EP1865275A2 - Expansion valve - Google Patents

Expansion valve Download PDF

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Publication number
EP1865275A2
EP1865275A2 EP07009857A EP07009857A EP1865275A2 EP 1865275 A2 EP1865275 A2 EP 1865275A2 EP 07009857 A EP07009857 A EP 07009857A EP 07009857 A EP07009857 A EP 07009857A EP 1865275 A2 EP1865275 A2 EP 1865275A2
Authority
EP
European Patent Office
Prior art keywords
expansion valve
axis
hole
power element
thread
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.)
Withdrawn
Application number
EP07009857A
Other languages
German (de)
English (en)
French (fr)
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
Publication of EP1865275A2 publication Critical patent/EP1865275A2/en
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • 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
    • F25B2341/068—Expansion valves combined with a sensor
    • F25B2341/0683—Expansion valves combined with a sensor the sensor is disposed in the suction line and influenced by the temperature or the pressure of the suction gas
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the invention relates to a mounting structure according to the preamble of claim 1, more particularly for mounting an expansion valve in a refrigeration cycle of an automotive air conditioner.
  • a refrigeration cycle of an automotive air conditioner comprises a compressor that compresses refrigerant, a condenser that condenses the compressed refrigerant, a receiver that temporarily stores refrigerant and separates the condensed refrigerant into a gas and a liquid, an expansion valve that throttles and expands the liquid refrigerant obtained by gas/liquid separation, and an evaporator that evaporates the refrigerant expanded by the expansion valve.
  • the expansion valve is implemented e.g. by a thermostatic expansion valve.
  • a known thermostatic expansion valve configured to sense the temperature and pressure of refrigerant at the outlet of an evaporator and to control the refrigerant flow rate to the evaporator includes a body with a first passage between a receiver and the evaporator, and a second return passage between the evaporator and a compressor.
  • a valve section in the first passage controls the flow rate.
  • a power element in the body at a location on the second passage side senses the temperature and pressure in the second passage, and controls the valve lift.
  • the body is made by cutting an extrusion-moulded blank of an aluminium alloy into a prism-like block to prepare a half-finished solid part.
  • the first and second passages, and a power element connection portion are formed, by cutting. The cutting process takes much time, degrades the yield from the material, and increases the manufacturing costs.
  • JP-A-10-267470 proposes a blow extrusion moulded body.
  • the second passage is simple and straight, the second passage simultaneously is formed by extrusion moulding. This omits a hole-forming process by cutting the second passage, saves material of the aluminium alloy, and is an improvement of the manufacturing efficiency of the body to some extent.
  • it is required to extrude the aluminium alloy in a fixed extruding direction and hence it can be applied only to a straight shape without a varying cross-section.
  • This technique cannot be applied to the formation of a first passage in the intermediate portion of which the valve section is integrally formed.
  • sealing surfaces for sealing members are to be formed for pipes leading to the compressor, the receiver, and the evaporator.
  • the sealing surfaces are formed as increased-diameter portions and cannot be formed by extrusion moulding. There is no other way than to perform cutting when forming these portions. For these reasons the saving of material and the improvement of the manufacturing efficiency as achieved are not sufficient.
  • a sealing portion is formed by a tool, such as a drill, the axis of the tool can become offset from the axis of the passage, so that off-centred load can be applied to the tool and the body during the cutting process, which can cause a trouble in cutting.
  • a juncture between the body and the power element has a screwing structure, which needs to thread a portion of the body. This also degrades the manufacturing efficiency and increases manufacturing costs.
  • It is an object of the present invention is to improve the manufacturing efficiency of a body of and to reduce the manufacturing cost of an expansion valve.
  • the expansion valve passes introduced refrigerant through a valve section in the body to throttle and expand the refrigerant.
  • the body accommodating the valve section is formed integrally with a thread part for connecting a power element by using forming dies.
  • an inlet port, an outlet port, a hole for receiving therein a valve element and a set value-adjusting member, a valve hole, a hole for receiving therein a member that transmits an actuating force dependent on temperature sensed by the power element to the valve element, and the thread part for having the power element connected thereto are formed integrally with the body.
