JP3112049B2 - Automatic shut-off valve with pressure control function - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

[Object of the invention]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid control valve applicable to a self-closing flush valve in a flush toilet, and more particularly, to a fluid control valve having both a water stop function and a pressure or flow rate control function. It relates to a control valve.

[0002]

2. Description of the Related Art An automatic closing type washing valve is used in a washing device of a flush toilet, and supply of washing water is automatically stopped after operating the washing valve manually or electrically. This type of self-closing flush valve has a pressure chamber defined by a diaphragm valve or a piston valve, which is provided with a metered orifice having a calibrated diameter. After the washing operation, the pressurized water from the water supply gradually flows into the pressure chamber through the metering orifice, and gradually closes the diaphragm valve or the piston valve. As described above, the pressure chamber and the orifice ease the closing operation of the cleaning valve and prevent the occurrence of the water hammer phenomenon in the water supply system. Another important function of the pressure chamber is to press the diaphragm valve or the piston valve with sufficient force toward the valve seat by the primary water pressure to perform a complete water stop.

[0003]

By the way, the water pressure of the water supply system differs from building to building, also from floor to floor within the same building, and also varies depending on the time of day. Water supply pressure to the device is 2 to 10 kg / cm
It fluctuates in the range of ² . If the primary water pressure of the flush valve is higher than necessary, the flow rate of flush water supplied to the toilet via the flush valve becomes excessive. For example, in the case of a urinal, there is a problem that water is splashed from the urinal.

Further, when the washing valve is provided with a pilot solenoid valve for opening a diaphragm valve or a piston valve, and this solenoid valve is driven by an electric control circuit, it is necessary to mass-produce the washing apparatus. It is convenient to set the energization time of the solenoid valve uniformly constant for all the cleaning devices. However, when the flow rate of the cleaning valve fluctuates due to the fluctuation of the water supply pressure as described above, the total amount of cleaning water per cleaning fluctuates when the energization time of the solenoid valve is set to be constant.
If the solenoid valve opening time is set long so that the optimum total flushing water per wash is obtained at the rated minimum water pressure, the total flushing water per flush will increase if the water pressure increases. It becomes excessive and wastes water resources. On the other hand, if the solenoid valve opening time is set short so that the optimal total flushing water per wash is obtained at the rated maximum water pressure, when operating at a lower water pressure, the Washing water volume is insufficient.

[0005] In order to solve such a problem, it is necessary to connect a constant flow valve to the automatic closing type cleaning valve. However, in that case, the size of the cleaning device becomes large, and the number of parts and the cost increase.

It is an object of the present invention to provide a compact automatic shut-off valve having a pressure control function or a flow control function.

[0007] In another aspect, an object of the present invention is to provide a compact automatic closure which is capable of obtaining a constant flow rate irrespective of fluctuations in water supply pressure and which is free from splashes when applied to a urinal cleaning apparatus. It is to provide a valve.

[0008] In another aspect, an object of the present invention is to provide a compact automatic closing device for a washing apparatus capable of obtaining an optimum amount of washing water per washing regardless of fluctuations in water supply pressure and contributing to water saving. It is to provide a valve.

In another aspect, an object of the present invention is to provide an automatic shut-off valve having a pressure control function or a flow control function, which can be driven by the energy of a dry battery.

[0010] In yet another aspect, it is an object of the present invention to provide a compact fluid control valve with complete water shutoff and pressure or flow control.

[0011]

Configuration of the Invention

SUMMARY OF THE INVENTION The fluid control valve of the present invention includes a housing having a fluid passage with a valve seat formed therein. A closing member is arranged downstream of the valve seat and receives the primary pressure upstream of the valve seat in the valve opening direction. A pressure receiving member such as a diaphragm or a piston for receiving a primary pressure upstream of the valve seat in the opposite direction is connected to the closing member, and the valve is closed by a force acting on the closing member in the valve opening direction by the primary pressure and the primary pressure. The force acting on the pressure receiving member in the direction is canceled.

The closing member is urged in the valve closing direction by hydraulic urging means having a pressure chamber. The closure member also
It is urged in the valve opening direction by mechanical urging means such as a compression coil spring. In the pressure chamber of this hydraulic biasing means,
Control means having an electromagnetic valve or the like selectively introduces a primary pressure upstream of the valve seat and a secondary pressure downstream of the valve seat.

The control of the secondary pressure is performed by applying the secondary pressure to the pressure chamber of the hydraulic biasing means. When a secondary pressure is applied to the pressure chamber, the degree of opening of the closing member is determined by the balance between the force of the secondary pressure in the pressure chamber and the force of the coil spring, and the secondary pressure is controlled to be constant. Since the flow rate Q of the fluid flowing through a given flow path is a function of the flow rate coefficient Cv of the flow path and the pressure P (Q = kCvP1 / ² ), the secondary pressure is controlled to be constant in this way. Then, the flow rate of the flow path becomes constant.

