US20060005556A1 - Flow rate control valve - Google Patents

Flow rate control valve Download PDF

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Publication number
US20060005556A1
US20060005556A1 US11/229,444 US22944405A US2006005556A1 US 20060005556 A1 US20060005556 A1 US 20060005556A1 US 22944405 A US22944405 A US 22944405A US 2006005556 A1 US2006005556 A1 US 2006005556A1
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United States
Prior art keywords
flow rate
control valve
rate control
evaporator
pressure
Prior art date
Legal status (The legal status 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 status listed.)
Abandoned
Application number
US11/229,444
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English (en)
Inventor
Hisatoshi Hirota
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
TGK Co Ltd
Original Assignee
TGK Co Ltd
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 TGK Co Ltd filed Critical TGK Co Ltd
Assigned to TGK CO., LTD. reassignment TGK CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HIROTA, HISATOSHI
Publication of US20060005556A1 publication Critical patent/US20060005556A1/en
Abandoned legal-status Critical Current

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/067—Control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F25B41/345—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by solenoids
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/028—Controlling a pressure difference
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/20—Control of fluid pressure characterised by the use of electric means
    • G05D16/2006—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means
    • G05D16/2013—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means
    • G05D16/2022—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means actuated by a proportional solenoid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/063—Feed forward expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2505—Fixed-differential control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2515—Flow valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • This invention relates to a flow rate control valve, and more particularly to a flow rate control valve used as an expansion device in a refrigeration cycle for an automotive air conditioner, which changes high-temperature, high-pressure refrigerant into low-temperature, low-pressure refrigerant to thereby deliver the refrigerant to an evaporator.
  • a refrigeration cycle for an automotive air conditioner uses, as a control valve for controlling a compressor, a differential pressure control type that controls the differential pressure across the compressor or suction pressure of the same such that it is substantially constant, it is considered preferable to use, as an expansion device, an expansion valve of a flow rate control type different in control method, so as to stabilize the controllability of the system.
  • a flow rate control valve of this kind has been described e.g. in Japanese Unexamined Patent Publication (Kokai) NO. 2001-153495.
  • the flow rate control valve includes a constant flow-rate mechanism.
  • the constant flow-rate mechanism is configured based on a principle that if the cross-sectional area of a passage through which refrigerant flows between a refrigerant inlet and a refrigerant outlet and the differential pressure across the passage are determined, the flow rate of refrigerant flowing through the control valve can be controlled to be constant, and hence by varying one of the cross-sectional area and the differential pressure by a solenoid, it is possible to cause refrigerant to flow at a constant flow rate corresponding to a value set by the solenoid.
  • the constant flow-rate mechanism includes a flow passage cross-sectional area control valve for controlling the cross-sectional area of the passage, and a constant differential pressure control valve for controlling the differential pressure between the inlet and the outlet of the flow passage cross-sectional area control valve to be substantially constant, and is configured such that the flow passage cross-sectional area of the flow passage cross-sectional area control valve is controlled by the solenoid, to thereby hold the flow rate of refrigerant flowing through the flow rate control valve at a predetermined constant flow rate corresponding to a flow passage cross-sectional area set by the solenoid (see FIG. 1 in Japanese Unexamined Paten Publication (Kokai) No. 2001-153495).
  • the constant flow-rate mechanism includes a restriction passage the cross-sectional area of which is not changed, and a differential pressure control valve for controlling the differential pressure between the inlet and the outlet of the restriction passage such that it is substantially constant, and is configured such that a differential pressure value set to the differential pressure control valve is controlled by the solenoid to thereby hold the flow rate of refrigerant flowing through the flow rate control valve at a predetermined constant flow rate corresponding to the differential pressure set by the solenoid (see FIG. 2 in Japanese Unexamined Paten Publication (Kokai) No. 2001-153495).