  • the housing by forming a housing that is connected to the thread part formed on the body, in a one-turn thread configuration such that an inner peripheral edge of a central opening thereof is continuously displaced in an axial direction over an angle range of smaller than 360 degrees, the housing can be simply formed by pressing. This makes it unnecessary to carry out thread cutting steps, and hence it is possible to further reduce the manufacturing cost of the expansion valve.
  • An expansion valve 1 in Fig. 1 (first embodiment) comprises a valve section 2 and a power element 3.
  • the valve section 2 includes a body 4.
  • the body 4 has sides integrally formed with a high-pressure, high-temperature refrigerant inlet port 5 connected to a receiver of the refrigeration cycle, and a low-temperature, low-pressure refrigerant outlet port 6 connected to an evaporator.
  • a valve hole 7 between the inlet and outlet ports 5, 6.
  • the valve hole 7 extends in a direction orthogonal to the axes of the inlet and outlet ports 5, 6.
  • the body 4 has a hole 8, larger in diameter than the valve hole 7 that extends downward from the valve hole 7 through the body 4 in the direction of the axis of the valve hole 7.
  • the hole 8 contains a valve element 9, triangular in cross-section.
  • the valve element 9 is urged by a spring 10 in valve closing direction.
  • the spring 10 is received by a spring-receiving member 11 press-fitted in the opening of the hole 8.
  • the load of the spring 10 is adjusted by the press-fitting depth of the spring-receiving member 11 in the opening of the hole 8, to adjust a set value of the expansion valve 1.
  • the body 4 is also formed with a hole 12, slightly smaller in diameter than the valve hole 7.
  • the hole 12 extends upward from the valve hole 7 through the body 4 in the direction of the axis of the valve hole 7.
  • the hole 12 contains a shaft 13 integrally formed with the valve element 9.
  • the shaft 13 has a reduced-diameter portion 13a facing a the inlet port 5, defining a refrigerant passage from the inlet port 5 into the valve hole 7.
  • a circumferential groove in the periphery of a of the shaft 13 within the valve hole 12 contains a V-packing 14 for preventing that high-pressure refrigerant leaks via a clearance between the shaft 13 and the body 4 from the inlet port 5 to the power element 3.
  • a protruding hollow cylindrical guide 15 is formed on a central part of an upper portion of the body 4 for guiding the shaft 13.
  • An external thread 16 is formed on the outer periphery of the guide 15.
  • the power element 3 comprises an upper housing 17, a lower housing 18 (thick metal discs), a diaphragm 19 made of a flexible metal sheet partitioning a space enclosed by the housings 17 and 18, and a disc 20 on the side of the diaphragm 19 facing the valve section 2.
  • the power element 3 is formed by welding the peripheral edges of the upper housing 17, the lower housing 18, and the diaphragm 19 to each other e.g. by TIG welding.
  • the temperature-sensing chamber is filled with saturated vapour gas via a gas introducing hole 21 formed in the upper housing 17.
  • the gas introducing hole 21 is closed by a metal ball 22 e.g. by resistance-welding.
  • the temperature-sensing chamber has to sense the temperature of refrigerant coming from the evaporator.
  • the lower housing 18 has gas-passing holes 25 and an open central portion integrally formed with a hollow cylindrical hub 23.
  • the hub 23 has an internal thread fitting on the external thread 15.
  • the gas-passing holes 25 lead refrigerant from the evaporator into a space below the diaphragm 19. The amount of introduced refrigerant is adjusted by either changing the size of each gas-passing hole or by varying the number of gas-passing holes.
  • the body 4 is formed by die-casting a metal, to dispense with mechanical machining such as cutting.
  • the body 4 in Fig. 4 can be made by die-casting of an aluminium alloy, a zinc alloy, or another metal.
  • an aluminium alloy die-casting apparatus including a first die 30, a second die 40, and a third die 50.
  • the first die 30 and the second die 40 are actuated by an actuator, not shown, in horizontal directions in Fig. 2.
  • the third die 50 is actuated by an actuator, not shown, in vertical directions.
  • the first die 30 on a side opposed to the second die 40 has a cavity 31 forming the portion of the body 4 with the inlet port 5. Within the cavity 31, a port and passage-forming portion 32 protrudes toward the second die 40, for forming the inlet port 5, and further, a thread-forming portion 33 forms half of the external thread 16.
  • the second die 40 on a side opposed to the first die 30 has a cavity 41 for forming the portion of the body 4 with the outlet port 6. Within the cavity 41, an outlet port passage-forming portion 42 protrudes toward the first die 30, and a thread-forming portion 43 forms the other half of the external thread 16.
  • the third die 50 has a cavity 51 forming the portion of the body 4 where the spring-receiving member 11 will be press-fitted.
  • a hole-forming portion 52, a valve hole-forming portion 53, and a hole-forming portion 54 are protruding upward for forming the hole 8, the valve hole 7, and the hole 12.