When the primary pressure is introduced into the pressure chamber of the hydraulic urging means by switching the control means, the closing member is pressurized toward the valve seat by the hydraulic urging means, and is brought into close contact with the valve seat, so that the water is stopped. Is performed. Preferably, the introduction of the primary pressure takes place via a communication passage with a throttle, the valve closing action being delayed in order to prevent the occurrence of a water hammer phenomenon.

In a preferred embodiment of the invention, the closing member and the hydraulic biasing means can be formed as a single piston valve or a diaphragm valve.

The above-mentioned features and effects, as well as other features and advantages of the present invention will become more apparent according to the description of the following embodiments.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below in detail with reference to the accompanying drawings showing embodiments of the present invention.

FIGS. 1 to 4 show a fluid control valve according to a first embodiment of the present invention. This fluid control valve can be used as an automatic shut-off valve of a cleaning device. FIG. 1 shows the components of the fluid control valve in a rest position before use, FIG. 2 shows a variation of the pressure receiving means shown in FIG.
Indicates the positional relationship of the components in the pressure control mode,
FIG. 4 shows the positional relationship of the components in the water stop mode.
Referring to FIG. 1, a fluid control valve 10 has a housing 12, which has an inlet 1 connected to a water pipe.
4 and an outlet 16 connected to, for example, a urinal (not shown), and a fluid passage 18 communicating between them. An annular valve seat 20 is formed in the housing 12 so as to cross the fluid passage 18, and a closing member 24 provided with a packing 22 is engaged with the valve seat 20 from the downstream side of the valve seat 20. I have.

Since the closing member 24 is disposed on the downstream side of the valve seat 20, the closing member 24 receives the primary pressure upstream of the valve seat 20 for the effective opening area of the valve seat 20, and releases the force due to the primary pressure. The force is received in the valve direction, but this force is offset by the force acting on the pressure receiving means 26 in the opposite direction due to the primary pressure. That is, in the embodiment shown in FIG. 1, the pressure receiving means 26 comprises a bellows type diaphragm 28 which is disposed coaxially with the valve seat 20 and on the side opposite to the closing member 24. Has been concluded. Diaphragm 28 is connected to closing member 24 by a valve shaft 32. The effective pressure receiving area of the diaphragm 28 is set to be equal to the effective pressure receiving area of the closing member 24, that is, the effective opening area of the valve seat 20. Therefore, the force acting on the closing member 24 in the valve opening direction (upward in FIG. 1) by the primary pressure is offset by the force acting downward on the diaphragm 28 by the primary pressure. Thus, the closure member 24 is not affected by the primary pressure.

In the embodiment shown in FIG. 1, the bellows diaphragm 28 has a function as a mechanical biasing means 34 for applying an upward spring force to the closing member 24, in addition to the function as the pressure receiving means 26. ing. For this reason, the bellows-type diaphragm 28 is attached to the housing 12 in a state where it is sufficiently compressed in the axial direction from its free extension state. However, a normal diaphragm may be used as the pressure receiving means 26 instead of the bellows-type diaphragm 28, and a separate compression coil spring may be used as the mechanical biasing means 34 to apply an upward spring force to the closing member 24. Alternatively, as in the variation shown in FIG. 2, a piston 36 slidably fitted in a bore of the housing 12 is used as the pressure receiving means 26 instead of the diaphragm 28, and a compression coil spring is used as the mechanical biasing means 34. 38 may be used. Also in this case, the effective pressure receiving area of the piston 36 is substantially equal to the effective pressure receiving area of the closing member 24.

Referring again to FIG. 1, the closure member 24 comprises
It is urged in the valve opening direction by the mechanical urging means 34 and urged in the valve closing direction toward the valve seat 20 by the hydraulic urging means 40. In the pressure control mode (FIG. 3), the urging force generated by the hydraulic urging means 40 changes according to the secondary pressure downstream of the valve seat 20 as will be described later, and between the closing member 24 and the valve seat 20. Is formed with a variable gap, which acts as a restrictor for the fluid passage 18 and causes a pressure drop across the valve seat 20. As will be described in more detail later, the closing member 24 is stabilized at a position where the urging force of the hydraulic urging means 40 and the urging force of the mechanical urging means 34 are balanced, and performs feedback control of the secondary pressure. In the water stopping mode (FIG. 4), the force of the hydraulic urging means 40 overcomes the force of the mechanical urging means 34, and the closing member 24 is pressed against the valve seat 20, so that the fluid passage 18 is shut off. Water is stopped. Therefore, in the water stop mode, the hydraulic biasing means 40 also acts as a hydraulic pressing means for pressing the closing member 24 to the valve seat 20.

