JPS62143111A - Water pressure booster system - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a pump water supply system, particularly a well water supply system, and more specifically, it proposes a control valve intended for such a system.

Water supply systems using water supplied by pumps are known. Such water systems include booster systems to maintain the required water pressure in tall buildings and small buildings in areas with inadequate or outdated public water systems, and systems that draw water from groundwater sources for use. It typically includes a well water system that supplies the water distribution system at appropriate pressure.

A typical known pump water system connects a pump driven by an electric motor to a water supply, e.g. a well or public water supply, and a pressure-operated switch that switches the pump on and off depending on the water pressure in the building. As a composition, there is. Although such a configuration satisfies the basic requirements of a booster system, it does not require frequent on-off cycling of the motor and pump, since opening the faucet reduces the pressure in the system to an extent that starts the pump. It tends to accompany To prevent excessive cycling of the pump, an accumulator is provided to accumulate a predetermined amount of pressurized water.
A small amount of water can be supplied without starting the pump. Additionally, in order to further improve the water pressure booster system, a water pressure control device has been installed, which allows water to be supplied under a nearly constant pressure and limits the discharge pressure when the pump is operating, so that the pressure remains constant during periods when there is sufficient demand for water supply. It has been proposed to prevent the switch from opening. The water pressure control device can be equipped with a delay function to limit the rate of pressure generation and delay the switch-off operation of the pump when the demand for water supply disappears.

No. 3,739,810, U.S. Pat. No. 3,782, discloses an arrangement in which a water pressure booster system includes an accumulator tank to supply a small amount of pressurized water when the faucet is opened without requiring activation of the pump and electric motor. No. 858,
No. 3.814.543, No. 3.865.512, No. 3.871.792, No. 3.876, 336 and No. 3.922°111 disclose related technology.

In known booster systems, diaphragm operated valves are commonly used to regulate system pressure and control accumulator tank refilling.

The use of pilot pressure in conjunction with a diaphragm to control the position of valves in booster systems, as well as the combined use of biasing means such as springs or pneumatics, is both known.

Diaphragms in control valves such as those described above have the disadvantage of being susceptible to malfunction due to breakage or insufficient sealing performance at the periphery.

Furthermore, in a booster system that uses both a diaphragm and a biasing means, it is necessary for the biasing means to apply a force sufficient to overcome the frictional force of the valve element to reliably close the valve. As a result, the force required to open the valve increases and the pressure drop across the control valve increases accordingly.

Known booster systems that use pilot pressure to control valve position usually require additional check valves to prevent backflow from the accumulator to the pump.

As a result, the configuration of the entire system becomes complicated, which not only increases the amount of maintenance work but also increases the possibility of malfunction. In addition, in a pump water supply system for a well, a check valve is generally arranged close to the pump at the bottom of the well.

U.S. Pat. No. 4,165,951 discloses a hydraulic booster system that includes a controller for controlling the pressure in the water distribution system by means of a balance piston valve. In this known hydraulic booster system, the flow from the pump is controlled by a throttle valve, which is actuated by the pressure difference between the system pressure and a constant pressure acting on the balance piston. Backflow towards the pump is prevented by a flow control/check valve located inside the throttle valve. A problem with the hydraulic booster system according to the US patent is that it is necessary to dispense a predetermined amount of fluid to adjust the pressure acting on the balance piston. Such discharge flow is discharged to a drain or returned to the suction side of the pump. FIG. 1 of the above-mentioned US patent is similar to FIG. 1 of the present application and shows an arrangement for returning fluid to the suction side of the pump. Flow through an orifice 80 in the balance piston 72, regulated by a backpressure regulator, is controlled by the pump 10.
is discharged towards the suction side. This is advantageous in the case of a booster pump, since the pressure control device can be placed close to the pump. However, in the case of deep well pumps, the pressure control device is placed at the ground level, and the pump may be placed at the bottom of the well about 150 to 200 meters underground, so this is not a practical solution.

The reason for returning the flow from the back pressure regulator to the suction side of the pump is
In the configuration shown in FIG. 1 of the above-mentioned patent, the water pressure in the chamber 84 has a value close to the pressure on the discharge side of the pressure regulator in the flow path 46, and the pressure drop in the pressure regulator causes the pressure in the back pressure regulator to increase. This is because the pressure on the outlet side is lower than the pressure inside the flow path 46. That is, since the back pressure regulator does not deliver fluid at a higher pressure, fluid must be delivered to the low pressure suction side of the pump or to the drain.

Patent documents describing known techniques related to the present invention include the following.

