JP5501755B2 - Constant flow valve - Google Patents

Description

  The present invention relates to a constant flow valve, and more particularly, to a constant flow valve that utilizes a drag force applied to a valve body by a fluid flow.

Conventionally, various constant flow valves have been proposed in order to keep the fluid flow rate constant.
By the way, the conventional constant flow valve uses the differential pressure of the fixed orifice as a principle of operation (see Patent Document 1), uses the differential pressure of the variable orifice and the balance of the spring (see Patent Document 2), There are some that use deformation of an elastic body (see Patent Documents 3 and 4).
However, the conventional constant flow valve has a problem that the flow rate of the fluid fluctuates due to a change in the pressure of the fluid, and that it cannot be adapted to a large flow rate.

JP 54-71432 A Japanese Patent Laid-Open No. 3-117788 Japanese Patent Laid-Open No. 8-4943 JP 11-336922 A

  In view of the problems of the conventional constant flow valve described above, the present invention is less susceptible to changes in fluid pressure and can be adapted to large flow rates by utilizing the drag applied to the valve body by the flow of fluid. The object is to provide a constant flow valve.

To achieve the above object, the constant flow valve of the present invention, by movably disposed mosquitoes-up-shaped valve body fluid passage, the moving direction of the valve body of the cylindrical valve body support A constant flow valve that targets gas as a fluid that changes the cross-sectional area of the flow path opening formed along the flow path, and forms a spring accommodating chamber over the valve body and the valve body support, and the spring accommodating chamber to dispose the spring biasing the valve element, facing the upstream side of the moving direction of the passage opening the valve body of the static pressure of the fluid before vacuum that will be vacuum me by the change in the cross-sectional area of the One end side of the valve body that becomes the pressure receiving surface of the fluid and the inner surface of the valve body as the other end side of the valve body that becomes the pressure receiving surface of the fluid facing the downstream side and the end surface that is applied to the flow path opening of the valve body are received as static pressure is equal, and a bus I accommodating chamber and the fluid flow path, communicated with the fluid passage formed in the valve body, the valve body The end surface of the passage opening is formed as an inclined surface facing the fluid side before decompression, and the pressure receiving surface facing the upstream side and the pressure receiving surface facing the downstream side of the valve body to which the static pressure of the fluid after decompression is applied are eliminated. Thus, the force due to the static pressure of the fluid applied in the moving direction of the valve body is balanced, and the force applied to the valve body by the flow of the fluid is attached with a spring that urges the valve body in a direction that balances the force. By balancing with the force, the cross-sectional area of the flow path opening formed along the moving direction of the valve body of the cylindrical valve body support is changed, and the fluid flow rate is kept constant regardless of the fluid pressure change. It was made to do.
In order to achieve the same object, the constant flow valve of the present invention has a cup-like valve body that is movably disposed in the fluid flow path, so that the valve body moves in the direction of movement of the valve body on the tip side of the end face of the valve body. A constant flow valve that targets gas as a fluid that changes a cross-sectional area of a flow path opening formed along the flow path, and forms a spring accommodation chamber over the valve body and the valve body support, and the spring accommodation A spring for urging the valve body is arranged in the chamber, and the static pressure of the fluid before decompression is reduced by the change in the cross-sectional area of the flow path opening. Static pressure received by one end side of the valve body that becomes the pressure receiving surface and the inner surface of the valve body as the other end side of the valve body that faces the downstream side and becomes the pressure receiving surface of the fluid and the end surface that covers the flow path opening of the valve body And the spring accommodating chamber and the fluid flow path are communicated with each other by a fluid passage formed in the valve body. The end surface of the valve opening of the valve body is formed on an inclined surface facing the fluid side before pressure reduction, and the pressure receiving surface facing the upstream side and the pressure receiving side facing the downstream side of the valve body where the static pressure of the fluid after pressure reduction is applied By eliminating the surface, it is configured to balance the force due to the static pressure of the fluid in the moving direction of the valve body, and the force applied to the valve body by the flow of the fluid is urged in the direction that balances the force By balancing with the urging force of the spring, the cross-sectional area of the flow path opening formed along the moving direction of the valve body is changed on the distal end side of the end face of the valve body, and the flow of the fluid is changed regardless of the fluid pressure change. It is characterized in that the flow rate is kept constant.

  According to the constant flow valve of the present invention, the flow path formed along the moving direction of the valve body by operating and balancing the valve body disposed in the fluid flow path by the drag applied to the valve body by the flow of fluid. By changing the cross-sectional area of the opening to keep the fluid flow rate constant regardless of the fluid pressure change, it is less susceptible to fluid pressure changes and uses deformation of orifices and elastic bodies. Therefore, it can be applied to large flow rates.