In the illustrated embodiment, the hydraulic biasing / pressing means 40 has a cylinder bore 42 formed in the housing 12 and a piston 44 slidably fitted in the cylinder bore 42. And the piston 4
A pressure chamber 46 is defined above 4. An annular space 48 formed below the piston 44 on the outer periphery of the valve seat 20 communicates with the outlet 16 and receives a secondary pressure or an atmospheric pressure downstream of the valve seat 20 depending on the operation mode of the fluid control valve 10. In the embodiment shown, the piston 44 and the closing member 24 are formed as one integral piston valve 50. The piston valve 50 is fitted into the cylinder bore 42 with a small clearance, and this clearance is sealed by a Y packing 51 mounted on the outer periphery of the piston valve 50. As will be apparent to those skilled in the art, a diaphragm is formed by defining a pressure chamber 46 using a conventional diaphragm (not shown) in place of the piston 44 and securing the closure member 24 to the diaphragm. Is also good.

The fluid under the primary pressure is introduced into the pressure chamber 46 of the hydraulic biasing means 40 in the water stop mode of the fluid control valve 10, and the fluid under the secondary pressure is introduced in the pressure control mode. . The introduction of the pressurized fluid into the pressure chamber 46 is selectively performed by a control means 52. The control means 52 includes a first communication passage 54 that communicates the fluid passage 18 upstream of the valve seat 20 with the pressure chamber 46; Fluid passage 1 downstream of valve seat 20
8 has a second communication path 56 that communicates with the pressure chamber 46, and switching means 58 that selectively connects these communication paths 54 and 56 to the pressure chamber 46.

In the embodiment shown, this switching means 58
Comprises a solenoid valve 60, which has a movable plunger 62. As shown, the second communication path 56
Is formed in a projection 64 projecting from the housing 12 into the pressure chamber 46 coaxially with the plunger 62, and a port 66 provided at the tip of the projection 64 is provided with a plunger 62.
Is opened and closed by a closing member made of a packing 68 provided at the tip of the. The port 70 of the first communication passage 54 is offset from the axis of the plunger 62,
The port 70 is opened and closed by a flange 72 of the plunger 62. This port 70 is the first
It is preferable to determine the diameter so as to act as a restriction of the communication passage 54.

To enable the solenoid valve 60 to be driven by the energy of the dry cell, the illustrated embodiment uses a latch-type solenoid valve 60 with a permanent magnet 74.
In the rest position shown in FIG. 1, the plunger 62 is biased toward the projection 64 by the compression coil spring 76, and the port 66 is closed. Solenoid coil 7
8, when the plunger 62 is attracted, the plunger 62 contacts the yoke 80, and a magnetic circuit of the permanent magnet 74 is formed through the plunger 62 and the yoke 80, as is well known. Even when the energization is stopped, the plunger 62 remains in the yoke 80 as shown in FIG.
Is latched at the position where it abuts. In this state, port 66 is open and port 70 is closed. When the solenoid coil 78 is energized in the reverse direction, the plunger 62 is released and returns to the rest position shown in FIG. 1, and the plunger 62 is moved to this position by the action of the compression coil spring 76 and the action of the fluid pressure in the pressure chamber 46. Is held. Coil spring 7
In order to minimize the power required to pull up the plunger 62 against the action of 6 and the action of the fluid pressure, and to allow the energy of the dry cell to operate the fluid control valve 10 for an extended period of time, the second Port 6 of communication passage 56
It is preferable that the diameter of 6 is as small as possible. Also,
In order to reliably latch the plunger 62 at the attraction position by the magnetic force of the permanent magnet 74 at the attraction position shown in FIG. 3, the plunger 62 is in close contact with the yoke 80 and there is no gap in the magnetic circuit by the permanent magnet 74. desirable. To this end, the plunger 62 is
It is preferable to set the axial dimension of the solenoid valve 60 so that a minute clearance is secured between the flange 72 and the cylinder bore 42.

In the embodiment shown in FIG.
Is provided with a stopper 82 in the form of a central projection. The stopper 82 abuts against the projection 64 of the housing 12 so that the stroke of the piston valve 50 is determined. When the fluid control valve 10 is used as a flush valve for a urinal, if the piston valve stroke of about 2 mm is secured, the pressure control function of the fluid control valve 10 can be exhibited in the pressure control mode. As previously mentioned,
The bellows type diaphragm 28 is attached to the housing 12 in a state where it is sufficiently compressed in the axial direction when the stopper 82 hits the projection 64 in the non-use state shown in FIG. 2
8 is given a predetermined sufficient preload.

The solenoid valve 60 of the fluid control valve 10 can be controlled by an electronic control unit 84. Fluid control valve 1
If 0 is applied to a urinal flushing device, the control device 84 can be configured and operated, for example, in accordance with the disclosure of US Pat. No. 4,742,583. As disclosed in the patent, the control device 84 emits an infrared pulse at a predetermined timing, and when the control device 84 detects the use of the urinal based on the reflected light from the human body, the control device 84 controls the solenoid coil 78 of the solenoid valve 60 for a predetermined time. Turn on electricity. Thereby, the plunger 62
Is attracted to the operating position as shown in FIG.
4 latches in this position.