  • the conventional flow rate control valve includes the restriction passage for creating the differential pressure, and the differential pressure control valve for controlling the differential pressure across the restriction passage such that it is constant, and hence suffers from the problem of being complicated in construction.
  • the present invention has been made in view of these problems, and an object thereof is to provide a flow rate control valve of a constant flow-rate control type, which is simple in construction.
  • the present invention provides a flow rate control valve that controls a flow rate of refrigerant which is throttled and expanded to be delivered to an evaporator, such that the flow rate is substantially constant, comprising a constant differential pressure control valve that controls a differential pressure before and after pressure loss caused by passage of refrigerant through the evaporator, such that the differential pressure is substantially constant.
  • FIG. 1 is a central longitudinal cross-sectional view of the construction of a flow rate control valve according to a first embodiment.
  • FIG. 2 is a central longitudinal cross-sectional view of the construction of a flow rate control valve according to a second embodiment.
  • FIG. 3 is an expanded cross-sectional view showing essential components of the flow rate control valve according to the second embodiment.
  • FIG. 4 is a central longitudinal cross-sectional view of the construction of a flow rate control valve according to a third embodiment of the present invention.
  • FIG. 5 is a central longitudinal cross-sectional view of the construction of a flow rate control valve according to a fourth embodiment of the present invention.
  • FIG. 1 is a central longitudinal cross-sectional view of the construction of a flow rate control valve according to a first embodiment of the present invention.
  • the flow rate control valve is capable of performing constant flow rate control only after it is connected to an evaporator 1 , and has a body block 2 provided with a high-pressure refrigerant inlet 3 to which refrigerant at pressure Po is supplied, a low-pressure refrigerant outlet 4 from which refrigerant is delivered to the evaporator 1 while being expanded, a return refrigerant inlet 5 to which refrigerant is returned from the evaporator 1 , and a return refrigerant outlet 6 from which the returned refrigerant is delivered to a compressor.
  • the high-pressure refrigerant inlet 3 has a strainer 7 disposed therein in a manner closing a passage formed therein.
  • the body block 2 has an upper portion thereof formed with a large-diameter hole, a central portion thereof formed with a cylinder concentric with the large-diameter hole and extending vertically, as viewed in FIG. 1 , and a lower portion thereof formed with a hole that communicates with the cylinder formed in the central portion thereof.
  • the hole in the lower portion of the body block 2 is communicated with the return refrigerant inlet 5 and the return refrigerant outlet 6 , by a return passage 8 , and an opening of the hole formed downward of the return passage 8 is closed by a packing pressed against the body block 2 by a screw 10 via a packing retainer 9 .
  • valve seat 11 The rim of an upper end of the cylinder formed in the central portion of the body block 2 forms a valve seat 11 , and a valve element 12 is disposed in a manner opposed to the valve seat 11 from above, as viewed in FIG. 1 , such that the valve element 12 can move to and away from the valve seat 11 .
  • the valve element 12 is integrally formed with a piston 13 , which serves as a pressure-sensing member axially movably disposed within the cylinder, with a small-diameter shaft connecting between the valve element 12 and the piston 13 .
  • a refrigerant passage communicating with the high-pressure refrigerant inlet 3 opens in a portion where the small-diameter shaft is located.
  • a chamber above the cylinder, formed by the large-diameter hole formed in the upper portion of the body block 2 is communicated with the low-pressure refrigerant outlet 4 via a refrigerant passage.
  • a solenoid Disposed on the top of the body block 2 is a solenoid which comprises a plunger 14 integrally formed with the valve element 12 , a core 15 disposed concentrically with the plunger 14 , an electromagnetic coil 16 disposed around the plunger 14 and the core 15 , a spring 17 disposed between the plunger 14 and the core 15 , and a yoke 18 surrounding the electromagnetic coil 16 .
  • the core 15 is in the form of a hollow cylinder, and has an adjustment screw 19 screwed therein which adjusts the load of the spring 17 .
  • the adjustment screw 19 as well has a hollow cylindrical shape, and forms a bearing that axially movably holds a shaft 20 having a lower end rigidly fixed to the plunger 14 .
  • the upper open end of the core 15 is hermetically closed by a ball 21 and a locking screw 22 .
  • the solenoid is screwed into the large-diameter hole formed in the top of the body block 2 , via a connecting portion 23 thereof.
