JPH09244749A - Method and valve for flow rate control - Google Patents

Abstract

PROBLEM TO BE SOLVED: To put functions including a shutoff valve function, etc., in one equipment by coping with a case wherein the supply pressure of fluid varies and remotely performing proportional control over a flow rate. SOLUTION: A main valve body 5 at the center part of a diaphragm 6 is arranged opposite a main valve seat 4 halfway in a flow passage extending from a water intake 2 to a water outlet 3 to open and close the flow passage, and a primary pressure chamber 7, a back pressure chamber 8, and a secondary pressure chamber 9 are provided. The primary pressure chamber 7 and back pressure chamber 8 are linked by a communication hole 14 and the back pressure chamber 8 and secondary pressure chamber 9 are communicated by a pilot valve hole 5a. A control valve member 10 provided penetrating the pilot valve hole 5a is constituted by integrating a pilot valve 12 which closes the pilot valve hole 5a and a differential pressure plate 13 in a main valve opening 4a extending from the main valve seat 4 to the water outlet 3. A water outlet flow rate Q which can be set with a generated force F operating on the control valve member 10 is controlled with constant differential pressure ΔP3 corresponding to the generated force F to obtain relation Q∝A4 (ΔP3)<1/2> , where A4 is the area of an annular pass hole around the differential pressure plate 13 and ΔP3 is differential pressure across the differential pressure plate 13.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid (incompressible fluid) such as water, hot water or oil used in various devices and factory equipment.
The present invention relates to a flow control method that enables remote control of a flow rate by an electric signal, and a flow control valve using the flow control method.

[0002]

2. Description of the Related Art First, FIG. 1 shows a general arrangement of a water supply pipe and various control devices which are attached to various devices and factory equipment, etc. and extend to a flow control valve. As for the arrangement of the flow control valve and the control device, since the feed water pressure is constantly changing, as shown in FIG. 1, the pipe pattern (a) and the pipe pattern (b) depend on the function of the flow control valve. ). That is, the pipeline pattern (a) is a case where the flow rate control valve does not correspond to the fluctuating pressure, and the pipeline pattern (b) is a case where the flow rate control valve corresponds to the fluctuating pressure.

[0003] The arrangement of each control device in the pipeline pattern (a) includes a solenoid valve having a so-called shut-off valve function for completely preventing water from entering the pipeline from the upstream side, and a governor for controlling the fluctuating pressure to a constant pressure. (Pressure regulator) and a flow control valve. As a technique corresponding to such a pipeline pattern (a), for example, a technique disclosed in Japanese Patent Application Laid-Open No. 4-302789 is known. The arrangement of each device in the conduit pattern (b) is the solenoid valve and the flow control valve from the upstream side as well. In this case, since no governor is provided, the fluctuating pressure is directly introduced into the flow control valve. The case corresponding to such a pipeline pattern (b) is a case of a gas instead of an incompressible fluid, which cannot be applied as it is, for example, Japanese Patent Publication No. 63-43632. Is known.

[0004]

In the prior art described above, in the case of the pipeline pattern (a) and the pipeline pattern (b) of FIG. 1, these control devices are not only expensive, but also the devices and the like. The design man-hours and assembly man-hours for assembling into the equipment are very complicated, and the electric control circuit for controlling each control device in cooperation with each other is complicated, and furthermore, these circumstances From the viewpoint of production, there was a problem that the mass productivity was greatly reduced. For this reason, in the past, various methods have been tried to cope with the above-described control devices by one unit, but have not been successful yet.

The technique disclosed in Japanese Patent Application Laid-Open No. 4-302789 is a technique in which a closing valve function and a flow control valve function are combined by providing a special place in a single valve housing. It was not a fusion. Therefore, there is a problem that the valve housing becomes large and the cost increases. Further, in this structure, there is a problem that a governor is absolutely necessary, and one casing cannot cope with the conduit pattern (b).

The technique disclosed in Japanese Patent Publication No. 63-43632 does not have the above-mentioned closing valve function. That is, in the embodiment shown in FIGS. 2 and 4, the operation of the leaf spring 8 and the extension coil spring 36 causes the embodiment shown in FIGS. In the embodiment shown in FIG. 3, the valve is normally in the open state, and in the embodiment shown in FIG. 3, the valve is in the closed state under the action of the compression coil spring 28. There is no spring 28.

Therefore, the pipe pattern (a) has a closing valve function of a solenoid valve, a pressure regulating function of a governor, and a flow control valve function, and the pipe pattern (b) has a function of a solenoid valve. The closing valve function and the flow control valve function can be collectively dealt with by one device, respectively, and there is no need to select the pipeline pattern (a) and the pipeline pattern (b), thereby reducing the equipment cost. Can also
Eliminate complicated electric circuits for controlling each control device in cooperation with each other, and significantly reduce design man-hours and assembly man-hours for assembling into devices, etc., and significantly improve mass productivity. Has been a conventional problem.

Accordingly, an object of the present invention is to provide a flow control method using a new control method which can cope with a case where the supply pressure of a fluid fluctuates and can control the flow proportionally by remote control. is there. And the present invention
A flow control valve that can cope with the case where the supply pressure of such fluid fluctuates, can proportionally control the flow rate by remote control, and is integrated as one device including a shutoff valve function,
Another object of the present invention is to provide a flow control valve such as a flow proportional control valve and a constant flow control valve using the flow control method based on the new control method described above.

[0009]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the invention according to claim 1 is directed to a main valve seat provided in a flow channel from an inlet to an outlet and a center of a diaphragm having a back pressure chamber. A main valve body that is disposed opposite to the main valve seat and that opens and closes the flowing water channel; a primary pressure chamber on the water inlet side with the diaphragm as a boundary; and an outlet with the diaphragm as a boundary. A secondary pressure chamber on the water port side, a communication hole communicating the primary pressure chamber with the back pressure chamber, a pilot valve hole communicating the back pressure chamber with the secondary pressure chamber, and penetrating the pilot valve hole. Control valve member provided as described above, wherein the control valve member is a pilot valve for closing the pilot valve hole, and a differential pressure plate provided in the main valve port on the water outlet side from the main valve seat. And the flow rate of the water outlet is controlled by the control valve section. A flow control method using a flow control valve that can be set corresponding by generating force to act on,
Let Q be the flow rate of the water outlet, A4 be the area of the passage hole around the differential pressure plate, and ΔP3 be the constant differential pressure before and after the differential pressure plate.
The following equation Q∝A4√ (ΔP3) is established to make the outlet flow rate Q the constant differential pressure Δ corresponding to the generated force acting on the control valve member.
It is characterized by a differential pressure control method that is controlled by P3.

More specifically, as shown in FIGS. 3 and 4, a main valve body 4 provided at the center of a diaphragm 6 is provided on a main valve seat 4 in the middle of a flow channel from an inlet 2 to an outlet 3. 5 are opposed to each other to open and close the water channel, and a primary pressure chamber 7, a back pressure chamber 8, and a secondary pressure chamber 9 are provided. The communication between the primary pressure chamber 7 and the back pressure chamber 8 is a communication hole 14, and the back pressure chamber 8 and the secondary pressure chamber 9
Are pilot valve holes 5a, which communicate with each other. A main valve port 4a extending from the main valve seat 4 to the water outlet 3 is provided vertically. The control valve member 10 provided so as to penetrate the pilot valve hole 5a is provided integrally with a pilot valve 12 for closing the pilot valve hole 5a and a differential pressure plate 13 in the main valve port 4a. . The outlet flow rate Q can be set by the generated force F applied to the control valve member 10. Then, the outlet flow rate Q is controlled by a constant differential pressure ΔP3 corresponding to the generated force F, and Q∝A4√ (ΔP3) where A4 is the annular passage hole area around the differential pressure plate 13, ΔP3
Is a flow rate control method using a novel differential pressure control method, in which the relationship between the differential pressures before and after the differential pressure plate 13 is established.

Here, as the main fields of application of such a technology, the following can be cited as typical ones among the above-mentioned apparatuses and factory facilities. B) In a hot-water storage type water heater, as a flow control valve for changing the mixing ratio of water to hot water to create an appropriate mixing hot water temperature. B) In a water heater for hot water supply, as a flow control valve for controlling the flow rate of feed water to create an appropriate hot water temperature. C) As a versatile flow control valve that can respond to devices with different flow rates. D) As a flow control valve for controlling the appropriate amount of cooling water for high-temperature heat treatment furnaces and air compressors.