U.S. Patent Nos. 4.471.907, 4.165.951, 2.761.389, 3. ．． No. 141.475, No. 1.656.132, No. 3.304.048, No. 2
．． No. 454.929, No. 3.694.105, No. 3.
No. 799.199, No. 2.360.816, No. 2.7
No. 12.322, No. 2.732.810, No. 4.00
No. 4.610, No. 2.829.670, No. 2.911
．． No. 010, No. 3.385.216, No. 3.756.
No. 558, No. 3.873.063, No. 2.127.1
No. 72, No. 2.219.070, No. 3.902.52
No. 2, No. 2.563.889, No. 2.975.803
No. 3.399.696, No. 3.613.716, No. 3.669.143 and No. 3.703.911
issue.

French patents L 479.426, 2.382.636, 904.652, 2.092.270, 857
．． No. 540, No. 2.175.391 and No. 868.
No. 263.

West German Publication No. 2.400.636, Publication No. 1.146.00
No. 7, Publication No. 1.293.034 and Patent No. 937
．． No. 866.

SUMMARY OF THE INVENTION An object of the present invention is to propose a pump water supply system having a control valve that can solve the various problems in the prior art described above.

Another object of the present invention is to propose a pump water supply system having a control valve that can regulate water pressure with low pressure loss even at high flow rates.

The purpose of the pond of the present invention is to propose a pump water supply system having a vine control valve that operates while overcoming the large frictional resistance caused by foreign objects introduced from the outside.

Another object of the invention is to propose a pump water system with a control valve that does not require recirculation of water towards the suction side of the pump or towards the drain.

Another object of the present invention is to propose a pump water supply system having a delay function that allows the pump to continue operating even when the demand for water supply disappears.

Another object of the present invention is to propose a pump water supply system having a compact and inexpensive control valve.

The object of an embodiment of the invention is to propose a pump water system with a control valve that does not require the use of springs as direct biasing means.

Another object of the invention is to propose a pump water system with a control valve that does not require the use of a diaphragm as a direct energizing means.

The pump water supply system according to the first embodiment of the present invention has a water supply source j
A control valve connected between the connected electric open drive pump, the accumulator tank, the pressure switch that controls on/off of the pump drive motor in response to the water pressure in the system, and the accumulator tank and pump. and a drain valve such as a faucet.

The control valve of the first embodiment controls the water pressure within the system as well as the refilling of the accumulator tank after the demand for water has disappeared. This control valve, unlike the diaphragm valve in known booster systems, is constructed as a balance piston and its inlet is connected to the outlet of a pump connected to the accumulator tank and to the water distribution system. The inlet from the pump is placed between the throttle valve and the balance piston in the slidable valve body to prevent the valve body from changing by mutually canceling out the forces derived from the pump discharge pressure. A biasing spring engages the top of the throttle valve and is disposed within a chamber within the valve casing, communicating the chamber with the inlet and outlet. An orifice is provided through the balance piston, and this orifice introduces the water that has passed through the piston into the chamber to create back pressure that acts on the piston.The back pressure opens the throttle valve and connects the pump and water supply system. communicate with the rest of the The amount of backpressure is determined by a small backpressure regulator and maintained at a nearly constant level. This regulator need not form part of the control valve and can be located remotely from the housing.

System pressure acts on the throttle valve in a direction that tends to close it. Problems caused by flow past the backpressure regulator can be overcome by a spring biasing the throttle valve toward the closed position. In other words, the displacement of the valve body is determined by the combination of the biasing force of the spring and the system pressure.
It will be controlled by a relatively constant back pressure difference.

A flow adjustment/check valve can be built into the throttle valve so that after the throttle valve is closed due to system pressure, a small flow of water is introduced into the system in addition to the flow from the back pressure regulator. . In this case, it is possible to refill the accumulator tank by continuing to operate the pump and its drive motor even after the water supply demand at the faucet disappears. When the internal pressure of the accumulator tank reaches a predetermined value, a pressure switch shuts down the pump's drive motor and a flow control/check valve prevents backflow from the water supply system to the pump. The present invention can also be applied to a water supply system in which a check valve is placed on the pump side at the bottom of a well, so in such a case there is no need to provide a flow rate adjustment/check valve as part of the control valve.

In order to balance the force acting on the slidable valve body by providing a biasing spring, the pressure in the lower chamber of the balance piston must be lower than the pressure in the upper channel (chamber) of the throttle valve. is also required to be large. If the pressure drop across the backpressure regulator is sufficiently low, fluid passing through the orifice of the balance piston can flow into the chamber on the discharge side of the pressure control device. This eliminates the need to return fluid to the discharge side of the pump. However, on the other hand, the pressure i [pressure R under the sail device must be at least equal to the effective pressure of the biasing spring, that is, the value obtained by dividing the spring force by the pressure receiving area of the throttle valve. The additional pressure drop due to the biasing spring is described in U.S. Patent No. 4.
The pressure drop can be set large compared to the pressure drop in the pressure control device disclosed in No. 165.951.

