシング 82ま たは外側弁部材 86に対して最も下流側の位置まで摺動した状態となっており、この ときの内側可変流路 88は、外側弁部材 86の下流側内周部 86cと内側弁部材 90の 外周突起 90bが当接して完全に閉鎖された状態となっている。  In the constant flow valve 80 shown in FIGS. 19 and 20, 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.
また、定流路 92は、図 19及び図 20に示すように、外側弁部材 86と内側弁部材 90 のそれぞれが、ケーシング 82に対して最も下流側の位置まで摺動して外側可変流路 84と内側可変流路 88が完全に閉鎖されている状態であっても、常に一定の流路断 面積で開放されている。また、本実施形態の定流量弁 80では、定流路 92を通過した 噴流は分散されるようになっており、噴流によるキヤビテーシヨンの発生を低減するよ うになつている。 [0055] 上述した本発明の第 5実施形態による定流量弁 80においては、ケーシング 82内の 水圧が高ぐ外側弁部材 86と内側弁部材 90のそれぞれが外側可変流路 84と内側 可変流路 88を完全に閉鎖した状態でも、常に一定の流路断面積で開放された複数 の定流路 92により、定流量弁 80の下流側へ流出される噴流を効果的に分散させる ことができ、噴流によるキヤビテーシヨンの発生を効果的に低減することができる。 また、上述した第 1〜第 4実施形態の定流量弁では、ケーシング内の水圧が所定以 上の高圧域になっても、外側可変流路または内側可変流路のいずれかの流路が最 小限の開度または流路断面積で開放されるように構成されているが、本実施形態の 定流量弁 80は、内側弁部材 90の軸心下流側端部 90cに形成された定流路 92が常 に一定の流路断面積で開放された簡易な構造であるため、特に、高圧域の水圧で は、第 1〜第 4実施形態の定流量弁に比べて流量をより精度よく管理することができ る。 Further, as shown in FIGS. 19 and 20, 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. Even when 88 is completely closed, the plurality of constant flow paths 92 that are always open with a constant flow cross-sectional area can effectively disperse the jets flowing out downstream of the constant flow valve 80, It is possible to effectively reduce the generation of the cavity due to the jet flow. In addition, in the constant flow valves of the first to fourth embodiments described above, 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.
[0056] なお、上述した本実施形態の定流量弁 80では、定流量弁 80の下流側へ流出され る噴流を分散させてキヤビテーシヨンの発生を効果的に低減する手段の一例として、 内側弁部材 90のノズル形状の軸心下流側端部 90cに定流路 92を形成した形態に ついて説明したが、このような形態に限定されず、他の形態についても適用可能であ る。  [0056] In the above-described constant flow valve 80 of the present embodiment, as an example of a means for effectively reducing the occurrence of the cavity by dispersing the jet flowing out downstream of the constant flow valve 80, an inner valve member Although the embodiment in which the constant flow path 92 is formed at the downstream end portion 90c of the 90 nozzle-shaped shaft center has been described, the present invention is not limited to such a configuration, and other configurations can be applied.
例えば、定流量弁 80の下流側へ流出される噴流を分散させてキヤビテーシヨンの 発生を効果的に低減する他の手段として、内側弁部材 90の下流側端部に形成され た流出口に突起状の力べ乱素子を設けてもよいし、その流出口の周縁に沿って間隔 を置いて切欠きを設けてもよい。あるいは、内側弁部材 90の下流側端部に形成され た流出口を扁平形状等の非円形形状にしてもよい。  For example, as another means of dispersing the jet flow flowing downstream of the constant flow valve 80 to effectively reduce the generation of the cavity, 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. Alternatively, the outlet formed at the downstream end of the inner valve member 90 may be a non-circular shape such as a flat shape.
図面の簡単な説明  Brief Description of Drawings
[0057] [図 1]本発明の第 1実施形態による定流量弁を示す分解斜視図である。 FIG. 1 is an exploded perspective view showing a constant flow valve according to a first embodiment of the present invention.
[図 2]本発明の第 1実施形態による定流量弁を示す斜視図である。  FIG. 2 is a perspective view showing the constant flow valve according to the first embodiment of the present invention.
[図 3]図 2に示す本発明の第 1実施形態による定流量弁の I I断面図である。  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.
[図 4]図 2に示す本発明の第 1実施形態による定流量弁の II II断面図である。  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.
[図 5]本発明の第 1実施形態の定流量弁における水圧と流量との関係、及び、水圧と 全流路断面積との関係をそれぞれ定性的に示した特性線図である。 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, and the water pressure FIG. 5 is a characteristic diagram qualitatively showing the relationship with the entire channel cross-sectional area.
[図 6]本発明の第 1実施形態による定流量弁の作動状態 Aを示す断面図である。  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.
[図 7]本発明の第 1実施形態による定流量弁の作動状態 Bを示す断面図である。 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.
[図 8]本発明の第 1実施形態による定流量弁の作動状態 Cを示す断面図である。 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.
[図 9]本発明の第 1実施形態による定流量弁の作動状態 Dを示す断面図である。 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.
