WO2020194677A1 - 冷凍サイクル装置 - Google Patents

冷凍サイクル装置 Download PDF

Info

Publication number
WO2020194677A1
WO2020194677A1 PCT/JP2019/013654 JP2019013654W WO2020194677A1 WO 2020194677 A1 WO2020194677 A1 WO 2020194677A1 JP 2019013654 W JP2019013654 W JP 2019013654W WO 2020194677 A1 WO2020194677 A1 WO 2020194677A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchange
refrigerant
exchange unit
heat exchanger
expansion device
Prior art date
Application number
PCT/JP2019/013654
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
中村　伸
前田　剛志
暁 八柳
森田　敦
龍一 永田
真哉 東井上
石橋　晃
繁佳 松井
篤史 高橋
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to EP19921695.3A priority Critical patent/EP3951287A4/de
Priority to CN201980094530.8A priority patent/CN113646597B/zh
Priority to US17/434,298 priority patent/US20220136740A1/en
Priority to PCT/JP2019/013654 priority patent/WO2020194677A1/ja
Priority to JP2021508609A priority patent/JP7123238B2/ja
Publication of WO2020194677A1 publication Critical patent/WO2020194677A1/ja

Links

Images

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
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • 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
    • 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
    • F25B39/04—Condensers
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0252—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units with bypasses
    • 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
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0254—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0417—Refrigeration circuit bypassing means for the subcooler
    • 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
    • F25B2500/31—Low ambient temperatures

Definitions

  • the present invention relates to a refrigeration cycle device, and more particularly to a connection between a heat exchanger functioning as an evaporator and an expansion device.
  • An air conditioner which is a type of refrigeration cycle device, cools the high-temperature and high-pressure gas refrigerant discharged by a compressor by heat exchange with the room air in an indoor heat exchanger that functions as a condenser in heating operation, and cools the temperature. Phase change to high-pressure liquid refrigerant. After that, the low temperature and high pressure liquid refrigerant is phase-changed to a low temperature and low pressure two-phase refrigerant by the expansion device. The two-phase refrigerant is heated by exchanging heat with air in an outdoor heat exchanger that functions as an evaporator, changes its phase to a low-temperature low-pressure gas refrigerant, and is sucked into a compressor. Then, the low-temperature and low-pressure gas refrigerant is compressed by the compressor and discharged again as the high-temperature and high-pressure gas refrigerant.
  • the defrosting operation of the outdoor heat exchanger is performed by a method such as allowing hot gas to flow into the outdoor heat exchanger.
  • the drain water generated by defrosting is dropped onto the drain pan and drained.
  • water may collect at the lower end of the heat exchanger due to the stagnation of drainage from the drain pan or the influence of surface tension.
  • the accumulated drain water may freeze during the heating operation, which may damage the outdoor heat exchanger. Therefore, a method of installing a heater in the drain pan to prevent the outdoor heat exchanger from freezing is known.
  • a refrigerant having a higher pressure (temperature) than the upper portion of the heat exchanger causes the lower portion of the heat exchanger to flow, thereby causing a drain pan and a lower portion of the heat exchanger. Frost formation and freezing are suppressed.
  • the heat transfer tube In order to further improve the heat transfer performance of the heat exchanger or to reduce the amount of refrigerant flowing in the heat transfer tube constituting the heat exchanger, the heat transfer tube The cross-sectional area of is sometimes reduced.
  • a heat transfer tube composed of a circular tube it is conceivable to reduce the outer diameter, or to make the cross section of the tube flat and to make the flow path in the tube a small diameter and multiple holes.
  • the cross-sectional area of the flow path of the heat transfer tube constituting the heat exchanger when the cross-sectional area of the flow path of the heat transfer tube constituting the heat exchanger is reduced, the flow path resistance in the lower portion of the heat exchanger where the number of branches of the refrigerant flow path is small is large. There was a problem of becoming.
  • the present invention is for solving the above-mentioned problems, and provides a refrigeration cycle device capable of suppressing freezing of the lower part of the heat exchanger where drain water tends to stay even when the diameter of the heat transfer tube is reduced.
  • the purpose is to get.
  • the refrigeration cycle device includes a refrigerant circuit in which a compressor, a first expansion device, and a first heat exchanger functioning as an evaporator during heating operation are connected by a refrigerant pipe, and the first heat is described.
  • the exchanger includes the first heat exchange unit and a second heat exchange unit connected in series with the first heat exchange unit in the refrigerant circuit, and the first expansion device is the refrigerant circuit. It is connected in parallel with the second heat exchange unit, and the second heat exchange unit is located below the first heat exchange unit.
  • the cross-sectional area of the refrigerant flow path of the heat transfer tube of the heat exchanger is reduced to reduce the amount of refrigerant flowing through the refrigerant circuit, while suppressing freezing of the drain pan and the lower part of the heat exchanger. can do.
  • FIG. 1 It is a circuit diagram of the refrigerant circuit 1 of the refrigeration cycle apparatus 100 which concerns on Embodiment 1.
  • FIG. It is a perspective view of the 1st heat exchanger 10 of the refrigeration cycle apparatus 100 which concerns on Embodiment 1.