In the pump water supply system according to the second embodiment of the present invention, the means for adjusting the flow rate of water supplied to the piping system from the pump connected to the water supply source includes an inlet flow path connected to the discharge side of the pump and a piping system. and a first outlet connected to the system.

A valve body without biasing means is freely slidably disposed within the housing. The valve body is provided with a throttle valve and a balance piston connected to the throttle valve. A back pressure regulator is provided to enable adjustment of the pressure acting on the pressure receiving surface of the balance piston on the side opposite to the throttle valve. A back pressure regulator is connected between the pressure receiving side of the balance piston and the second outlet of the housing. The main components in this example are a flow regulator and a venturi.

The flow regulator has an inlet connected between the outlet of the pump and the inlet channel of the housing, and an outlet. The venturi has an inlet, a throat, and an outlet. The inlet of the venturi is connected to the outlet of the flow regulator W. An outlet of the venturi connects to a piping system connected to a first outlet of the housing. The area of minimum pressure in the venturi is generally between the inlet and throat of the venturi, connecting it to the second outlet of the housing. The throat of the venturi can also be connected to the second outlet of the housing. Alternatively, a deformable disk having a central passageway may be placed at the mouth of the venturi approximately perpendicular to the longitudinal axis of the venturi.

The suction provided by such an arrangement creates a point of minimum pressure between the deformable disk and the throat of the venturi. The connection to the outlet in the housing is then located at such a point of minimum pressure at the mouth of the venturi.

The flow regulator adjusts the flow of fluid that bypasses the control valve so that when the throttle valve closes, the accumulator is refilled with a nearly constant flow of fluid. can be maintained constant.

The pressure limited f&lI device in the second embodiment has the advantage of low pressure drop over the prior art while eliminating the need for fluid return to the suction side of the pump.

The pressure control valve in the second embodiment does not require fluid to be returned from the back pressure regulator to the suction side of the pump and does not involve additional pressure drop due to biasing springs. As a result, it is possible to arrange such a pressure control valve at a location away from the pump, especially a submerged deep well pump.

Advantageously, the flow regulator and venturi are contained within a single nosing. In this case, it is advantageous to provide the flow regulator with a deformable disc having a central flow channel. The disk is positioned so that the central flow path approximately coincides with the center of flow within the venturi. The disk is further positioned proximate the throat of the venturi to serve as the entrance to the venturi.

The water pressure booster system according to the present invention includes an electric motor-driven pump connected to a water supply source, a check valve, an accumulator tank, and a pressure switch that controls on/off the electric motor for driving the pump in response to the water pressure in the system. , a control valve connected between the accumulator tank and the pump, and a drain valve such as a faucet. The control valve controls the water pressure in the system and also controls the refilling of the accumulator tank after the demand for water supply disappears.

This control valve, in contrast to the diaphragm valve in known booster systems, is configured as a balance piston, with its inlet connected to the pump and its outlet connected to the accumulator tank and to the piping system.

The inlet from the pump is placed between the throttle valve and the balance piston in the slidable valve body to prevent displacement of the valve body by mutually canceling out the forces resulting from the pump discharge pressure.

The magnitude of the pressure acting behind the balance piston is determined and maintained at a more or less constant level by a pilot backpressure regulator connected to the valve housing.

System pressure acts on the throttle valve in a direction that tends to close it. Displacement of the valve body is therefore controlled exclusively by the differential pressure between the system pressure and a relatively constant back pressure, and biasing elements such as diaphragms and springs are not required.

A flow regulator may be built into the throttle valve, and after the throttle valve is closed due to system pressure, a small flow of water may be introduced into the system in addition to the flow from the back pressure regulator. In this case, it is possible to refill the accumulator tank by continuing to operate the pump and its drive motor even after the demand for water supply at the faucet disappears.

When the internal pressure of the accumulator tank reaches a predetermined value, a pressure switch shuts off the pump drive motor and a check valve prevents backflow from the system to the pump.

Hereinafter, the present invention will be explained with reference to the drawings.

Since the present invention is an improvement on the control valve of U.S. Pat. No. 4,165,951, the known control valve will first be described. FIG. 1 shows the water pressure booster system described in the above-referenced U.S. patent, which includes a water pump 10, an electric motor 12 driving the water pump, a control valve assembly 14, an accumulator tank 16, and a pressure actuated switch 18. It is equipped with

The pump 10 is of an appropriate type depending on the application, such as a shallow well pump, and its suction side is connected via a conduit 20 to a water source, such as a well or a water supply system. The discharge side of pump 10 connects to control valve assembly 14 via conduit 22 . a flow path is provided through the control valve assembly 14;
One side of the passageway 46 is connected to the pressure switch 18 via conduits 24 and 26, and the other side is connected to the conduit 20 and the faucet 3.
Connect to the water distribution system of the building indicated by 0. FIG. 1 is only an exemplary diagram, and the number of faucets can be set as appropriate.