According to the first aspect of the present invention, a flowing water channel, a water inlet, a water outlet, a main valve seat, a main valve opening, a diaphragm, a back pressure chamber, a main valve body, a primary pressure chamber, a secondary pressure chamber, and communication. Using a flow rate control valve including a hole, a pilot valve hole, a control valve member, a pilot valve, and a differential pressure plate, in the relationship of the outlet flow rate Q, the passage hole area A4 around the differential pressure plate, and the constant differential pressure ΔP3 before and after the differential pressure plate, ∝ A4√ (ΔP3) is satisfied, and the flow rate is controlled by a differential pressure control method that controls the outlet flow rate Q with a constant differential pressure ΔP3 corresponding to the generated force that acts on the control valve member. It can be used when the pressure fluctuates,
The flow rate can be controlled proportionally by remote control. It is also possible to perform proportional control of the flow rate manually and constant control of the flow rate by setting a fixed point.

According to a second aspect of the present invention, in the valve housing, the flow channel, the water inlet, the water outlet, the main valve seat, the main valve port, the diaphragm, the back pressure chamber, the main valve body, the primary pressure chamber, A flow control valve, comprising a secondary pressure chamber, a communication hole, a pilot valve hole, a control valve member, a pilot valve, and a differential pressure plate, wherein the flow control method according to the differential pressure control method according to claim 1 is applied, A solenoid as an external operating means of the generated force acting on the control valve member, and externally operating and controlling the amount of current supplied to the solenoid so that the generated force applied to the control valve member can be increased or decreased. It is characterized by having been constituted so that.

Specifically, for example, as shown in FIG. 6, a water inlet 2, a water outlet 3, a main valve seat 4, a main valve port 4a, a main valve body 5, a pilot valve Hole 5a, diaphragm 6, primary pressure chamber 7, back pressure chamber 8, secondary pressure chamber 9, control valve member 10, pilot valve 12, differential pressure plate 13, communication hole 14
A solenoid 15 is used as an external operating means of the generated force F. A plunger 11 which is moved forward and backward by the solenoid 15 is provided on the control valve member 10 to externally control the amount of current supplied to the solenoid 15. This is a flow proportional control valve that can increase or decrease the generated force F. In addition, as shown in FIG. 8, a flow rate proportional control valve having a plurality of notches A4 'formed around the differential pressure plate 13, or as shown in FIG. It may be a flow rate proportional control valve having a plurality of cutout grooves A4 ″ formed on the surface.

As described above, according to the differential pressure control system according to the first aspect, the amount of the generated force acting on the control valve member is controlled by externally controlling the amount of current supplied to the solenoid as the external operating means. Since it is a flow control valve as a flow proportional control valve configured to enable the change, it can cope with the fluctuation of the supply pressure of the fluid, and the flow can be proportionally controlled by remote control.
It will be one device.

According to a third aspect of the present invention, in the valve housing, the flow channel, water inlet, water outlet, main valve seat, main valve port, diaphragm, back pressure chamber, main valve body, primary pressure chamber, A flow control valve, comprising a secondary pressure chamber, a communication hole, a pilot valve hole, a control valve member, a pilot valve, and a differential pressure plate, wherein the flow control method according to the differential pressure control method according to claim 1 is applied, An electric motor as an external operating means of the generated force applied to the control valve member, and a tension coil spring interposed between a movable member operated by driving the electric motor and the control valve member, The amount of rotation by driving the electric motor is converted into a linear amount of motion, and the amount of rotation by driving the electric motor is externally operated and controlled so as to be given to the tension coil spring as an amount of extension, and the amount of rotation is applied to the control valve member. Increase / decrease in power It is characterized by being configured so as to enable further.

Specifically, as shown in FIG. 12, a water inlet 2, a water outlet 3, a main valve seat 4, a main valve
a, main valve body 5, pilot valve hole 5a, diaphragm 6,
Primary pressure chamber 7, back pressure chamber 8, secondary pressure chamber 9, control valve member 1
0, a pilot valve 12, a differential pressure plate 13, and a communication hole 14. A motor 18 and a tension coil spring 21 are used as external operating means of the generated force F. An extension coil spring 21 is provided between the control valve member 10 and the amount of rotation of the motor 18 is externally controlled so as to convert the amount of rotation of the motor 18 into a linear amount of motion and give the amount of extension to the extension coil spring 21. This is a flow proportional control valve that can increase or decrease the generated force F.

As described above, according to the differential pressure control system according to the first aspect, the movable member driven by the electric motor converts the amount of rotation by driving the electric motor as the external operating means into a linear amount of movement. The amount of rotation by driving the electric motor is externally operated and controlled so as to give as an amount of extension to a tension coil spring interposed between the control valve member and the control valve member, so that the generated force acting on the control valve member can be increased or decreased. Flow control valve as a flow proportional control valve configured to
It is possible to cope with the case where the supply pressure of the fluid fluctuates, and to control the flow rate proportionally by remote control.

According to a fourth aspect of the present invention, in the valve housing, the flow channel, water inlet, water outlet, main valve seat, main valve port, diaphragm, back pressure chamber, main valve body, primary pressure chamber, A flow control valve, comprising a secondary pressure chamber, a communication hole, a pilot valve hole, a control valve member, a pilot valve, and a differential pressure plate, wherein the flow control method according to the differential pressure control method according to claim 1 is applied, An electric motor as an external operating means of the generated force applied to the control valve member, and a compression coil spring interposed between a movable member operated by driving the electric motor and the control valve member; The amount of rotation by the drive of the electric motor is converted into a linear amount of motion, and the amount of rotation by the drive of the electric motor is externally operated and controlled so as to be given to the compression coil spring as a contraction amount, and is applied to the control valve member. Increase / decrease in power It is characterized by being configured so as to enable further.

Specifically, as shown in FIG. 13, a water inlet 2, a water outlet 3, a main valve seat 4, a main valve
a, main valve body 5, pilot valve hole 5a, diaphragm 6,
Primary pressure chamber 7, back pressure chamber 8, secondary pressure chamber 9, control valve member 1
0, a pilot valve 12, a differential pressure plate 13, and a communication hole 14. A motor 18 and a compression coil spring 22 are used as external operation means of the generated force F. A compression coil spring 22 is provided between the control valve member 10 and the amount of rotation of the motor 18 is externally controlled so as to convert the amount of rotation of the motor 18 into a linear amount of motion and to give the compression coil spring 22 a contraction amount. This is a flow proportional control valve that can increase or decrease the generated force F.

As described above, according to the differential pressure control system according to the first aspect, the movable member driven by the electric motor is converted from the amount of rotation by the driving of the electric motor as the external operating means into the amount of linear movement. The amount of rotation by driving the electric motor is externally operated and controlled so as to give as a contraction amount to a compression coil spring interposed between the control valve member and the control valve member, and the generated force acting on the control valve member can be increased or decreased. Flow control valve as a flow proportional control valve configured to
It is possible to cope with the case where the supply pressure of the fluid fluctuates, and to control the flow rate proportionally by remote control.

According to a fifth aspect of the present invention, in the valve housing, the flow channel, water inlet, water outlet, main valve seat, main valve port, diaphragm, back pressure chamber, main valve body, primary pressure chamber, A flow control valve, comprising a secondary pressure chamber, a communication hole, a pilot valve hole, a control valve member, a pilot valve, and a differential pressure plate, wherein the flow control method according to the differential pressure control method according to claim 1 is applied, A flow setting operation member as an external operation means of the generated force acting on the control valve member, and a tension coil provided between the movable member operated by operating the flow setting operation member and the control valve member And a manual operation from the outside so as to give an operation amount of the flow rate setting operation member to the tension coil spring as an extension amount, so that the generated force acting on the control valve member can be increased or decreased. It is characterized by having constituted .

More specifically, as shown in FIG. 14, a water inlet 2, a water outlet 3, a main valve seat 4, a main valve
a, main valve body 5, pilot valve hole 5a, diaphragm 6,
Primary pressure chamber 7, back pressure chamber 8, secondary pressure chamber 9, control valve member 1
0, a pilot valve 12, a differential pressure plate 13, and a communication hole 14. A flow setting knob 25 and a tension coil spring 21 are used as external operating means of the generated force F. The sliding operation is performed by operating the flow setting knob 25. A tension coil spring 21 is provided between the sliding member 20a to be operated and the control valve member 10, and an operation amount of the flow rate setting knob 25 is given to the tension coil spring 21 as an extension amount, and the above-described operation is manually performed from outside. This is a manual variable flow rate proportional control valve capable of increasing and decreasing the force F.