  • FIG. It is explanatory drawing of the cross-sectional structure of the 1st heat exchanger 10 of FIG. It is explanatory drawing of the structure which looked at the 1st heat exchanger 10 which concerns on Embodiment 1 from the front.
  • a cross-sectional view of a flat tube which is an example of a heat transfer tube 20 used in the first heat exchanger 10 of the first embodiment is shown.
  • FIG. 1 It is a circuit diagram of the refrigerant circuit 101 of the refrigerating cycle apparatus 1100 which is a comparative example of the refrigerating cycle apparatus 100 of Embodiment 1.
  • FIG. It is a perspective view of the 1st heat exchanger 110 of the refrigeration cycle apparatus 1100 which concerns on a comparative example. It is a figure which shows the characteristic at the time of a heating operation of the refrigeration cycle apparatus 1100 of a comparative example. It is a figure which shows the characteristic at the time of a heating operation of the refrigeration cycle apparatus 100 which concerns on Embodiment 1.
  • FIG. It is an enlarged view of the part A of FIG. It is a circuit diagram of the refrigerant circuit 201 of the refrigeration cycle apparatus 200 which concerns on Embodiment 2.
  • FIG. 1 It is a perspective view of the 1st heat exchanger 110 of the refrigeration cycle apparatus 1100 which concerns on a comparative example. It is a figure which shows the characteristic at the time of a heating operation of the refrigeration cycle apparatus 1100 of
  • FIG. 2 It is a perspective view of the 1st heat exchanger 210 of the refrigeration cycle apparatus 200 which concerns on Embodiment 2.
  • FIG. It is a figure which shows the characteristic at the time of a heating operation of the refrigeration cycle apparatus 200 which concerns on Embodiment 2.
  • FIG. It is a figure which shows the characteristic at the time of a heating operation of the refrigeration cycle apparatus 200 which concerns on Embodiment 2.
  • FIG. It is a circuit diagram of the refrigerant circuit 301 of the refrigeration cycle apparatus 300 which concerns on Embodiment 3.
  • FIG. 3 It is a perspective view of the 1st heat exchanger 310 of the refrigeration cycle apparatus 300 which concerns on Embodiment 3.
  • FIG. It is a figure which shows the characteristic at the time of a heating operation of the refrigeration cycle apparatus 300 which concerns on Embodiment 3.
  • FIG. It is a figure which shows the characteristic at the time of a heating operation of the refrigeration cycle apparatus 300 which concerns on Embodiment 3.
  • FIG. It is a circuit diagram of the refrigerant circuit 401 of the refrigeration cycle apparatus 400 which concerns on Embodiment 4.
  • FIG. It is a perspective view of the 1st heat exchanger 410 of the refrigeration cycle apparatus 400 which concerns on Embodiment 4.
  • FIG. It is a figure which shows the characteristic at the time of a heating operation of the refrigeration cycle apparatus 400 which concerns on Embodiment 4.
  • FIG. 1 is a circuit diagram of a refrigerant circuit 1 of the refrigeration cycle device 100 according to the first embodiment.
  • the refrigeration cycle device 100 shown in FIG. 1 is, for example, an air conditioner.
  • the compressor 2, the four-way valve 7, the first heat exchanger 10, the first expansion device 5, and the second heat exchanger 3 are connected by a refrigerant pipe, and the refrigerant is used. It constitutes the circuit 1.
  • the refrigeration cycle device 100 is an air conditioner
  • the refrigerant flows in the refrigerant pipe, and the flow of the refrigerant is switched by the four-way valve 7 to switch between the heating operation and the cooling operation or the defrosting operation. Can be done.
  • the air conditioner is illustrated as the refrigerating cycle device 100, but the refrigerating cycle device 100 is, for example, refrigerating a refrigerator, a freezer, a vending machine, an air conditioner, a refrigerating device, a water heater, or the like. It is used for applications or air conditioning applications.
  • the compressor 2, the second heat exchanger 3, the first expansion device 5, the first heat exchanger 10, and the four-way valve 7 constitute a refrigerant circuit 1 in which the refrigerant can circulate.
  • a refrigerating cycle is performed in which the refrigerant circulates in the refrigerant circuit 1 while changing the phase.
  • the compressor 2 compresses the refrigerant.
  • the compressor 2 is, for example, a rotary compressor, a scroll compressor, a screw compressor, a reciprocating compressor, or the like.
  • the first heat exchanger 10 functions as an evaporator when the refrigeration cycle device 100 is in the heating operation, and functions as a condenser when the refrigeration cycle device 100 is in the cooling operation.
  • the first heat exchanger 10 is composed of a first heat exchange unit 11 and a second heat exchange unit 12.
  • the second heat exchange unit 12 is located below the first heat exchange unit 11.
  • the second heat exchanger 3 functions as a condenser when the refrigeration cycle device 100 is in the heating operation, and functions as an evaporator when the refrigeration cycle device 100 is in the cooling operation. However, in the second heat exchanger 3, the refrigerant temperature may drop due to the pressure loss in the pipe during the heating operation, and a part of the second heat exchanger 3 may act as an evaporator.