The accumulator 16 and the pressure switch 18 can be of standard type commercially available.

For example, the accumulator 16 is manufactured and sold by the applicant:
Relevant product name WELL-X-TROL j lNX-
202 type, and the pressure switch may be built into the pump.

The electric motor 12 is connected to the pressure switch 18 by a power supply cable 32.
Connect to power via. Depending on the arrangement of the pressure booster system, the pump 1 may be driven by an internal combustion engine or other power source instead of the electric motor 12.

The control valve assembly 14 includes a housing 34, a slidable valve body 36, and a backpressure regulator 38, as shown in detail in FIG.
It is equipped with An inlet passage 40 is formed in the housing 34 which connects to the discharge side of the pump 10 via a conventional threaded joint and conduit 22. Accumulator tank 1
A similar channel 42 is provided for connection with 6. Coaxially connected to the flow path 42 is another flow path 46 which connects the control valve assembly 14 to the faucet 30. This flow path extends at right angles to the plane of the paper of FIG. 2 and is shown diagrammatically in FIG. housing 3
4 are also formed with threaded channels 48,50 for connection with a pressure gauge and suction side conduit 20, respectively. An access plug 52 is threadedly coupled to the top of the housing 34 to allow the valve body 36 to be easily installed and removed. access plug 5
An annular skirt 54 is vertically disposed on the valve body 2 and extends into the housing 34 to limit upward displacement of the valve body 36. A passageway 56 may be provided within the access plug 52 to connect the pressure switch 18 to a line pressure source.

A back pressure regulator 38 is connected to the lower part of the housing 34.

The regulator 38 can be connected directly to the housing 34 as shown in FIG. 2, or can be separated by a conduit connection. Note that the regulator 38 can be a standard commercially available product. Generally, backpressure regulator 38 includes a housing 58 that may be threadedly coupled to housing 34;
8, a screw 62 screwed to the housing 58, and a sealing member 6B extending between the screw 62 and the diaphragm 60 and attached to the diaphragm 60 against the bottom of the housing 34. A spring 64 that blocks the flow path 68 by pressing the spring 64 is provided. As shown in the figure, this flow path 68 is connected to the flow path 5 described above.
It is connected to 0.

A central shaft 70 is provided on the valve body 36, a balance piston 72 is disposed at its lower end, and a throttle valve 74 is disposed at its upper end. A seal member 76 is provided on the outer periphery of the balance piston 72 to seal between the outer periphery and the inner periphery 78 of the housing 34. An orifice 80 is provided through the balance piston '12, and the orifice communicates between a central chamber 82 and a lower chamber 84 within the housing 34. The cross-sectional area of the orifice 80 is approximately 0.65 to 3.25
The two lower chambers 84, each having a diameter of 1 mm', also communicate with the back pressure regulator 30 by a conduit 86.

The throttle valve 74 is provided with a plurality of valve guide members 88 that are spaced apart from each other in the inner circumferential direction of the throttle valve 74 and extend in the longitudinal direction. These guide members 88 hold the valve body 36 in a positional relationship in which its longitudinal centerline coincides with the centerline of the housing 34 while the valve body 36 is being moved up and down. The throttle valve 74 is formed to have an outer shape that restricts the flow of fluid between the central chamber 82 and the upper chamber 90. That is, for example, the second
As shown in the figure (angle formed by the outer surface with respect to the center line, 7.<
It can have a progressively increasing truncated conical shape or a truncated paraboloid shape as shown in FIG. In either case, the flow rate of fluid between the central chamber 82 and the upper chamber 90 is configured to increase as the valve body 36 rises.

When the valve body 36 is in its lowermost position as shown in FIG. , the seal member is in this case housing 3
The valve seat 94 is brought into contact with the valve seat 94 defined by the top surface of the inner protrusion 96 having a cylindrical shape.

The upper portion of the valve body 36 includes a flow control/check valve 98. This valve 98 is arranged between a lower valve seat 100 and an upper valve seat 100 depending on the pressure difference between the central chamber 82 and the upper chamber 90.
It can be freely displaced between. When the pressure in the upper chamber 90 is greater than the pressure in the central chamber 82, the flow rate adjustment/
Check valve 98 is pushed up into engagement with valve seat 102 .