In this position, the port 7 of the first communication passage 54
0 is closed by the flange 72 of the plunger 62,
The port 66 of the second communication path 56 is opened. Accordingly, the secondary pressure P2 downstream of the valve seat 20 is applied to the pressure chamber 46 via the second communication passage 56, and the piston valve 50 is urged toward the valve seat 20 with a force F2 corresponding to the secondary pressure. You. Valve seat 2
0 is under a secondary pressure, so that the pressure chamber 4
The force F2 acting on the piston valve 50 in the valve closing direction due to the secondary pressure P2 in 6 is equal to the product of the effective opening area S _VS of the valve seat 20 and the secondary pressure P2 (F2 = P2 × S _VS ). As described above, the force acting on the piston valve 50 in the valve opening direction due to the primary pressure P1 at the inlet 14 is offset by the force acting on the diaphragm 28 in the valve closing direction due to the primary pressure.
On the other hand, the bellows-type diaphragm 2
8, a spring force FB acting in the valve opening direction is applied, and a sufficient preload is applied to the diaphragm 28, so that this force FB can be considered to be substantially constant regardless of the position of the piston valve 50. . Thus, the piston valve 50 is stable at a position where the secondary pressure P2 by the force F2 and the spring forces FB are balanced, secondary pressure P2 is feedback-controlled such that P2 = FB / S _VS. Thus, the secondary pressure P2 of the fluid control valve 10 is independent of the primary pressure P1,
Bellows-type diaphragm 2 as mechanical biasing means 34
8, the secondary pressure P2 is controlled to be constant in the pressure control mode. Therefore, the flow rate of the water supplied to the urinal is also constant.

When a predetermined amount of water is supplied to the urinal, the controller 84 energizes the solenoid coil 78 in the reverse direction for a predetermined time. As a result, the plunger 62 is released,
It returns to the rest position (water stop position) shown in FIG. In this position, the second communication path 56 is shut off and the first communication path 54 communicates with the pressure chamber 46, so that water under the primary pressure P1 at the fluid inlet 14 flows into the pressure chamber 46. First communication passage 5
4 is provided with a throttle 70 having a predetermined diameter, so that water under the primary pressure gradually flows into the pressure chamber 46 and the piston valve 5
0 is gradually closed. When the piston valve 50 is pressurized by the water pressure P1 in the pressure chamber 46 and the closing member 24 of the piston valve 50 comes into close contact with the valve seat 20, the water stoppage is completed and the pressure at the fluid outlet 16 becomes the atmospheric pressure. Is also reflected in the space 48 on the outer periphery of the valve seat 20. Therefore, the piston valve 50 has a primary pressure P for its effective pressure receiving area _SPN.
1 acts, and the force F1 becomes F1 = P1 × _SPN . The minimum force F _MIN required for complete water stoppage is determined by the spring force FB of the bellows-type diaphragm 28 and the packing 22 of the closing member 24.
Because it is the sum of the compression force F _COM of (F _MIN = FB +
F _COM ), F1 ≧ FB + at rated minimum pressure P1 _MIN
The effective pressure receiving area S _PN of the piston valve 50 so that F _COM is obtained.
Is designed to completely stop water in the water stop mode.

The embodiment using the solenoid valve 60 driven by the electronic control unit 84 as the switching means 58 for selectively connecting the communication passages 54 and 56 to the pressure chamber 46 has been described above. Alternatively, a manual valve manually operated by a push button and a lever mechanism can be used. Instead of opening and closing the communication paths 54 and 56 at the same time by one electromagnetic valve 60, a single shutoff valve may be provided in each of the communication paths 54 and 56.

FIGS. 5 and 6 show a second embodiment of the present invention. In the first embodiment of the invention described above with reference to FIGS. 1 to 4 and its variants, the piston valve 50 (diaphragm valve in the variant) and the pressure chamber 46 have a secondary pressure in the pressure control mode. And act as hydraulic urging means 40 for urging the closing member 24 in the valve closing direction in response to the pressure, and as a hydraulic pressurizing means for pressing the closing member 24 to the valve seat 20 by the primary pressure in the water stop mode. Was something. The second embodiment shown in FIGS. 5 and 6 is characterized in that the hydraulic biasing means and the hydraulic pressurizing means are separately provided.

Referring to FIGS. 5 and 6, FIG. 5 shows the positional relationship of the components in the pressure control mode, and FIG. 6 shows the positional relationship in the water stop mode. 5 and 6, components having the same functions as those of the first embodiment are denoted by the same reference numerals, and description thereof is omitted. Only the difference will be described. In the fluid control valve 100 of the second embodiment, the piston valve 50 of the hydraulic biasing means 40 is the first valve.
Housing 1 without using Y packing 51 of the embodiment
The second cylinder bore 42 is fitted. Piston valve 50
A sufficient clearance is provided between the outer periphery of the cylinder bore 42 and the cylinder bore 42, so that the annular space 4 is provided in the pressure control mode.
The secondary pressure of 8 is introduced into the pressure chamber 46 through this clearance. Therefore, in the pressure control mode shown in FIG. 5, the secondary pressure is adjusted by the balance between the urging force of the hydraulic pressure based on the secondary pressure in the pressure chamber 46 and the spring force of the bellows diaphragm 28 in the first embodiment. Is feedback-controlled in the same manner as described above.