  • the first heat exchanger 10 and the second heat exchanger 3 include, for example, a fin-and-tube heat exchanger, a microchannel heat exchanger, a finless heat exchanger, a shell-and-tube heat exchanger, and a heat pipe heat exchanger. , Double tube heat exchanger, plate heat exchanger, etc.
  • the first expansion device 5 expands the refrigerant to reduce the pressure.
  • the first expansion device 5 is, for example, an electric expansion valve capable of adjusting the flow rate of the refrigerant.
  • the first expansion device 5 may be not only an electric expansion valve but also a mechanical expansion valve using a diaphragm as a pressure receiving portion, a capillary tube, or the like.
  • the four-way valve 7 switches the flow path of the refrigerant in the refrigeration cycle device 100 and changes the circulation direction of the refrigerant in the refrigerant circuit 1.
  • the four-way valve 7 is switched so as to connect the discharge port of the compressor 2 and the second heat exchanger 3 and to connect the suction port of the compressor 2 and the first heat exchanger 10 during the heating operation. Further, the four-way valve 7 connects the discharge port of the compressor 2 and the first heat exchanger 10 during the cooling operation and the dehumidification operation, and connects the suction port of the compressor 2 and the second heat exchanger 3. Can be switched.
  • a blower 6 is arranged in the vicinity of the first heat exchanger 10. Further, in the second heat exchanger 3, a blower 4 is arranged in the vicinity thereof.
  • the first heat exchanger 10 is an outdoor heat exchanger mounted on the outdoor unit, and the blower 6 sends outside air to the first heat exchanger 10 to exchange heat between the outside air and the refrigerant.
  • the second heat exchanger 3 is an indoor heat exchanger mounted on the indoor unit, and the blower 4 introduces the indoor air into the housing of the indoor unit and sends the indoor air to the indoor heat exchanger. , Heat exchange is performed between the indoor air and the refrigerant to harmonize the temperature of the indoor air.
  • the configuration of the refrigerant circuit 1 of the refrigeration cycle device 100 according to the first embodiment will be described based on the flow of the refrigerant in the operating state of cooling and heating.
  • the refrigerant discharged from the compressor 2 flows into the first heat exchange section 11 of the first heat exchanger 10 via the four-way valve 7.
  • the refrigerant flowing out of the first heat exchange unit 11 branches into two refrigerant flow paths, one passing through the first expansion device 5 and the other passing through the second heat exchange unit 12. After that, the refrigerant that has passed through the first expansion device 5 and the refrigerant that has passed through the second heat exchange unit 12 merge, pass through the second heat exchanger 3 and the four-way valve 7 in this order, and are sucked into the compressor 2.
  • the refrigerant discharged from the compressor 2 flows into the second heat exchanger 3 via the four-way valve 7.
  • the refrigerant flowing out of the second heat exchanger 3 branches into two refrigerant flow paths, one of which passes through the first expansion device 5 and the other of which passes through the second heat exchanger 12 of the first heat exchanger 10. ..
  • the refrigerant that has passed through the first expansion device 5 and the refrigerant that has passed through the second heat exchange unit 12 merge, pass through the first heat exchange unit 11 and the four-way valve 7 in this order, and are sucked into the compressor 2.
  • the refrigerant circuit 1 of the refrigerating cycle apparatus 100 includes a branch portion 90 in which the refrigerant pipe is branched between the second heat exchanger 3 and the first heat exchanger 10 and the first expansion device 5. That is, no other expansion device is provided between the second heat exchanger 3 and the branch portion 90.
  • FIG. 2 is a perspective view of the first heat exchanger 10 of the refrigeration cycle apparatus 100 according to the first embodiment.
  • FIG. 2 schematically shows a part of the refrigerant pipe connected to the first heat exchanger 10.
  • the first heat exchanger 10 includes a first heat exchange unit 11 and a second heat exchange unit 12.
  • the second heat exchange unit 12 is located below the first heat exchange unit 11.
  • the first heat exchange unit 11 and the second heat exchange unit 12 each include two heat exchange units arranged in series in the flow direction of the air flowing into the first heat exchanger 10.
  • the first heat exchange unit 11 includes a first windward heat exchange unit 11a as a heat exchange unit located on the leeward side, and a first leeward heat exchange unit 11b as a heat exchange unit located on the leeward side.
  • the first leeward heat exchange section 11a and the first leeward heat exchange section 11b are connected by a header 14 at an end portion.
  • the refrigerant flowing out of the first leeward heat exchange section 11b is configured to flow into the first leeward side heat exchange section 11a.
  • the second heat exchange unit 12 includes a second windward heat exchange unit 12a as a heat exchange unit located on the leeward side, and a second leeward heat exchange unit 12b as a heat exchange unit located on the leeward side.
  • the second leeward side heat exchange unit 12a and the second leeward side heat exchange unit 12b are connected by a header 14 at an end portion.
  • the refrigerant flowing out of the second windward side heat exchange unit 12a is configured to flow into the second leeward side heat exchange unit 12b.
  • the first heat exchange unit 11 and the second heat exchange unit 12 constituting the first heat exchanger 10 each include a heat transfer tube 20.
  • the heat transfer tubes 20 are arranged in parallel in the z direction shown in FIG. In the first embodiment, the z-axis is along the direction of gravity.