As described above, according to the differential pressure control system of the first aspect, the operation amount of the flow setting operation member as the external operation means is controlled by the movable member operated by the operation of the flow setting operation member. Manually operated from the outside to give as an extension amount to the tension coil spring interposed between the valve member,
Since the flow control valve as a manual variable flow proportional control valve configured to allow the increase or decrease of the generated force acting on the control valve member, it is possible to cope with the case where the supply pressure of the fluid fluctuates, and the flow rate is manually operated. Increase / decrease control can be performed, and furthermore, it is integrated as one device including the closing valve function and the like.

According to a sixth aspect of the present invention, in the valve housing, the flowing water channel, the water inlet, the water outlet, the main valve seat, the main valve port, the diaphragm, the back pressure chamber, the main valve body, the primary pressure chamber, A flow control valve, comprising a secondary pressure chamber, a communication hole, a pilot valve hole, a control valve member, a pilot valve, and a differential pressure plate, wherein the flow control method according to the differential pressure control method according to claim 1 is applied, A coil spring for urging the control valve member in a valve opening direction as an external operation means of the generated force acting on the control valve member, and a solenoid provided for opening and closing a closing valve function for the control valve member are provided. And a closing valve function, wherein the generated force acting on the control valve member is obtained by a spring force of the coil spring, thereby enabling a constant control of the flow rate.

Specifically, for example, as shown in FIG. 15, a water inlet 2, a water outlet 3, a main valve seat 4,
Main valve port 4a, main valve element 5, pilot valve hole 5a, diaphragm 6, primary pressure chamber 7, back pressure chamber 8, secondary pressure chamber 9, control valve member 10, pilot valve 12, differential pressure plate 13, communication hole 1
And a solenoid 30 and a tension coil spring 21 are used as external operating means of the generated force F.
The sliding member 32 and the control valve member 10 slid by 0
A solenoid 30 is provided for opening and closing the closing valve function without being involved in the generated force F. The generated force F is obtained by setting a fixed point of the tension coil spring 21. This is a constant flow control valve with a closing valve function that enables constant flow control. Alternatively, as shown in FIG. 16, a solenoid 3
0 and the compression coil spring 22 are used, and the control valve member 10 and the bottom 3 of the valve housing 1 which are moved forward and backward by the solenoid 30
c, a compression coil spring 22 is provided.
Is for opening / closing the closing valve function without being involved in the generated force F. The generated force F is obtained by setting a fixed point of the compression coil spring 22 so that the flow rate can be controlled to be constant. It is a flow control valve.

As described above, according to the differential pressure control system according to the first aspect, a coil spring which has a closing valve function of a solenoid for the control valve member and urges the control valve member in the valve opening direction as an external operating means. Due to the spring force, the generated force acting on the control valve member is obtained, so that the flow control valve is a constant flow control valve with a closing valve function configured to enable constant control of the flow rate. In addition to being able to control the flow rate,
This is a single device including the closing valve function and the like.

According to a seventh aspect of the present invention, in the valve housing, the flow channel, water inlet, water outlet, main valve seat, main valve port, diaphragm, back pressure chamber, main valve body, primary pressure chamber, A flow control valve, comprising a secondary pressure chamber, a communication hole, a pilot valve hole, a control valve member, a pilot valve, and a differential pressure plate, wherein the flow control method according to the differential pressure control method according to claim 1 is applied, A coil spring is provided between the valve housing and the control valve member, and the generated force acting on the control valve member is obtained by a spring force of the coil spring, thereby enabling constant control of the flow rate. It is characterized by having such a configuration.

Specifically, for example, in FIG. 12, the motor 18 and the screw feed mechanism 20 which are the external operation means of the generated force F are eliminated, and only the tension coil spring 21 is used. Is a constant flow control valve capable of controlling the flow constant in accordance with the generated force F set in advance at a fixed point. Alternatively, in FIG. 13, the motor 18 and the screw feed mechanism 20 which are the external operation means of the generated force F are eliminated, and only the compression coil spring 22 is used. This is a constant flow control valve capable of controlling the flow constant in accordance with the force F.

As described above, according to the differential pressure control system of the first aspect, the generated force acting on the control valve member by a spring force of a coil spring interposed between the valve housing and the control valve member. Thus, since the flow rate control valve is a constant flow rate control valve configured to enable constant flow rate control, it is possible to cope with a case where the supply pressure of the fluid fluctuates and to control the flow rate constant.

[0031]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of a control method of a flow control method according to the present invention and embodiments of a flow control valve will be described with reference to FIGS.

<Overview of Control System> First, before describing a new control system according to the present invention, a conventional control system will be described. Conventional pressure or flow control methods are:
The same applies to the governor described above.
This is represented by the pressure control technology disclosed in Japanese Patent No. 3632. That is, this conventional control method is commonly called
This is called a secondary pressure control method, and has long been known as the only method capable of controlling the pressure or flow rate of a fluid including gas.

FIG. 2 shows a main part of a structure corresponding to FIG. 1 (conventional example) of Japanese Patent Publication No. 63-43632. As shown in FIG. The pressure is P10, and the pressure in the secondary pressure chamber downstream of the valve body is P2.
0, the pressure receiving area of the valve element is SvX, the pressure receiving area of the diaphragm is SdX, and FX acting on the opposite side of the valve element with the diaphragm as a boundary is a spring force. Balance the power like. FX + P10 ・ SvX-P10 ・ SdX-P20 ・ Sv
X = 0 P20 = (FX + P10.SvX-P10.SdX) /
SvX Since SvX and SdX are set to be substantially equal, the forces of P10.SvX and P10.SdX are canceled. When this is arranged, P20 ≒ FX / SvX is obtained.

The outlet flow rate (QX) is determined by the stable supply P20. That is, QX = αAX√ (2g · P20 / r) where α is a coefficient, AX is the outlet area, g is the acceleration of gravity, and r is the specific gravity of the fluid. As described above, since α, g, and r are coefficients and constants, Qx∝AX√ (P20) is obtained. Accordingly, the flow rate QX largely depends on the secondary pressure P20.
It is commonly called a secondary pressure control system. The conventional control method has the above features, and hereinafter, the conventional pressure control method is referred to as a secondary pressure control method.

Next, a new control method according to the present invention will be described. Note that the control method of the present invention can be called a differential pressure control method because it depends on a differential pressure, as described later, when expressed in accordance with a conventional name. FIG. 3 is a configuration diagram for explaining the outline of the present invention and a new control method, and is a diagram showing a valve closed state, and FIG. 4 is a diagram showing the valve open state similarly. First, in FIG. 3, 1 is a valve housing, 2 is a water inlet, 3 is a water outlet, 4 is a main valve seat for closing a water passage from the water inlet 2 to the water outlet 3, and 4a is a main valve port. The main valve port 4a is provided vertically on the downstream side of the main valve seat 4 (actually, the operating range of the differential pressure plate 13 described later). Reference numeral 5 denotes a main valve body for closing the main valve seat 4, 6 denotes a flexible diaphragm, and the diaphragm 6 has an inner side on the annular outer peripheral surface of the main valve body 5 and an outer side on the valve housing 1.
A primary pressure chamber 7, a back pressure chamber 8, and a secondary pressure chamber 9 are formed in an airtight manner inside.

The main valve body 5 is provided with a pilot valve hole 5a and a pilot valve seat 5b communicating from the back pressure chamber 8 to the secondary pressure chamber 9 at the center thereof. The valve member 10 is provided so as to penetrate. The control valve member 10 includes a plunger 11 which is a sliding member and a pilot valve 12 which is seated on a pilot valve seat 5b.
The differential pressure plate 13 is formed integrally on the shaft by linking the shaft 13a with an appropriate distance. The above-mentioned appropriate distance between the pilot valve 12 and the differential pressure plate 13 corresponds to the main valve body 5
The flow rectification region and the pressure stabilization region of the fluid flowing by opening the valve, the lift amount of the main valve, and the like are taken into consideration. The primary pressure chamber 7 and the back pressure chamber 8 are communicated by a communication passage 14.

The plunger 11 has a function of linking the generated force F corresponding to the flow rate set value from outside to the inside of the vessel as described later, and a function of improving the attitude control accuracy of the control valve member 10. . Here, the linkage of the generated force F to the inside of the vessel is not necessarily limited to the plunger 11. For example, in a fifth embodiment described later, the spring control shaft 20e plays this role. A specific example of the means for operating the plunger 11 from the outside will be described in an embodiment described later.

