WO2014155816A1 - Soupape de détente et dispositif de cycle de refroidissement utilisant celle-ci - Google Patents

Soupape de détente et dispositif de cycle de refroidissement utilisant celle-ci Download PDF

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Publication number
WO2014155816A1
WO2014155816A1 PCT/JP2013/080569 JP2013080569W WO2014155816A1 WO 2014155816 A1 WO2014155816 A1 WO 2014155816A1 JP 2013080569 W JP2013080569 W JP 2013080569W WO 2014155816 A1 WO2014155816 A1 WO 2014155816A1
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WIPO (PCT)
Prior art keywords
refrigerant
expansion valve
partition
branch
chamber
Prior art date
Application number
PCT/JP2013/080569
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English (en)
Japanese (ja)
Inventor
裕輔 島津
Original Assignee
三菱電機株式会社
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Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2015507947A priority Critical patent/JP5823078B2/ja
Priority to EP13880458.8A priority patent/EP2980510B1/fr
Priority to CN201420097141.5U priority patent/CN203785346U/zh
Publication of WO2014155816A1 publication Critical patent/WO2014155816A1/fr

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    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • 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
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • 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
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F25B41/45—Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow control on the upstream side of the diverging point, e.g. with spiral structure for generating turbulence
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/005—Outdoor unit 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2500/12—Sound