  • the first heat exchanger 10 is not limited to the one installed so that the z direction is aligned with the gravity direction, and may be installed with the z direction tilted, for example. That is, the plurality of heat transfer tubes 20 may be arranged in parallel in the vertical direction.
  • the header 14 connects the upper header 14a that connects the first windward heat exchange unit 11a and the first leeward heat exchange unit 11b, and the second windward heat exchange unit 12a and the second leeward heat exchange unit 12b.
  • the lower header 14b is provided.
  • the upper header 14a and the lower header 14b are integrally formed, but the inside is partitioned into a plurality of spaces, and at least the refrigerant of the first heat exchange section 11 and the refrigerant of the second heat exchange section 12 are used. Is formed so as not to mix.
  • the first windward heat exchange unit 11a and the first leeward heat exchange unit 11b do not have to be connected by the header 14.
  • the end portions of the heat transfer tube 20 included in the first windward heat exchange section 11a and the heat transfer tube 20 included in the first leeward side heat exchange section 11b may be connected to each other by a U-shaped tube.
  • the second windward heat exchange section 12a and the second leeward heat exchange section 12b do not have to be connected by the header 14, and the ends of the heat transfer tubes 20 are connected to each other by a U-shaped tube. You may.
  • the first heat exchange unit 11 includes a plurality of heat transfer tubes 20.
  • the first leeward heat exchange unit 11a and the first leeward heat exchange unit 11b each include a plurality of heat transfer tubes 20 having the same number, and are connected by a header 14.
  • the plurality of heat transfer tubes 20 are arranged in parallel in the z direction. Further, the plurality of heat transfer tubes 20 of the first windward heat exchange portion 11a are connected to the windward collecting pipe 13a at the end in the y direction.
  • a plurality of heat transfer tubes 20 of the first leeward heat exchange section 11b are also connected to the leeward collecting pipe 13b at the end in the y direction.
  • the collecting pipes 13a and 13b are connected to the refrigerant pipes constituting the refrigerant circuit 1 and serve as an inflow portion or an outflow portion of the refrigerant to the first heat exchange portion 11.
  • the collecting pipes 13a and 13b may be divided into a plurality of parts. For example, among the plurality of heat transfer tubes 20 of the first leeward heat exchange section 11b, the upper three heat transfer tubes 20, the middle three heat transfer tubes 20, and the lower three heat transfer tubes 20 are different from each other. It may be connected to a collecting pipe.
  • the second windward heat exchange unit 12a and the second leeward heat exchange unit 12b constituting the second heat exchange unit 12 each have one heat transfer tube 20.
  • the second leeward side heat exchange unit 12a and the second leeward side heat exchange unit 12b may have a plurality of heat transfer tubes 20.
  • the first heat exchange unit 11 has nine heat transfer tubes 20 arranged in the z direction
  • the second heat exchange unit 12 has one heat transfer tube 20 in the z direction. That is, the number of the heat transfer tubes 20 arranged in parallel in the first heat exchange unit 11 is larger than the number of heat transfer tubes 20 arranged in parallel in the second heat exchange unit 12.
  • the number of heat transfer tubes 20 is not limited to this.
  • the number of refrigerant flow paths in each of the first heat exchange unit 11 and the second heat exchange unit 12 can be appropriately set. However, the number of refrigerant flow paths of the first heat exchange unit 11 located at the upper part is larger than the number of refrigerant flow paths of the second heat exchange unit 12.
  • the high-pressure liquid refrigerant condensed by the second heat exchanger 3, which at least a part of the refrigerating cycle apparatus 100 functions as a condenser, is split into two at the branch portion 90 of the refrigerant pipe and is installed in the first expansion apparatus 5.
  • the circuit is branched in parallel to the connected circuit and the bypass circuit 95 connected to the second windward heat exchange unit 12a.
  • the refrigerant flowing into the first expansion device 5 expands, that is, reduces the pressure, and becomes a low-temperature gas-liquid two-phase refrigerant.
  • the refrigerant flowing out of the first expansion device 5 merges with the refrigerant that has passed through the second leeward heat exchange section 12b.
  • a refrigerant passes through a device such as the first expansion device 5, it depends on the shape of the flow path of the first expansion device 5, the circulation amount of the refrigerant in the refrigerant circuit 1, and the flow mode of the refrigerant.
  • a predetermined flow resistance is generated.
  • the flow phase of the refrigerant is a physical property of the refrigerant, and changes depending on the state of the refrigerant such as a gas phase, a liquid phase, or a gas-liquid two-phase.
  • the flow resistance of the first expansion device 5 causes a pressure loss in the flow of the refrigerant passing through the first expansion device 5. That is, the pressure of the refrigerant that has passed through the first expansion device 5 decreases.
  • the refrigerant flowing into the second windward heat exchange section 12a flows in the heat transfer tube 20 and flows into the header 14 for moving from the second windward heat exchange section 12a to the second leeward heat exchange section 12b.
  • the internal space of the header 14 is divided, and the header 14 is divided according to the positions of a plurality of heat transfer tubes 20 arranged in parallel in the z direction.
  • the internal space of the header 14 is divided, and a lower header 14b is formed at the lower part of the header 14.