In the fluid control valve 100, the piston valve 50 is pressurized to the valve seat 20 by the hydraulic pressurizing means 102 in the water stop mode. For this reason, a second cylinder bore 104 is formed in the housing 12, and the internal space of the cylinder bore 104 is divided by a diaphragm 106 into a second pressure chamber 108 and a third chamber 110. The third chamber 110 communicates with the atmosphere by a bleed hole 112 formed in the wall of the housing 12, and the third chamber 110 functions as an atmospheric pressure chamber. The first pressure chamber 108 has a first pressure chamber for introducing a fluid under a primary pressure.
Communication path 54 and second communication path 56 for introducing secondary pressure
Are opened, and these communication passages 54 and 56 are selectively opened and closed by a solenoid valve 60 as in the first embodiment. The diaphragm 106 is fixed to an output shaft 114 which also serves as a diaphragm holder and a stopper, and is urged upward by a compression coil spring 116. The coil spring 116 is set so as to generate a spring force smaller than the force acting on the diaphragm 106 by the primary pressure and larger than the force acting on the diaphragm 106 by the secondary pressure. Therefore, as shown in FIG. 5, when the first communication passage 54 is shut off by the solenoid valve 60 in the pressure control mode and the secondary pressure is applied to the second pressure chamber 108 via the second communication passage 56, , The output shaft 114 is remote from the valve shaft 32 and does not interfere with the movement of the piston valve 50. Therefore, the piston valve 50 is displaced according to the secondary pressure in the pressure chamber 46, and performs feedback control of the secondary pressure.

In the water stopping mode, as shown in FIG. 6, the plunger 62 of the solenoid valve 60 is released, the second communication path 56 is shut off, and the first communication path 54 is opened. Accordingly, the fluid under the primary pressure flows into the second pressure chamber 108 via the throttle 70. As the pressure in the second pressure chamber 108 increases, the diaphragm 106 pushes down the output shaft 114 against the action of the coil spring 116. The output shaft 114 eventually comes into contact with the valve shaft 32 and pushes it down, and the closing member 24
To the valve seat 20. In this way, the water stoppage is performed using the primary pressure as in the first embodiment.

In the first embodiment, the Y packing 51 is fitted around the outer periphery of the piston valve 50. On the other hand, in the second embodiment, since the Y packing is not used, the sliding resistance of the piston valve 50 is reduced. It has the advantage of being small.

In the first and second embodiments described above, the flange 72 of the plunger 62 of the solenoid valve 60 completely closes the port 70 of the first communication passage 54 in the pressure control mode shown in FIGS. It is desirable. However, when the latch type solenoid valve 60 is used,
As described above, in order to securely latch the plunger 62 in the operating position by the magnetic force of the permanent magnet 74, the flange 72 and the port 70 of the plunger 62 in the operating position are required.
It is preferable to secure a small clearance with the end face. For this reason, when the specifications are set so that sufficient water stoppage is performed under a low primary pressure (for example, 1 kg / cm ² ), when the fluid control valve is used under a higher primary pressure, the pressure is reduced. In the control mode, fluid under the primary pressure leaks into the pressure chamber 46 or 108 and the pressure chamber 46 or 108
Due to the increase in the pressure inside, the piston valve 50 may be unintentionally closed in spite of the pressure control mode.

FIG. 7 shows a variation of the second embodiment.
The purpose is to eliminate such inconvenience. FIG.
In the second embodiment, components having the same functions as those of the second embodiment are denoted by the same reference numerals, and description thereof is omitted. The main difference from the second embodiment is that the diameter of the output shaft 114 of the hydraulic pressurizing means 102 is increased, and the first communication passage 54 and the third chamber 110 are communicated with each other by the passage 120. The primary pressure is applied to the chamber 110 to make the chamber 110 function as a third pressure chamber.

In the pressure control mode shown in FIG.
The secondary pressure in the second pressure chamber 108 acts on the diaphragm 106 of the hydraulic pressurizing means 102 downward. But,
The primary pressure in the third pressure chamber 110 acts on the diaphragm 106 upward, and the force applied to the output shaft 114 by the secondary pressure in the first pressure chamber 46 acts upward,
Further, the force of the coil spring 116 acts upward. Therefore, the first communication passage 5 formed by the flange 72 of the plunger 62
The output shaft 114 will not pressurize the valve shaft 34 even if the primary pressure leaks into the second pressure chamber 108 due to insufficient closure of the port 70 of the fourth. Therefore, even if the primary pressure is high (for example, 5 kg / cm ² ), the variation in FIG.
A pressure control function can be exhibited.