At least one, and preferably a plurality of radial grooves 204 are provided in the valve seat 102 from the opening of the flow passage 104 to the valve seat 102.
By extending to the outer periphery of the valve 02, the structure allows fluid to pass even when the check valve 98 and the valve seat 102 are engaged. When two grooves 204 are formed, the width of the grooves is about 2 to 5 mm and the depth is about 1 to 2 grooves, so that the fluid can be flowed at a flow rate of about 1.9 to 3.8 β/min. Supply from the pump via valve 14 becomes possible. The flow rate adjustment/check valve 98 has a durometer hardness of 40.
Constructed of ~70 elastic materials. Fluid enters the flow path 104 from the central chamber 82 through the flow path 106, around the check valve 98, and through the radial groove 204. The reason why fluid is allowed to flow through check valve 98 in this position will be discussed later.

When check valve 98 engages valve seat 100, fluid is prevented from flowing between upper chamber 90 and central chamber 82 through the check valve.

A screen 10g is placed between the throttle valve 74 and the balance piston 72 to protect various flow paths within the valve body 36 from being blocked by foreign matter such as dust.

The operation of the known hydraulic booster system and control valve according to U.S. Pat. No. 4,165,951 will now be described with reference to FIGS. 4-6.

As an initial condition, the faucet 30 is in a closed state, and the electric motor 12 is in a closed state.
Assume that the pump is in the OFF state, that the accumulator 16 is filled to its entire volume, and that the valve body 36 and check valve 98 are in the positions shown in FIG. When the faucet 30 is opened, water in the piping system and in the accumulator 16 is initially discharged from the faucet. If the demand for water supply is large, the pressure in conduit 24.26.28 will drop by one degree to the set pressure of pressure switch 18. At this point, pressure switch 18 is closed, activating electric @ 12 and pump 10. The discharge water of pump 10 enters control valve assembly 14 via flow path 40 .

Balance piston 72 and throttle valve 74 are of equal diameter. The forces acting on the balance piston 72 and the throttle valve 74 are equal in magnitude and act in opposite directions. Therefore, the pressure of the fluid flowing into the flow path 40 does not cause any force to displace the valve body 36.

When the pilot pressure acting on the lower side of the Noranis piston 72 exceeds the system pressure in the upper chamber 90, "'i" f51
16 is displaced upwardly, spacing seal member 92 from its valve seat. When the pressure within central chamber 82 exceeds the system pressure, flow control/check valve 98 is also displaced upward, as shown in FIG. The fluid passing between the central chamber 82 and the upper chamber 90 is throttled by the throttle valve 74 as described above. The position of the throttle valve 74 relative to the valve seat 94 and the degree of throttling that corresponds to that position are determined by the pressure difference between the upper chamber 90 and the lower chamber 84.

Fluid passes through orifice 80 to lower chamber 84 and flow path 86.
flow inside. However, since the seal member 66 closes the flow path 68, further flow of the fluid is blocked.

Therefore, fluid pressure is created under the balance piston 72. When the fluid pressure reaches a predetermined level, the thrust exerted by the fluid pressure on diaphragm 60 overcomes the spring force of spring 64. Therefore, the sealing member 66
opens the flow path 68 and allows fluid to flow through the flow path 68 to the suction side conduit 20 of the pump. In other words, back pressure AI! The '11 device 38 controls the level of pressure applied to the lower side of the balance piston 74.The pressure level can be manually adjusted by turning the screw 62, and the pressure level can be adjusted manually by turning the screw 62. The pressure switch 18 is set to an intermediate value between the cut-in and cut-out pressures.In other words, the set value of the pressure switch is approximately 2.1 to 3.5 k in gauge pressure.
g/cm2, the regulator setting is also about 2.8 kg/cm2 in gauge pressure.

Valve body 36 continuously controls fluid flow to the system while faucet 30 is open. When the faucet 30 is closed,
The pressure within the piping system increases to exceed the pilot pressure acting on the balance piston 72. At that point, the valve body 36 begins to displace downward. The rate of pressure rise within the piping system and accumulator decreases as the throttle valve 74 approaches the valve seat 94 and the throttling effect exerted on the fluid flow to the upper chamber 90 increases. This allows electric motor 12 and pump 10 to operate for a longer period of time and prevents undesired on-off cycling of electric motor 12 and pump 10.

”The pressure in the second side chamber 90 and the piping system is controlled by the throttle valve 7.
4 gradually increases until it is completely closed as shown in FIG. At that point, the pressure in the central chamber 82 is greater than the pressure in the upper chamber 90, thus maintaining the flow control/check valve in the upper position allowing fluid flow as described above. Fluid flowing into the upper chamber 90 via the check valve 98 is used to refill the accumulator 16. The resiliency of the flow control/check valve 98 allows the filling time of the accumulator 16 to be held approximately constant regardless of the differential pressure between the pump discharge pressure and the system pressure. In other words, if the differential pressure is large, the extent to which the check valve 98 deforms into the radial groove 204 described above becomes large.
It is possible to prevent an increase in flow rate due to a large differential pressure.