[図 10]本発明の第 1実施形態による定流量弁において、図 2の III III断面による作 動状態 Dを示す断面図である。 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.
[図 11]本発明の第 1実施形態による定流量弁において、図 2の II II断面による作動 状態 Dを示す断面図である。  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.
[図 12]本発明の第 2実施形態による定流量弁を示す図 8と同様な断面図である。 圆 13]本発明の第 2実施形態の第 1変形例による定流量弁に使用される内側圧縮コ ィルばねを示す斜視図である。  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.
圆 14]本発明の第 2実施形態の第 2変形例による定流量弁に使用される内側圧縮コ ィルばねを示す斜視図である。 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.
[図 15]本発明の第 3実施形態による定流量弁を示す図 8と同様な断面図である。 圆 16]本発明の第 4実施形態による定流量弁を示す斜視図である。  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.
圆 17]図 16に示す本発明の第 4実施形態による定流量弁の IV— IV断面図である。 [17] 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.
[図 18]図 16に示す本発明の第 4実施形態による定流量弁の V— V断面図である。 圆 19]本発明の第 5実施形態による定流量弁を示す斜視図である。  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.
圆 20]図 19に示す本発明の第 5実施形態による定流量弁の VI— VI断面図である。 符号の説明 20] 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
1, 30, 50, 60, 80 定流量弁  1, 30, 50, 60, 80 Constant flow valve
2, 62, 82 ケーシング  2, 62, 82 Casing
4 外側圧縮コイルばね  4 Outer compression coil spring
6, 66, 86 外側弁部材  6, 66, 86 Outer valve member
8, 40, 45 内側圧縮コイルばね  8, 40, 45 Inner compression coil spring
10, 70, 90 内側弁部材  10, 70, 90 Inner valve member
12 蓋 , 74, 84 外側可変流路, 76, 88 内側可変流路 アーチ部 12 lid , 74, 84 Outer variable flow path, 76, 88 Inner variable flow path Arch
凹部  Recess
支持突起  Support protrusion
翼部  Wings
噴流分散部 Jet dispersion part
, 46 コイルばね素線 ゴム管 , 46 Coil spring wire Rubber tube
溝  Groove
平リング Flat ring
, 44 ばねの座卷部 ばね素線連結弾性部材a, 47b 長孔 , 44 Spring seat collar Spring element connecting elastic member a, 47b Long hole
オイル  Oil
溝  Groove
Oリング  O-ring
内側弁部材の前方開口 疋流路  Front opening of inner valve member 疋 Flow path

Claims

請求の範囲 The scope of the claims
[1] 供給される水の圧力の変動によらず流出させる水の流量を所定量に調整する定流 量弁であって、  [1] A constant flow valve that adjusts the flow rate of water to flow out regardless of fluctuations in the pressure of supplied water.
流入口と流出口が形成された定流量弁本体と、  A constant flow valve body formed with an inlet and an outlet;
この流量弁本体の内側に上記定流量弁本体に対して摺動可能に配置され、この摺 動により、外周部と上記定流量弁本体の内周部との間に形成される第 1流路の断面 積を変化させる外側弁部材と、  A first flow path is formed inside the flow valve body so as to be slidable with respect to the constant flow valve body, and is formed between the outer peripheral portion and the inner peripheral portion of the constant flow valve main body by the sliding. An outer valve member that changes the cross-sectional area of
上記外側弁部材の内側に上記外側弁部材に対して摺動可能に配置され、この摺 動により、外周部と上記外側弁部材の内周部との間に形成される第 2流路の断面積 を変化させる内側弁部材と、  The outer valve member is slidably disposed on the inner side of the outer valve member, and the sliding of the second flow path formed between the outer peripheral portion and the inner peripheral portion of the outer valve member is caused by this sliding. An inner valve member that changes area,
上記定流量弁本体と上記外側弁部材との間に配置され、上記外側弁部材を軸方 向に付勢し、上記外側弁部材に水圧が作用すると上記外側弁部材を摺動させ、上 記第 1流路の断面積を減少させるように縮む外側コイルばねと、  It is arranged between the constant flow valve body and the outer valve member, urges the outer valve member in the axial direction, and slides the outer valve member when water pressure acts on the outer valve member. An outer coil spring that shrinks to reduce the cross-sectional area of the first flow path;
上記外側弁部材と上記内側弁部材との間に配置され、上記内側弁部材を軸方向 に付勢し、上記内側弁部材に水圧が作用すると上記内側弁部材を摺動させ、上記 第 2流路の断面積を減少させるように縮む内側コイルばねと、  The second valve is disposed between the outer valve member and the inner valve member, urges the inner valve member in the axial direction, and slides the inner valve member when water pressure acts on the inner valve member. An inner coil spring that shrinks to reduce the cross-sectional area of the path;
を有することを特徴とする定流量弁。  A constant flow valve characterized by comprising:
[2] 上記内側コイルばねのばね定数は、上記外側コイルばねのばね定数よりも大きい 請求項 1記載の定流量弁。 2. The constant flow valve according to claim 1, wherein a spring constant of the inner coil spring is larger than a spring constant of the outer coil spring.