In the water stopping mode, when the primary pressure is introduced into the second pressure chamber 108 by releasing the plunger 62 of the solenoid valve 60, the diaphragm 106 outputs the output against the secondary pressure in the first pressure chamber 46. The shaft 114 is pushed down, and the piston valve 50 is closed. After the water is stopped, the fluid outlet 16 has the atmospheric pressure, and as a result, the first pressure chamber 46 also has the atmospheric pressure.
Diaphragm 106 ensures that piston valve 50 remains closed.

[0040]

According to the present invention, the secondary pressure is controlled to be constant in the pressure control mode, so that the fluid control valve of the present invention functions as a pressure control valve or a constant flow valve during fluid supply. . In the water stopping mode, the closing member 24 is pressed against the valve seat 20 by the action of the primary pressure, so that the water stopping operation is reliably performed. In the first embodiment of the present invention, these two functions are achieved only by selectively introducing the primary pressure or the secondary pressure into the pressure chamber 46 by switching the solenoid valve 60, so that one common piston valve 50 is provided. (Or a diaphragm valve), so that the fluid control valve can be extremely compact.

Since the fluid control valve of the present invention has a pressure control function (and a flow rate control function) and a water stop function as described above, when applied to a washing valve, the primary water pressure varies widely. Even under such conditions, a constant flow rate can always be obtained, contributing to water saving and preventing splashing of splashes.

Since this cleaning valve is operated only by opening and closing the ports 66 and 70 of the communication path by the solenoid valve 60, it can be driven by a dry battery.

When a latch-type solenoid valve is used as the solenoid valve 60, the cleaning valve can be operated for a long time by the energy of the dry battery.

[Brief description of the drawings]

FIG. 1 is a schematic cross-sectional view of a first embodiment of the fluid control valve of the present invention, showing components in a rest position prior to use.

FIG. 2 is a partial cross-sectional view showing a variation of the pressure receiving means of the first embodiment.

FIG. 3 is a partially cut-away schematic sectional view of the first embodiment, showing a positional relationship of components in a pressure control mode.

FIG. 4 is a partially cut-away schematic sectional view of the first embodiment, showing a positional relationship of components in a water stop mode.

FIG. 5 is a schematic sectional view of a fluid control valve according to a second embodiment of the present invention, which is in a pressure control mode.

FIG. 6 is a schematic cross-sectional view of the second embodiment, showing a state in a water stop mode.

FIG. 7 is a schematic cross-sectional view of a variation of the second embodiment, showing the pressure control mode.

[Explanation of symbols]

 10, 100: Fluid control valve 12: Control valve housing 14: Fluid inlet 16: Fluid outlet 18: Fluid passage 20: Valve seat 24: Closing member 26: Pressure receiving member 34: Mechanical biasing means 40: Hydraulic bias Means 42: Cylinder bore of housing 44: Piston 46: Pressure chamber (first pressure chamber) 50: Piston valve 52: Control means 54: First communication path 56: Second communication path 58: Switching means 60: Solenoid valve 102: Liquid Pressure type pressurizing means 108: Second pressure chamber 110: Third pressure chamber

Continuation of front page (72) Inventor Hiroyuki Matsushita 2-1-1 1-1 Nakajima, Kokurakita-ku, Kitakyushu-shi, Fukuoka Prefecture Totoki Co., Ltd. (56) References JP-A-2-46376 (JP, A) JP-A-Hei 3-292483 (JP, A) Japanese Utility Model 3104585 (JP, U) Japanese Utility Model 3-104580 (JP, U) Japanese Utility Model 62-25764 (JP, Y2) Japanese Utility Model 55-62525 (JP, U2) Y2) (58) Field surveyed (Int. Cl. ⁷ , DB name) F16K 21/00-21/20 F16K 31/12-31/42 E03D 3/04

Claims (17)