When the accumulator 16 is refilled, the pressure in the piping system reaches the cut-off level of the pressure switch, stopping the motor 12 and pump 10. And check valve 98
contacts the valve seat 100 to prevent backflow from the upper chamber 90 to the central chamber 82. That is, the hydraulic booster system N;C:
The initial state shown in FIG. 4 is the state in which the mother has given birth and is ready to start a new operating cycle.

Figures 7a and 7b show a control valve 216 according to a first embodiment of the invention, in which like reference numerals refer to components that correspond to the previously described known control valves.

In this first embodiment, a spring 206 loads the throttle valve toward the closed position for the purpose of appropriately adjusting the flow rate of fluid passing through the back pressure regulator. That is, by providing the spring 206, the pressure inside the chamber 84 is reduced to the flow path 46.
This balances the force acting on the slidable valve body 36 as being greater than the pressure within. If the pressure drop across the backpressure regulator is sufficiently low, conduit 24 or 2 provides fluid passing through orifice 80 of balance piston 72 to backpressure regulator 50 and outflow from chamber 90.
8. Such a configuration eliminates the need to return fluid to the suction side of the pump. However, the pressure drop in the pressure regulating device must be set to at least a value equal to the effective pressure of the spring 206, that is, the value obtained by dividing the spring force by the pressure receiving area of the thread valve.

The additional pressure drop due to spring 206 is described in U.S. Patent No. 4.
165.951 can be set considerably larger compared to the pressure drop in the hydraulic control device described in No. 165.951.

Figures 8a-10b illustrate a control valve 214 according to a second embodiment of the present invention, with like reference numerals representing corresponding components in the previously described control valves.

The pump system shown diagrammatically in FIGS. 8a and 8b as a preferred embodiment of the second embodiment of the invention is disclosed in U.S. Pat.
．． No. 165.951, the control valve 214 is connected to the pump 10 (not shown) by a conduit 110 and a semi-submerged water supply (not shown) is connected to the pump 10 (not shown) via a discharge pipe 120. (for example, a faucet 30). Note that the pressure gauge 182 is connected to the access plug 52.
It is attached to the threaded channel 56 of the. The discharge system includes an accumulator 6 as a water tank and a pressure activation switch 18.
is provided to enable the pump 10 to be controlled. Pressure control valve 21
The back pressure regulator (BPR) 38 of 4 is provided with an outlet 50 and an outlet conduit 122 connects the vent to the throat 122 of the moon 30 . The high pressure side inlet 224 of the bench November 30 is attached to the inlet conduit 110 of the pressure control valve 214, and the branch conduit 140 is connected to the inlet conduit 110 of the pressure control valve 214.
Connected via pressure regulator 150 and branch conduit 228 . Outlet 226 of venturi 130 connects to outlet 120 of pressure control valve 214 via conduit 160. An orifice 80 is disposed within the balance piston 72.

According to the above configuration, the pressure is controlled as follows.

That is, the pressure regulating valve 214 is supplied with pressurized water at a gauge pressure of, for example, about 4.2 kg/cm 2 from the pump 10 . The pressure of this pressurized water can be detected by a pressure gauge 198. The back pressure regulator 38 connects the inside of the chamber 84 to a pressure gauge 194.
a predetermined pressure that can be detected at, e.g. approximately 3.5 k
Adjust to maintain g/cm2 gauge pressure. In this case, the flow path 4 that can be detected by the pressure gauge 202
If the pressure inside the valve body 6 is also about 3.5 kg/cm2 in gauge pressure, the slidable valve body 36 can be balanced. Venturi 130 is connected to gauge pressure line 4- at its inlet 224.
Connect to a pressure source of 2 kg/cm2 (pressure gauge 198).
, and at its outlet 226 the gauge pressure line 3
．． 5 kg/cm" (pressure gauge 202), the flow regulator 150 and venturi 1
Flow can be created through 30 in the direction shown. In this example, flow regulator 150 adjusts the flow rate of fluid supplied from conduit 110 via conduit 140 to approximately 15,2β/m
in to reduce the pressure at the nozzle inlet 224 of the venturi 130 to about 3.8 kg/cm" gauge pressure. From the conduit 228 a flow rate of about 15.24!/min and a gauge pressure line of 3.8 kg/cm. The venturi 130, which is supplied with fluid at a pressure of 3.2 kg/cm2, delivers fluid through conduit 122 at a pressure line of 3.2 kg/cm2.
Suction at a flow rate of E/+r+in, approximately 3.5 kg/c
+n2 gauge pressure is discharged through conduit 160 into conduit 122. That is, in this example, the back pressure regulator 38 (eighth
b) operates with a pressure drop of approximately OJ kg/cm'' in gauge pressure at a flow rate of approximately 3.8 β/+y+in, and maintains the inside of the chamber 84 at a gauge pressure line of 3.5 kg/cm''. is discharged into the low pressure side conduit 120 of the pressure control valve 214.