[3] 上記外側弁部材は、上記外側弁部材を横断するように延びるアーチ部と、このァー チ部に形成され上記内側弁部材を軸方向に摺動可能に支持する支持突起と、を備 え、上記内側弁部材には、上記支持突起を摺動可能に受け入れる凹部が形成され ている請求項 1又は 2に記載の定流量弁。 [3] 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. The constant flow valve according to claim 1 or 2, wherein the inner valve member is formed with a recess for slidably receiving the support protrusion.
[4] 上記アーチ部は、上記外側弁部材の下流側を整流するように翼状に形成されてい る請求項 3記載の定流量弁。 4. The constant flow valve according to claim 3, wherein the arch portion is formed in a wing shape so as to rectify the downstream side of the outer valve member.
[5] 上記第 1流路又は上記第 2流路は、それらの流路断面積が最も減少した場合にお いても通水状態に維持される請求項 1又は 2に記載の定流量弁。 [5] The constant flow valve according to claim 1 or 2, wherein the first flow path or the second flow path is maintained in a water passage state even when the cross-sectional area of the flow paths is the smallest.
[6] 上記外側弁部材の支持突起の下流側端部は、上流側から下流側に向力つて広が り形状に形成され、上記第 2流路からの噴流を分散させる噴流分散部を備えて 、る 請求項 3乃至 5の何れか 1項に記載の定流量弁。 [6] The downstream end portion of the support protrusion of the outer valve member is widened from the upstream side to the downstream side. The constant flow valve according to any one of claims 3 to 5, further comprising a jet dispersion portion that is formed in a circular shape and disperses the jet flow from the second flow path.
[7] 上記内側弁部材の下流側端部には、常に一定の流路断面積を有する第 3流路が 形成され、この第 3流路は噴流を分散させるように構成されている請求項 1又は 2に 記載の定流量弁。 [7] The third flow path having a constant flow path cross-sectional area is always formed at the downstream end of the inner valve member, and the third flow path is configured to disperse the jet flow. Constant flow valve as described in 1 or 2.
[8] 上記内側コイルばね又は上記外側コイルばねの座卷部のコイルばね素線には、振 動による騒音を防止する騒音防止手段が設けられている請求項 1乃至 7の何れか 1 項に記載の定流量弁。  [8] According to any one of claims 1 to 7, wherein the coil spring element wire of the inner coil spring or the outer coil spring has a noise preventing means for preventing noise caused by vibration. The constant flow valve described.
[9] 上記騒音防止手段は、上記内側コイルばね又は上記外側コイルばねの座卷部の コイルばね素線とその隣り合うコイルばね素線とを連結するように両コイルばね素線 に一体的に取り付けられているばね素線連結弾性部材によって構成されている請求 項 8記載の定流量弁。  [9] The noise prevention means is integrated with both coil spring strands so as to connect the coil spring strands of the inner coil spring or the outer flange of the outer coil spring and the adjacent coil spring strands. 9. The constant flow valve according to claim 8, wherein the constant flow valve is constituted by an attached spring wire connecting elastic member.
[10] 上記外側弁部材の支持突起と上記内側弁部材の凹部には、上記内側弁部材の軸 方向の共振を抑制する共振抑制手段が設けられている請求項 3乃至 6の何れか 1項 に記載の定流量弁。  10. The resonance suppression means for suppressing resonance in the axial direction of the inner valve member is provided in the support protrusion of the outer valve member and the recess of the inner valve member. The constant flow valve described in 1.
[11] 上記内側コイルばね又は上記外側コイルばねの端部には、弾性部材が配置されて いる請求項 1乃至 8の何れか 1項に記載の定流量弁。  11. The constant flow valve according to any one of claims 1 to 8, wherein an elastic member is disposed at an end of the inner coil spring or the outer coil spring.
[12] 上記外側弁部材又は上記内側弁部材の下流側部分には、円周方向に突出する板 状の複数の弁体脚部が形成され、これらの弁体脚部は、上記定流量弁本体に対す る上記外側弁部材の摺動又は上記外側弁部材に対する上記内側弁部材の摺動を 案内するように構成されて 、る請求項 1又は 2に記載の定流量弁。  [12] A plurality of plate-like valve body legs projecting in the circumferential direction are formed on the downstream side portion of the outer valve member or the inner valve member, and these valve body legs are formed by the constant flow valve. 3. The constant flow valve according to claim 1, wherein the constant flow valve is configured to guide sliding of the outer valve member relative to a main body or sliding of the inner valve member relative to the outer valve member.
[13] 上記外側弁部材又は上記内側弁部材の弁体脚部には、径方向に突出する突部が 形成され、この突部は、上記外側弁部材を上記定流量弁本体に係止又は上記内側 弁部材を上記外側弁部材に係止するように構成されている請求項 12に記載の定流  [13] The valve body leg portion of the outer valve member or the inner valve member is formed with a protruding portion that protrudes in the radial direction. The constant flow according to claim 12, wherein the inner valve member is configured to be locked to the outer valve member.
PCT/JP2006/305088 2005-03-18 2006-03-15 Constant flow rate valve WO2006100973A1 (en)

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