WO2002061516A1 - Unite soupape et systeme de regulation de debit - Google Patents

Unite soupape et systeme de regulation de debit Download PDF

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Publication number
WO2002061516A1
WO2002061516A1 PCT/JP2002/000483 JP0200483W WO02061516A1 WO 2002061516 A1 WO2002061516 A1 WO 2002061516A1 JP 0200483 W JP0200483 W JP 0200483W WO 02061516 A1 WO02061516 A1 WO 02061516A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
flow rate
casing
valve seat
discharge
Prior art date
Application number
PCT/JP2002/000483
Other languages
English (en)
Japanese (ja)
Inventor
Eiji Tsutsui
Yoshio Miyake
Original Assignee
Ebara Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ebara Corporation filed Critical Ebara Corporation
Priority to JP2002562026A priority Critical patent/JPWO2002061516A1/ja
Publication of WO2002061516A1 publication Critical patent/WO2002061516A1/fr

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Classifications

    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D7/00—Control of flow
    • G05D7/06—Control of flow characterised by the use of electric means
    • G05D7/0617—Control of flow characterised by the use of electric means specially adapted for fluid materials
    • G05D7/0629—Control of flow characterised by the use of electric means specially adapted for fluid materials characterised by the type of regulator means
    • G05D7/0635—Control of flow characterised by the use of electric means specially adapted for fluid materials characterised by the type of regulator means by action on throttling means
    • G05D7/0641—Control of flow characterised by the use of electric means specially adapted for fluid materials characterised by the type of regulator means by action on throttling means using a plurality of throttling means
    • G05D7/0664—Control of flow characterised by the use of electric means specially adapted for fluid materials characterised by the type of regulator means by action on throttling means using a plurality of throttling means the plurality of throttling means being arranged for the control of a plurality of diverging flows from a single flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
    • F16K11/14—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by one actuating member, e.g. a handle
    • F16K11/16—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by one actuating member, e.g. a handle which only slides, or only turns, or only swings in one plane
    • F16K11/163—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by one actuating member, e.g. a handle which only slides, or only turns, or only swings in one plane only turns
    • F16K11/166—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by one actuating member, e.g. a handle which only slides, or only turns, or only swings in one plane only turns with the rotating spindles at right angles to the closure members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F16K31/047—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/44—Mechanical actuating means
    • F16K31/52—Mechanical actuating means with crank, eccentric, or cam
    • F16K31/524—Mechanical actuating means with crank, eccentric, or cam with a cam
    • F16K31/52408—Mechanical actuating means with crank, eccentric, or cam with a cam comprising a lift valve
    • F16K31/52416—Mechanical actuating means with crank, eccentric, or cam with a cam comprising a lift valve comprising a multiple-way lift valve