  Then, by balancing the drag acting on the valve body with the biasing force of the spring that biases the valve body in the direction that balances the drag, the biasing means that biases the valve body in the direction that balances the drag can be simplified. Can be configured.

It is structure explanatory drawing which shows the 1st reference example of a constant flow valve. It is structure explanatory drawing which shows 1st Example of the constant flow valve of this invention. It is structure explanatory drawing which shows 2nd Example of the constant flow valve of this invention. It is structure explanatory drawing which shows the 2nd reference example of a constant flow valve. It is structure explanatory drawing which shows the 3rd reference example of a constant flow valve. It is structure explanatory drawing which shows the 4th reference example of a constant flow valve. It is structure explanatory drawing which shows 3rd Example of the constant flow valve of this invention. It is structure explanatory drawing which shows the 5th reference example of a constant flow valve. It is structure explanatory drawing which shows the 6th reference example of a constant flow valve. It is structure explanatory drawing which shows the 7th reference example of a constant flow valve. It is structure explanatory drawing which shows the 8th reference example of a constant flow valve. It is structure explanatory drawing which shows the 9th reference example of a constant flow valve. It is structure explanatory drawing which shows the 10th reference example of a constant flow valve. It is structure explanatory drawing which shows the 11th reference example of a constant flow valve. It is structure explanatory drawing which shows the 12th reference example of a constant flow valve. It is structure explanatory drawing which shows the 13th reference example of a constant flow valve. It is explanatory drawing which shows one Example of the inert gas fire extinguishing equipment to which the constant flow valve of this invention is applied. It is explanatory drawing which shows the arrangement | positioning position of a constant flow valve.

  Hereinafter, embodiments of the constant flow valve of the present invention will be described with reference to the drawings.

FIG. 1 shows a first reference example of a constant flow valve.
By operating and balancing the valve body 11 disposed in the fluid flow path 14 by the drag D applied to the valve body 11 by the flow of fluid, the flow path opening 12 formed along the moving direction of the valve body 11 is interrupted. The area is changed, and the flow rate of the fluid is kept substantially constant regardless of the change in the pressure of the fluid.
Here, the drag D applied to the valve body 11 can be obtained by the following equation (1).
D = (ρ / 2) U ² FC _D
[rho: the density of the fluid U: fluid velocity F: projected area of the valve body 11 to a plane perpendicular to the flow of the fluid C _D: the shape of the drag coefficient (valve body 11, the attitude, Nameraara and Reynolds number of the surface Dimensionless number determined by Re)
In this reference example, the drag applied to the valve body 11 is balanced with the urging force of the spring 13 (also in the following embodiments) as an elastic body that urges the valve body 11 in a direction that balances the drag D. I have to.

More specifically, the constant flow valve 1 is configured such that the cup-like valve body 11 disposed in the fluid flow path 14 is dragged against one end side (outer surface side) 11a of the valve body 11 by the fluid flow, By balancing the urging force of the spring 13 applied to the other end side (inner surface side) 11b of the body 11, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11 is substantially changed. The fluid flow rate is maintained substantially constant regardless of the fluid pressure change.
Then, the valve housing 11 c formed through the valve body 11 provided with the spring 13 and the valve body support 11 e and the fluid flow path 14 are communicated with each other by a fluid passage 11 d formed in the valve body 11, thereby allowing the valve body 11. The differential pressure is prevented from acting on.

  In the constant flow valve 1, when the velocity (flow rate) of the fluid flowing through the fluid flow path 14 is increased, the valve body 11 moves and balances in the direction of decreasing the cross-sectional area of the flow path opening 12, If the speed (flow rate) of the fluid flowing through the fluid flow path 14 is reduced while the increase in the speed (flow rate) is suppressed, the valve element 11 moves in the direction of increasing the cross-sectional area of the flow path opening 12. Therefore, the fluid flow rate is maintained substantially constant by suppressing the fluid velocity (flow rate) from decreasing.

FIG. 2 shows a first embodiment of the constant flow valve of the present invention.
The constant flow valve 1 includes a cup-shaped valve body 11 disposed in a fluid flow path 14, a drag force applied to one end side (outer surface side) 11 a of the valve body 11 by a fluid flow, and the other end side of the valve body 11. By balancing the biasing force of the spring 13 applied to the (inner surface side) 11b, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11 is substantially changed, and the pressure of the fluid is changed. Regardless, the flow rate of the fluid is kept substantially constant.
The spring housing chamber 11c formed over the valve body 11 and the valve body support body 11e provided with the spring 13 and the fluid flow path 14 are communicated with each other through the fluid passage 11d formed in the valve body 11, thereby reducing the downstream side. oriented fluid inside surface 11b of the valve body 11 as a pressure receiving surface (here of the inner surface 11b of the valve body 11, and an inner surface 11b ₁ constituting the spring accommodating chamber 11c which is disposed a spring 13 for urging the valve body 11 The inner surface 11b ₂ is located on the outer peripheral side, and the same applies to the following embodiments.) And the end surface 15 of the valve body 11 on the flow path opening 12 is changed in the cross-sectional area of the flow path opening 12. Thus, the static pressure of the fluid before the pressure reduction is applied so that the differential pressure does not act on the valve body 11.
The operation of this embodiment is the same as that of the constant flow valve of the first reference example.