The upper portion of the slidable valve body 36 is designed as described in U.S. Pat.
5,951 and shown in FIGS. 1 to 6 may also be provided. In the present invention, the flow through the backpressure regulator 38 and venturi 130 is added to the flow through the flow control/check valve.

When the pump is used for deep wells, a so-called foot valve (not shown) is usually provided on the upstream side of the pump, so it is generally necessary to provide a check valve to prevent backflow from the conduit 120 of the water distribution system. There is no such check valve in conduit 12.
0 to conduit 110, the check valve is installed downstream of the confluence of conduits 120 and 160 in conduit 120 or conduit 160.
or may be located in conduit 110 upstream of the confluence of conduits 110, 140.

Regarding the most preferred embodiment of the second embodiment of the present invention, the ninth embodiment
The explanation will be as follows with reference to FIG. 9A and FIG. 9B. In this example, the flow regulator and venturi 232 are incorporated into a single housing 200.

A shoulder 230 separates the inlet chamber 210 from the venturi inlet 220 within the housing 200 . Shoulder part 230
supports a disk 240 of elastomeric material. This disc is a "doll" well known to those skilled in the art.
It operates as a type of flow regulator. The Doll flow regulator is deformable.

The orifice 234 of the Doll flow regulator 240 functions as a nozzle for the venturi 236 and creates a jet that is directed into the throat 250 of the venturi 236 . Doll flow regulator 240 is operated as a jet pump or suction means. Conduit 122 connects inlet chamber 220 of venturi 236 to outlet 50 of backpressure regulator 38 . Instead of the Doll flow regulator, another flow regulator may be used that throttles the orifice in response to an increase in differential pressure.

10a as yet another specific example of the second embodiment of the present invention.
10b, the supply conduit 1
10 and the flow regulator 150 or conduit 140 leading to the Dole regulator. That is, a short pipe 170 having a closed end 176 and an orifice 180 formed in a direction opposite to the flow of the σ:i body in the conduit +10 is attached to the inlet flow path 40 of the pressure control valve 214. When the inlet pressure of the control valve decreases due to a decrease in the discharge pressure of the pump and the flow rate of the fluid passing through the conduit 110 is large, the above-described configuration recovers the dynamic pressure component of the inflowing fluid and restores it. This can be converted into static pressure within the conduit 140 to ensure a high supply pressure to the venturi.

According to the second embodiment of the invention described above, U.S. Pat.
It is possible to operate the known pressure control valve described in No. 165.951 without having to return fluid from a back pressure regulator to the suction side of the pump and without creating an additional pressure drop due to the spring. It becomes possible.

Therefore, the advantage is that such a pressure control valve can be placed at a location away from a submerged deep well pump, etc.
asked.

[Brief explanation of drawings]

Figure 1 is a route map showing a known hydraulic booster system, Figure 2 is a sectional view of the known control valve in Figure 1, and Figure 3 is a sectional view of the known control valve in Figure 1.
Figures: Figures 4 to 6 are sectional views showing different operating positions of the known control valve in Figure 2, Figures 7a and 7 Figure 7h is a sectional view showing the essential parts of the first embodiment of the control valve according to the present invention, Figure 8a is a route diagram showing the second embodiment of the hydraulic booster system according to the present invention, and Figure 8b is a cross-sectional view of the main part of the first embodiment of the control valve according to the present invention. FIG. 9a is a cross-sectional view showing the essential parts of the second embodiment of the control valve of the present invention included in the water pressure booster system, in which the second embodiment of the water pressure booster system of the present invention is combined with a venturi device and a flow rate regulator. Figure 9b is a cross-sectional view similar to Figure 8b showing the control valve of the present invention included in the hydraulic booster system of Figure 9a, Figure 10a is a route diagram showing a modified example, and Figure 10a is a conduit leading to a supply pipe and a flow rate regulator. the second of the connections between
FIG. 10b, a sectional view showing a modification of the embodiment, is a sectional view similar to FIG. 8b, showing an embodiment of the control valve of the present invention used in combination with the connection portion of FIG. 10a. 10...Pump 12...Electric motor 14...
・Control valve assembly 16...Accumulator 18...
・Pressure operation switch 30...faucet 34...housing 36
...Valve body 38...Back pressure regulator 58...
・Housing 60...Diaphragm 64...
Spring 72... Balance piston 74... Throttle valve 80... Orifice 98...
・Flow rate adjustment/check valve 130...Venturi 150...Flow rate regulator 170
... Short pipe 180 ... Orifice 214.
... Control valves 232, 236 ... Bench lily 240 ... Disc

Claims (1)