FIG. 3 shows a state in which the function of the flow control valve is stopped.
In a so-called operation waiting state, this is called a normal state. In this normal state, the pilot valve 12 is always closed. The valve closing seating force f at this time is equal to a primary pressure P1 described later.
The control valve member 10 may have its own weight, as long as it has the ability to close when it is introduced into the back pressure chamber 8 through the communication passage 14. When the self-weight is too small to have the closing ability, a valve-closing spring (not shown) having a small force to compensate for the self-weight may be provided.

The new control method of the present invention will be described below in the following order. 1) Closing valve function 2) Open / close control of main valve element 5 by external operation 3) Flow control valve function 4) Flow proportional control function 5) Overall summary (action and operation)

1) Closing valve function In FIG. 3, Sd is the pressure receiving area of the diaphragm 6, Sv
Is the area of the main valve port 4a, and the back pressure chamber 8 is the pilot valve 1
2 is in a closed state, and the primary pressure P1 fills the primary pressure chamber 7 and the back pressure chamber 8 through the communication hole 14,
The main valve element 5 is in a valve closed state due to a difference in generated force corresponding to the main valve port area Sv. That is, a force acts on the valve-closing side from the difference in the generated force of Sd · P1> (Sd−Sv) P1 (1). However, in this case, since the description is complicated, the area of the pilot valve hole 5a and the axial area of the control valve member 10 are neglected. As is apparent from the equation (1), this difference in the generated force does not collapse even if P1 fluctuates, and the valve closing state can be stably maintained. To release the closing valve function, the control valve member 10 is pulled up to open the pilot valve 12, and the pressure in the back pressure chamber 8 is reduced.

2) Opening / closing control of main valve element 5 by external operation In FIG. 4, Q is the flow rate of water outlet 3, and Q 1 is communication hole 14.
, Q2 is the flow rate of the pilot valve 12, Q3 is the flow rate of the main valve body 5, A1 is the area of the communication hole 14, A2 is the lift passage area of the pilot valve 12, and A3 is the differential pressure plate 13.
A4 is the area of the annular passage hole around the differential pressure plate 13 (= Sv-A3). Further, FIG. 4 shows a state in which the flow rate proportional control valve is operating under a certain condition. In the back pressure chamber 8, the flow rate Q2 is increased by opening the pilot valve 12.
Then, the pressure changes from the state of FIG. 3 to the pressure P2. P3 is the pressure in the secondary pressure chamber 9, and P4 is the pressure after passing through the differential pressure plate 13. What constitutes the flow rate Q of the water outlet 3 at this time is Q3 flowing from the main valve side and Q2 flowing from the pilot valve side through the communication hole 14. That is, Q = Q2 + Q3. This Q2 is a main valve element 5 integral with the diaphragm 6.
, And the amount is considered to be extremely small as compared with the passing flow rate Q3 of the main valve body 5.

Incidentally, as a diaphragm, a main valve body integral with the diaphragm, a pilot valve with a solenoid, and the like, there is a valve structure of a flush valve which has long been used as a flush water supply valve for toilets and the like. The difference from the flash valve is that the pilot valve 12 of the present invention is provided integrally with a differential pressure plate 13 on the downstream side. The differential pressure plate 13 plays an important role in the present invention as described later, and it is considered that the presence of the differential pressure plate 13 satisfies the following balance equation. That is, in FIG. 4, the force balance by pressure is: P1 (Sd−Sv) + P3 · Sv−P2 · Sd = 0 However, in this case, the plunger shaft area of the control valve member 10, the pilot valve hole area, etc. Has been neglected due to its complexity.

By transposing this equation as follows and concluding it by P1 (Sd-Sv) + P3.Sv = P2.Sd Sv, Sd and rearranging the equation, (P1-P2) Sd = (P1-P3) Sv (2) Here, P1-P2 = ΔP1 (differential pressure) and P2-P3 = ΔP2 (differential pressure), and P1-P3 = ΔP1 + ΔP2 are substituted into the formula (1) from both formulas. Then, ΔP1 · Sd = (ΔP1 + ΔP2) Sv ΔP1 (Sd−Sv) = ΔP2 · Sv That is, ΔP1 / ΔP2 = Sv / (Sd−Sv) = (constant in pressure balance) (3)

Next, considering the flow rate balance, assuming that the force balance by pressure is established as described above, it is considered that the flow rates of the entrance Q1 and the exit Q2 of the back pressure chamber 8 are the same. Therefore, if further developed using the simplified formula used in the above-mentioned conventional secondary pressure control method, Q1 = Q2, A1√ (ΔP1) = A2√ (ΔP2), ie, ΔP1 / ΔP2 = (A2 / A1) 2 Power = (constant in flow rate balance) (4) Therefore, the expressions (3) and (4) can be evaluated on the same basis. ΔP1 / ΔP2 = Sv / (Sd−Sv) = (A2 / A1) square = constant (5)

Considering the expression (5) by replacing the meaning of the expression with the operation surface of the related components, when the control valve member 10 is pulled up in the axial direction by an external control signal from the state shown in FIG. Since the condition of the expression 5) is secured, the main valve element 5 is pulled up almost simultaneously so as to follow the control valve member 10. Also, when the control valve member 10 is pulled down in the axial direction, the main valve body 5 similarly follows the condition (5), so that the main valve body 5 descends by following operation, and the control valve member 10 is lowered. When a command to continue the operation is continued, the main valve body 5 finally reaches the main valve seat 4 and the valve is completely closed. That is, it means that the main valve body 5 can be freely controlled by the control valve member 10 from opening to closing.

3) Flow control valve function As described above, the flow rate at the water outlet 3 is Q = Q2 + Q3. Here, Q2 is neglected due to its small amount for ease of explanation in the following, and hereinafter Q = Q3. In FIG. 4, F is a force generated by receiving an external signal and corresponding to a certain flow rate set value. The balance formula with the force opposing the generated force F is as follows: F−ΔP3 · A3 = 0 (6) where ΔP3 (differential pressure) = P3−P4 Also, the main valve body 5 is opened at this time. The passing flow rate is as follows: Q {A4} (ΔP3) (7) By substituting the above equation (6) for expansion, Q {A4} (F / A3) (8)

That is, the differential pressure ΔP3 and the flow rate Q are often dependent on the generated force F from the equation (8), and the Q can be appropriately determined by controlling the generated force F from the outside. Is. As described above, since the control method according to the present invention largely depends on the differential pressure ΔP3, it can be called a differential pressure control method. by this,
The difference from the above-mentioned conventional secondary pressure control method is clear. Therefore, hereinafter, the control method of the present invention is referred to as a differential pressure control method. If the generated force F is considered as a fixed force that does not correspond to an external signal, it can be used as a simple constant flow control valve.

4) Flow Proportional Control Function The state shown in FIG. 4 indicates that the flow rate Q is in a stable control state with respect to the generated force F corresponding to the set value, as described above. FIG. 5 shows a flow rate characteristic diagram with respect to the fluctuating supply pressure P1. It should be noted that the same function has been confirmed in the prototype stage for function confirmation by the present applicant. First, in FIG. 5, a case where the flow rate is changed from F to F1 on the increasing side from the state shown in FIG. 5 will be considered. Here, F1 is the generated force corresponding to the flow rate including the increase instruction, ΔF1 is the generated force corresponding to the increase,
Q 'is the flow rate including the increased amount after the increase, P3' is the secondary pressure after the increase, P4 'is the pressure after passing through the differential pressure plate after the increase, ΔP
3 'is the differential pressure after the increase.

Therefore, the equation (6) after the increase is: F1 = F + ΔF1 = ΔP3 ′ · A3 (9) ΔP3 ′ = P3′-P4 ′ The equation (8) after the increase is Q '∝A4√ (ΔP3') (10) Q'∝A4√ ((F + ΔF1) / A3) (11) That is, from the comparison between the equation (11) and the equation (8), It is understood that the flow rate Q 'after the increase is increased by the generated force ΔF1 corresponding to the increase.