  • the first to third dies 30, 40, 50 are formed in opposed surfaces with injection passage-forming grooves, not shown, for pouring in molten aluminium alloy, and exhaust passage-forming grooves, not shown, for evacuating the cavities 31, 41, and 51, and with insertion holes for inserting tools for releasing the casting from the dies.
  • molten aluminium alloy is poured via the injection holes into the tightly fastened die set of the first to third dies 30, 40, 50.
  • the aluminium alloy may be an Al-Si-Cu alloy having excellent castability.
  • the third die 50 is pulled downward and then the first and second dies 30, 40, 40 are separated from each other.
  • the first and second dies 30, 40 are moved in horizontal directions while causing inserted releasing tools to be pushed against the casting.
  • the body 4 can be formed integrally with the inlet port 5, the outlet port 6, the valve hole 7, the holes 8 and 12, and the external thread 16..
  • the respective axes of the inlet and outlet ports 5, 6 can be identical or parallel with each other.
  • the hole 8, the valve hole 7, and the hole 12 are disposed on the same axis in a direction orthogonal to the direction of the axes of the ports 5, 6, and, such that they have respective inner diameters sequentially reduced in the mentioned order.
  • the die apparatus may comprise a plurality of sets of first to third dies 30, 40, 50 in parallel with each other, which all are simultaneously operated in the three directions. This allows to easily construct a die-casting apparatus which permits a plurality of castings to be obtained at any given time.
  • the die-cast body 4 in Figs 3A, 3B has a hollow cylindrical part 5a defining the inlet port 5 and extending in the direction of separating the first die 30, a hollow cylindrical part 6a defining the outlet port 6 and extending in the direction of separating the second die 40, and a hollow cylindrical part 8a defining the hole 8 and a guide 15 defining the hole 12, extending in the direction of separating the third die 50.
  • the external thread 16 on the outer periphery of the guide 15 is a partial thread in which portions of an outer peripheral surface of the guide 15 facing in directions at right angles to the respective directions of separating the first and second dies 30, 40 are not threaded, and comprise a thread portion 16a formed on an outer peripheral portion facing in the direction of separating the first die 30 and a thread portion 16b formed on an outer peripheral portion in the direction of separating the second die 40.
  • the body 4 is shown with an extending part 4a extended in a direction at right angles to the respective directions of separating the first and second dies 30, 40, serving to position the expansion valve 1 when incorporated in the refrigeration cycle later.
  • the expansion valve 1 in Figs 4 and 5 is mounted in a return low-pressure pipe between the evaporator 60 and the compressor, such that the expansion valve 1 is accommodated in the pipe in its entirety.
  • the connection of the inlet port 5 to a high-pressure pipe 61 through which condensed liquid refrigerant is supplied and the connection of the outlet port 6 via which the expanded refrigerant is delivered to an inlet pipe 62 of the evaporator 60 are also established within the return low-pressure pipe.
  • the evaporator 60 in Fig. 4 is integrally formed with a casing 64 e.g. by furnace brazing, such the casing 64 surrounds the inlet pipe 62 and a refrigerant outlet port 63.
  • An end of the low-pressure pipe 65 is welded to a joint 66 (via a portion indicated by a black triangle), and the joint 65 is hermetically connected to the casing 64 by a pipe clamp 67.
  • the low-pressure pie 65 and the high-pressure pipe 61 commonly form a double pipe with the high-pressure pipe 61 coaxially arranged within the low-pressure pipe 65.
  • the expansion valve 1 carries a heat insulation cover 68 made of resin or rubber attached to cover the power element 3.
  • the expansion valve 1 is positioned in Fig. 5 in the centre of the casing 64.
  • the extended part 4a of the body 4 and the heat insulation cover 68 have respective outer contours fitting into the inner shape of the casing 64.
  • the expansion valve 1 is mounted as follows: As the evaporator 60 and the casing 64 are integrally welded such that the inlet pipe 62 of the evaporator 60 protrudes into the casing 64, first, an O-ring is fitted on the inlet pipe 62, and then the expansion valve 1 is pushed into the casing 64 until the inlet pipe 62 is fitted in the outlet port 6. An O-ring is fitted on the inlet port 5 of the expansion valve 1 in advance, or at this time. The inlet port 5 then is positioned such that it can be fitted in the high-pressure pipe 61, and the joint part 66 having O-rings fitted beforehand in respective grooves formed by bending the end portion of the joint part 66 is pushed into the casing 64. Finally, a connecting portion of the casing 64 and that of the joint part 66 are connected by the pipe clamp 67.