FIG. 3 shows a second embodiment of the constant flow valve of the present invention.
The constant flow valve 1 includes a cup-shaped valve body 11 disposed in a fluid flow path 14, a drag force applied to one end side (outer surface side) 11 a of the valve body 11 by a fluid flow, and the other end side of the valve body 11. By balancing the biasing force of the spring 13 applied to the (inner surface side) 11b, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11 is substantially changed, and the pressure of the fluid is changed. Regardless, the flow rate of the fluid is kept substantially constant.
Then, the valve housing 11 c formed through the valve body 11 provided with the spring 13 and the valve body support 11 e and the fluid flow path 14 are communicated with each other by a fluid passage 11 d formed in the valve body 11, thereby allowing the valve body 11. The differential pressure is prevented from acting on.
The operation of this embodiment is the same as that of the constant flow valve of the first reference example.

FIG. 4 shows a second reference example of the constant flow valve.
The constant flow valve 1 includes a cup-shaped valve body 11 disposed in a fluid flow path 14, a drag force applied to one end side (outer surface side) 11 a of the valve body 11 by a fluid flow, and the other end side of the valve body 11. By balancing the biasing force of the spring 13 applied to the (inner surface side) 11b, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11 is substantially changed, and the pressure of the fluid is changed. Regardless, the flow rate of the fluid is kept substantially constant.
Then, the spring housing chamber 11c formed in the valve body 11 provided with the spring 13 and the fluid flow path 14 are communicated with each other by a fluid passage 11d that also serves as the fluid flow path 14 formed in the valve body 11, so that the valve body No differential pressure is applied to 11.
The operation of this reference example is the same as that of the constant flow valve of the first reference example.

FIG. 5 shows a third reference example of the constant flow valve.
The constant flow valve 1 includes a cup-shaped valve body 11 disposed in a fluid flow path 14, a drag force applied to one end side (outer surface side) 11 a of the valve body 11 by a fluid flow, and the other end side of the valve body 11. By balancing the biasing force of the spring 13 applied to the (inner surface side) 11b, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11 is substantially changed, and the pressure of the fluid is changed. Regardless, the flow rate of the fluid is kept substantially constant.
Then, the spring housing chamber 11c formed over the valve body 11 provided with the spring 13 and the valve body support 11e and the fluid flow path 14 are communicated with each other by a fluid passage 11d also serving as the fluid flow path 14 formed in the valve body 11. By doing so, the differential pressure is prevented from acting on the valve body 11.
The operation of this reference example is the same as that of the constant flow valve of the first reference example.

FIG. 6 shows a fourth reference example of the constant flow valve.
The constant flow valve 1 includes a cup-like valve body 11 disposed in a fluid flow path 14, a drag force applied to one end side (inner surface side) 11 a of the valve body 11 by a fluid flow, and the other end side of the valve body 11. By balancing the urging force of the spring 13 applied to the (outer surface side) 11b, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11 is substantially changed, and the pressure of the fluid is changed. Regardless, the flow rate of the fluid is kept substantially constant.
Then, the spring housing chamber 11c formed in the valve body support 11e provided with the spring 13 and the fluid flow path 14 are communicated with each other by a fluid passage 11d formed in the valve body 11, so that a differential pressure is applied to the valve body 11. I try not to work.
The operation of this reference example is the same as that of the constant flow valve of the first reference example.

FIG. 7 shows a third embodiment of the constant flow valve of the present invention.
The constant flow valve 1 includes a cup-shaped valve body 11 disposed in a fluid flow path 14, a drag force applied to one end side (outer surface side) 11 a of the valve body 11 by a fluid flow, and the other end side of the valve body 11. By balancing the biasing force of the spring 13 applied to the (inner surface side) 11b, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11 is substantially changed, and the pressure of the fluid is changed. Regardless, the flow rate of the fluid is kept substantially constant.
Then, the valve housing 11 c formed through the valve body 11 provided with the spring 13 and the valve body support 11 e and the fluid flow path 14 are communicated with each other by a fluid passage 11 d formed in the valve body 11, thereby allowing the valve body 11. The differential pressure is prevented from acting on.
The operation of this embodiment is the same as that of the constant flow valve of the first reference example.