In FIG. 5, when the flow rate is reduced,
When the setting is changed from F2 to F2, F2 is the generated force corresponding to the flow rate including the weight reduction instruction, ΔF2 is the generated force corresponding to the weight reduction, Q ″ is the flow rate including the reduced quantity, and P3 ″ is the secondary pressure after the reduction. , P4 ″ is the pressure after passing through the differential pressure plate after weight loss, ΔP3 ″
Is the differential pressure after weight loss. F2 = F−ΔF2 = ΔP3 ″ · A3 (12) ΔP3 ″ = P3 ″ −P4 ″ Q ″ {A4} ((F−ΔF2) / A3) (13) That is, (13) From the comparison between the expression and the expression (8), it is understood that the flow rate Q ″ after the decrease is reduced by the generated force ΔF2 corresponding to the decrease. As described above, the flow rate can be precisely increased and decreased with respect to the set value by the external operation, and the flow rate can be controlled to be constant, thereby proving the flow proportional control function.

5) Overall Summary (Operation and Operation) The flow proportional control valve of the present invention is in the normal state shown in FIG. 3 when waiting for operation, and completely prevents fluid from entering the pipeline from the upstream side. In the so-called closing valve function state. In this state, when the control valve member 10 receives a signal from the outside and is pulled up by the generated force F corresponding to the flow rate setting value against the dead weight and the valve closing spring force f, the pilot valve integrated with the control valve member 10 The valve 12 is raised and the pilot valve hole 5a is opened. The state shown in FIG. 4 has been started by the pilot valve 12. As a result, in the back pressure chamber 8, the primary pressure changes from the primary pressure P1 to the pressure P2, Q1 flows, and the relationship of the above equation (4) is established, the main valve element 5 is pulled up, and the main valve seat 4 is opened. When the pilot valve 12 is opened, the flow rate Q3 flows through the main valve port 4a, and a differential pressure ΔP3 is generated across the differential pressure plate 13 integrated with the pilot valve 12, and the generated force F To balance against. This balance position determines the valve opening amount of the main valve body 5 and controls the flow rate Q.

More specifically, if a situation occurs in which the differential pressure ΔP3 is to be increased under some circumstances, the pilot valve 12 is lowered against the generated force F, and the above equation (5) is obtained. Is indirectly reduced, and Q is controlled to the set value. If a situation arises in which the pressure difference ΔP3 is to be reduced under some circumstances, the pilot valve 12 is pulled up by the generated force F, and the relationship of the formula (5) is reversed. Q is controlled to a set value by indirectly increasing the lift amount of a certain main valve body 5. As described above, the differential pressure ΔP3 is always caught, and the lift amount of the main valve body 5 is finely adjusted to control the flow rate to the set value. In order to complete the use and reach the above-mentioned normal state, the generated force F is turned off by an external operation signal. Then, the control valve member 10 is lowered by the valve closing spring force f, and the pilot valve 12 is closed.

Next, each embodiment of the flow control valve which embodies the flow control method according to the present invention as described above will be described in order. In the following embodiments, the same reference numerals are given to the portions having the same functions in FIGS.
Avoid duplication of the description and focus on the characteristic part.

<First Embodiment> FIG. 6 is a longitudinal sectional view showing a flow control valve (flow proportional control valve) as a first embodiment of the present invention, and FIG. It is an arrow A view showing a water mouth part. In the first embodiment, as shown in FIG. 6, a solenoid 15 is used as means for externally operating a generated force F acting on the plunger 11 of the control valve member 10. That is, the valve housing 1 is
As shown in FIG. 6, the main body 1 a having the water inlet 2 and the water outlet 3 and the lid 1 b having the plunger sliding pipe 1 f protruding in a bottomed cylindrical shape are bounded by the mounting position of the diaphragm 6. And the large-diameter opening portion 1 of the main body portion 1a
The annular tubular portion 1e of the lid portion 1b is fitted airtightly to c. And outside the plunger sliding pipe 1f,
A solenoid 15 is assembled so as to cover the bobby hole. The solenoid 15 is fixed to the main body 1a by a plurality of small screws 16, and at this time, the outer peripheral edges of the lid 1b and the diaphragm 6 are also fixed to the main body 1a. Is done. In addition,
The outer peripheral edge of the diaphragm 6 is the stepped portion 1 of the large-diameter open portion 1c.
d, and is hermetically sandwiched between the end face of the annular tubular portion 1e.

Here, the solenoid 15 is such that the strength of the magnetic field that causes the force F to act on the plunger 11 is adjusted so as to be determined by the current density. The strength can be determined appropriately. Therefore, the iron-based magnetic material is suitable as the material of the plunger 11. Further, when actually controlling the flow rate, what is determined by collecting relational data between the magnetic field strength (generated force F) and the control current with respect to the control flow rate value is used.

Further, as shown in FIG. 6, the seating surface 5 of the main valve body 5 airtightly provided at the center of the diaphragm 6 is provided.
f has a frusto-conical shape, and has a function of being guided by the ridge of the main valve seat 4 and centered when seated on the main valve port 4a. As a result, the reliability of the valve closing function is improved, and since the seating surface 5f is inclined, the valve closing operation becomes slower and the vibration of the valve is suppressed. I have. And the seating surface 5f of the main valve body 5
On the side opposite to the rear chamber 8, a disc-shaped guide plate 5 c that slides on the inner surface of the annular tubular portion 1 e is provided integrally via a tubular body 5 d. The disc-shaped guide plate 5c is provided with a plurality of cutout grooves 5e for fluid circulation so as to divide the disc-shaped guide plate 5c in the circumferential direction. The notch groove 5e facilitates dispersion of the fluid from the communication passage 14 to the entire back pressure chamber 8.

Here, the control valve member 10 is provided on the side of the differential pressure plate 13 disposed in the main valve port 4a and the pilot valve 12 and the plunger 11 having a truncated cone shape in consideration of the assemblability. It is divided, and the valve shaft 13a of the differential pressure plate 13 is fitted into the base of the pilot valve 12 to be integrated. Further, the truncated cone shape of the pilot valve 12 improves the valve closing function as well as the function of the seating surface 5f of the main valve body 5,
This is due to consideration of the function of suppressing the occurrence of valve vibration.

In the control valve member 10, the plunger 11 is slidable with respect to the plunger sliding pipe 1f, and hermetically sealed by an O-ring 11a. The downstream differential pressure plate 13 has a guide shaft 10b extending in the axial direction slidably fitted in a bearing hole of an arm 3a provided across the water outlet 3 as shown in FIG. As a result, the posture control accuracy is ensured. The axial gap between the arm 3a and the differential pressure plate 13 is provided with a distance so as not to come into contact with each other even when the respective seating surfaces of the main valve body 5, the pilot valve 12, and the like are worn. The arm 3a serves as a support member for the control valve member 10 in the assembly process.

Further, the plunger 1 of the control valve member 10
At the center of 1, a communication hole 10a is formed from the secondary pressure chamber 9 toward the foremost bottom space 1g of the plunger sliding pipe 1f. The communication hole 10a cancels the force acting on the control valve member 10 by the action of the pressure P3 in the secondary pressure chamber 9. Therefore, the pressure receiving area of the plunger 11 is substantially the same as the area of the pilot valve hole 5a due to the presence of the communication hole 10a. The communication hole 10a is expected to be difficult to drill when the control valve member 11 is further downsized. In such a case, two points are shown in FIG. The same function can be obtained even when the secondary pressure chamber 9 and the bottom space 1g of the foremost end of the plunger sliding pipe 1f are directly communicated with each other by the external communication passage 10a 'shown by a chain line. In the main valve element 5, a surface extending from the frusto-conical seating surface 5f to the pilot valve hole 5a and the pilot valve seat 5b includes:
Although not shown, by providing an elastic member such as rubber or plastic by, for example, a method such as adhesion coating, adhesive attachment, or assembling, the sealing property at the time of closing the valve can be further improved.

According to the flow rate control valve having the configuration according to the first embodiment as described above, that is, the flow rate proportional control valve, in the outline of the above-described new control method, in particular, in the above 5) Overall description The same operation and operation as described can be obtained.

<Second Embodiment> FIG. 8 is a partial longitudinal sectional view showing the vicinity of a differential pressure plate of a flow control valve (flow proportional valve) according to a second embodiment of the present invention. FIG. 9 is a view on arrow B showing the differential pressure plate. In the second embodiment, the structure around the differential pressure plate 13 is improved based on the above-described first embodiment as a basic structure. That is, as shown in FIGS. 8 and 9, the annular passage hole area A4 in the above-described first embodiment has the differential pressure plate 13 as shown in FIGS.
A plurality of (four in the illustrated example, radially) notched holes A around the circumference of
It is divided and set as 4 '. In this case, regarding the posture control accuracy function based on the relationship between the guide shaft 10b and the bearing hole of the arm 3a in the first embodiment described above, the outer peripheral surface of the differential pressure plate 13 is the inner peripheral surface of the main valve port 4a. This is supported by sliding the surface. As for the gap in the axial direction between the arm 3a and the differential pressure plate 13 in the first embodiment described above, one that fulfills the same function as improving the assemblability is provided on the inner periphery of the water outlet 3. Step 3a '. Note that the other configuration is the same as the first configuration.
Is the same as that of the embodiment.