Definitions

  • the present invention relates to an expansion valve having a refrigerant distribution function and a refrigeration cycle apparatus using the expansion valve.
  • the refrigeration cycle apparatus is provided with an expansion valve that depressurizes the high-pressure refrigerant and changes it into a low-pressure, low-dryness gas-liquid two-phase state, and an evaporator is connected downstream of the expansion valve. Then, the refrigerant enters a gas-liquid two-phase state in the expansion valve, and in the evaporator, the refrigerant exchanges heat with air or water, resulting in a low-pressure, high-dryness gas-liquid two-phase state or a superheated gas state.
  • an evaporator is comprised with the multipass heat exchanger which consists of a several path
  • Patent Document 1 discloses an expansion valve having a valve chamber section and a refrigerant branch chamber section partitioned by a partition wall, and the valve chamber section and the refrigerant branch chamber section are communicated by a throttle section provided on the partition wall. It is disclosed. The refrigerant that has flowed into the expansion valve is decompressed by the throttle and flows into the refrigerant branch chamber in a sprayed state (gas-liquid two-phase state), and is divided into a plurality of branch pipes in the refrigerant branch chamber. .
  • Patent Document 2 discloses an expansion valve including a valve body that adjusts the opening degree of the orifice from the refrigerant inlet to the refrigerant outlet through the orifice and the refrigerant branch chamber.
  • the refrigerant outlets are arranged at equal intervals around the orifice in the circumferential direction of the refrigerant distribution chamber, the valve body is downstream of the orifice, and the refrigerant distribution chamber is a flow path that gradually advances to the outer peripheral side. While the refrigerant expands from the orifice to the refrigerant distribution chamber, it is guided by a projecting rectifier provided in the orifice, and is uniformly distributed to the refrigerant outlet.
  • the refrigerant immediately after flowing out of the expansion valve is a spray flow and is in a state where it is easily distributed uniformly.
  • the refrigerant flowing into the evaporator is not necessarily a spray flow, and is, for example, a slag flow or a plug flow at the evaporator inlet. There is a case. Then, the gas-liquid of the refrigerant in the gas-liquid two-phase state is separated, and there are cases where appropriate distribution to each path cannot be performed due to the influence of gravity.
  • the refrigerant flowing out from the valve chamber is in a spray state in the refrigerant distribution chamber as in Patent Document 1, the refrigerant affects each other in the refrigerant distribution chamber up to each branch pipe, resulting in turbulence.
  • the flow is uniform. If the refrigerant flow rate is sufficiently large, the non-uniform flow collides with the wall surface of the refrigerant distribution chamber to become a uniform flow again, and the refrigerant can be distributed to each branch pipe at the intended distribution ratio in the refrigerant distribution chamber. .
  • the collision energy is small and the flow is not uniform, and it may not be possible to appropriately distribute to each branch pipe.
  • the flow rate of refrigerant flowing through the expansion valve is small. In other words, the refrigerant may not be distributed to each branch pipe at the intended distribution ratio.
  • the refrigerant flowing from the orifice into the refrigerant distribution chamber is expanded and enters the refrigerant outlet provided at equal intervals in the circumferential direction. Instead, it is distributed while being guided by the valve body, the refrigerant distribution chamber, and the rectifying unit.
  • the refrigerants affect each other, resulting in turbulence and an uneven flow. As a result, there is a possibility that it is not uniformly distributed.
  • a reverse flow is not assumed, and there is a risk of generating refrigerant noise in the case of a gas-liquid two-phase flow.
  • it is not equal distribution and cannot be intentionally distributed to different ratios.
  • the present invention has been made to solve the above-described problems, and provides an expansion valve capable of accurately distributing a refrigerant to an intended distribution ratio in a refrigerant distribution chamber and a refrigeration cycle apparatus using the expansion valve. It is for the purpose.
  • the expansion valve of the present invention has a valve chamber and a refrigerant branch chamber partitioned by a partition wall, and a throttle portion that communicates between the valve chamber and the refrigerant branch chamber opens in the partition wall and communicates with the refrigerant branch chamber.
  • the partition portion divides the refrigerant distribution chamber for each of the plurality of branch ports, the refrigerant is reduced or reduced while distributing the refrigerant to each branch port at the intended distribution ratio regardless of the refrigerant flow rate.
  • the pressure such as expansion can be adjusted.
  • FIG. 2B is a schematic diagram showing a state of an A-A ′ cross section in the first housing of FIG. 2A. It is an upper surface schematic diagram which shows an example of the division part in the expansion valve of FIG. 2A. It is a side surface schematic diagram which shows an example of the division part in the expansion valve of FIG. 2A.
  • FIG. 2B is a schematic diagram showing a state of an A-A ′ cross section in the first housing of FIG. 2A. It is a cross-sectional schematic diagram which shows Embodiment 3 of the expansion valve of this invention.
  • FIG. 6B is a schematic diagram showing a cross-sectional view taken along the line A-A ′ in the first housing of FIG. 6A. It is a cross-sectional schematic diagram which shows Embodiment 4 of the expansion valve of this invention.
  • FIG. 8 is a schematic top view illustrating a state of a partition portion in the second housing in FIG. 7.
  • FIG. 8 is a schematic view showing a state of an A-A ′ cross section in the first housing of FIG. 7.
  • Embodiment 5 of the refrigeration cycle apparatus of this invention is a schematic diagram showing Embodiment 5 of the refrigeration cycle apparatus of this invention.
  • FIG. 1 is a refrigerant circuit diagram showing Embodiment 1 of the refrigeration cycle apparatus of the present invention.
  • the refrigeration cycle apparatus 1 performs both cooling operation and heating operation, and has a configuration in which an outdoor unit 1A and an indoor unit 1B are connected by a liquid pipe 9A and a gas pipe 9B.
  • the outdoor unit 1A includes a compressor 2, a flow path switch 3, and an outdoor heat exchanger 4.
  • the compressor 2 sucks the refrigerant, compresses the refrigerant, and discharges it in a high temperature / high pressure state.
  • the compressor 2 has a discharge side connected to the flow path switch 3 and a suction side connected to the suction pipe 9.
  • the flow path switching unit 3 switches between a heating flow path and a cooling flow path in accordance with switching of an operation mode of cooling operation or heating operation, and includes, for example, a four-way valve.
  • the flow path switching unit 3 connects the discharge side of the compressor 2 and the outdoor heat exchanger 4 and connects the suction side of the compressor 2 and the gas pipe 9B. Then, the refrigerant discharged from the compressor 2 flows to the outdoor heat exchanger 4 side, and the refrigerant flowing out from the indoor unit 1B flows into the outdoor unit 1A side through the gas pipe 9B.
  • the flow path switch 3 connects the suction side of the compressor 2 and the outdoor heat exchanger 4 and connects the discharge side of the compressor 2 and the gas pipe 9B. Then, the refrigerant discharged from the compressor 2 flows to the indoor unit 1B side, and the refrigerant flowing out of the indoor unit 1B flows into the outdoor unit 1A through the liquid pipe 9A.
  • a four-way valve is used as the flow path switching device 3 is illustrated, the present invention is not limited to this. For example, a plurality of two-way valves may be combined.