  • the inlet port 5 is connected to the high-pressure pipe 61, and the outlet port 6 is connected to the inlet pipe 62 of the evaporator 60. Because the expansion valve 1 is accommodated in the low-pressure return pipe from the evaporator 60, together with the juncture to the high-pressure pipe 61 the entire arrangement is leakagesafe. Even if a minute amount of high-pressure refrigerant leaks out via the O-ring at the juncture, the leaked out refrigerant will remain in the low-pressure return pipe but cannot leak out into the atmosphere.
  • the refrigerant is supplied through the inlet pipe 62 to the evaporator 60, and is evaporated in the evaporator 60 to flow out from the refrigerant outlet 63.
  • the refrigerant delivered from the evaporator 60 is returned to the compressor via the casing 64 and the low-pressure pipe 65.
  • the temperature of the refrigerant returning from the evaporator 60 is high due to heat exchange with high-temperature air in a vehicle compartment.
  • the diaphragm 19 actuates the valve element 9 in valve opening direction.
  • the expansion valve 1 is fully opened.
  • the diaphragm 19 controls the expansion valve 1 in valve closing direction to control the flow rate.
  • the expansion valve 1 detects the temperature at the outlet of the evaporator 60, and controls the flow rate to the evaporator 60 such that the refrigerant maintains a predetermined degree of superheat.
  • the power element 3 Since the power element 3 is disposed in the low-pressure return pipe from the evaporator 60 the temperature could immediately be detected by the entire power element 3. For this reason, the power element 3 would have a very short temperature-sensing time constant, and the response to a change in the temperature of refrigerant would be so sensitive as to perform an excessive feedback correction on the operation of the valve section 2, which can result in a periodic pressure variation (hunting). To eliminate this inconvenience, the provided heat insulation cover 68 somewhat blocks the heat transfer to the upper housing 17 to increase the temperature-sensing time constant.
  • the expansion valve 1 a in Figs 6, 7 differs from the first embodiment, in that in the body 4 the respective axes of the inlet port 5 and the outlet port 6 are orthogonal to each other.
  • This body 4 is also formed by a die-casting apparatus having a three-way separable die structure.
  • the first die 30 forms the extended part 4a and the thread portion 16a of the external thread 16.
  • the valve element 9, the spring 10 urging the valve element 9 in the valve closing direction, and the spring-receiving member 11 for receiving the spring 10 are disposed within the outlet port 6 of the body 4.
  • the expansion valve 1 a is advantageous in a case where it is arranged such that the longitudinal direction of the double pipe formed by the high-pressure pipe 61 and the low-pressure pipe 65 extending from an engine room where the compressor is disposed to the vehicle compartment where the evaporator 60 is disposed is substantially at right angles to directions in which the inlet pipe 62 of the evaporator 60 and the refrigerant outlet port 63 open.
  • the return low-pressure pipe containing the expansion valve 1 a is bent at a right angle. More specifically, the evaporator 60 is integrally formed with the inlet pipe 62 and a connecting part 64a by furnace brazing.
  • the casing 64 is connected to the connecting part 64a by the pipe clamp 67, and the joint part 66 is welded to an upper portion of the casing 64.
  • the joint part 66 is connected to the low-pressure pipe 65 by the pipe clamp 67.
  • the body 4 has an outer shape in which extended parts 4a are extended in respective three directions up to the vicinity of the inner surface of the casing 64 (Fig. 7). This facilitates positioning the expansion valve 1 a, when inserting it into the casing 64 and connecting the outlet port 6 to the inlet pipe 62.
  • the expansion valve 1 b in Figs 8, 9 (third embodiment) has a different construction of the juncture between the power element 3 and the body 4.
  • the power element 3 of the expansion valves 1 and 1 a has the internal thread 24 in the inner periphery of the hub 23 extended outward from the central opening of the lower housing 18.
  • the internal thread 24 is formed by tapping or pressing the hub 23 after the lower housing 18 is formed by pressing. Therefore, the configuration of the power element 3 of the expansion valves 1 and 1 a requires fabrication for forming the internal thread 34.
  • the power element 3 of the expansion valve 1b in Figs 8, 9 is configured such that the internal thread 24 is simultaneously formed when the lower housing 18 is formed by pressing.
  • the inner periphery of the central opening of the lower housing 18 is formed with a thread such that the thread has a cut-out in an angle range of about 60 degrees within the whole circumference, and is continuously displaced in axial direction over a remaining angle of about 300 degrees.
  • the axial displacement between the ends of the thread assumed to be formed over an angle range of 360 degree is substantially equal to the thread pitch of the external thread 16 on the guide 15.