Definitions

  • the present invention relates to a valve unit and a flow control system, and particularly to a method for controlling a fluid.
  • FIG. 4 is a diagram showing an example of a conventional hot water circulation system for air conditioning.
  • the conventional hot water circulation system for air conditioning consists of a tank 10 that stores hot water supplied from a heat source, a pump (fluid machine) 12 that sucks hot water stored in the tank 10 and pumps it, and a pump 1 2
  • An upstream main pipe 14 provided on the discharge side, a forward header 16 connected to the upstream main pipe 14, and a plurality of system-specific pipes 18 branched from the forward header 16. It mainly includes a return header 20 provided downstream of the system-specific piping 18, and a downstream main piping 22 connecting the return header 20 and the tank 10.
  • the piping 18 for each system is provided with a flow rate detecting device (flow rate detecting means) 24 such as an electromagnetic flow meter and a flow rate adjusting device (flow rate adjusting means) such as a solenoid valve. 26 and a fan coil unit And other air conditioning loads 28 are provided. Furthermore, a bypass pipe 30 is arranged between the outgoing header 16 and the return header 20, and the bypass pipe 30 is connected to the bypass pipe 30. Is provided with a flow rate detecting device (flow rate detecting means) 24 such as an electromagnetic flow meter and a flow rate adjusting device (flow rate adjusting means) 26 such as a solenoid valve.
  • the solenoid valve widely used as the flow control device 26 generally includes a valve casing having a suction port and a discharge port, a pulp body housed inside the valve casing, and a pulp body. It comprises a screw mechanism for changing the distance or gap between the valve seats, and a driving device for driving the screw mechanism.
  • detection signals from the flow rate detection device 24 and the air conditioning load 28 are input to the controller 32, and the control signal output from the controller 32 is used to control the pump.
  • the flow rate adjusting device (26) controls the flow rate of each system piping (18) and the bypass piping (30).
  • the pump 12 when the air conditioning load 28 starts operation, the pump 12 starts and hot water circulates in the system, but the required flow rate in each system is such that the hot water flows to the air conditioning load 28.
  • This amount of heat is ensured by adjusting the opening of the flow control device 26 because it changes momentarily according to the amount of heat to be transmitted.
  • the pump 12 since the pump 12 is operated at a constant speed, when the air conditioning load 28 is small, not only does the operating flow rate of the pump 12 become too small, but it also corresponds to the cutoff operating pressure of the pump in the piping system. High pressure is applied, causing inconvenience. For this reason, the required minimum operating flow rate is ensured by adjusting the opening of the flow rate adjusting device 26 of the bypass pipe 30.
  • room A keeps warming quickly in the early morning and maintains heating and stops heating in the evening
  • room B maintains heating from morning to midnight
  • room C has a temperature of 10 am to noon.
  • the required flow rate of hot water for each system is specified by several types of operation modes, for example, to about 25 ° C from noon to 2:00 pm to about 25 ° C.
  • the valve or flow meter is provided for each system as in a conventional system, the smaller the system becomes, the smaller the space cost that the valve or flow meter occupies in the system becomes. The ratio increases, and it becomes a factor that hinders the entire system.
  • the present invention has been made in view of the above, and has a simple structure, a compact and highly reliable valve unit for system-specific flow control useful for energy saving, and a flow control suitable for using this pulp unit.
  • the purpose is to provide a system.
  • the invention according to claim 1 is a valve casing provided with a suction port and a plurality of discharge ports, and provided with a valve seat inside each of the discharge outlets, and is capable of being seated on each valve seat of the valve casing.
  • a valve body provided and urged in the direction of the valve seat; and a valve opening provided at a position facing the valve seat along the axial direction of the rotatable main shaft and abutting against each of the valve bodies.
  • a cam for adjusting the pressure.
  • a cam having an arbitrary cam shape is used to By giving the proper rotation angle position, the flow rate ratio of the fluid discharged from each discharge port is determined by the cam shape and the cam angular position.
  • the flow rate discharged from each outlet cannot be controlled completely independently of each other, but the flow rate discharged from each discharge port can be controlled collectively.
  • the opening of the valve is adjusted via the cam mechanism, the flow rate ratio discharged from each discharge port can be arbitrarily and easily changed by using cams with different cam shapes. .
  • the invention according to claim 2 is the valve unit according to claim 1, further comprising a motor for rotating the main shaft, wherein at least a stator of the motor has an airtight structure.
  • At least the stator of the motor has an airtight structure, so that the handled fluid leaks out of the unit, and the insulation of the motor stator winding due to the intrusion of the handled fluid (for example, water). Deterioration can be prevented. As a result, a shaft seal device such as a mechanical seal becomes unnecessary, and the entire valve unit becomes compact and highly reliable.
  • a servomotor is used as the motor, and a servomotor configured structurally as a canned motor or a motor configured as a resin mold motor is used.
  • Servo motors are now widely used as power sources for various automatic machines such as robots and NC machine tools, and as motors that can control the stop position of rotational speed as instructed. .