  • the outdoor heat exchanger 4 performs heat exchange between the refrigerant and air (outside air), and for example, a heat transfer tube that allows the refrigerant to pass therethrough, and a heat transfer area between the refrigerant that flows through the heat transfer tube and the outside air. It has the structure provided with the fin for enlarging.
  • the outdoor heat exchanger 4 is connected between the flow path switch 3 and the liquid pipe 9A and functions as a condenser that condenses and liquefies the refrigerant during the cooling operation, and evaporates and vaporizes the refrigerant during the heating operation. It functions as an evaporator.
  • the indoor unit 1B includes an expansion valve 5, an indoor heat exchanger 7, and a header 8.
  • the expansion valve 5 functions as a pressure reducing valve or an expansion valve that adjusts the pressure of the refrigerant that passes through the indoor heat exchanger 7, and is connected between the liquid pipe 9 ⁇ / b> A and the indoor heat exchanger 7.
  • the indoor heat exchanger 7 functions as an evaporator (heat absorber) during cooling operation and functions as a condenser (heat radiator) during heating operation.
  • the indoor side heat exchanger 7 heat-exchanges between indoor air and a refrigerant
  • the indoor heat exchanger 7 is a multi-pass heat exchanger having a plurality of paths, for example, a heat exchanger having two paths.
  • the expansion valve 5 has a distribution function of distributing the refrigerant to each path of the indoor heat exchanger 7 through the capillary tube 6. During the cooling operation, the refrigerant distributed by the expansion valve 5 flows into each path of the indoor heat exchanger 7 and merges at the header 8. During the heating operation, the refrigerant flows into each path of the indoor heat exchanger 7 from the header 8, and the refrigerant flowing out from each path joins at the expansion valve 5.
  • the refrigerant used in the refrigeration cycle apparatus 1 described above it is desirable to use a low GWP refrigerant in a small amount from the viewpoint of preventing global warming, and R32, HFO refrigerant, HCFO refrigerant, flammability having a relatively high GWP. If a refrigerant or the like is used, GWP can be reduced as compared with a conventional chlorofluorocarbon refrigerant.
  • the refrigerant flow in the refrigeration cycle apparatus 1 during cooling operation and heating operation will be described.
  • First, an example of the operation of the refrigeration cycle apparatus 1 during the cooling operation will be described with reference to FIG.
  • the discharge side of the compressor 2 and the gas pipe 9B are connected by the flow path switch 3, and the outdoor heat exchanger 4 and the suction side of the compressor 2 are connected.
  • coolant of a low pressure gas is compressed in the compressor 2, and becomes high pressure gas.
  • the refrigerant in the high-pressure gas state is heat-exchanged with the outside air in the outdoor heat exchanger (condenser) 4 and is condensed by transferring the energy of the refrigerant to a heat source (air or water) to become a high-pressure liquid refrigerant.
  • the refrigerant is depressurized by the expansion valve 5 through the liquid pipe 9A to be in a low-pressure two-phase state, branches at the expansion valve 5, passes through the capillary tube 6, and enters each path of the indoor heat exchanger 7.
  • the indoor heat exchanger (evaporator) 7 as the refrigerant passes through the path in the indoor heat exchanger 7, the refrigerant absorbs the energy of the load-side water or outdoor air and evaporates to become low-pressure gas. At this time, water or air that has been heat exchanged with the refrigerant is cooled. Then, the refrigerant
  • the discharge side of the compressor 2 and the gas pipe 9B are connected by the flow path switch 3, and the outdoor heat exchanger 4 and the suction side of the compressor 2 are connected.
  • the refrigerant enters the compressor 2 with a low-pressure gas and is compressed into a high-pressure gas. Thereafter, the refrigerant in the high-pressure gas state flows through the gas pipe 9 ⁇ / b> B and branches into a plurality of paths of the indoor heat exchanger (condenser) 7 through the header 8.
  • the energy of the refrigerant is transferred to water or air on the load side.
  • the refrigerant condenses to become a high-pressure liquid refrigerant, and heat-exchanged water and indoor air are heated.
  • the high-pressure liquid refrigerant flows into the expansion valve 5 from the indoor heat exchanger (condenser) 7 through the capillary tube 6.
  • the refrigerants that have passed through the plurality of paths of the indoor heat exchanger 7 are collected and reduced in pressure to be in a low-pressure two-phase state.
  • the low-pressure two-phase refrigerant passes through the liquid pipe 9 ⁇ / b> A and reaches the outdoor heat exchanger 4.
  • the outdoor heat exchanger (evaporator) 4 the refrigerant absorbs the energy of outside air and air and evaporates to become low-pressure gas. Thereafter, the flow returns to the suction side of the compressor 2 via the flow path switch 3.
  • FIG. 2A is a schematic cross-sectional view showing Embodiment 1 of the expansion valve of the present invention
  • FIG. 2B is a schematic partial cross-sectional view showing Embodiment 1 of the expansion valve of the present invention, see FIGS. 2A and 2B.
  • the expansion valve 5 will be described.
  • FIG. 2A the case where the number of passes of the indoor side heat exchanger 7 is two is illustrated.
  • the expansion valve 5 has a distribution function of distributing and condensing the refrigerant to each path of the indoor heat exchanger 7, and includes a main body unit 10, a valve body 13, and a partition part 20.
  • the main unit 10 has a valve chamber BC and a refrigerant branch chamber SC that are partitioned by a partition wall 11.
  • the main body unit 10 includes a first housing 10a in which the valve chamber BC is formed, and a second housing 10b in which the refrigerant distribution chamber SC is formed.
  • the first housing 10a is formed, for example, by cutting a brass cast product into a cylindrical shape, and has a flat partition wall 11 orthogonal to the cylindrical portion.
  • a valve chamber BC partitioned by the cylindrical portion and the partition wall 11 is formed in the first housing 10a.
  • a connection port P1 leading to the valve chamber BC is formed on the side surface of the first housing 10a, and a pipe 30 leading to the liquid pipe 9A (see FIG. 1) is attached to the connection port.
  • a refrigerant flows between the valve chamber BC and the liquid pipe 9 ⁇ / b> A via the connection port P ⁇ b> 1 and the pipe 30.
  • the partition wall 11 is formed with a circular throttle portion 12 through which the valve chamber BC and the refrigerant distribution chamber SC communicate.
  • the second housing 10b is formed, for example, in a cylindrical shape, one opening is attached to the partition wall 11 side, and the attachment member 14 in which a plurality of branch ports P2 are formed is fixed to the other opening.
  • a branch pipe 15 is attached to each of the plurality of branch ports P2 of the attachment member 14 so as to protrude into the refrigerant distribution chamber SC by brazing or the like.
  • the valve body 13 adjusts the opening degree of the throttle portion 12 and is disposed on the throttle portion 12 in the valve chamber BC.
  • the valve body 13 has a conical tip, and is arranged so that the tip moves in the throttle portion 12 by a driving device (not shown) provided in the upper portion of the first housing 10a. And according to the position of this valve body 13, the passage area of the throttle part 12 of the micro passage formed by the periphery (valve seat) of the throttle part 12 and the valve body 13 changes, and the opening degree of the throttle part 12 is changed. Can be adjusted.
  • the partition unit 20 partitions the refrigerant branch chamber SC for each of the plurality of branch ports P2, and is disposed in the refrigerant branch chamber SC.
  • 3A is a schematic view showing a state of a partition portion in the second housing 10b of FIG. 2A
  • FIG. 3B is a schematic view showing a state of a cross section AA ′ in the first housing 10a of FIG. 2A