  • the lower header 14b connects the heat transfer tube 20 of the second windward heat exchange section 12a and the heat transfer tube 20 of the second leeward heat exchange section 12b.
  • the refrigerant that has passed through the lower header 14b flows into the second leeward heat exchange section 12b, flows through the heat transfer tube 20, and then merges with the refrigerant that has passed through the first expansion device 5.
  • the heat transfer tube 20 has a predetermined flow resistance even when the refrigerant flows through the heat transfer tube 20.
  • the flow resistance is generated according to the shape of the flow path in the heat transfer tube 20, the circulation amount of the refrigerant in the refrigerant circuit 1, and the flow mode of the refrigerant, and causes a pressure loss in the flow of the refrigerant.
  • the refrigerant that has passed through the second heat exchange unit 12 and the refrigerant that has passed through the first expansion device 5 merge and flow into the first heat exchange unit 11.
  • the first heat exchange unit 11 has a plurality of heat transfer tubes 20.
  • the refrigerant is distributed to a plurality of heat transfer tubes 20 by the leeward collecting pipe 13b, and the refrigerant flows into each of the heat transfer tubes 20 in parallel.
  • the refrigerant that has flowed into the plurality of heat transfer tubes 20 in parallel passes through the first leeward heat exchange section 11b, passes through the upper header 14a, and flows into the first leeward heat exchange section 11a.
  • the refrigerant that has passed through the plurality of heat transfer tubes 20 of the first windward heat exchange section 11a joins at the windward collecting pipe 13a. That is, the refrigerants branched into the plurality of refrigerant flow paths in the first heat exchange unit 11 merge at the windward collecting pipe 13a and flow out from the first heat exchanger 10.
  • the refrigerant flowing out of the first heat exchanger 10 is sucked into the compressor 2 via the four-way valve 7.
  • the circulation amount ratio of the refrigerant branched into each of the first expansion device 5 and the second heat exchange unit 12 is the pressure loss generated in the first expansion device 5 and the pressure loss generated in the second heat exchange unit 12.
  • the ratio will be equal. That is, the circulation amount ratio of the refrigerant varies depending on the flow path shapes of the first expansion device 5 and the second heat exchange unit 12, the decompression of the refrigerant, and the change in the flow aspect accompanying the heat balance.
  • the pressure loss ⁇ P is expressed by the following equation.
  • ⁇ P pressure loss [Pa]
  • ⁇ friction loss coefficient
  • L flow path length [m]
  • d flow path equivalent diameter [m]
  • G mass velocity [kg / (m 2 ⁇ s] )]
  • ⁇ Working fluid density [kg / m 3 ]
  • Re Reynolds number [-].
  • the friction loss coefficient ⁇ depends on the range of values taken by the Reynolds number Re.
  • the equivalent diameter d of the flow path is the diameter of the refrigerant flow path when the cross-sectional shape of the refrigerant flow path is circular.
  • A the cross-sectional area of the flow path [Pa]
  • l the length of the edge of the flow path [m].
  • the equivalent diameter d is the diameter of the refrigerant flow path having a circular cross-sectional shape equivalent to the non-circular cross-sectional shape of the refrigerant flow path.
  • the pressure loss increases in a narrow refrigerant flow path or a long refrigerant flow path.
  • the flow phase of the refrigerant is a gas-liquid two-phase state
  • the liquid and the gas are mixed in a complicated state, and the pressure loss increases.
  • the capacitance coefficient Cv value peculiar to the shape of the first expansion device 5 is basically set.
  • the pressure loss ⁇ P is expressed.
  • ⁇ P pressure loss [Pa]
  • ⁇ working fluid density [kg / m 3 ]
  • ⁇ water water density [kg / m 3 ] (fixed value)
  • Q volumetric flow rate [m 3 / min]
  • Cv Capacity coefficient [ ⁇ ]
  • FIG. 3 is an explanatory view showing a cross-sectional structure of the first heat exchange section 11 and the second heat exchange section 12 of the first heat exchanger 10 according to the first embodiment.
  • a part of the cross-sectional structure of the first heat exchanger 10 in the cross section passing through the points A1, A2, A3, and A4 shown in FIG. 2 is shown.
  • the cross section passing through the points A1, A2, A3, and A4 is a cross section parallel to the xz plane.
  • FIG. 3 shows a state seen from the direction of the arrow Y1 shown in FIG. That is, FIG. 3 shows a cross section perpendicular to the tube axis of the heat transfer tube 20. As shown in FIG.
  • the first heat exchanger 10 is formed by inserting a heat transfer tube 20 into each of a plurality of notches 31 included in the fins 30 extending in the longitudinal direction in the z direction. ..
  • the heat transfer tube 20 has a flat cross-sectional shape, and the long axis of the cross-sectional shape is oriented in the x direction and the short axis is oriented in the z direction. Air flows into the first heat exchanger 10 in the x direction, passes between the fins 30 and the heat transfer tube 20, and heat exchange is performed between the air and the refrigerant flowing in the heat transfer tube 20.
  • FIG. 4 is an explanatory view of the structure of the first heat exchanger 10 according to the first embodiment as viewed from the front. As shown in FIG. 4, the airflow flowing into the first heat exchanger 10 during the heating operation flows in the direction from the front to the back of the drawing.