  • the invention according to claim 3 is configured such that the valve casing is divided into a casing body and a discharge header, and the casing body and the discharge header are both open and have no undercut portion.
  • a pulp unit according to claim 1 or 2 characterized by: ADVANTAGE OF THE INVENTION According to this invention, productivity at the time of manufacturing a lightweight valve unit by injection molding using PPS (polyphenylene sulfide) resin etc. can be improved. In other words, in order to manufacture a member having an undercut portion by injection molding, it is necessary to use a core mold made of a low melting point alloy or the like, which significantly impairs productivity.
  • the invention according to claim 4 is a valve casing provided with a suction port and a plurality of discharge ports, and provided with a plurality of valve seats inside each of which communicates with the plurality of discharge ports, and each valve of the valve casing.
  • a plurality of valve bodies provided so as to be freely seated on the seat; and an actuator for individually driving the plurality of valve bodies to individually adjust the pulp opening between each valve body and each valve seat.
  • This is a pulp unit characterized by having:
  • the present invention includes an actuator for individually driving a plurality of valve bodies.
  • This actuator is composed of a plurality of driving elements individually connected to a plurality of valve bodies.
  • As the driving element there is a piezoelectric element utilizing a piezoelectric effect.
  • the opening / closing timing and opening degree of each valve body can be individually controlled.
  • the flow rate discharged from a plurality of discharge ports can be simultaneously controlled by one valve unit, and the flow rate ratio discharged from each discharge port can be arbitrarily and easily changed.
  • valve unit according to any one of the first to fourth aspects, a system-specific piping connected to each of the discharge ports of the valve unit, and a suction port of the valve unit.
  • a variable-speed controllable fluid machine installed in the upstream main pipe, and the valve unit A flow control system, wherein pulp control and variable speed control of the fluid machine are linked to control a flow rate in each system-specific pipe.
  • the fluid machine is operated at a variable speed so that the absolute value of the flow rate matches the required value. Power consumption during partial load operation can be reduced as compared with speed operation. At the same time, the rotational speed of the fluid machine can be reduced to reduce the value of the minimum flow (minimum operable water volume), thereby eliminating the bypass piping.
  • the invention according to claim 6 is characterized in that a flow detection device is provided in a part of the system-specific piping, and a flow rate in the system-specific piping is controlled by a signal of the flow detection device.
  • 6 is a flow control system according to 5.
  • the absolute value of the flow rate for each system can be grasped, and this absolute value matches the required value.
  • the system can function rationally.
  • FIG. 1 is a sectional view showing a valve unit according to an embodiment of the present invention.
  • FIG. 2 is a graph showing an example of the relationship between the time in the valve unit shown in FIG. 1 and the flow rate discharged from each discharge port.
  • Fig. 3 shows a flow control system equipped with the valve unit shown in Fig. 1. It is.
  • FIG. 4 is a diagram showing an example of a conventional flow control system. BEST MODE FOR CARRYING OUT THE INVENTION
  • FIG. 1 shows a valve unit according to an embodiment of the present invention.
  • the valve unit 38 shown in FIG. 1 includes a pulp casing 44 divided into a casing main body 40 and a discharge header 42, and a motor 46.
  • the casing body 40 and the discharge header 42 are both integrated and have no undercut portion.
  • the casing body 40 of the valve casing 44 is provided with a suction port 48, and the discharge header 42 is provided with a plurality (three in the figure) of discharge ports 50.
  • the casing body 40 has a cylindrical cylinder portion 52, and the inside of the cylinder portion 52 communicates with the suction port 48. Further, a valve seat 54 is provided inside each of the discharge ports 50 communicating with the cylinder 52. A valve body 56 is disposed so as to be freely seated on each of the valve seat portions 54. The valve body 56 is biased in the direction of the valve seat portion 54 by a spring 58. ing. A main shaft 60 as an output shaft of the motor 46 extends along the inside of the cylinder portion 52. A cam 64 is provided at a position facing each valve seat 54 along the axial direction of the main shaft 60, and the cam 64 comes in contact with the shaft 62 of the pulp body 56. To operate the pulp body 56.
  • the cylinder portion 52 of the valve casing 44 has a shape in which one end is closed and the other end is open.
  • a first bearing 66 that supports the main shaft 60 is provided inside the closed end side of the cylinder portion 52.
  • Ma A motor 46 is connected to the open end of the cylinder 52 by a bolt (not shown).
  • An O-ring 68 for sealing is interposed at the connection between the cylinder 52 and the motor 46.
  • the motor 46 is a so-called servo motor capable of accurately controlling the rotation angle position of the spindle 60 by a supply voltage or the like.
  • the stator 70 of the motor 46 is integrally embedded in a motor casing 72 formed by molding a thermosetting unsaturated polyester resin, for example.
  • the motor casing 72 is formed in a shape in which the valve casing 44 side is open, and the valve casing 44 and the motor casing 72 form a sealed container as a whole to prevent leakage of the fluid to be handled. ing.
  • a second bearing 74 for supporting the main shaft 60 is provided on the closed end side of the motor casing 72.