[Claims] 1. In a water pressure booster system for controlling water pressure in a piping system having a pump connected to a water supply source, the control device for controlling the flow rate in the piping system includes: (a) pump discharge; a housing having an inlet passageway connected to the side and an outlet passageway connected to the piping system; (b) a throttle valve slidably disposed within the housing and a balance piston connected to the throttle valve; (c) a valve body having an orifice formed in the balance piston to allow water to pass from one side to the other; (c) an urging force for urging the throttle valve toward its closed position; and (d) pressure control means connected between the other side of the balance piston and the suction side of the pump to control the pressure acting on the other side of the balance piston. Water pressure booster system. 2. The hydraulic booster system according to claim 1, wherein the biasing means includes a spring, the housing has an inlet chamber and an outlet chamber, and the spring has an inlet chamber and an outlet chamber between the inlet and the outlet of the housing. and is held in operational contact with the throttle valve.
A hydraulic booster system characterized in that a check valve is disposed in a bypass flow path that bypasses the throttle valve to reduce the inflow flow to the piping system when the hop is activated when the throttle valve is closed. 3. (a) a housing having an inlet passage and an outlet passage; (b) a central portion slidably disposed within the housing and having a throttle valve formed at one end and a balance piston formed at the other end; (c) a biasing means for biasing the throttle valve towards its closed position; (c) a valve body having a shaft and having a throttle valve and a balance piston arranged such that the inlet passage is located therebetween; and (d) a control means for adjusting the pressure acting on the balance piston to control the amount of displacement of the valve body according to the differential pressure between the adjusted pressure and the pressure in the outlet flow path; A hydraulic booster system comprising: 4. In the water pressure booster system according to claim 3, the outer shape of the throttle valve is a truncated paraboloid, and the throttle valve supplies water in inverse proportion to the distance from the valve seat. A water pressure booster system characterized by squeezing. 5. A water pressure booster system for controlling water pressure in a piping system having a pump connected to a water supply source, in which a control device for controlling the flow rate in the piping system is: (a) connected to the discharge side of the pump; (b) a throttle valve and a throttle valve disposed within the housing so as to be freely slidable without biasing means; a balance piston connected to the valve body; and (c) a pressure surface and a second outlet of the housing for adjusting the pressure acting on the pressure surface of the balance piston on the side facing away from the throttle valve. (i) a flow rate regulating means having an inlet connected to a connection between the discharge side of the pump and the inlet channel of the housing, and an outlet; and (ii) having an inlet, a throat, and an outlet, the inlet being connected to the outlet of the flow regulating means, and the outlet being connected to the piping system connected to the first outlet of the housing; A hydraulic booster system further comprising: venturi means having a bottom pressure point connected to a second outlet of the housing. 6. A hydraulic booster system according to claim 5, wherein a deformable disk having a central passage is disposed at the inlet of the venturi means at right angles to the central longitudinal axis of the venturi means, and Hydraulic booster system, characterized in that a connection to two outlets is arranged between said deformable disk and the throat of the venturi means. 7. Scope of Claims In the water pressure booster system according to claim 6, the diameter of the throttle valve is set equal to the diameter of the balance piston, and the force of the valve body caused by the force exerted on the valve body by the water flowing into the housing is A hydraulic booster system characterized by preventing displacement. 8. The water pressure booster system according to claim 6, including a flow rate adjustment means disposed in a bypass flow path that bypasses the throttle valve, and when the pump is in an operating state when the throttle valve is closed. The hydraulic booster system is characterized in that the inflow flow rate into the piping system is reduced, and when the pump is stopped, backflow from the piping system passing through the bypass flow path is prevented. 9. (a) a housing having an inlet passage and an outlet passage; (b) disposed within the housing for free sliding movement without biasing means, a throttle valve at one end and a throttle valve at the other end; (c) a valve body having a central shaft in which a balance piston is respectively formed, a throttle valve and a balance piston being arranged such that said inlet flow path is located therebetween; (c) a pressure acting on the balance piston; (d) control means disposed within the throttle valve and configured to control the amount of displacement of the valve body according to the pressure difference between the adjusted pressure and the pressure in the outlet flow path; controlling the fluid flow between the inlet channel and the outlet channel when the inlet side pressure is greater than the outlet side pressure, and when the outlet side pressure is greater than the inlet side pressure; A hydraulic booster system characterized in that it comprises a valve comprising: a flow regulating means for blocking the flow of fluid; and (e) a pressure detecting means having an opening directed upstream in the flow direction in the inlet channel. 10. The water pressure booster system according to claim 9, wherein the pressure detection means includes a tube projecting into the inlet flow path, the inner end of the tube is a closed end, and the outer end is an open end. . A hydraulic booster system, characterized in that the opening is formed on a side of the tube that does not face the housing.