  • the first heat exchanger 10 is configured by arranging a plurality of heat transfer tubes 20 in parallel in the z direction with the tube axes directed in the y direction.
  • the plurality of heat transfer tubes 20 are composed of, for example, flat tubes.
  • the plurality of flat tubes are formed in a flat shape having a major axis and a minor axis in a cross section perpendicular to the tube axis.
  • the long axis of the plurality of flat tubes is oriented in the x direction.
  • FIG. 5 shows a cross-sectional view of a flat tube which is an example of the heat transfer tube 20 used in the first heat exchanger 10 of the first embodiment.
  • the flat tube is made of a metal material having thermal conductivity. As a material constituting the flat tube, for example, aluminum, aluminum alloy, copper, or copper alloy is used.
  • the flat tube is manufactured by extrusion by extruding the heated material through the holes in the die to form the internal flow path 21 shown in FIG.
  • the flat tube may be manufactured by a drawing process in which a material is pulled out from a hole in a die to form a cross section shown in FIG.
  • the method for manufacturing the heat transfer tube 20 can be appropriately selected according to the cross-sectional shape of the heat transfer tube 20.
  • the heat transfer tube 20 is not limited to a flat tube, and may be, for example, a heat transfer tube having a circular or elliptical cross-sectional shape.
  • FIG. 6 is a circuit diagram of the refrigerant circuit 101 of the refrigeration cycle device 1100, which is a comparative example of the refrigeration cycle device 100 of the first embodiment.
  • FIG. 7 is a perspective view of the first heat exchanger 110 of the refrigeration cycle apparatus 1100 according to the comparative example.
  • FIG. 7 schematically shows a part of the refrigerant pipe connected to the first heat exchanger 110.
  • the refrigerating cycle device 100 according to the first embodiment and the refrigerating cycle device 1100 of the comparative example differ in the refrigerant circuit configuration on the downstream side of the second heat exchanger 3 in the refrigerant flow direction during the heating operation.
  • the refrigerant pipe is branched downstream of the second heat exchanger 3, and the first expansion apparatus 5 and the second heat exchange unit 12 are parallel to each other.
  • the refrigerants are arranged in the above, and after the refrigerants have passed through the respective units, they merge into the first heat exchange unit 11.
  • the first expansion apparatus 5 and the second heat exchange unit 112 are connected in series on the downstream side of the second heat exchanger 3, and the refrigerant is used. Will flow into the first heat exchange section 111 after passing through the first expansion device 5 and the second heat exchange section 112 in order.
  • the number of refrigerant flow paths of the first heat exchange unit 111 and the number of refrigerant flow paths of the second heat exchange unit 112 of the comparative example are the first heat exchanger according to the first embodiment. It is set in the same manner as 10.
  • FIG. 8 is a diagram showing the characteristics of the refrigeration cycle device 1100 of the comparative example during the heating operation.
  • FIG. 8 is a Ph diagram showing the transition between the pressure of the refrigerant and the enthalpy when the refrigeration cycle apparatus 1100 is heated.
  • the high-pressure gas refrigerant (P 01 ) discharged from the compressor 2 flows into the second heat exchanger 3, which is an indoor heat exchanger, after passing through the four-way valve 7.
  • the symbol represented by adding a subscript to "P" shown in parentheses is a symbol shown on the Ph diagram of FIG.
  • the refrigerant has the enthalpy and pressure of the points indicated by the symbols shown in parentheses.
  • the refrigerant flowing into the second heat exchanger 3 exchanges heat with the room air in the second heat exchanger 3 and is cooled (condensed). At this time, the temperature of the refrigerant is higher than the temperature of the indoor air.
  • the refrigerant is cooled by the room air in the second heat exchanger 3 and becomes a high-pressure liquid-phase refrigerant at the outlet of the second heat exchanger 3.
  • the high-pressure liquid refrigerant (P 11 ) that has passed through the second heat exchanger 3 is depressurized by the first expansion device 5.
  • the gas-liquid two-phase state refrigerant (P 21 ) that has passed through the first expansion device 5 flows into the second heat exchange section 112 and is depressurized by the flow path in the heat transfer tube 20.
  • the refrigerant (P 21 ) that has passed through the first expansion device 5 is in a gas-liquid two-phase state, but the pressure is reduced due to the decompression in the first expansion device 5. It may be a liquid single-phase refrigerant.
  • a refrigerant flow path is formed by one heat transfer tube 20. Therefore, the gas-liquid two-phase state refrigerant passing through the second heat exchange section 112 causes a pressure loss ⁇ P according to the above equation (1). That is, the gas-liquid two-phase state refrigerant passing through the second heat exchange unit 112 is depressurized.
  • the temperature of the refrigerant is determined according to the pressure.
  • the temperature of the refrigerant becomes the saturation temperature at a predetermined pressure. That is, the temperature of the gas-liquid two-phase refrigerant also decreases due to the reduced pressure.
  • heat exchange is performed according to the temperature of the working fluid outside the heat transfer tube 20.
  • the refrigerant temperature is higher than the out-of-tube working fluid temperature, the refrigerant is cooled (condensed) and the out-of-tube working fluid is heated.