  • a lead wire 76 for supplying power from a power supply to the motor 46 is drawn out of the motor casing 72, and the lead wire 76 is a motor stator winding wire 78. It is connected to the.
  • FIG. 1 shows an example in which the resin mold is not applied to the inner peripheral side of the motor stator 70, when the fluid to be handled is water, the inner peripheral side of the motor stator is also applied.
  • the resin mold By applying the resin mold, it is possible to prevent water from penetrating into the stator winding portion and deteriorating electrical insulation.
  • a motor rotor 80 is disposed inside the motor casing 72, and the motor rotor 80 is fixed to the main shaft 60.
  • the main shaft 60 and the plurality of cams 64 rotate as a body when the motor 46 is driven.
  • a motor coating is applied to the motor rotor 80 to prevent corrosion according to the type of fluid handled.
  • the main shaft 60 and the cam 64 are made of stainless steel or PPS (polyphenylene sulfide). Molded separately or integrally with resin. Separate spindle 60 and cam 6 4 In the case of molding by using the main shaft 60 and the cam 64, they are integrated by a method such as bonding or press fitting.
  • the bearings 66 and 74 a ball bearing or the like is used when the fluid to be handled is a gas, and a ceramic slide bearing or the like is used when the fluid to be handled is a liquid.
  • the valve body 56 is formed in a conical shape, and the valve body 56 is provided with a shaft portion 62 extending along the axis of the valve body 56.
  • the shaft portion 62 is guided by a guide portion 40a provided on the casing body 40 and a guide portion 42a provided on the discharge header 42.
  • the valve body 56 is formed in a conical shape, and the valve body 56 engages with the valve seat 54 on the side surface of the cone. Therefore, when the pulp body 56 moves away from the valve seat 54 by the cam 64, the valve body 56 and the valve seat 54 cannot be moved with respect to the axial movement of the valve body 56. It acts to reduce the amount of increase in the actual gap.
  • the opposing surfaces of the valve body 56 and the valve seat 54 are both conical side surfaces, the axial movement distance of the valve body 56 and the valve body 56 and the valve seat 54 When compared with the distance between the opposing surfaces, the distance between the opposing surfaces can be made considerably smaller than the distance moved in the axial direction. Thus, even if there is a slight dimensional error in the shape (profile) of the cam 64, the error of the flow rate control is reduced. Furthermore, this conical shape has the effect of smoothly guiding the fluid without disturbing the fluid, and can reduce the pressure loss of the valve.
  • the valve body 56 is manufactured by, for example, injection molding a PPS resin.
  • a discharge header 42 is fixed to the side of the casing body 40 opposite to the cylinder portion by bolts (not shown).
  • a gasket 82 for sealing is interposed between the casing body 40 and the valve seat 54.
  • the discharge header 42 is manufactured by, for example, injection molding PPS resin, and the valve body 5 6 And the same number of discharge sections 42b as the number of the discharge sections.
  • a coil spring 58 made of stainless steel or the like is arranged around the shaft portion 62 of the valve body 56 and on the discharge header side, and the coil spring 58 is connected to the valve body 56 by discharging. It is provided between the headers 42.
  • the valve body 56 is pressed against the valve seat 54 by the urging force of the coil spring 58, and the tip of the shaft 62 is pressed against the cam 64.
  • the guide portions 40a, 42a provided on the casing body 40 and the discharge header 42 are formed in a cylindrical shape, and the inside of these guide portions 40a, 42a is formed by the shaft portion 6 of the valve body 56. 2 is designed to slide.
  • the main body 40 and the guide portion 40a are connected by a plurality of ribs 40b, and the discharge header 42 and the guide portion 42a are connected by a plurality of ribs 42c.
  • the fluid to be handled flows through the gap between the adjacent ribs 40b and 40b and the adjacent ribs 42c and 42c. It also has the effect of smoothly rectifying the flow in the axial direction of the valve body 56, and can suppress the circumferential component of the flow, which has the effect of reducing the pressure loss of the valve.
  • the casing body 40 and the discharge header 42 are integrally formed in an open shape without an undercut portion. That is, in the casing body 40, the mold corresponding to the inside of the cylinder part 52 is on the motor 46 side, and the mold corresponding to the inside of the suction port 48 is from the cylinder part 52 side to the suction port 48 side. In addition, a mold corresponding to the inside of the valve seat 54 is drawn out from the cylinder 52 to the valve seat 54.
  • the discharge header 42 is formed in a shape that can be formed by a mold that is divided into two vertically.
  • the guide portions 40a and 42a of the vanoleb body 56 provided on the casing body 40 and the discharge header 42 are provided with the casing body 40 and the discharge header.
  • the ribs 40b and 42c extending from the outlet header 42 are integrally formed to secure a passage for the fluid to be handled. With such a configuration, for example, it is possible to improve productivity when manufacturing a lightweight valve unit 38 by injection molding using a PPS resin or the like.
  • the rotational position of the cam 64 is adjusted so that all three valves are closed, i.e., the motor 4 is set so that all valve bodies 56 are seated in each valve seat 54. Positioned by 6. Then, when the pump or the like starts operating and fluid pressure is applied to the suction port 48 of the palpuunit 38, and the cam 64 rotates slowly by the motor 46, for example, the discharge port 50 located at the center The pulp body 56 of the valve corresponding to (hereinafter referred to as the discharge port B) is slowly lifted from the valve seat 54 by the cam 64, and the valve is gradually opened.