  • the effective diameter of the valve seat 11 and that of the piston 13 are approximately equal to each other, and hence the pressure Po of refrigerant supplied to a space between the valve element 12 and the piston 13 has no influence on the motions of the valve element 12 and the piston 13 since a force in a direction of pushing the valve element 12 upward and a force in a direction of pushing the piston 13 downward are approximately equal to each other and canceled out.
  • pressure Px from the low-pressure refrigerant outlet 4 of the flow rate control valve which is pressure on the downstream side of the valve element 12 , acts on the valve element 12
  • pressure from the return passage 8 of refrigerant acts on the lower surface of the piston 13 , so that the valve element 12 and the piston 13 is axially moved from respective positions set by the solenoid, in response to the differential pressure between pressure at the inlet of the evaporator 1 and pressure Pe at the outlet of the evaporator 1 .
  • the flow rate control valve functions as a constant differential pressure control valve for providing control such that the differential pressure between the pressure at the inlet of the evaporator 1 and the pressure Pe at the outlet of the evaporator 1 is substantially constant.
  • the flow rate control valve causes refrigerant to flow into the evaporator 1 at a substantially constant flow rate dependent on electric current that energizes the solenoid.
  • FIG. 2 is a central longitudinal cross-sectional view of the construction of a flow rate control valve according to a second embodiment of the present invention
  • FIG. 3 is an expanded cross-sectional view showing essential components of the flow rate control valve according to the second embodiment. It should be noted that component elements in FIGS. 2 and 3 identical or similar to those shown in FIG. 1 are designated by identical reference numerals, and detailed description thereof is omitted.
  • the flow rate control valve according to the second embodiment is configured to prevent internal leakage of refrigerant when the flow rate control valve is closed, and reverse the direction of actuation of the valve element 12 by the solenoid.
  • a flexible valve sheet 24 is disposed on a seating surface of the valve element 12 via which the valve element 12 is seated on the valve seat 11 to thereby prevent leakage of refrigerant from a valve section
  • a diaphragm 25 is disposed on a surface of the piston 13 at which the pressure Pe from the outlet of the evaporator 1 is received, to thereby substantially completely prevent leakage of refrigerant from the high-pressure refrigerant inlet 3 to the return passage 8 via the sliding portion of the piston 13 .
  • a space where the valve element 12 is disposed is closed by an adjustment screw 26 screwed into the body block 2 , and a spring 27 for urging the valve element 12 in the valve-closing direction is disposed between the valve element 12 and the adjustment screw 26 .
  • the load of the spring 27 can be adjusted by the screwing amount of the adjustment screw 26 .
  • the diaphragm 25 has its periphery brought into intimate contact with the body block 2 by press-fitting a ring member 28 in the body block 2 .
  • the diaphragm 25 has an effective diameter approximately equal to the effective diameter of the valve seat 11 , and a disk 29 having an end face approximately equal to the lower end face of the piston 13 is contact with the central portion of the diaphragm 25 .
  • a spring 30 causes the disk 29 to urge the diaphragm 25 in the valve-opening direction of the valve section.
  • the solenoid has the core 15 disposed toward the diaphragm 25 , and the plunger 14 disposed on a side opposite from the core 15 .
  • the plunger 14 is rigidly fitted on the shaft 31 .
  • the shaft 31 is disposed in a manner extending through the core 15 , and has a foremost end thereof in contact with the disk 29 . Therefore, by feeding electric current to the electromagnetic coil 16 , the solenoid acts to push the diaphragm 25 , the piston 13 , and the valve element 12 in the valve-opening direction.
  • the present flow rate control valve is responsive to the differential pressure between the pressure at the inlet of the evaporator 1 and the pressure Pe at the outlet of the evaporator 1 received by the valve element 12 and the diaphragm 25 , to control the differential pressure to be substantially constant, to thereby cause refrigerant to flow into the evaporator 1 at a constant flow rate dependent on electric current that energizes the solenoid.
  • the flow rate control valve is capable of substantially completely preventing internal leakage of refrigerant in a closed state during deenergization of the solenoid, so that e.g. when an inflammable gas, such as HFC-152a, propane, or butane, or carbon dioxide is used as refrigerant, the evaporator 1 can be isolated from a circuit on the condenser side in case the evaporator 1 is damaged, to thereby prevent a fire or oxygen deficiency from being caused by refrigerant having flowed from the evaporator 1 into the vehicle compartment. In this case, it is necessary to isolate the evaporator 1 also from a circuit on the suction side of the compressor by providing a check valve 32 in a manner inserted into a circuit on the outlet side of the evaporator 1 .