  • This means that the central opening of the lower housing 18 has a one-turn thread structure. This allows to form the lower housing 18 by pressing in its entirety, including the internal thread 24, and by combining it with the body 4 formed by die-casting without requiring other fabrication steps. Thus the cost of the expansion valve 1 can be further reduced.
  • the power element 3 does not have protruding portions.
  • the heat insulation cover 68 is simplified in shape.
  • the upper housing 17 has a generally outwardly inflating shape.
  • a central portion including the gas introducing hole 21 defines a recess, such that the metal ball 22 does not protrude beyond the outermost surface of the upper housing 17.
  • the expansion valve 1 b is mounted within the casing 64 integrally formed with the evaporator 60.
  • the inlet pipe 62 of the evaporator 60 connected to the outlet port 6 is formed by recessing a plate forming a header part of the evaporator 60 such that the hollow cylindrical part 6a of the outlet port 6 is fitted therein.
  • the low-pressure pipe 65 is directly connected to the casing 64 at an expanded end and by using a pipe clamp 67. The connection is performed by fixing the casing 64 and a backup ring 69 by the pipe clamp 67, in a state where the backup ring 69 holds the casing 64, the low-pressure pipe 65, and the O-ring, on the atmosphere side.
  • the valve element 9 acts in valve opening direction when the inlet port 5 receives high-pressure refrigerant.
  • the valve element 9 is acting in valve closing direction when high-pressure refrigerant is received at the inlet port 5.
  • the inlet port 5 and the hole 8 receiving the valve element 9 communicate with each other, and the hole 12 receiving the shaft 13 and the outlet port 6 communicate with each other.
  • the fourth embodiment is configured such that the relation between the inlet port 5 and the outlet port 6 is inverted compared to the first embodiment.
  • the configuration of the juncture between the power element 3 and the body 4 is also changed.
  • the hub 23 formed with the internal thread 24 protrudes outward from the central opening of the lower housing 18.
  • the hub 23 is formed by bending inward the inner periphery of the central opening of the lower housing 18, and the inner peripheral surface of the bent portion of the hub 23 is formed with the interior thread. This reduces the overall height of the expansion valve 1 c to reduce the total size.
  • the internal thread 24 can be preferably formed by rolling. The rolled internal thread is easier to form than a pressed thread. This reduces the cost of fabrication.
  • the heat insulation cover 68 on the power element 3 is integrally formed with fixing legs 68a by resin-moulding. Although not shown, each fixing leg 68a has a hook at an end. The hook engages at a stepped portion of the body 4 to fix the heat insulation cover 68.
  • the manner of mounting the expansion valve 1 c is modified compared with the cases of the first to third embodiments.
  • the first and third embodiments not only the high-pressure pipe 61 and the low-pressure pipe 65 but also the inlet pipe 65 and the casing 64 are formed by a double pipe, respectively.
  • the expansion valve 1, 1 a, and 1b is mounted in an intermediate portion of the double pipe.
  • the pipe upstream of and the low-pressure pipe 65 downstream of the evaporator are separate pipes, and the expansion valve 1 c is mounted in the intermediate portions of the pipes.
  • the inlet pipe 62 extending from the evaporator and the low-pressure pipe 65a have their ends integrally joined to the casing 64 e.g. by welding, and the end of the high-pressure pipe 61 opposed to that of the inlet pipe 62 and the end of the low-pressure pipe 65b opposed to that of the low-pressure pipe 65a are rigidly joined to a disc-shaped joint part 66 by welding.
  • the casing 64 and the joint part 66 are connected by the pipe clamp 67.
  • the pipe extending from the evaporator to the compressor passes refrigerant lower in density than refrigerant flowing through the pipe extending to the evaporator, and hence has a larger diameter than the pipe extending to the evaporator.
  • the low-pressure pipe 65b connected to the joint 66 has a foremost joint portion with a flatted shape (Fig. 11) to prevent the size of the joint 66 from becoming larger.
  • the foremost end of the low-pressure pipe 65a connected to the casing 64 also has a flatted shape.
  • the body 4 is described to be formed by die-casting of an aluminium alloy, it may instead be formed by injection moulding of a resin or the like by using the three-way separable dies structure.
  • the material of the resin body may be a polyphenylene sulfide (PPS) which has excellent heat resistance, good mechanical properties, etc.
  • PPS polyphenylene sulfide
  • the resin has a material mixed therein which makes noise generated inside the body difficult to be transmitted to the outside.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
  • Valve Housings (AREA)
EP07009857A 2006-06-07 2007-05-16 Expansion valve Withdrawn EP1865275A2 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006157946A JP2007327672A (ja) 2006-06-07 2006-06-07 膨張弁