  • the refrigerant temperature is lower than the temperature of the out-of-tube working fluid, the refrigerant is heated (evaporated) and the out-of-tube working fluid is cooled.
  • the out-of-tube working fluid is the outside air.
  • the refrigerant that has flowed into the first heat exchange unit 111 evaporates at the first heat exchange unit 111, and the low-pressure gas refrigerant (P 41 ) passes through the four-way valve 7 and is sucked into the compressor 2.
  • the refrigerant (P) flowing into the first heat exchange unit 111 31 ) The pressure may be lower than in the ideal state. That is, as shown in FIG. 8, the pressure of the refrigerant flowing into the first heat exchange section 111 of the first heat exchanger 110 that functions as an evaporator may be lower than the appropriate evaporator pressure P0. Such a state is likely to occur when the number of refrigerant flow paths in the second heat exchange unit 112 is small, the refrigerant flow paths inside the heat transfer tube 20 are thin, and the refrigerant flow paths are long.
  • the pressure difference between the suction part (P 41 ) and the discharge part (P 01 ) of the compressor 2 becomes large, and the compressor 2 There was a problem that the amount of work and power consumption increased. As a result, the refrigerating cycle apparatus 1100 becomes less efficient and impairs energy saving.
  • the temperature of the refrigerant flowing in the first heat exchanger 111 becomes lower as the pressure decreases and the first heat exchanger 110 used as the outdoor heat exchanger is operated in a low outside air temperature, it arrives. The amount of frost may increase and the heat exchange performance may deteriorate.
  • the pressure of the first heat exchanger 110 is to be operated at an appropriate value P0, it is necessary to further increase the opening degree of the first expansion device 5. Since the pressure loss ⁇ P in the second heat exchange section 112 depends on the shape of the heat transfer tube 20 of the second heat exchange section 112, the pressure loss ⁇ P in the second heat exchange section 112 alone is between points P 21 and P 31 in FIG. It is difficult to adjust to reduce the pressure difference of the refrigerant in. Therefore, to further increase the pressure of the refrigerant at the point P 31 of FIG. 8, the opening degree of the first expansion device 5 is increased, it is necessary to increase the refrigerant flowing through the first expansion device 5.
  • the opening degree of the first expansion device 5 is increased, it is necessary to reduce the pressure reduction amount between points P 11 ⁇ point P 21 of FIG.
  • the electric expansion valve, the mechanical expansion valve, the capillary tube, etc. used as the first expansion device 5 have a finite opening adjustment range, and considering the control of the refrigerating capacity of the refrigeration cycle device 1100, the first expansion device 5 is used. 1
  • FIG. 9 is a diagram showing the characteristics of the refrigeration cycle device 100 according to the first embodiment during the heating operation.
  • FIG. 10 is an enlarged view of part A in FIG.
  • FIG. 9 is a Ph diagram showing the transition between the pressure of the refrigerant and the enthalpy when the refrigeration cycle device 100 is heated.
  • the high-pressure gas refrigerant (P 01 ) discharged from the compressor 2 passes through the four-way valve 7 and flows into the second heat exchanger 3, which is an indoor heat exchanger.
  • the refrigerant exchanges heat with the indoor air and cools (condenses). At this time, the temperature of the refrigerant is higher than that of the indoor air.
  • the refrigerant is cooled by the room air in the second heat exchanger 3 and becomes a high-pressure liquid-phase refrigerant at the outlet of the second heat exchanger 3.
  • the high-pressure liquid refrigerant (P 11 ) that has passed through the second heat exchanger 3 is branched into two, distributed to the second heat exchange section 12 and the first expansion device 5, and is expanded, that is, depressurized.
  • the refrigerant flowing into the second heat exchange section 12 is depressurized by the refrigerant flow path in the heat transfer tube 20 in the same manner as the refrigerant flowing into the second heat exchange section 112 in the comparative example.
  • the temperature of the refrigerant is determined according to the pressure. That is, the temperature decreases as the pressure of the refrigerant decreases.
  • the refrigerant flowing into the first expansion device 5 is expanded (decompressed) and becomes a low-pressure gas-liquid two-phase refrigerant (P 21 ).
  • the first expansion device 5 is adiabatic expansion in which heat exchange of the refrigerant is not performed, the enthalpy value of the gas-liquid two-phase refrigerant (P 21 ) is the same as that in the state before expansion (P 11 ). is there.
  • the ratio of the refrigerant circulation amount distributed to the second heat exchange unit 12 and the first expansion device 5 is the magnitude of the flow resistance in the heat transfer tube 20 of the second heat exchange unit 12 and the first expansion. It is uniformly determined by the difference from the magnitude of the flow resistance due to the expansion throttle of the apparatus 5.
  • the pressure loss ⁇ P of the heat transfer tube 20 is calculated by the above equation (1).
  • the friction loss coefficient ⁇ , the flow path length L, and the equivalent diameter d of the flow path are determined by the shape of the heat transfer tube 20 and the number of heat transfer tubes 20 included in the second heat exchange section 12. is there.
  • the mass velocity G is determined by the amount of the refrigerant flowing into the second heat exchange section 12, and the working fluid density ⁇ varies depending on whether the refrigerant is single-phase or gas-liquid two-phase. Is what you do.