(57) [Claims] A housing having a fluid passage having a fluid inlet and a fluid outlet; a valve seat traversing the fluid passage; and controlling a flow of the fluid flowing through the fluid passage in cooperation with the valve seat. A movable closing member disposed downstream of the valve seat for receiving fluid pressure upstream of the valve seat (hereinafter, primary pressure) in a valve opening direction; and a housing for receiving primary pressure in a direction opposite to the direction. A pressure-receiving member arranged and having an effective pressure-receiving area substantially equal to the effective pressure-receiving area of the closing member; and a force and a primary pressure that connect the closing member and the pressure-receiving member to each other, and act on the closing member by the primary pressure in the valve-opening direction. A connection means for canceling a force acting on the pressure receiving member in the opposite direction, a biasing means for biasing the closing member in a valve opening direction, and a pressure chamber disposed in the housing, and a fluid in the pressure chamber. To pressure Hydraulic biasing means for biasing the closing member in the valve closing direction, and control means for selectively communicating the fluid passage upstream of the valve seat and the fluid passage downstream of the valve seat with the pressure chamber. The secondary pressure is controlled by introducing the fluid pressure downstream of the valve seat (hereinafter, secondary pressure) into the pressure chamber, and the fluid under the primary pressure upstream of the valve seat is transferred to the pressure chamber. A fluid control valve, wherein the valve is closed by being introduced into the fluid control valve. 2. The control means includes: a first communication passage communicating the fluid passage upstream of the valve seat with the pressure chamber; and a second communication passage communicating the fluid passage downstream of the valve seat with the pressure chamber. 2. The fluid control valve according to claim 1, further comprising a communication passage, and switching means for selectively connecting the first communication passage and the second communication passage to the pressure chamber. 3. The switching means comprises a single two-position valve, which in its first position connects the first communication passage to the pressure chamber and shuts off the second communication passage. In the second position, the first communication path is shut off and the second communication path is closed.
3. The fluid control valve according to claim 2, wherein the communication passage is connected to the pressure chamber. 4. The fluid control valve according to claim 3, wherein said single two-position valve is a solenoid valve. 5. The fluid control valve according to claim 4, wherein the solenoid valve is a latch type solenoid valve. 6. The fluid control valve according to claim 3, wherein said single two-position valve is a manual valve. 7. The switching means comprises separate shut-off valves provided in the first communication passage and the second communication passage, respectively.
Based fluid control valve. 8. A throttle is provided in the first communication path,
A fluid control valve according to any one of claims 2 to 7, wherein the valve closing movement of the closing member is mitigated by restricting the introduction of fluid under primary pressure into the pressure chamber. . 9. The fluid control valve according to claim 1, wherein the pressure receiving member has a piston slidably supported by a housing. 10. The pressure receiving member according to claim 1, wherein the pressure receiving member has a bellows diaphragm for urging the closing member in a valve opening direction, and the bellows diaphragm also serves as the urging means. Fluid control valve based on either. 11. The hydraulic biasing means includes a piston slidably fitted in the pressure chamber, wherein the piston and the closing member are integrally connected to each other to form one piston valve assembly. A fluid control valve according to any one of claims 1 to 10, characterized in that: 12. The hydraulic biasing means includes a diaphragm disposed in the pressure chamber, wherein the diaphragm and the closing member are integrally connected to each other to form one diaphragm valve assembly. A fluid control valve according to any of the preceding claims. 13. A housing comprising: a fluid passage having a fluid inlet and a fluid outlet; a valve seat traversing the fluid passage; and a cylinder bore formed downstream of the valve seat coaxially with the valve seat. A fluid pressure upstream of the valve seat is slidably fitted to the cylinder bore to define a pressure chamber in cooperation with the cylinder bore and to control the flow of fluid flowing through the fluid passage in cooperation with the valve seat. A piston valve for receiving pressure in the valve opening direction and receiving fluid pressure in the pressure chamber in a valve closing direction; and a valve disposed in the housing to receive fluid pressure upstream of a valve seat in the valve closing direction of the piston valve. A pressure-receiving member having an effective pressure-receiving area substantially equal to the effective opening area of the seat; connecting the piston valve and the pressure-receiving member to each other; Upstream Connecting means for canceling the force acting on the pressure receiving member in the opposite direction by the fluid pressure, urging means for urging the piston valve in the valve opening direction, and a fluid passage upstream of a valve seat and the pressure chamber. A first communication passage having a communication restriction, a second communication passage communicating the fluid passage downstream of the valve seat with the pressure chamber, and alternatively the first communication passage and the second communication passage are selected from the group consisting of: A single switching valve connected to the pressure chamber, and the second communication path is connected to the pressure chamber to control the fluid pressure downstream of the valve seat, and the first communication path is connected to the pressure chamber. An automatic closing valve, which is closed by being connected. 14. A housing comprising: a fluid passage having a fluid inlet and a fluid outlet; a valve seat traversing the fluid passage; and a pressure chamber formed downstream of the valve seat coaxially with the valve seat. Disposed in the pressure chamber downstream of the valve seat to control the flow of fluid flowing through the fluid passage in cooperation with the valve seat;