FIG. 8 shows a fifth reference example of the constant flow valve.
The constant flow valve 1 includes a cup-shaped valve body 11 disposed in a fluid flow path 14, a drag force applied to one end side (outer surface side) 11 a of the valve body 11 by a fluid flow, and the other end side of the valve body 11. By balancing the biasing force of the spring 13 applied to the (inner surface side) 11b, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11 is substantially changed, and the pressure of the fluid is changed. Regardless, the flow rate of the fluid is kept substantially constant.
Then, the valve housing 11 c formed through the valve body 11 provided with the spring 13 and the valve body support 11 e and the fluid flow path 14 are communicated with each other by a fluid passage 11 d formed in the valve body 11, thereby allowing the valve body 11. The differential pressure is prevented from acting on.
The operation of this reference example is the same as that of the constant flow valve of the first reference example.

FIG. 9 shows a sixth reference example of the constant flow valve.
The constant flow valve 1 includes a ring-shaped valve body 11 disposed in a fluid flow path 14, a drag applied to the one end side 11 a of the valve body 11 by a fluid flow, and a spring applied to the other end side 11 b of the valve body 11. 13, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11 is substantially changed, and the flow rate of the fluid is substantially constant regardless of the pressure change of the fluid. It is intended to be held in.
Then, by communicating the spring accommodating chamber 11c formed in the valve body support 11e provided with the spring 13 and the fluid flow path 14 by the fluid passage 11d also serving as the fluid flow path 14 formed in the valve body 11, The differential pressure is prevented from acting on the valve body 11.
The operation of this reference example is the same as that of the constant flow valve of the first reference example.

FIG. 10 shows a seventh reference example of the constant flow valve.
This constant flow valve 1 has a rod-shaped cylindrical valve body 11 disposed in a fluid flow path 14 and a drag force applied to the one end side 11a of the flange portion 11f of the valve body 11 by a fluid flow. By balancing the urging force of the spring 13 applied to the other end 11b of the portion 11f, the cross-sectional area of the flow passage opening 12 formed along the moving direction of the valve body 11 is substantially changed, and the pressure of the fluid The flow rate of the fluid is kept substantially constant regardless of the change.
The spring housing chamber 11c formed between the flange 11f of the valve body 11 provided with the spring 13 and the valve body support 11e and the fluid flow path 14 are communicated with each other by a fluid passage 11d formed in the valve body 11. This prevents the differential pressure from acting on the valve body 11.
The operation of this reference example is the same as that of the constant flow valve of the first reference example.

FIG. 11 shows an eighth reference example of the constant flow valve.
The constant flow valve 1 includes a valve body 11 disposed in a fluid flow path 14, a drag force applied to one end side 11 a of the valve body 11 by a fluid flow, and a spring 13 applied to the other end side 11 b of the valve body 11. By balancing the force, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11 is substantially changed, and the flow rate of the fluid is kept substantially constant regardless of the change in the pressure of the fluid. It is what I did.
Then, the spring accommodating chamber 11c formed on the other end side 11b of the valve body 11 provided with the spring 13 and the fluid flow path 14 are communicated with each other by a fluid passage 11d formed in the valve body 11, thereby allowing the valve body 11 to The differential pressure is prevented from acting.
The operation of this reference example is the same as that of the constant flow valve of the first reference example.

FIG. 12 shows a ninth reference example of the constant flow valve.
The constant flow valve 1 includes a valve body 11 provided with a flanged cylindrical body 11g disposed in the fluid flow path 14, and a drag force applied to one end side 11a of the flanged cylindrical body 11g of the valve body 11 by a fluid flow. By balancing the urging force of the spring 13 applied to the flange 11h of the flanged cylindrical body 11g of the valve body 11, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11 is substantially reduced. The flow rate of the fluid is kept substantially constant regardless of the change in the pressure of the fluid.
And while forming the fluid channel | path 11d in the valve body 11, the spring accommodating chamber 11i formed between the collar part 11h of the flanged cylinder 11g of the valve body 11 which arrange | positioned the spring 13, and the valve body support body 11e, The passage 15 formed in the main body casing 10 communicates with the atmosphere so that no differential pressure acts on the valve body 11.
The operation of this reference example is the same as that of the constant flow valve of the first reference example.