  • FIG. 4 is an expansion of FIG.
  • It is a schematic diagram which shows an example of the division part 20 in the valve 5, and the division part 20 is demonstrated with reference to FIGS. 4A is a schematic top view of the partition part 20,
  • FIG. 4B is a schematic side view of the partition part 20, and
  • FIG. 4C is a developed schematic view of the partition part 20, and the refrigerant is equally distributed to the two branch ports P2.
  • the partition portion 20 is integrally formed of, for example, plate-like stainless steel (SUS) and has a fixed piece 21, a partition wall 22, and an elastic piece 23.
  • the fixing piece 21 is a part for fixing the partition part 20 in the refrigerant distribution chamber SC and is formed in a semicircular shape.
  • the outer shape of the fixed piece 21 is the same as the inner diameter of the second housing 10b or smaller than the inner diameter of the second housing 10b.
  • a hole 21a to be inserted into the branch pipe 15 is formed in the fixed piece 21. By inserting the branch pipe 15 into the hole 21a, the partition portion 20 is fixed to the mounting member 14 and brazed.
  • the diameter of the hole 21a is substantially the same as the diameter of the branch pipe 15, or is formed so as to have a minute gap.
  • the fixed piece 21 is fixed to the mounting member 14 and the branch pipe 15 by brazing or the like.
  • the branch pipe 15 described above is projected into the refrigerant branch chamber SC so as to be connected to the fixed piece 21, and one branch pipe 15 among the plurality of branch pipes 15 is placed in the refrigerant branch chamber SC. It only has to protrude.
  • the partition wall 22 is a flat plate-like member extending from the fixed piece 21 toward the throttle portion 12, and divides the refrigerant branch chamber SC into a plurality of branch ports (see arrows in FIG. 2A).
  • the width of the partition wall 22 is formed larger than the inner diameter of the second housing 10b, and both ends of the partition wall 22 are fixed to the inner peripheral surface of the second housing 10b.
  • the upper edge 22 a of the partition wall 22 is located in the opening of the diaphragm 12 in a vertical view with respect to the partition wall 11. That is, as shown in FIG. 3B, in FIG.
  • the partition wall is located at a position where the upper edge 22a of the partition wall 22 can be seen through the opening of the throttle portion 12 when viewed downward in the valve chamber BC in the AA ′ cross-sectional direction. 22 is arranged.
  • the height of the partition wall 22 is formed to extend to a position directly below the throttle portion 12.
  • a recess 22b is formed in the approximate center of the upper edge 22a of the partition wall 22, and the distance D1 between the lowermost end of the recess 22b and the lower surface 11a of the partition wall 11 where the throttle portion 12 is open is It is formed to be smaller than the diameter R1 of the portion 12 (D1 ⁇ R1).
  • the maximum separation dimension between the lower surface 11a of the partition wall 11 where the throttle part 12 opens and the upper edge 22a of the partition wall 22 is smaller than the dimension of the diameter R1 of the throttle part 12.
  • the upper edge 22a of the partition wall 22 extends to a position directly below the throttle portion 12, so that the refrigerant immediately flows out of the throttle portion 12 and before it diffuses unevenly. Since the refrigerant is distributed, the refrigerant is distributed at the distribution ratio as designed for each branch port P2 regardless of the flow rate of the refrigerant and the state of the refrigerant, and generation of refrigerant flow noise can be minimized.
  • the recess 22b is formed to prevent the valve element 13 from contacting the upper edge 22a of the partition wall 22.
  • the first embodiment the example in which the concave portion 22b is formed in the approximate center of the upper edge 22a of the partition wall 22 is shown.
  • the distance D1 is a distance between the upper edge 22a of the partition wall 22 and the lower surface 11a of the partition wall 11 in which the throttle portion 12 is opened.
  • FIG. 2B is a partial schematic cross-sectional view showing Embodiment 1 of the expansion valve of the present invention.
  • a taper portion 22 c in which the plate thickness of the partition wall 22 decreases toward the throttle portion 12 side may be formed on the upper edge 22 a of the partition wall 22.
  • the partition wall 22 is arrange
  • the sectional area of the refrigerant distribution chamber SC (the area of the throttle portion 12) is divided at an equal area ratio.
  • the distribution ratio since the distribution ratio is set as intended by changing the arrangement position of the partition wall 22, the distribution ratio can be easily set according to the type of the heat exchanger.
  • the elastic piece 23 is in contact with the partition wall 11 and urges the partition wall 22 toward the fixed piece 21 side by an elastic force, and is formed in a semicircular shape.
  • the outer shape of the elastic piece 23 is the same as the inner diameter of the second housing 10b or smaller than the inner diameter of the second housing 10b.
  • an opening 23 a is formed in the elastic piece 23, and the refrigerant flows through the opening 23 a between the throttle portion 12 and the branch pipe 15.
  • the diameter of the semicircle of the opening 23a is formed to be substantially the same as or slightly larger than the diameter of the throttle portion (valve seat) 12.
  • the second housing 10b, the valve body 13, and a driving device (not shown) are attached to the first housing 10a, and the first assembly assembly is assembled.
  • the branch pipe 15 is inserted and fixed to the branch port P2 of the mounting member 14 so as to protrude.
  • the hole 21a of the division part 20 is inserted in the branch piping 15 protruded from the attachment member 14, and a 2nd assembly assembly is assembled.
  • the second assembly assembly is attached to the first assembly assembly, and the expansion valve 5 is completed.
  • the elastic piece 23 comes into contact with the partition wall 11 and the partition wall 22 is urged toward the mounting member 14, and the phase (rotation direction) of the mounting member 14 so that the partition wall 22 is positioned at a predetermined position. Is adjusted.
  • the attachment member 14 is fixed to the second housing 10b, so that the restriction part 12 on the main body unit 10 side and the partition on the attachment member 14 side are provided. It is possible to easily align the phase (rotation direction) with the unit 20.
  • the refrigerant can be distributed to each branch pipe 15 at an intended distribution ratio regardless of the refrigerant flow rate and the refrigerant state.
  • the refrigerant since the refrigerant is branched by the partition part 20 immediately below the throttle part 12, it can be distributed regardless of the flow rate.
  • a refrigerant flow noise may be generated by colliding (front) with the wall surface of the refrigerant branch chamber SC when the refrigerant flow is branched.
  • the refrigerant state in the pipe 30 is a gas-liquid two-phase state such as a slag flow or a plug flow, a discontinuous state in which gas and liquid alternately flow into the throttle portion 12 enters the refrigerant branch chamber SC.
  • the refrigerant branch chamber SC since it enters into the refrigerant branch chamber SC that is branched at the partition part 20 and expands the path, it is easy to diffuse the energy, and generation of discontinuous refrigerant flow noise can be suppressed.
  • partition part 20 is a plate-shaped member and the area of the normal part direction of the partition part 20 is small, generation
  • coolant flow noise can be suppressed.
  • the contact is made by the elasticity (spring) of the partition portion 20, sound generation due to vibration of the contact portion can be prevented.
  • the refrigerant flows into the refrigerant branch chamber SC of the second housing 10b from the plurality of branch pipes 15 and flows into the valve chamber BC of the first housing 10a through the throttle portion 12. Thereafter, the refrigerant in the valve chamber BC flows from the connection port P1 toward the liquid pipe 9A via the pipe 30.