  • an inflammable gas such as HFC-152a, propane, or butane, or carbon dioxide
  • the check valve 32 By providing the check valve 32 in piping between the return refrigerant outlet 6 of the flow rate control valve, which communicates with the return passage 8 , and the suction side of the compressor, and using the above-described flow rate control valve capable of preventing internal leakage of refrigerant as an expansion valve, it is possible to isolate the evaporator 1 as a component part of a refrigeration cycle for an automotive air conditioner, which is disposed in the vehicle compartment, from the refrigeration cycle when the automotive air conditioner is not operated. In this case, in stopping the automotive air conditioner, for example, the compressor is allowed to rotate for some time after stoppage of energization of the solenoid, and then stop.
  • FIG. 4 is a central longitudinal cross-sectional view of the construction of a flow rate control valve according to a third embodiment of the present invention. It should be noted that component elements in FIG. 4 identical or similar to those shown in FIGS. 1 and 2 are designated by identical reference numerals, and detailed description thereof is omitted.
  • the flow rate control valve according to the third embodiment is formed by providing the flow rate control valve shown in FIG. 1 with the internal leakage-preventing mechanism of the flow rate control valve shown in FIG. 2 and a backflow preventing mechanism for isolating the evaporator 1 from the refrigeration cycle during stoppage of the automotive air conditioner.
  • the flow rate control valve is configured such that the valve element 12 is intimately seated on a valve seat-forming member 33 press-fitted in a passage between the high-pressure refrigerant inlet 3 and the low-pressure refrigerant outlet 4 via the valve sheet 24 , and a cylinder below the piston 13 is sealed by the diaphragm 25 .
  • the diaphragm 25 has a central portion thereof attached to the piston 13 by a holding member 34 , and the piston 13 is rigidly fixed to the valve element 12 integrally formed with the plunger 14 of the solenoid.
  • the check valve 32 is interposed in the return passage 8 communicating with the return refrigerant outlet 6 , at a location between a branch position at which the return passage 8 branches into a space where the diaphragm 25 receives the pressure Pe from the outlet of the evaporator 1 , and the refrigerant outlet 6 .
  • the check valve 32 is configured such that a spring provided toward the return refrigerant outlet 6 urges the valve element, and when the differential pressure between the suction pressure of the compressor and the pressure Pe at the outlet of the evaporator 1 becomes equal to or higher than a predetermined value, the check valve 32 opens to allow refrigerant to flow from the evaporator 1 to the compressor.
  • the flow rate control valve controls the differential pressure across the evaporator 1 such that it is substantially constant, to thereby cause refrigerant to flow into the evaporator 1 at a constant flow rate dependent on electric current that energizes the solenoid.
  • FIG. 5 is a central longitudinal cross-sectional view of the construction of a flow rate control valve according to a fourth embodiment of the present invention. It should be noted that component elements in FIG. 5 identical or similar to those shown in FIG. 4 are designated by identical reference numerals, and detailed description thereof is omitted.
  • the check valve 32 disposed in the return passage 8 is moved from the location toward the return refrigerant outlet 6 shown in FIG. 4 to a location toward the return refrigerant inlet 5 .
  • the flow rate control valve is responsive to the differential pressure obtained by adding the differential pressure across the evaporator 1 and the differential pressure across the check valve 32 , received by the valve element 12 and the diaphragm 25 , to control the differential pressure to be substantially constant, to thereby cause refrigerant to flow into the evaporator 1 at a constant flow rate dependent on electric current that energizes the solenoid.
  • the flow rate control valve is configured such that the constant differential pressure control valve automatically closes when the solenoid is deenergized
  • the flow rate control valve may be configured such that the constant differential pressure control valve automatically closes when the solenoid is energized.
  • the evaporator is regarded as a restriction passage and the flow rate control valve is configured to include the constant differential pressure control valve for controlling the differential pressure across the evaporator to be substantially constant.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Thermal Sciences (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Air-Conditioning For Vehicles (AREA)
US11/229,444 2003-03-06 2005-09-02 Flow rate control valve Abandoned US20060005556A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2003059353A JP2004270975A (ja) 2003-03-06 2003-03-06 流量制御弁
JP2003-059353 2003-03-06
PCT/JP2004/002673 WO2004079468A1 (ja) 2003-03-06 2004-03-03 流量制御弁