FIG. 13 shows a tenth reference example of the constant flow valve.
The constant flow valve 1 includes a valve body 11 disposed in a fluid flow path 14, a drag force applied to one end side 11 a of the valve body 11 by a fluid flow, and a spring 13 applied to the other end side 11 b of the valve body 11. By balancing the force, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11 is substantially changed, and the flow rate of the fluid is kept substantially constant regardless of the change in the pressure of the fluid. It is what I did.
Then, the spring accommodating chamber 11c formed on the other end side 11b of the valve body 11 provided with the spring 13 and the fluid flow path 14 are communicated with each other by a fluid passage 11d formed in the valve body 11, thereby allowing the valve body 11 to The differential pressure is prevented from acting.
Here, the spring 13 is configured to be able to arbitrarily adjust the magnitude of the urging force by the adjusting member 16, thereby increasing or decreasing the flow rate of the fluid, that is, increasing the magnitude of the urging force. By doing so, the flow rate of the fluid is increased, and on the other hand, the flow rate of the fluid can be decreased by reducing the magnitude of the urging force.
Further, the valve body 11 is held by a spring 11j so as to be positioned within a predetermined range.
The operation of this reference example is the same as that of the constant flow valve of the first reference example.

FIG. 14 shows an eleventh reference example of the constant flow valve.
This reference example uses a magnet 16a as a biasing means for biasing the valve body 11 in a direction commensurate with the drag applied to the valve body 11, instead of the spring 13 of each of the above embodiments and reference examples. Thus, the problem of spring breakage due to fatigue can be eliminated.
The constant flow valve 1 includes a ring-shaped valve body 11 disposed in a fluid flow path 14, a drag applied to the one end side 11 a of the valve body 11 by a fluid flow, and a magnet applied to the other end side 11 b of the valve body 11. By balancing the urging force of 16a, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11 is substantially changed, and the flow rate of the fluid is substantially constant regardless of the change in the pressure of the fluid. It is intended to be held in.
Then, the intermediate chamber 11k formed in the valve body support 11e provided with the magnet 16a and the fluid flow path 14 are communicated with each other by a fluid passage 11d that also serves as the fluid flow path 14 formed in the valve body 11, so that the valve The differential pressure is prevented from acting on the body 11.
Here, the magnet 16a as an urging means for urging the valve body 11 has the same poles, for example, N poles, facing the other end side 11b of the valve body 11 and the valve body support 11e. Try to arrange.
The operation of this reference example is the same as that of the constant flow valve of the first reference example.

FIG. 15 shows a twelfth reference example of the constant flow valve.
In this reference example, similarly to the eleventh reference example, a magnet 16b is used as a biasing means that biases the valve body 11 in a direction that balances the drag applied to the valve body 11.
The constant flow valve 1 includes a ring-shaped valve body 11 disposed in a fluid flow path 14, a drag acting on one end side 11 a of the valve body 11 due to a fluid flow, and a magnet applied to the same one end side 11 a of the valve body 11. By balancing the urging force of 16b, the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve element 11 is substantially changed, and the flow rate of the fluid is substantially constant regardless of the change in the pressure of the fluid. It is intended to be held in.
Then, the intermediate chamber 11k formed in the valve body support 11e and the fluid flow path 14 are communicated with each other by a fluid passage 11d that also serves as the fluid flow path 14 formed in the valve body 11, so that a differential pressure is applied to the valve body 11. I try not to work.
Here, the magnet 16b as an urging means for urging the valve body 11 is opposed to one end side 11a of the valve body 11 and the main body casing 10 on the upstream side thereof with different poles, for example, an S pole and an N pole ( In this reference example, they are arranged so as to face each other with the magnetic body 16c therebetween.
The operation of this reference example is the same as that of the constant flow valves of the first reference example and the eleventh reference example.

FIG. 16 shows a thirteenth reference example of the constant flow valve.
This reference example uses magnets 16a and 16b as urging means for urging the valve body 11 in a direction commensurate with the drag applied to the valve body 11, as in the eleventh and twelfth reference examples. .
The constant flow valve 1 includes a ring-shaped valve body 11 disposed in a fluid flow path 14, a drag applied to the one end side 11 a of the valve body 11 by a fluid flow, and a magnet applied to the other end side 11 b of the valve body 11. 16a and the biasing force of the magnet 16b applied to the same one end side 11a of the valve body 11 are substantially changed to change the cross-sectional area of the flow path opening 12 formed along the moving direction of the valve body 11, The flow rate of the fluid is kept substantially constant regardless of the pressure change of the fluid.
Then, the intermediate chamber 11k formed in the valve body support 11e and the fluid flow path 14 are communicated with each other by a fluid passage 11d that also serves as the fluid flow path 14 formed in the valve body 11, so that a differential pressure is applied to the valve body 11. I try not to work.
Here, the magnet 16a as an urging means for urging the valve body 11 has the same poles, for example, N poles, facing the other end side 11b of the valve body 11 and the valve body support 11e. On the other hand, the magnet 16b is opposed to the one end side 11a of the valve body 11 and the main body casing 10 on the upstream side thereof with different poles, for example, the S pole and the N pole (in this reference example, the magnetic body 16c). So as to be opposed to each other.
The operation of this reference example is the same as the constant flow valves of the first reference example, the eleventh reference example, and the twelfth reference example.