  • each branch pipe 15 when the refrigerant state passing through each branch pipe 15 is a gas-liquid two-phase state such as a slag flow or a plug flow, gas and liquid flow discontinuously from the throttle portion 12 into the valve chamber BC.
  • the refrigerant at the outlet of the indoor heat exchanger (condenser) 7 when the refrigerant at the outlet of the indoor heat exchanger (condenser) 7 is in a gas-liquid two-phase state, the refrigerant is concentrated in the refrigerant branch chamber SC where the flow velocity becomes slow, so that the discontinuity of the gas-liquid becomes remarkable and the throttle Since the refrigerant flows into the portion 12, the refrigerant flow noise may increase.
  • the expansion valve 5 since the expansion valve 5 has a refrigerant distribution function, the refrigerant flow can be performed while performing distribution at an intended distribution ratio regardless of the refrigerant flow rate and the refrigerant state. Generation of sound can be suppressed. Further, since the refrigerant can be depressurized or expanded while having a distribution function, the number of parts is small, and space saving, high workability, and low cost can be achieved. In particular, when the diameter of the heat exchanger is reduced in order to reduce the refrigerant amount, the number of passes inevitably increases, but it is possible to cope with the increase in the number of passes without additionally providing a distributor.
  • the refrigerant can be in a uniform state, and the refrigerant can be evenly distributed.
  • a pipe connecting the branch pipe and the evaporator is used. There is no choice but to adjust the flow resistance (pipe length). Since the pressure loss increases accordingly, it is necessary to increase the required port diameter or pipe diameter of the expansion valve 5, which increases the cost.
  • the distribution ratio can be adjusted depending on the position where the partition wall 22 is arranged, so that it can be easily set to the intended distribution ratio.
  • FIG. FIG. 5 is a schematic view showing Embodiment 2 of the partition portion in the expansion valve of the present invention, and the partition portion 120 will be described with reference to FIG. 5A is a schematic top view of the partition part 120, FIG. 5B is a schematic side view of the partition part 120, FIG. 5C is a developed schematic view of the partition part 120, and FIG. 5D is AA ′ in the first housing 10a of FIG.
  • the schematic diagram which shows the mode of a cross section is shown, respectively,
  • part which has the same structure as the partition part 20 of FIG. 4 is attached
  • the partition 120 in FIG. 5 is different from the partition 20 in FIG. 4 in the number of branches and the structure of the elastic piece 123.
  • the partition 120 in FIG. 5 is attached to the mounting member 14 having the three branch ports P2, and is formed so as to partition the refrigerant distribution chamber SC into three spaces by bending a plate-like member.
  • the A branch pipe 15 is inserted into each of the plurality of branch ports P2, and the fixed piece 121 is disposed on the two branch ports P2 and has a hole 121a for insertion into the two branch pipes 15. ing.
  • three partition walls 122 are formed on the fixed piece 121 corresponding to the three branch ports P2.
  • the elastic piece 123 is formed of a plate-like piece that contacts the partition wall 11 while avoiding the throttle portion 12.
  • the upper edge 122 a of the partition wall 122 is located in the opening of the diaphragm 12 in a vertical view with respect to the partition wall 11. That is, as shown in FIG. 5D, in FIG. 2A, the partition wall is located at a position where the upper edge 122a of the partition wall 122 can be seen through the opening of the throttle portion 12 when viewed from the valve chamber BC in the AA ′ cross-sectional direction. 122 is arranged.
  • a concave portion 122b is formed on the upper edge 122a of the partition wall 122, and a distance D1 between the lowermost end of the concave portion 122b and the lower surface 11a of the partition wall 11 where the throttle portion 12 opens is a diameter R1 of the throttle portion 12. (D1 ⁇ R1, see FIG. 2A). That is, the maximum distance between the lower surface 11a of the partition wall 11 where the aperture 12 is opened and the upper edge 122a of the partition wall 122 is smaller than the diameter R1 of the aperture 12.
  • the upper edge 122a of the partition wall 122 (the lowermost end of the recess 122b) extends to a position immediately below the throttle portion 12, so that the refrigerant immediately flows out of the throttle portion 12 and diffuses unevenly. Since the refrigerant is distributed, the refrigerant is distributed at the distribution ratio as designed for each branch port P2 regardless of the flow rate of the refrigerant and the state of the refrigerant, and generation of refrigerant flow noise can be minimized.
  • the recess 122b is formed to prevent the valve body 13 from contacting the upper edge 122a of the partition wall 122.
  • the concave portion 122b is formed in the approximate center of the upper edge 122a of the partition wall 122 is shown.
  • the distance D1 is a distance between the upper edge 122a of the partition wall 122 and the lower surface 11a of the partition wall 11 in which the throttle portion 12 is opened.
  • the upper edge 122a of the partition wall 122 may be formed with a tapered portion in which the thickness of the partition wall 122 decreases toward the throttle portion 12 as shown in FIG. 2B. .
  • FIG. FIG. 6A is a schematic diagram showing Embodiment 3 of the expansion valve of the present invention
  • FIG. 6B is a schematic diagram showing a cross-sectional view taken along the line AA ′ in the first housing 10a of FIG. 6A, with reference to FIGS. 6A and 6B.
  • the expansion valve 205 will be described.
  • symbol is attached
  • 6A is different from the expansion valve 5 in FIG. 2A in that the partition 220 is made of a wall surface of the branch pipe 15.
  • an auxiliary housing 10c is fixed to the second housing 10b by brazing or the like, and an attachment member 14 having a branch port is attached to the auxiliary housing 10c.
  • the plurality of branch pipes 15 are arranged in the refrigerant distribution chamber SC in a state of extending from the branch port P2 to just below the throttle portion 12. And the wall surface of the branch pipe 15 functions as the partition part 220, and in the refrigerant
  • the upper edge 220 a of the partition part 220 (branch pipe 15) is located in the opening of the throttle part 12 in a vertical view with respect to the partition wall 11. That is, as shown in FIG. 6B, in FIG. 6A, the partitioning portion is located at a position where the upper edge 220a of the partitioning portion 220 can be seen through the opening of the throttle portion 12 when viewed downward from the inside of the valve chamber BC in the AA ′ cross-sectional direction. 220 is arranged.
  • the distance D1 between the upper edge 220a of the partition 220 and the lower surface 11a of the partition wall 11 where the diaphragm 12 opens is formed to be smaller than the diameter R1 of the diaphragm 12 (D1 ⁇ R1).
  • the refrigerant is distributed immediately after flowing out from the throttle part 12 and before spreading unevenly. Regardless of the size of the refrigerant and the state of the refrigerant, the refrigerant is distributed at the distribution ratio as designed for each branch port P2, and generation of refrigerant flow noise can be minimized.
  • the upper edge 220a of the partition part 220 is formed with a tapered part in which the plate thickness of the partition part 220 decreases toward the throttle part 12 as shown in FIG. 2B. Also good.
  • the partition part 220 is formed of a branch pipe, it is possible to perform distribution according to the intended distribution ratio regardless of the refrigerant flow rate and the refrigerant state.
  • the branch pipe 15 also serves as the partition portion 20, the number of parts is small, and the cost and the work efficiency can be improved.