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2004/002673 Continuation WO2004079468A1 (ja) 2003-03-06 2004-03-03 流量制御弁

Publications (1)

Publication Number Publication Date
US20060005556A1 true US20060005556A1 (en) 2006-01-12

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ID=32958845

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/229,444 Abandoned US20060005556A1 (en) 2003-03-06 2005-09-02 Flow rate control valve

Country Status (5)

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US (1) US20060005556A1 (de)
EP (1) EP1600841B1 (de)
JP (1) JP2004270975A (de)
DE (1) DE602004017843D1 (de)
WO (1) WO2004079468A1 (de)

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WO2007039056A2 (en) 2005-09-19 2007-04-12 John Joe O'sullivan Training device
DE102009060499A1 (de) * 2009-12-22 2011-06-30 JENOPTIK Robot GmbH, 40789 Verfahren und Anordnung zur Erfassung von Verkehrsverstößen in einem Ampelbereich
US20110308274A1 (en) * 2008-11-20 2011-12-22 Danfoss A/S An expansion valve comprising a diaphragm and at least two outlet openings
US20130074536A1 (en) * 2010-04-16 2013-03-28 Jugurtha BENOUALI Thermostatic Expansion Device And Air Conditioning Loop Comprising Such A Thermostatic Expansion Device
US20130227977A1 (en) * 2011-01-20 2013-09-05 Mitsubishi Electric Corporation Air-conditioning apparatus
WO2018065071A1 (de) * 2016-10-07 2018-04-12 Bitzer Kühlmaschinenbau Gmbh Halbhermetischer kältemittelverdichter
US20190043347A1 (en) * 2015-09-17 2019-02-07 Volkswagen Aktiengesellschaft Device, method, and computer program for providing traffic jam information via a vehicle-to-vehicle interface
RU2771541C1 (ru) * 2021-03-17 2022-05-05 Битцер Кюльмашиненбау Гмбх Полугерметичный компрессор холодильного агента (варианты)

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JP5292540B2 (ja) * 2008-08-22 2013-09-18 株式会社テージーケー 膨張装置
JP5773610B2 (ja) * 2010-10-18 2015-09-02 株式会社不二工機 複合弁
CN103543227B (zh) * 2013-10-28 2014-11-26 徐继承 一种含有自动置换装置的低压液化气体检验用进样蒸发器
CN103529150B (zh) * 2013-10-28 2015-05-06 徐继承 一种含有恒温气化装置的低压液化气体检验用进样蒸发器
CN106337938B (zh) * 2015-07-06 2019-11-05 杭州三花研究院有限公司 流量控制阀、该流量控制阀的控制方法及其控制系统
KR101734265B1 (ko) * 2015-08-28 2017-05-11 현대자동차 주식회사 차량용 에어컨 시스템의 팽창밸브 및 이를 포함하는 차량용 에어컨 시스템
JP2020041658A (ja) * 2018-09-13 2020-03-19 株式会社不二工機 複合弁

Citations (14)

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US3855836A (en) * 1973-01-24 1974-12-24 Hitachi Ltd Device for controlling coolant pressure in evaporator
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WO2004079468A1 (ja) 2004-09-16
EP1600841B1 (de) 2008-11-19

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