<Third Embodiment> FIG. 10 is a partial longitudinal sectional view showing the vicinity of a differential pressure plate of a flow control valve (flow proportional valve) according to a third embodiment of the present invention. FIG.
1 is a C arrow view showing the differential pressure plate. In the third embodiment, similarly to the second embodiment, the differential pressure plate 1 has a basic structure based on the first embodiment.
It is an improvement around No. 3. That is, the annular passage hole area A4 in the first embodiment described above is:
As shown in Fig. 10 and Fig. 11, a plurality of (eight in the illustrated example, radially) notched grooves A4 "are divided and set on the inner peripheral surface of the main valve port 4a. All are the same as those of the second embodiment.

<Fourth Embodiment> FIG. 12 is a longitudinal sectional view showing a flow control valve (flow proportional control valve) as a fourth embodiment to which the present invention is applied. In the fourth embodiment, as means for externally operating the generated force F acting on the plunger 11 of the control valve member 10, FIG.
As shown in FIG. 7, a motor 18 and a tension coil spring 21 are used. That is, in FIG. 12, reference numeral 18 denotes a DC motor with an encoder (or a position meter);
Is a speed reducer, 20 is a screw feed mechanism, and 21 is a tension coil spring. The extension coil spring 21 is inside the plunger sliding pipe 1f, and one end thereof is hooked and attached to an end mounting hole of the plunger 11 and the other end thereof is mounted to a mounting hole of the sliding member 20a. , Sliding member 20a
Is applied to the control valve member 10 as a spring generating force. The plunger 11
Is provided with an O-ring 11a for sealing. Since the plunger 11 is made of a material for the purpose of controlling the attitude of the plunger 11, the first material described above is used.
It is not necessary to limit to the iron type as in the embodiment. The sliding member 20a has an O-ring 20 for sealing.
Since e is provided, the secondary pressure P3 does not leak out due to sliding.

The fitting groove 20b at the outer end of the sliding member 20a is rotatably engaged with a hole formed in the bottom plate 20d of the cap-shaped large gear 20c that meshes with the gear 19a of the speed reducer 19. . Also, on the inner surface of the large gear 20c,
The screw is provided on the entire surface, and the external thread 1h of the plunger sliding pipe 1f is screwed. Accordingly, when the DC motor 18 rotates by a rotation amount (rotation angle) corresponding to the set value of the encoder, the large gear 20c moves in the axial direction while rotating on the external thread 1h of the plunger sliding pipe 1f. The amount of movement of the large gear 20c depends on the sliding member 2
Oa acts on the tension coil spring 21 as an amount of expansion or contraction. The amount of expansion or contraction of the tension coil spring 21 is the generated force F acting on the plunger 11 of the control valve member 10. It should be noted that a stepping motor, an ultrasonic motor, or the like can be used as the DC motor 18, and further downsizing as a control device can be expected.

The flow control valve having the configuration according to the fourth embodiment as described above, that is, the flow proportional control valve also provides the above-mentioned outline of the new control method, particularly, the above 5).
The same operation and operation as described in the overall summary can be obtained.

<Fifth Embodiment> FIG. 13 is a longitudinal sectional view showing a flow control valve (flow proportional control valve) as a fifth embodiment to which the present invention is applied. According to the fifth embodiment, the means for externally operating the generated force F acting on the plunger 11 of the control valve member 10 is shown in FIG.
As shown in FIG. 7, a motor 18 and a compression coil spring 22 are used. Here, in each embodiment described above,
The control valve member 10 is pulled up by the generated force F. However, in the fifth embodiment, the control valve member 1
It works to push up 0. That is, FIG.
3, the water outlet 3 of the main body 1a of the valve housing 1 is provided at a bent position relaying a spring chamber 3b provided on a downstream shaft of the main valve port 4a.

The cap-shaped large gear 20c linked to the DC motor with encoder 18, the speed reducer 19, and the screw feed mechanism 20 is screwed with the screw 3f of the sliding pipe 3d projecting from the bottom 3c of the spring chamber 3b. And the DC motor 1
8 is transmitted to the spring control shaft 20e. The spring control shaft 20e can be slid in an airtight manner by a sealing O-ring 20g. A compression coil spring 22 is arranged in the spring chamber 3b, and one end on the upstream side thereof is arranged on the differential pressure plate 1.
3 is seated on the downstream spring seat 13b, and the other end on the downstream side is seated on a spring seat 20f rotatably attached to the indoor end of the spring control shaft 20e.

The flow control valve having the configuration according to the fifth embodiment as described above, that is, the flow control valve, also in the outline of the above-described new control method, particularly the above 5).
The same operation and operation as described in the overall summary can be obtained.

<Sixth Embodiment> FIG. 14 is a longitudinal sectional view showing a flow control valve (manual variable flow proportional control valve) as a sixth embodiment to which the present invention is applied. This sixth
In this embodiment, a manual knob 25 is provided in place of the motor drive unit in the above-described fourth embodiment (see FIG. 12). That is, in FIG. 14, 25 is a flow rate setting knob which is a manual knob, and 26 is a flow rate display plate provided at the end of the plunger sliding pipe 1f. As shown in the figure, the flow rate setting knob 25 is provided integrally with a screw shaft 25a which is screwed with the inner screw of the plunger sliding pipe 1f. The sliding member 20a linked with the rotation is rotatably engaged.

FIG. 14 shows a normal state corresponding to FIG. 6. In this state, the flow rate setting knob 2
Reference numeral 5 indicates a zero or OFF position of a flow rate scale (not shown) on the flow rate display plate 26, and indicates a state in which the control valve member 10 is in the closed valve function state and the generated force F is not acting on the control valve member 10. When the flow rate setting knob 25 is rotated and stopped at the target flow rate set value, the tension coil spring 21 is stretched by the screw shaft 25a, and the generated force F acts on the control valve member 10 so that the predetermined flow rate is reduced. can get.

The flow control valve having the configuration according to the sixth embodiment as described above, that is, the manual variable flow proportional control valve is also used in the outline of the new control method described above.
The same operation and operation as described in the above 5) Overall description can be obtained.

<Seventh Embodiment> In this seventh embodiment, although not shown, a compression coil spring 21 is used instead of the tension coil spring 21 in the sixth embodiment (see FIG. 14). It corresponds to the coil spring. As an example using the compression coil spring, for example, the compression coil spring 22 in the fifth embodiment (see FIG. 13) described above is used.
Is mentioned. That is, in the seventh embodiment, for example,
In place of the motor drive unit in the fifth embodiment described above, a component corresponding to the flow rate setting knob 25 and the flow rate display plate 26 in the sixth embodiment (see FIG. 14) is provided. Becomes

The flow control valve having the configuration according to the seventh embodiment as described above, that is, the manual variable flow proportional control valve is also used in the outline of the new control method described above.
The same operation and operation as described in the above 5) Overall description can be obtained.

<Eighth Embodiment> FIG. 15 is a longitudinal sectional view showing a flow control valve (constant flow control valve) as an eighth embodiment to which the present invention is applied. In the eighth embodiment, when the above 4) the flow proportional control function in the outline of the new control method described above is not used and the 1) closing valve function and 3) the flow control valve function are regarded as important. , A tension coil spring 21 is used as a source of the generated force F. That is, in FIG. 15, reference numeral 30 denotes a solenoid, and the solenoid 30 needs to have a linear characteristic in a relationship between a current and a magnetic field like the solenoid 15 in the above-described first embodiment (see FIG. 6). It does not. Also, this solenoid 30
Is a plunger sliding pipe 1f of the lid 1b of the valve housing 1.
Is mounted and fixed so as to cover the outside through a pedestal 31.

The sliding member 32 inside the plunger sliding pipe 1f and linked to one end of the extension coil spring 21 is arranged in the magnetic field region of the solenoid 30. Therefore, when the solenoid 30 is actuated (excited) by receiving a signal from the outside, the sliding member 32 is pulled up by the indicated L dimension until it abuts on the bottom of the tip of the plunger sliding pipe 1f. The L dimension is set in consideration of the initial tension of the tension coil spring 21 and the generated force F corresponding to the flow rate set value described above. In addition, it is a matter of course that an iron-based magnetic material is appropriate for the material of the sliding member 32, and in the illustrated example, a conductive hole 32 a for pressure relief is formed through the center of the sliding member 32. ing.