FIG. 17 shows an embodiment of an inert gas fire extinguishing facility to which the constant flow valve of the present invention is applied.
This inert gas fire extinguishing equipment has a plurality of, for example, two fire extinguishing sections 6-1 and 6-2, and, for example, nitrogen gas is used as an inert gas fire extinguishing agent, and this is pressurized to a high pressure gas container. Is used as a fire extinguishing agent storage container B1 by storing in a fire extinguishing facility in a state filled with (18 MPa at 35 ° C.). The inert gas fire extinguishing equipment of this embodiment includes three fire extinguishing agent storage containers B1, and each fire extinguishing agent storage container B1 is connected to a connecting pipe 3 via a container valve 2, and further connected to the connecting pipe 3. It connects to the one collecting pipe 4, and this collecting pipe 4 is connected to main piping 5-1, 5-2 extended to each fire extinguishing division 6-1, 6-2. Selection valves 9-1 and 9-2 are disposed in the main pipes 5-1 and 5-2 so that an inert gas fire extinguisher is selectively sent to the fire extinguishing sections 6-1 and 6-2. Main pipes 5-1 and 5-2 extending to the fire extinguishing sections 6-1 and 6-2 are connected to branch pipes 7-1 and 7-2 respectively disposed in the fire extinguishing sections 6-1 and 6-2. The branch pipes 7-1 and 7-2 are connected to fire extinguishing agent jet heads 8-1 and 8-2 arranged in a plurality of positions in the fire extinguishing sections 6-1 and 6-2.

By the way, since each fire extinguishing section 6-1 and 6-2 usually differ in the volume, naturally the quantity of the inert gas fire extinguishing agent required for extinguishing fire also differs. For this reason, the diameters of the main pipes 5-1 and 5-2 are changed according to the volumes of the fire extinguishing sections 6-1 and 6-2, and the fire extinguishing sections 6-1 and 6-6 to be extinguished in the event of a fire. The inert gas fire extinguishing equipment is configured so that the number of fire extinguishing agent storage containers B1 corresponding to 2 is opened.
In the figure, 10-1 and 10-2 are selection valve opening devices, 11-1 and 11-2 are start-up gas containers, 12-1 and 12-2 are start-up gas container opening solenoids, 13- Reference numerals 1 and 13-2 denote start-up gas pipes for controlling the selection valves 9-1 and 9-2 and the opening of a constant-pressure gas container B2 as a constant-pressure gas source to be described later. 2 and the non-return valves 14-1 and 14-2 are arranged at appropriate positions in the middle of the connection. The numbers 1 and 2 at the end of these members correspond to the numbers 1 and 2 at the end of the fire extinguishing section, respectively.

In this case, the container valve 2 is a pressure-reducing valve that regulates the gas pressure P of the inert gas extinguisher on the discharge side of the container valve 2 to be equal to or lower than the reference gas pressure P0 defined by the gas pressure P1 of the constant pressure gas source. It is desirable.
The pressure control valve is based on the gas pressure P of the inert gas extinguisher on the discharge side of the pressure control valve until the pressure P2 of the inert gas fire extinguisher in the fire extinguisher storage container B1 drops below the reference gas pressure P0. Since it has a function of maintaining the gas pressure P0, even when the pressure P2 of the inert gas extinguisher in the extinguishing agent storage container decreases due to the release of the inert gas extinguishing agent, the inertness on the discharge side of the pressure control valve By maintaining the gas pressure P of the gas extinguishing agent at the reference gas pressure P0, the discharge amount of the inert gas extinguishing agent can be kept constant.
On the other hand, although the pressure control valve has the above-mentioned advantages, the discharge amount of the inert gas fire extinguisher largely fluctuates within the set release time, specifically, the inert gas fire extinguisher is discharged from the start of the release of the inert gas fire extinguisher. While 1/2 of the set release time (for example, 1 minute) has not elapsed, the discharge amount of the inert gas fire extinguisher decreases as the pressure P2 of the inert gas fire extinguisher in the fire extinguisher storage container B1 decreases. The problem is that the capacity of the inert gas fire extinguishing equipment's fire extinguishing agent distribution path is not fully utilized, and a large amount of inert gas fire extinguishing agent is released in a short time from the start of releasing the inert gas fire extinguishing agent. Therefore, there is a problem that it is necessary to increase the capacity (opening area) of the pressure avoidance damper 16 provided to prevent the internal pressure in the fire extinguishing sections 6-1 and 6-2 from increasing.