  • the partition part 220 (branch pipe 15) is not in direct contact with the second housing 10b in the refrigerant distribution chamber SC, it is possible to prevent the generation of noise due to the installation of the partition part 220.
  • the second assembly assembly is assembled by fixing the attachment member 14 to the auxiliary housing 10c with the plurality of branch pipes 15 attached thereto, and the auxiliary housing 10c is assembled to the first assembly. It is designed to be fixed to the assembly. Thereby, the operation
  • FIG. 7 is a schematic view showing Embodiment 4 of the expansion valve of the present invention
  • FIG. 8A is a schematic view showing a state of a partition portion in the second housing 10b of FIG. 7
  • FIG. 8B is an A- view in the first housing 10a of FIG.
  • FIG. 7 is a schematic view showing a state of an A ′ cross section, and the expansion valve 305 will be described with reference to FIGS. 7, 8A, and 8B.
  • 7, 8 ⁇ / b> A, and 8 ⁇ / b> B portions where the expansion valve 305 has the same configuration as the expansion valve 5 of FIG. 2 are denoted by the same reference numerals, and description thereof is omitted.
  • the expansion valve 305 of FIGS. 7, 8A, and 8B is different from the expansion valve 5 of FIG.
  • the partition 320 has the same outer shape as the inner surface of the refrigerant branch chamber SC, and has a cylindrical shape that is the same as or smaller than the radius of the second housing 10b. Thereby, generation
  • a plurality of through holes 320 a extending from the narrowed portion 12 to the branch port P ⁇ b> 2 are formed in the partition portion 320, and an annular leaf spring 321 is disposed between the partition wall 11 and the partition portion 320.
  • Each through hole 320a is curved so that the cross-sectional area decreases from the narrowed portion 12 toward the branch port P2, and adjacent through holes 320a are partitioned by a plate-like portion having a curved surface. Further, the leaf spring 321 urges the partition part 320 toward the mounting member 14 to suppress the generation of mechanical sound due to the vibration of the partition part 320.
  • the branch pipe 15 does not protrude from the branch port P2 to the refrigerant branch chamber SC side, and the distributed refrigerant flows directly into the branch port P2.
  • the upper edge 320b of the partition part 320 is located in the opening of the diaphragm part 12 in a vertical view with respect to the partition wall 11. That is, as shown in FIG. 8B, in FIG. 7, the upper edge is located at a position where the upper edge 320b of the partition part 320 can be seen through the opening of the throttle part 12 when viewed downward from the valve chamber BC in the AA ′ cross-sectional direction. 320b is arranged.
  • a concave portion 320c is formed in the upper edge 320b of the partition portion 320.
  • a distance D1 between the lowermost end of the concave portion 320c and the lower surface 11a of the partition wall 11 where the throttle portion 12 opens is a diameter R1 of the throttle portion 12. (D1 ⁇ R1). That is, the maximum separation dimension between the lower surface 11a of the partition wall 11 where the throttle part 12 opens and the upper edge 320b of the partition part 320 is smaller than the dimension of the diameter R1 of the throttle part 12.
  • the upper edge 320b of the partition 320 (the lowermost end of the recess 320c) extends to a position directly below the throttle 12, so that the refrigerant has just flowed out of the throttle 12 and before it diffuses unevenly. Since the refrigerant is distributed, the refrigerant is distributed at the distribution ratio as designed for each branch port P2 regardless of the flow rate of the refrigerant and the state of the refrigerant, and generation of refrigerant flow noise can be minimized.
  • the recessed part 320c is formed in order to prevent the valve body 13 from contacting the upper edge 320b of the partition part 320.
  • the concave portion 320c is formed on the upper edge 320b of the partition portion 320 is shown.
  • the distance D1 is a distance between the upper edge 320b of the partition part 320 and the lower surface 11a of the partition wall 11 where the throttle part 12 opens.
  • the upper edge 320b of the partition part 320 is formed with a tapered part in which the plate thickness of the upper edge 320b decreases toward the throttle part 12 as shown in FIG. 2B. Also good.
  • the refrigerant can be distributed at an intended distribution ratio regardless of the refrigerant flow rate and the refrigerant state, as in the first to third embodiments. At the same time, generation of refrigerant flow noise can be suppressed. Moreover, since the partition part 320 is made of an integrally molded product, the number of parts is small, and the cost and workability can be improved.
  • FIG. 9 is a schematic view showing Embodiment 5 of the refrigeration cycle apparatus of the present invention.
  • the refrigeration cycle apparatus 400 will be described with reference to FIG.
  • the expansion valve 5 of FIG. 2 is illustrated, the expansion valves 205 and 305 of FIGS. 5 and 6 may be used.
  • the refrigeration cycle apparatus 400 has a configuration in which a plurality of indoor units 1B are connected to a single outdoor unit 400A. Furthermore, the outdoor unit 400A has an accumulator 405 on the suction side of the compressor 2. The accumulator 405 stores surplus refrigerant or surplus refrigerant with respect to a transient change in operation. The accumulator 405 is supplied with refrigerant from the flow path switching unit 3 side and to the suction side of the compressor 2 via the suction pipe 9. A refrigerant is supplied.
  • the outdoor heat exchanger 404 is connected to the flow path switching unit 3 through the header 403 and is connected to the liquid pipe 9A through the expansion valve 5.
  • the expansion valve 5 collects the refrigerant that has flowed out from each path of the outdoor heat exchanger 404 and flows out toward the liquid pipe 9A.
  • the expansion valve 5 distributes the refrigerant flowing from the liquid pipe 9A to each path of the outdoor heat exchanger 404 and flows out.
  • the expansion valve 5 in which the outdoor heat exchanger 404 suppresses the refrigerant flow noise with an intended distribution ratio can be used for the multi-pass heat exchanger.
  • the liquid pipe density is reduced by providing the expansion valves 5 on the outdoor unit 400A side and the indoor unit 1B side, respectively, the amount of refrigerant can be reduced.
  • the expansion valve 5 is provided at both ends of the liquid pipe 9A, the expansion valve 5 can be controlled so that the refrigerant in the liquid pipe 9A is in a gas-liquid two-phase state. Thereby, since the pressure loss of the refrigerant in the two-phase gas phase state is larger than the pressure loss of the liquid refrigerant, unnecessary pressure loss can be reduced.
  • the embodiment of the present invention is not limited to the above embodiment.
  • the indoor heat exchanger 7 in FIG. 1 and the outdoor heat exchanger 404 in FIG. 9 exemplify the case where the number of passes is two
  • FIG. 3 exemplifies the case where the number of passes is three. Four or more may be provided.
  • the main body unit 10 includes the first housing 10a and the second housing 10b as separate members, but may be integrally formed.
  • the fixing piece 21 is attached so that the hole 21a is positioned on the branch port P2. It may be fixed to the member 14.
  • 1,400 Refrigeration cycle apparatus 1A, 400A outdoor unit, 1B indoor unit, 2 compressor, 3 flow path switch, 4, 404 outdoor heat exchanger, 5, 205, 305 expansion valve, 6 capillary tube, 7 chambers Inner heat exchanger, 8 header, 9 suction pipe, 9A liquid pipe, 9B gas pipe, 10 body unit, 10a first housing, 10b second housing, 10c auxiliary housing, 11 partition wall, 12 throttle part, 13 valve body, 14 mounting member, 15 branch piping, 20, 120, 220, 320 partition, 21, 121 fixed piece, 21a, 121a hole, 22, 122 partition wall, 22a, 122a, 220a, 320b upper edge, 22b, 122b, 320c Concave part, 22c taper part, 23, 123 elastic piece, 23a opening, 30 piping 205 expansion valve, 320a through hole 321 leaf spring 404 headers, 405 accumulator, BC valve chamber, P1 connection port, P2 branch port, SC refrigerant flow chamber.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
  • Lift Valve (AREA)