FIG. 15 shows a normal state corresponding to FIG. 6, in which the pilot valve 12 is closed, that is, a state in which the closing valve function is activated.
Upon receiving a signal from the outside, the solenoid 30 is excited to raise the sliding member 32 by the dimension L until the sliding member 32 abuts against the bottom of the tip of the plunger sliding pipe 1f.
It is a fixed point setting limited to the set value of the dimension),
The tension coil spring 21 obtains the generated force F, and continuously controls the set flow rate. Therefore, a control valve having such control characteristics is generally referred to as a constant flow control valve or a constant flow valve. In particular, in the eighth embodiment, the control valve also has the shutoff valve function at the same time. , A constant flow control valve with a closing valve function.

<Ninth Embodiment> FIG. 16 is a longitudinal sectional view showing a flow control valve (a constant flow control valve with a closing valve function) as a ninth embodiment of the present invention. In the ninth embodiment, as in the eighth embodiment (see FIG. 15), a constant flow control valve with a closing valve function is used. The present embodiment is largely different from the eighth embodiment in that the spring 22 is used. That is, in FIG.
A solenoid 30 similar to that of the eighth embodiment is provided, and a sliding member made of an iron-based magnetic material is provided at the upper end of the control valve member 10 inside the plunger sliding pipe 1f. A small diameter compression coil spring 41 and a small diameter compression coil spring 41 are arranged in a loose state. When the solenoid 30 is turned on, the sliding member 40 is pulled up against the spring force of the small-diameter compression coil spring 41.

In the downstream spring chamber 3b, a compression coil spring 22 is engaged with a spring seat 13b provided on one end of the differential pressure plate 13 and a spring seat 42 provided with a conical end on the other end. Are located. The spring seat 42 is provided with an airtight and screw-engaged spring force adjusting adjuster 4 in a boss 3g projecting from the bottom 3c of the spring chamber 3b.
3 is held at the apex of the cone and is linked to the adjuster 43 for adjusting the spring force. Therefore, the generated force F, which is the spring force of the compression coil spring 22, is appropriately set to a fixed point by the spring force adjusting adjuster 43 during assembly adjustment.

FIG. 16 shows a normal state corresponding to FIG. 6. In this state, the pilot valve 12 is closed, that is, a state in which the closing valve function is activated.
In order to maintain this state continuously, the spring force of the small-diameter compression coil spring 41 is set slightly larger than the generated force F. Therefore, the valve closing state is released and the water outlet 3
When the solenoid 30 is turned on, the sliding member 40 is pulled up, and the axial restraint of the control valve member 10 is released, the control valve member 10 is controlled by the above-described differential pressure control method. As a result, the set flow rate corresponding to the generated force F continues to flow. When the use is stopped, the solenoid 30 automatically returns to the normal state just by turning off the solenoid 30. That is, the sliding member 40 is pushed down by the small-diameter compression coil spring 41, the control valve member 10 is pushed down, the pilot valve 12 is closed, and subsequently the main valve body 5 is closed, and the normal state described above is reached.

<Tenth Embodiment> Although not shown in the tenth embodiment, only the above-mentioned 3) flow control valve function in the outline of the new control method described above is emphasized. , A constant flow control valve or a constant flow valve. That is, the tenth embodiment is
The motor 18 and the screw feed mechanism 20 in the above-described fourth embodiment (see FIG. 12) are eliminated, the sliding member 20a is fixed, and the generated force F due to the spring force of the extension coil spring 21 is fixed. It is set to be set. Such a constant flow control valve may be configured.

<Eleventh Preferred Embodiment> Although not shown, the eleventh preferred embodiment is basically similar to the tenth preferred embodiment described above. The difference is that a spring is used. That is, the first
In one embodiment, the motor 18 and the screw feed mechanism 20 in the above-described fifth embodiment (see FIG. 13) are eliminated, the sliding member 20a is fixed, and the spring of the compression coil spring 22 is fixed. The force F generated by the force is set at a fixed point. Such a constant flow control valve may be configured.

In each of the above embodiments, each flow control valve according to the present invention is, as described above, a fluid (such as an incompressible fluid) such as water, hot water or oil used in various devices and factory facilities. ) Is used for flow control. Also, regarding the specific detailed structure of each flow control valve according to the present invention,
Of course, it can be changed as appropriate.

[0083]

As described above, according to the flow rate control method according to the invention of claim 1, in the relation of the outlet flow rate Q, the passage hole area A4 around the differential pressure plate, and the constant differential pressure ΔP3 before and after the differential pressure plate. , Q∝A4√ (ΔP3) is satisfied and the flow rate is controlled by a differential pressure control method in which the outlet flow rate Q is controlled by a constant differential pressure ΔP3 corresponding to the generated force acting on the control valve member. It is possible to cope with the case where the supply pressure of the fluid fluctuates, and the flow rate can be proportionally controlled by remote control. It is also possible to perform proportional control of the flow rate manually and constant control of the flow rate by setting a fixed point.

According to the flow control valve according to the second aspect of the present invention, the differential pressure control method according to the first aspect is applied,
A flow proportional control valve that externally controls the amount of current supplied to a solenoid as an external operating means to increase or decrease the generated force acting on the control valve member. In addition to being able to respond, the flow rate can be proportionally controlled by remote control, and furthermore, it can be integrated as one device including a closing valve function and the like. Therefore, it is possible to reduce the equipment cost and simplify the control circuit, and to significantly improve the productivity, thereby contributing to a significant improvement in mass productivity.

According to the flow control valve according to the third aspect of the present invention, the amount of rotation by driving the electric motor as the external operating means is converted into the amount of linear movement by applying the differential pressure control method according to the first aspect. And controlling the rotation amount by driving the electric motor from the outside so as to give as an amount of extension to a tension coil spring interposed between the movable member operated by driving the electric motor and the control valve member. Since it is a flow rate proportional control valve for increasing or decreasing the generated force acting on the member, it is possible to cope with the case where the supply pressure of the fluid fluctuates, and the flow rate can be proportionally controlled by remote control, and It can be integrated as one device including the shut-off valve function and the like. Therefore, it is possible to reduce the equipment cost and simplify the control circuit, and to significantly improve the productivity, thereby contributing to a significant improvement in mass productivity.

According to the flow control valve of the present invention, the amount of rotation by the driving of the electric motor as the external operating means is converted into the amount of linear movement by applying the differential pressure control method of the first aspect. And controlling the amount of rotation by driving the electric motor from outside so as to give as a contraction amount to a compression coil spring interposed between the movable member operated by driving the electric motor and the control valve member, Since it is a flow rate proportional control valve for increasing or decreasing the generated force acting on the member, it is possible to cope with the case where the supply pressure of the fluid fluctuates, and the flow rate can be proportionally controlled by remote control, and It can be integrated as one device including the shut-off valve function and the like. Therefore, it is possible to reduce the equipment cost and simplify the control circuit, and to significantly improve the productivity, thereby contributing to a significant improvement in mass productivity.

Further, according to the flow control valve according to the fifth aspect of the present invention, the differential pressure control system according to the first aspect is applied, and the operation amount of the flow setting operation member as the external operation means is controlled by the flow setting valve. Increase or decrease of the generated force acting on the control valve member by manually operating the tension valve spring interposed between the movable member operated by the operation of the operating member and the control valve member as an extension amount. Is a manual variable flow rate proportional control valve that can cope with fluctuations in the supply pressure of the fluid, and can increase or decrease the flow rate by manual operation. It can be put together as a device. Therefore, it is possible to reduce the equipment cost, greatly improve the productivity, and contribute to a great improvement in the mass productivity.

According to a sixth aspect of the present invention, there is provided a flow rate control valve to which the differential pressure control method according to the first aspect is applied, the control valve member has a solenoid-operated closing valve function by a solenoid, and is provided as an external operating means. A constant flow control valve with a closing valve function that obtains the generated force acting on the control valve member by a spring force of a coil spring that urges the control valve member in the valve opening direction and performs a constant flow rate control. In this case, it is possible to cope with the case where the supply pressure fluctuates, to control the flow rate to be constant, and to combine them as one device including a shutoff valve function and the like. Therefore, it is possible to reduce the equipment cost and simplify the control circuit, and to significantly improve the productivity, thereby contributing to a significant improvement in mass productivity.