  • the discharge port B The pulp body 56 of the valve corresponding to
  • the handled fluid is guided from the suction port 48 to a space formed inside the cylinder part 52 of the casing body 40 and the motor casing 72, and then the valve at the position corresponding to the discharge port B It passes through the outer periphery of the main body guide portion 40a, passes through the gap between the valve main body 56 and the valve seat portion 54, and is guided to the discharge header 42. Further, the fluid guided to the discharge header 42 is discharged from the discharge port B to the outside through the outer periphery of the valve main body guide portion 42a of the discharge header 42 ( each of the three valves is individually provided). Since a cam shape (profile) is provided, a desired flow rate can be discharged from each discharge port 50 by switching the rotation angle position of the main shaft 60 by the motor 46.
  • FIG. 2 is a graph in which the horizontal axis represents time (time) and the vertical axis represents the flow rate of the handling liquid discharged from each discharge port 50.
  • the line A represents the flow rate discharged from the discharge port located on the left side of FIG.
  • Line (line) B is the flow rate discharged from the discharge port located in the center of Fig. 1
  • line (line) C is the flow rate discharged from the discharge port located on the right side of Fig. 1, respectively. Is shown.
  • the flow rate for each system as shown in Fig. 2 can be obtained. Control becomes possible. Also, by transmitting the rotation angle position of the spindle 60 to be executed from the outside to the motor 46 using a signal instead of a timer, that is, by selecting the mode to be executed from a finite number of options, A flow control system can be realized.
  • FIG. 1 an example is shown in which a plurality of cams 64 are used to individually drive each valve body 56, but an actuator that drives each pulp body individually is used.
  • This actuator can be composed of a plurality of driving elements.
  • a piezoelectric element may be used as the driving element.
  • FIG. 3 is a diagram showing a flow control system according to an embodiment of the present invention using the valve unit 38 shown in FIG.
  • the same or equivalent members as those in the conventional example shown in FIG. 4 are denoted by the same reference numerals, and the description thereof is partially omitted.
  • a fluid machine (pump) 12 for sucking and pumping hot water stored in a tank 10 for example, a fluid machine operated at a variable speed by a frequency converter (inverter) is used.
  • Suction of pulp unit 38 into upstream main pipe 14 connected to the discharge side of pump 12 Mouth 4 8 is connected.
  • Each discharge port 50 of the valve unit 38 is connected to each system-specific piping 18 and branched into respective systems.
  • Each system-specific piping 18 is connected to an air conditioning load 28 Each is provided.
  • a return header 20 is provided on the downstream side of the system-specific piping 18, and the return header 20 and the tank 10 are connected by a downstream main piping 22.
  • a flow rate detection device such as an electromagnetic flow meter is provided in one of the system-specific pipings 18. While feeding, the controller 32 issues a command to change the mode of the valve unit 38 and to change the rotation speed of the pump 12. That is, the flow rate can be changed by changing the mode to be executed as described above, and the flow rate (absolute value) can be changed by changing the rotation speed of the pump.
  • the flow rate ratio for each system is determined from time to time by the shape of the cam 64 (see Fig. 1) housed inside the valve unit 38 and the angular position of the cam, so the absolute value of the flow rate is the required value. It is only necessary to operate the pumps 12 at a variable speed so that For this reason, a flow detection device (for example, an electromagnetic flow meter) 24 is provided only in a typical system-specific piping 18, and the flow rate of all the system-specific piping is controlled by a signal of the flow detection device 24. I have.
  • the suction port 48 is provided integrally on the side periphery of the cylinder section 52 of the valve casing 44, and serves to handle the fluid supplied from the pump 12. It is connected to an upstream main pipe 14 provided on the discharge side of the pump 12 so as to be taken into the slot 38.
  • the valve casing 44 is manufactured by, for example, injection molding using PPS resin in order to reduce the weight and improve productivity.
  • the handling fluid is a liquid and the pump is used as the fluid machine.However, even if the handling fluid is a gas and the fluid machine is a blower pro or a compressor, etc.
  • the valve unit according to the invention can likewise be applied effectively.
  • the flow rate discharged from a plurality of discharge ports can be simultaneously controlled by one valve unit. Further, by using a plurality of cams having different cam shapes, the flow rate ratio discharged from each discharge port can be arbitrarily and easily changed. Further, according to the flow rate control system of the present invention, it is possible to simplify the system as well as to make it compact, to enhance reliability, and to contribute to energy saving. Industrial applicability
  • the present invention relates to a pulp unit used for discharging a fluid while controlling a flow rate flowing through each system by branching a fluid into system-specific piping, and a flow rate control system using the pulp unit.
  • INDUSTRIAL APPLICABILITY The present invention is applicable to a fluid supply system that branches and supplies a fluid to a plurality of locations.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Multiple-Way Valves (AREA)