  Therefore, in this embodiment, an appropriate position of the fire extinguishing agent flow path from the fire extinguishing agent storage container B1 to the fire extinguishing agent jet head 8, in this embodiment, the collecting pipe on the upstream side of the selection valves 9-1 and 9-2. 4 is provided with the constant flow valve 1 to control the flow rate of the inert gas extinguishing agent, so that at least 1/2 of the set release time of the inert gas extinguishing agent from the start of the inert gas extinguishing agent release. More preferably, the discharge amount of the inert gas extinguishing agent is kept substantially constant until 2/3 has elapsed.

  In this case, the inert gas extinguishing agent stored in the extinguishing agent storage container B1 is stored in the extinguishing agent storage container B1 within the set release time of the inert gas extinguishing agent so that the inert gas extinguishing agent can be used effectively. It is desirable to release more than 90% of the inert gas fire extinguishing agent being used.

  The constant flow valve 1 has a function of maintaining the discharge amount of the inert gas extinguishing agent substantially constant regardless of the fluctuation (decrease) in the gas pressure Pin of the inert gas extinguishing agent on the introduction side of the constant flow valve 1. As long as the structure is not particularly limited, various constant flow valves as shown in FIGS. 1 to 16 can be used.

  In addition to the collecting pipe 4 on the upstream side of the selection valves 9-1 and 9-2, the position where the constant flow valve 1 is disposed is integrated with the fire extinguishing agent ejection head 8 as shown in FIG. 18B, as shown in FIG. 18B, disposed on the branch pipe 7 upstream of the fire extinguishing agent jet head 8, or as shown in FIG. 18C, downstream of the selection valve 9. 18 (d), as shown in FIG. 18 (d), disposed in the connecting pipe 3 downstream of the container valve 2, or as shown in FIG. 18 (e) It can be set as an arbitrary position on the flow path of the fire extinguishing agent from the fire extinguishing agent storage container B1 to the fire extinguishing agent ejection heads 8-1, 8-2.

  This inert gas fire extinguishing equipment is configured by controlling the flow rate of the inert gas fire extinguishing agent by arranging the constant flow valve 1 at an appropriate position in the fire extinguishing agent flow path from the fire extinguishing agent storage container B1 to the fire extinguishing agent jet head 8. The discharge amount of the inert gas fire extinguisher is from the start of the release of the inert gas fire extinguisher until at least 1/2 of the set release time of the inert gas fire extinguisher, more preferably 2/3. Since it is kept at a substantially constant (here, “substantially constant” includes fluctuations of about ± 20%), the setting of the inert gas extinguishing agent is started from the start of the release of the inert gas extinguishing agent. The discharge amount of the inert gas fire extinguisher decreases as the pressure P2 of the inert gas fire extinguisher in the fire extinguisher storage container B1 decreases while 1/2 of the discharge time, more preferably 2/3 does not elapse. Dispensing fire extinguishing agent for inert gas fire extinguishing equipment The capacity of the road can be fully utilized and a large amount of inert gas extinguishing agent is not released in a short time from the start of releasing the inert gas extinguishing agent, so that the internal pressure in the fire extinguishing sections 6-1 and 6-2 increases. Therefore, it is not necessary to increase the capacity (opening area) of the pressure-reducing damper 16 provided to prevent this.

Further, in this embodiment, the pressure regulating valve that regulates the gas pressure P of the inert gas extinguishing agent on the discharge side of the container valve 2 to the reference gas pressure P0 or less defined by the gas pressure P1 of the constant pressure gas source. And a constant pressure valve (1) for controlling the flow rate of the inert gas extinguishing agent at an appropriate position in the extinguishing agent flow path from the extinguishing agent storage container B1 to the extinguishing agent ejection head 8, thereby controlling the pressure control valve ( The pressure of the inert gas extinguishing agent downstream of the container valve 2) and the constant flow valve 1 is sequentially reduced, and a secondary device downstream of the pressure control valve (container valve 2) and the constant flow valve 1 is required. Since the pressure resistance is reduced, it is not necessary to increase the pressure resistance grade of the secondary equipment of the fire extinguishing equipment, and the equipment cost can be reduced. The degree of pressure reduction by the pressure control valve (container valve 2) and the constant flow valve 1 should be designed comprehensively including the pressure resistance grade of the secondary equipment of the fire extinguishing equipment, In the case of existing fire extinguishing equipment, it should be designed according to the pressure resistance grade of the secondary equipment of the existing fire extinguishing equipment.
In this embodiment, the example in which the pressure control valve (container valve 2) is used in combination has been described. However, the same effect can be obtained with the constant flow valve 1 alone.