Further, according to the flow control valve according to the present invention, the differential pressure control system according to the first aspect is applied, and the coil spring is interposed between the valve housing and the control valve member. Is a constant flow control valve that obtains the generated force acting on the control valve member by the spring force of the constant flow control valve that performs constant control of the flow rate. Can be controlled. Therefore, it is possible to reduce the equipment cost, greatly improve the productivity, and contribute to a great improvement in the mass productivity.

[Brief description of drawings]

FIG. 1 is a general layout diagram showing a water supply pipeline leading to a flow control valve and each control device.

FIG. 2 is a configuration diagram for explaining a conventional control method.

FIG. 3 is a configuration diagram for explaining an outline of the present invention and a new control method, and is a diagram showing a valve closed state.

FIG. 4 is a configuration diagram for explaining the outline of the present invention and a new control method, similarly to FIG. 3, and is a diagram showing a valve open state.

FIG. 5 is a flow rate characteristic diagram for explaining the flow rate proportional control characteristic of the present invention.

FIG. 6 is a longitudinal sectional view showing a flow control valve as a first embodiment to which the present invention is applied.

FIG. 7 is a view as viewed in the direction of the arrow A, showing a water outlet of FIG. 6;

FIG. 8 is a partial longitudinal sectional view showing the vicinity of a differential pressure plate of a flow control valve as a second embodiment to which the present invention is applied.

FIG. 9 is a view on arrow B showing the differential pressure plate of FIG. 8;

FIG. 10 is a partial longitudinal sectional view showing the vicinity of a differential pressure plate of a flow control valve as a third embodiment to which the present invention is applied.

FIG. 11 is a view as viewed in the direction of arrow C, showing the differential pressure plate of FIG. 10;

FIG. 12 is a longitudinal sectional view showing a flow control valve as a fourth embodiment to which the present invention is applied.

FIG. 13 is a longitudinal sectional view showing a flow control valve as a fifth embodiment to which the present invention is applied.

FIG. 14 is a longitudinal sectional view showing a flow control valve as a sixth embodiment to which the present invention is applied.

FIG. 15 is a longitudinal sectional view showing a flow control valve as an eighth embodiment to which the present invention is applied.

FIG. 16 is a vertical sectional view showing a flow rate control valve as a ninth embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Valve housing 2 Water inlet 3 Outlet 4 Main valve seat 5 Main valve body 6 Diaphragm 7 Primary pressure chamber 8 Back pressure chamber 9 Secondary pressure chamber 10 Control valve member 11 Plunger 12 Pilot valve 13 Differential pressure plate 14 Communication passage 15 Solenoid 16 Small screw 18 Motor 19 Reducer 20 Screw feed mechanism 21 Tension coil spring 22 Compression coil spring 25 Knob for setting flow rate 26 Flow rate display plate 30 Solenoid 31 Pedestal 32 Sliding member 40 Sliding member 41 Compression coil spring 42 Spring seat 43 Adjuster for adjusting spring force

Claims (7)

[Claims] 1. A main valve seat provided in a flow passage extending from an inlet to an outlet, and a main valve seat provided at a central portion of a diaphragm having a back pressure chamber, the main valve seat being disposed to face the main valve seat. A main valve body that opens and closes, a primary pressure chamber on the water inlet side with the diaphragm as a boundary, a secondary pressure chamber on the water outlet side with the diaphragm as a boundary, the primary pressure chamber and the back pressure chamber. A communication hole that communicates, a pilot valve hole that communicates the back pressure chamber and the secondary pressure chamber, a control valve member provided so as to penetrate the pilot valve hole, the control valve member, A pilot valve for closing a pilot valve hole and a differential pressure plate provided in the main valve opening on the side of the water outlet from the main valve seat are integrated, and the flow rate of the water outlet is controlled by the control valve. Flow control that can be set by the generated force applied to the member The use, the flow rate of the water outlet Q, the passage open area around the difference pressure plate A4, a constant differential pressure before and after the difference pressure plate as .DELTA.P3,
The following equation Q∝A4√ (ΔP3) is established to control the outlet flow rate Q with the constant differential pressure ΔP3 corresponding to the generated force acting on the control valve member. Flow control method by pressure control method. 2. A flow housing, a water inlet, a water outlet, a main valve seat, a main valve opening, a diaphragm, a back pressure chamber, a main valve body, and
A flow control valve to which the flow rate control method according to claim 1 is applied, comprising a primary pressure chamber, a secondary pressure chamber, a communication hole, a pilot valve hole, a control valve member, a pilot valve, and a differential pressure plate. There is provided a solenoid as an external operating means for the generated force to be applied to the control valve member, and the amount of current supplied to the solenoid is externally controlled to increase or decrease the generated force to be applied to the control valve member. A flow control valve characterized by being configured to be changeable. 3. A flow housing, a water inlet, a water outlet, a main valve seat, a main valve opening, a diaphragm, a back pressure chamber, a main valve body, in a valve housing,
A flow control valve to which the flow rate control method according to claim 1 is applied, comprising a primary pressure chamber, a secondary pressure chamber, a communication hole, a pilot valve hole, a control valve member, a pilot valve, and a differential pressure plate. There is an electric motor as an external operation means of the generated force that acts on the control valve member, and a tension coil spring interposed between the movable member operated by the drive of the electric motor and the control valve member. The control valve member is configured to control the rotation amount by driving the electric motor from the outside so as to convert the rotation amount by driving the electric motor into a linear momentum and provide the tension coil spring as an extension amount. A flow control valve, which is configured to be capable of increasing / decreasing the generated force to be applied to the flow control valve. 4. A flow housing, a water inlet, a water outlet, a main valve seat, a main valve opening, a diaphragm, a back pressure chamber, a main valve body, and
A flow control valve to which the flow rate control method according to claim 1 is applied, comprising a primary pressure chamber, a secondary pressure chamber, a communication hole, a pilot valve hole, a control valve member, a pilot valve, and a differential pressure plate. There is an electric motor as an external operation means of the generated force to be applied to the control valve member, and a compression coil spring provided between the movable member operated by the drive of the electric motor and the control valve member. The control valve member is configured to control the rotation amount by driving the electric motor from the outside so as to convert the rotation amount by driving the electric motor into a linear momentum and give the compression coil spring as a contraction amount. A flow control valve, which is configured to be capable of increasing / decreasing the generated force to be applied to the flow control valve. 5. A flow housing, a water inlet, a water outlet, a main valve seat, a main valve opening, a diaphragm, a back pressure chamber, a main valve body,
A flow control valve to which the flow rate control method according to claim 1 is applied, comprising a primary pressure chamber, a secondary pressure chamber, a communication hole, a pilot valve hole, a control valve member, a pilot valve, and a differential pressure plate. And a flow rate setting operation member as an external operation means of the generated force to be applied to the control valve member, and a movable member operated by operation of the flow rate setting operation member and the control valve member. A tension coil spring that is provided, and is manually operated from the outside to give the operation amount of the flow rate setting operation member as an extension amount to the tension coil spring to increase or decrease the generated force that acts on the control valve member. A flow control valve characterized by being configured to enable it. 6. A flow housing, a water inlet, a water outlet, a main valve seat, a main valve opening, a diaphragm, a back pressure chamber, a main valve body,
A flow control valve to which the flow rate control method according to claim 1 is applied, comprising a primary pressure chamber, a secondary pressure chamber, a communication hole, a pilot valve hole, a control valve member, a pilot valve, and a differential pressure plate. There is provided a coil spring for urging the control valve member in the valve opening direction as an external operation means of the generated force applied to the control valve member, and an opening / closing operation of a closing valve function for the control valve member. A solenoid is provided, a closing valve function is provided, and the force generated on the control valve member is obtained by the spring force of the coil spring to enable constant control of the flow rate. Flow control valve. 7. The flow channel, the water inlet, the water outlet, the main valve seat, the main valve seat, the diaphragm, the back pressure chamber, the main valve body, inside the valve housing,
A flow control valve to which the flow rate control method according to claim 1 is applied, comprising a primary pressure chamber, a secondary pressure chamber, a communication hole, a pilot valve hole, a control valve member, a pilot valve, and a differential pressure plate. And a coil spring provided between the valve housing and the control valve member, wherein the spring force of the coil spring obtains the generated force to act on the control valve member to control the flow rate constantly. A flow control valve characterized by being configured so as to enable.