Publications (1)

Publication Number Publication Date
EP1865275A2 true EP1865275A2 (en) 2007-12-12

Family

ID=38512149

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07009857A Withdrawn EP1865275A2 (en) 2006-06-07 2007-05-16 Expansion valve

Country Status (5)

Country Link
US (1) US20070283717A1 (ko)
EP (1) EP1865275A2 (ko)
JP (1) JP2007327672A (ko)
KR (1) KR20070117464A (ko)
CN (1) CN101086296A (ko)

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JP5550601B2 (ja) 2011-04-27 2014-07-16 株式会社鷺宮製作所 温度膨張弁
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JP5535997B2 (ja) * 2011-08-05 2014-07-02 株式会社鷺宮製作所 シール構造及び温度膨張弁
JP2013129353A (ja) * 2011-12-22 2013-07-04 Mitsubishi Heavy Ind Ltd 車両用空調装置
JP5724904B2 (ja) * 2012-02-20 2015-05-27 株式会社デンソー 膨張弁
CN103574062B (zh) * 2012-08-06 2016-10-05 珠海格力电器股份有限公司 电子膨胀阀
US9523465B2 (en) * 2013-04-24 2016-12-20 GM Global Technology Operations LLC Lubrication system thermostat, and method thereof
JP2015094571A (ja) * 2013-11-14 2015-05-18 株式会社デンソー 膨脹弁
CN110836562A (zh) * 2018-08-17 2020-02-25 浙江盾安禾田金属有限公司 电子膨胀阀及使用该电子膨胀阀的空调系统
JP7027367B2 (ja) * 2019-03-25 2022-03-01 株式会社鷺宮製作所 温度式膨張弁、および、それを備える冷凍サイクルシステム
JP7045345B2 (ja) * 2019-04-25 2022-03-31 株式会社鷺宮製作所 膨張弁および冷凍サイクルシステム
JP7482498B2 (ja) * 2020-01-15 2024-05-14 株式会社不二工機 膨張弁および冷凍サイクル装置

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CN101852307B (zh) * 2009-03-30 2011-09-28 浙江春晖智能控制股份有限公司 热力膨胀阀

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