Abstract

La présente invention concerne une soupape de détente pouvant diviser avec précision un liquide de refroidissement dans une chambre de division de flux de liquide de refroidissement selon un taux de division cible ; et un dispositif de cycle de refroidissement utilisant celle-ci. La soupape de détente est équipée : d'une unité de corps (10) présentant une chambre de soupape (BC) et une chambre de division de flux de liquide de refroidissement (SC) qui sont séparées par une cloison de séparation (11), une partie de rétrécissement (12) qui forme une ouverture dans la cloison de séparation de façon à raccorder la chambre de soupape à la chambre de division de flux de liquide de refroidissement et une pluralité d'orifices de ramification (P2, P2) formés de façon à se raccorder à l'intérieur de la chambre de division de flux de liquide de refroidissement ; d'un corps de soupape (13) permettant d'ajuster le degré d'ouverture de la partie de rétrécissement ; et d'une partie de segmentation en forme de plaque (20) permettant de segmenter la chambre de division de flux de liquide de refroidissement en fonction de chacun des orifices de ramification, positionnée à l'intérieur de la chambre de division de flux de liquide de refroidissement. À l'intérieur, au moins une partie du bord supérieur (22a) de la partie de segmentation est positionnée à l'intérieur de l'ouverture de la partie de rétrécissement vu depuis un angle perpendiculaire par rapport à la cloison de séparation.
PCT/JP2013/080569 2013-03-26 2013-11-12 Soupape de détente et dispositif de cycle de refroidissement utilisant celle-ci WO2014155816A1 (fr)