Abstract

L'invention concerne une unité soupape utilisée pour libérer, tout en le régulant, un débit de liquide s'écoulant à travers des systèmes, par la répartition du liquide dans des tuyaux destinés à ces systèmes, ainsi qu'un système de régulation de débit simplifié, dont la taille est réduite par l'utilisation de l'unité soupape. L'unité soupape (38) comporte une enveloppe de soupape (44) pourvue d'un orifice d'aspiration (48) et d'une pluralité d'orifices de distribution (50), et des parties siège de soupape (54) disposées à l'intérieur des orifices de distribution, des corps de soupape (56) disposés de sorte à être assis sur les parties siège de soupape (56) de l'enveloppe de soupape et alimentés dans le sens des parties siège de soupape, ainsi que des cames (64) disposées le long de la direction axiale d'un arbre principal (60) rotatif, dans des positions opposées aux parties siège de soupape, qui sont amenées en contact avec les corps de soupape, de sorte à régler les ouvertures des soupapes.
PCT/JP2002/000483 2001-01-31 2002-01-24 Unite soupape et systeme de regulation de debit WO2002061516A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2002562026A JPWO2002061516A1 (ja) 2001-01-31 2002-01-24 バルブユニット及び流量制御システム

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001-24641 2001-01-31
JP2001024641 2001-01-31

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WO2002061516A1 true WO2002061516A1 (fr) 2002-08-08

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Cited By (15)

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WO2005100835A1 (fr) * 2004-04-17 2005-10-27 Norgren Limited Controle de soupapes d'alimentation de fluide
EP1790891A1 (fr) 2005-11-25 2007-05-30 Leotech S.r.l. Appareil de distribution
JP2008173597A (ja) * 2007-01-22 2008-07-31 Techno Excel Co Ltd 水道蛇口直結型浄水器
FR2950124A1 (fr) * 2009-09-17 2011-03-18 Johnson Controls Neige Vanne pour la distribution d'eau et d'air dans les installations de pulverisation d'eau sous pression
FR2995391A1 (fr) * 2012-09-11 2014-03-14 Myneige Sas Dispositif pour la fabrication de neige de culture, installation d'enneigement comprenant un tel dispositif et procede de fonctionnement d'un tel dispositif
CN104373626A (zh) * 2013-08-12 2015-02-25 株式会社泰可诺高槻 多方向性切换阀
CN104373635A (zh) * 2013-08-12 2015-02-25 株式会社泰可诺高槻 阀构造
CN106838367A (zh) * 2016-10-17 2017-06-13 东莞市倍益清环保科技有限公司 一种可360°旋转实现三种出水形式的龙头式***装置
JP2017219196A (ja) * 2016-05-02 2017-12-14 ジーイー・エナジー・プロダクツ・フランス・エスエヌセー 多方向弁
EP2524124B1 (fr) * 2010-01-14 2018-04-04 Mann + Hummel GmbH Ensemble soupape de commande pour un circuit de liquide
WO2018077348A1 (fr) * 2016-10-28 2018-05-03 Helbako Gmbh Dispositif de répartition d'eau de lave-vitre à soupapes multiples
CN108223843A (zh) * 2016-12-22 2018-06-29 深圳安吉尔饮水产业集团有限公司 饮水机排污装置
CN108223841A (zh) * 2017-11-30 2018-06-29 包头稀土研究院 室温磁制冷机用筒式换向阀及其制冷方法
JP2020172950A (ja) * 2019-04-08 2020-10-22 メタウォーター株式会社 配管ユニット
CN115094720A (zh) * 2022-06-13 2022-09-23 杭州路顺环境建设有限公司 一种高粘复合改性环保沥青的路面复合铺装***及其方法