A diaphragm valve for receiving fluid pressure upstream of the valve seat in the valve opening direction and receiving fluid pressure in the pressure chamber in the valve closing direction; and a housing for receiving fluid pressure upstream of the valve seat in the valve closing direction of the diaphragm valve. A pressure-receiving member disposed and having an effective pressure-receiving area substantially equal to the effective opening area of the valve seat; and connecting the diaphragm valve and the pressure-receiving member to each other, and acting on the diaphragm valve in a valve-opening direction by fluid pressure upstream of the valve seat. Connecting means for canceling the force acting on the pressure receiving member and the force acting in the opposite direction by the fluid pressure upstream of the valve seat; biasing means for biasing the diaphragm valve in the valve opening direction; and a fluid passage upstream of the valve seat. A first communication passage having a throttle communicating with the pressure chamber; a second communication passage communicating a fluid passage downstream of a valve seat with the pressure chamber; and a first communication passage and a second communication passage. Alternatively A single switching valve connected to the pressure chamber, wherein a second communication path is connected to the pressure chamber to control fluid pressure downstream of a valve seat, and the first communication path is connected to the pressure chamber. An automatic shut-off valve, which is closed by being connected to a valve. 15. A housing having a fluid passage having a fluid inlet and a fluid outlet, a valve seat traversing the fluid passage, and controlling a flow of a fluid flowing through the fluid passage in cooperation with the valve seat. A movable closing member disposed downstream of the valve seat for receiving fluid pressure upstream of the valve seat (hereinafter, primary pressure) in a valve opening direction; and a housing for receiving primary pressure in a direction opposite to the direction. A pressure-receiving member arranged and having an effective pressure-receiving area substantially equal to the effective pressure-receiving area of the closing member; and a force and a primary pressure that connect the closing member and the pressure-receiving member to each other, and act on the closing member by the primary pressure in the valve-opening direction. A connection means for canceling the force acting on the pressure receiving member in the opposite direction, a biasing means for biasing the closing member in a valve opening direction, and a pressure chamber communicating with the fluid passage downstream of a valve seat. Downstream fluid pressure Hydraulic urging means for urging the closing member in the valve closing direction in response to the pressure, and a communication passage with a throttle which is opened and closed by an electromagnetic valve and communicates with a fluid passage upstream of the valve seat. A hydraulic pressurizing means for pressurizing the closing member in a valve closing direction, wherein the fluid pressure downstream of the valve seat is introduced into the pressure chamber, whereby the fluid pressure downstream of the valve seat is controlled, and An automatic closing valve, wherein the closing member is closed by pressurizing the closing member by a pressure type pressurizing means. 16. A housing comprising: a fluid passage having a fluid inlet and a fluid outlet; a valve seat traversing the fluid passage; and a cylinder bore formed coaxially with the valve seat downstream of the valve seat; Slidably fitted to the cylinder bore to control the flow of fluid flowing through the fluid passage in cooperation with a valve seat;
A piston defining a first pressure chamber communicating with the fluid passage downstream of the valve seat, receiving the fluid pressure upstream of the valve seat in a valve opening direction, and receiving the fluid pressure in the first pressure chamber in a valve closing direction; A valve, a pressure receiving member disposed in the housing to receive a fluid pressure upstream of a valve seat in a valve closing direction of the piston valve, the pressure receiving member having an effective pressure receiving area substantially equal to an effective opening area of the valve seat; Connecting means for connecting the members to each other, and canceling the force acting on the piston valve in the valve opening direction by the fluid pressure upstream of the valve seat and the force acting in the opposite direction on the pressure receiving member by the fluid pressure upstream of the valve seat. An urging means for urging the piston valve in a valve opening direction; and a second pressure chamber disposed in the housing, wherein the closing member moves in a valve closing direction in accordance with a fluid pressure in the second pressure chamber. Hydraulic pressurizing means for pressurizing And control means for selectively communicating the fluid passage upstream of the valve seat and the fluid passage downstream of the valve seat with the second pressure chamber. The fluid pressure downstream of the valve seat is controlled by the balance between the force acting on the piston valve in the valve closing direction and the force acting on the piston valve in the valve opening direction by the urging means. An automatic closing valve, wherein the piston valve is pressurized and closed by being introduced into the second pressure chamber. 17. A housing comprising: a fluid passage having a fluid inlet and a fluid outlet; a valve seat crossing the fluid passage; and a cylinder bore formed coaxially with the valve seat and downstream of the valve seat; Slidably fitted to the cylinder bore to control the flow of fluid flowing through the fluid passage in cooperation with a valve seat;
A piston defining a first pressure chamber communicating with the fluid passage downstream of the valve seat, receiving the fluid pressure upstream of the valve seat in a valve opening direction, and receiving the fluid pressure in the first pressure chamber in a valve closing direction; A valve, a pressure receiving member disposed in the housing to receive a fluid pressure upstream of a valve seat in a valve closing direction of the piston valve, the pressure receiving member having an effective pressure receiving area substantially equal to an effective opening area of the valve seat; Connecting means for connecting the members to each other, and canceling the force acting on the piston valve in the valve opening direction by the fluid pressure upstream of the valve seat and the force acting in the opposite direction on the pressure receiving member by the fluid pressure upstream of the valve seat. A biasing means for biasing the piston valve in a valve opening direction; a second pressure chamber and a third pressure chamber divided by a diaphragm, wherein the third pressure chamber is provided in a fluid passage upstream of a valve seat. Connected to the second pressure chamber A hydraulic pressurizing means for pressurizing the closing member in a valve closing direction in accordance with a fluid pressure in the fluid chamber; and selecting the fluid passage upstream of the valve seat and the fluid passage downstream of the valve seat as the second pressure chamber. And a force acting on the piston valve in the valve closing direction by the fluid pressure in the first pressure chamber and a force acting on the piston valve in the valve opening direction by the urging means. A fluid pressure downstream of the valve seat is controlled by the balance, and a fluid in a fluid passage upstream of the valve seat is introduced into the second pressure chamber, whereby the piston valve is pressurized and closed. .