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JP2015507947A JP5823078B2 (ja) 2013-03-26 2013-11-12 膨張弁及びこれを用いた冷凍サイクル装置
EP13880458.8A EP2980510B1 (fr) 2013-03-26 2013-11-12 Soupape de détente et dispositif de cycle de refroidissement utilisant celle-ci
CN201420097141.5U CN203785346U (zh) 2013-03-26 2014-03-05 膨胀阀及使用该膨胀阀的制冷循环装置

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PCT/JP2013/058755 WO2014155518A1 (fr) 2013-03-26 2013-03-26 Vanne d'expansion et dispositif de cycle de refroidissement l'utilisant
JPPCT/JP2013/058755 2013-03-26

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3070418A3 (fr) * 2015-03-18 2017-01-11 Hiref S.p.A. Système de réfrigération
CN107270594A (zh) * 2017-07-18 2017-10-20 海信科龙电器股份有限公司 一种节流短管及空调器
WO2018002983A1 (fr) * 2016-06-27 2018-01-04 三菱電機株式会社 Dispositif à cycle de réfrigération

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020083362A1 (fr) * 2018-10-27 2020-04-30 浙江三花智能控制股份有限公司 Vanne d'expansion électronique

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4710952U (fr) * 1971-02-26 1972-10-09
JPH062990A (ja) * 1992-06-19 1994-01-11 Daikin Ind Ltd 冷媒分流器
JPH0618864U (ja) * 1992-08-17 1994-03-11 東洋ラジエーター株式会社 冷媒分流器
JP2004183955A (ja) * 2002-12-02 2004-07-02 Sharp Corp 冷媒分流器
WO2008001803A1 (fr) * 2006-06-29 2008-01-03 Daikin Industries, Ltd. Valve d'expansion avec structure de division du débit et unité de réfrigeration l'utilisant
WO2009004760A1 (fr) * 2007-07-02 2009-01-08 Daikin Industries, Ltd. Vanne électrique et dispositif de congélation
JP2009024937A (ja) 2007-07-19 2009-02-05 Daikin Ind Ltd 冷媒分流室結合型膨張弁及びこれを用いた冷凍装置
JP2010032185A (ja) 2008-07-31 2010-02-12 Sanden Corp 膨張装置
JP2010190523A (ja) * 2009-02-19 2010-09-02 Mitsubishi Heavy Ind Ltd 冷媒分配器

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3381486B2 (ja) * 1995-10-27 2003-02-24 松下電器産業株式会社 分流器
JP2000081256A (ja) * 1998-09-04 2000-03-21 Daikin Ind Ltd 分流器およびそれを備えた熱交換器
JP5045252B2 (ja) * 2007-06-06 2012-10-10 パナソニック株式会社 空気調和機
JP2009019783A (ja) * 2007-07-10 2009-01-29 Daikin Ind Ltd 冷媒分流室一体化構造の膨張弁及びこれを用いた冷凍装置
JP2011033281A (ja) * 2009-08-03 2011-02-17 Daikin Industries Ltd 冷媒分流器及びこれを備える冷媒回路
JP5174084B2 (ja) * 2010-04-30 2013-04-03 三菱電機株式会社 冷却機及び冷凍サイクル装置

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4710952U (fr) * 1971-02-26 1972-10-09
JPH062990A (ja) * 1992-06-19 1994-01-11 Daikin Ind Ltd 冷媒分流器
JPH0618864U (ja) * 1992-08-17 1994-03-11 東洋ラジエーター株式会社 冷媒分流器
JP2004183955A (ja) * 2002-12-02 2004-07-02 Sharp Corp 冷媒分流器
WO2008001803A1 (fr) * 2006-06-29 2008-01-03 Daikin Industries, Ltd. Valve d'expansion avec structure de division du débit et unité de réfrigeration l'utilisant
WO2009004760A1 (fr) * 2007-07-02 2009-01-08 Daikin Industries, Ltd. Vanne électrique et dispositif de congélation
JP2009024937A (ja) 2007-07-19 2009-02-05 Daikin Ind Ltd 冷媒分流室結合型膨張弁及びこれを用いた冷凍装置
JP2010032185A (ja) 2008-07-31 2010-02-12 Sanden Corp 膨張装置
JP2010190523A (ja) * 2009-02-19 2010-09-02 Mitsubishi Heavy Ind Ltd 冷媒分配器

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3070418A3 (fr) * 2015-03-18 2017-01-11 Hiref S.p.A. Système de réfrigération
WO2018002983A1 (fr) * 2016-06-27 2018-01-04 三菱電機株式会社 Dispositif à cycle de réfrigération
JPWO2018002983A1 (ja) * 2016-06-27 2018-09-27 三菱電機株式会社 冷凍サイクル装置
US20190137146A1 (en) * 2016-06-27 2019-05-09 Mitsubishi Electric Corporation Refrigeration cycle apparatus
US10883745B2 (en) 2016-06-27 2021-01-05 Mitsubishi Electric Corporation Refrigeration cycle apparatus
CN107270594A (zh) * 2017-07-18 2017-10-20 海信科龙电器股份有限公司 一种节流短管及空调器

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