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JP4732439B2 (ja) * 2004-04-17 2011-07-27 ノルグレン・リミテッド 流体供給バルブの制御
JP2007532840A (ja) * 2004-04-17 2007-11-15 ノルグレン・リミテッド 流体供給バルブの制御
CN100445620C (zh) * 2004-04-17 2008-12-24 诺格伦有限公司 对流体供给阀的控制
WO2005100835A1 (fr) * 2004-04-17 2005-10-27 Norgren Limited Controle de soupapes d'alimentation de fluide
EP1790891A1 (fr) 2005-11-25 2007-05-30 Leotech S.r.l. Appareil de distribution
JP2008173597A (ja) * 2007-01-22 2008-07-31 Techno Excel Co Ltd 水道蛇口直結型浄水器
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WO2011033226A1 (fr) * 2009-09-17 2011-03-24 Johnson Controls Neige Vanne pour la distribution d'eau et d'air dans les installations de pulverisation d'eau sous pression
FR2950124A1 (fr) * 2009-09-17 2011-03-18 Johnson Controls Neige Vanne pour la distribution d'eau et d'air dans les installations de pulverisation d'eau sous pression
CN102612617B (zh) * 2009-09-17 2013-11-27 江森自控公司 用于在加压喷水的设备中分配水和空气的阀
RU2527222C2 (ru) * 2009-09-17 2014-08-27 Джонсон Контроулз Нэж Вентиль для распределения воды и воздуха в установках распыления воды под давлением
US9004458B2 (en) 2009-09-17 2015-04-14 Johnson Controls Neige Valve for dispensing water and air in installations that spray water under pressure
EP2524124B1 (fr) * 2010-01-14 2018-04-04 Mann + Hummel GmbH Ensemble soupape de commande pour un circuit de liquide
FR2995391A1 (fr) * 2012-09-11 2014-03-14 Myneige Sas Dispositif pour la fabrication de neige de culture, installation d'enneigement comprenant un tel dispositif et procede de fonctionnement d'un tel dispositif
WO2014041302A1 (fr) * 2012-09-11 2014-03-20 Myneige Sas Dispositif pour la fabrication de neige de culture, installation d'enneigement comprenant un tel dispositif et procédé de fonctionnement d'un tel dispositif
US9429349B2 (en) 2012-09-11 2016-08-30 Technoalpin France Device for producing artificial snow, snow cover facility comprising such a device, and method for the operation of such a device
JP2015057564A (ja) * 2013-08-12 2015-03-26 株式会社テクノ高槻 多方向切替バルブ
CN104373635A (zh) * 2013-08-12 2015-02-25 株式会社泰可诺高槻 阀构造
US9556962B2 (en) 2013-08-12 2017-01-31 Techno Takatsyki, Co., Ltd Multi-directional selector valve
CN104373626A (zh) * 2013-08-12 2015-02-25 株式会社泰可诺高槻 多方向性切换阀
EP2837864A3 (fr) * 2013-08-12 2015-03-04 Techno Takatsuki Co., Ltd. Soupape de sélecteur multidirectionnel
JP7037239B2 (ja) 2016-05-02 2022-03-16 ジーイー・エナジー・プロダクツ・フランス・エスエヌセー 多方向弁
JP2017219196A (ja) * 2016-05-02 2017-12-14 ジーイー・エナジー・プロダクツ・フランス・エスエヌセー 多方向弁
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WO2018077348A1 (fr) * 2016-10-28 2018-05-03 Helbako Gmbh Dispositif de répartition d'eau de lave-vitre à soupapes multiples
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JP2020172950A (ja) * 2019-04-08 2020-10-22 メタウォーター株式会社 配管ユニット
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CN115094720B (zh) * 2022-06-13 2024-04-02 杭州路顺环境建设有限公司 一种高粘复合改性环保沥青的路面复合铺装***及其方法

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