As described above, the constant flow valve of the present invention has been described based on a plurality of embodiments. However, the present invention is not limited to the configurations described in the above embodiments, and the configurations are appropriately set within the scope of the present invention. Ru can be changed.

The constant flow valve of the present invention has a characteristic that it is not easily affected by a change in the pressure of the fluid and can be adapted to a large flow rate by utilizing a drag applied to the valve body by the flow of the fluid. from addition can be suitably used in applications of the constant flow valve of the inert gas fire extinguishing equipment, it can be widely used in the constant flow valve of the various applications that target gas.

DESCRIPTION OF SYMBOLS 1 Constant flow valve 10 Main body casing 11 Valve body 11c Spring accommodating chamber 11d Fluid passage 11k Intermediate chamber 12 Flow path opening 13 Spring (elastic body)
14 Fluid flow path 15 Passage 16a Magnet 16b Magnet

Claims (2)

By movably disposed mosquito-up shaped valve body (11) in the fluid flow path (14), formed along the moving direction of the valve body (11) of the cylindrical valve body support member (11e) The flow rate opening (12) is a constant flow valve that targets gas as a fluid that changes the cross-sectional area of the flow passage opening (12), and is applied to the valve body (11) and the valve body support (11e). ) is formed, is disposed a spring (13) for biasing the valve element (11) in the spring accommodation chamber (11c), it is depressurized I by the changes in the cross-sectional area of the flow passage opening (12) One end side (11a) of the valve body (11) which becomes the pressure receiving surface of the fluid facing the upstream side in the moving direction of the valve body (11) to which the static pressure of the fluid before depressurization is applied, and the downstream side of the fluid the inner surface _{(11b (11b 1, 11b 2} )) of the valve body of the other end of the valve body as a pressure receiving surface (11) (11) and the valve As static pressure flow openings (12) in such end face (15) and receives the (11) are equal, play it accommodating chamber (11c) fluid flow path (14), the valve (11) The end face (15) applied to the flow passage opening (12) of the valve body (11) is formed as an inclined surface facing the fluid side before pressure reduction, and is connected after the pressure reduction. By eliminating the pressure receiving surface facing the upstream side and the pressure receiving surface facing the downstream side of the valve body (11) to which the static pressure of the fluid is applied, the force due to the static pressure of the fluid applied in the moving direction of the valve body (11) is balanced. In this configuration, the force applied to the valve body (11) by the flow of fluid is balanced with the biasing force of the spring (13) that biases the valve body (11) in a direction that balances the force. Formed along the moving direction of the valve body (11) of the valve body support body (11e) The flow openings (12) to change the cross-sectional area of the constant flow valve, characterized in that so as to hold the flow rate of the fluid irrespective of the pressure variation of the fluid constant. By movably disposed mosquito-up shaped valve body (11) in the fluid flow path (14), formed along the moving direction of the valve body (11) on the distal end side of the end face of the valve body (11) The flow rate opening (12) is a constant flow valve that targets gas as a fluid that changes the cross-sectional area of the flow path opening (12), and is placed over the valve body (11) and the valve body support (11e). 11c) is formed, it is disposed a spring (13) for biasing the valve element (11) in the spring accommodation chamber (11c), vacuum I by the changes in the cross-sectional area of the flow passage opening (12) the valve body according the static pressure of the fluid before depressurization is Ru is one end side of the moving direction of the upstream side facing the valve body as a pressure receiving surface of the fluid in the (11) (11) (11a ), facing the downstream side fluid the inner surface _{(11b (11b 1, 11b 2} )) of the valve body of the other end of the pressure receiving surface and becomes the valve body (11) (11) and the valve As static pressure flow openings (12) in such end face (15) and receives the (11) are equal, play it accommodating chamber (11c) fluid flow path (14), the valve (11) The end face (15) applied to the flow passage opening (12) of the valve body (11) is formed as an inclined surface facing the fluid side before pressure reduction, and is connected after the pressure reduction. By eliminating the pressure receiving surface facing the upstream side and the pressure receiving surface facing the downstream side of the valve body (11) to which the static pressure of the fluid is applied, the force due to the static pressure of the fluid applied in the moving direction of the valve body (11) is balanced. The valve body is configured by balancing the force applied to the valve body (11) by the flow of fluid with the biasing force of the spring (13) that biases the valve body (11) in a direction that balances the force. It is formed along the moving direction of the valve body (11) on the tip side of the end face of (11) The flow openings (12) to change the cross sectional area of the constant flow valve characterized in that so as to hold the flow rate of the fluid irrespective of the pressure variation of the fluid constant.