  • the pressure loss ⁇ P is determined by the equation 2. When the opening degree is small (when Cv is small), the flow rate is small and the pressure loss ⁇ P is large. Further, when the opening degree is large (when Cv is large), the flow rate is large and the pressure loss ⁇ P is small.
  • the decompression of the refrigerant in the section where the second heat exchange unit 12 and the first expansion device 5 are connected in parallel that is, the decompression of the refrigerant in the section from P 11 to P 31 is the first. 1 It can be controlled by the opening degree of the expansion device 5.
  • the refrigeration cycle device 100 according to the first embodiment is parallel to the refrigerant flow path in which the first expansion device 5 is installed even when the flow resistance in the heat transfer tube 20 of the second heat exchange unit 12 is large.
  • the bypass circuit 95 is configured in the above. Therefore, as compared with the case where the second heat exchange unit 12 or the first expansion device 5 is installed independently in series, the flow resistance of the refrigerant flow path in the portion where the refrigerant circuits 1 are in parallel is reduced. Therefore, it is not necessary to increase the opening degree of the first expansion device 5, and the opening degree of the first expansion device 5 is not insufficient.
  • a liquid refrigerant having a high pressure and a temperature higher than the temperature of the room air can flow into the second heat exchange section 12 including the lowermost stage of the first heat exchanger 10. Therefore, it is possible to prevent the drain water accumulated in the lower part of the first heat exchanger 10 from freezing.
  • the refrigeration cycle device 100 includes a refrigerant circuit 1 in which a compressor 2, a first heat exchanger 10, and a first expansion device 5 are connected by a refrigerant pipe.
  • the first heat exchanger 10 includes a first heat exchange unit 11 and a second heat exchange unit 12 connected in series with the first heat exchange unit 11 in the refrigerant circuit 1.
  • the first expansion device 5 is connected in parallel with the second heat exchange unit 12 in the refrigerant circuit 1, and the second heat exchange unit 12 is located below the first heat exchange unit 11.
  • the refrigerant flowing out from the second heat exchanger 3 is first distributed to the first expansion device 5 and the second heat exchanger 12.
  • the refrigerant flows in a saturation temperature range corresponding to the pressure difference between the upstream side and the downstream side of the first expansion device 5 of the conventional refrigerant circuit 101. That is, the second heat exchange unit 12 according to the first embodiment is used as an evaporator because the temperature of the refrigerant is higher than the inlet of the first heat exchanger 110 used as the evaporator of the refrigerant circuit 101 of the comparative example. It is possible to prevent the accumulated water at the bottom of the first heat exchanger 10 from freezing.
  • the second heat exchange unit 12 is a bypass circuit 95 with respect to the first expansion device 5.
  • the maximum opening degree of the first expansion device 5 can be reduced. Therefore, when the pressure loss ⁇ P of the refrigerant passing through the second heat exchange unit 12 is large, the opening degree of the first expansion device 5 is unlikely to be insufficient, and the range in which the pressure of the refrigerant in the evaporator can be controlled is widened.
  • the heat transfer tube 20 when a flat tube is used for the heat transfer tube 20 of the first heat exchanger 10, the refrigerant flow path is narrow and the pressure loss may increase when the refrigerant is circulated.
  • the heat transfer tube 20 has a thin refrigerant flow path.
  • the thickness of the flat tube in the minor axis direction is 1 mm or less, and further. It is desirable to use a flat tube of 0.8 mm or less.
  • the first heat exchanger 10 which functions as an evaporator
  • the first heat The pressure loss ⁇ P at the second heat exchange section 112 at the bottom of the exchanger 10 is high. Therefore, there is a problem that the pressure at the first heat exchange unit 111 becomes lower than the appropriate evaporator pressure P0 unless the opening degree of the first expansion device 5 is increased.
  • the first expansion device 5 since the second heat exchange unit 12 and the first expansion device 5 having a large pressure loss are arranged in parallel, the first expansion device 5 The pressure in the evaporator can be controlled appropriately without widening the opening range of.
  • first heat exchange section 11 and the second heat exchange section 12 of the first heat exchanger 10 are integrally formed, there is an advantage that the assembling property is improved when the first heat exchanger 10 is manufactured. is there.
  • the number of refrigerant flow paths of the first heat exchange unit 11 is larger than the number of refrigerant flow paths of the second heat exchange unit 12. Since the first heat exchanger 10 is composed of two elements, a first heat exchange unit 11 and a second heat exchange unit 12, the first heat exchange unit 11 and the second heat exchange unit 12 are connected in series. , The pressure loss ⁇ P of the first heat exchanger 10 can be increased. In particular, when used as an evaporator, the number of refrigerant path branches of the second heat exchange unit 12 on the upstream side of the refrigerant flow with respect to the first heat exchange unit 11 is made smaller than the number of refrigerant path branches of the first heat exchange unit 11.
  • the pressure loss ⁇ P in the second heat exchange unit 12 can be increased. Therefore, while suppressing the freezing of the accumulated water at the lowermost part of the first heat exchanger 10, the refrigerant flowing into the first heat exchange unit 11 without providing an additional expansion device on the downstream side of the second heat exchange unit 12 The pressure can be reduced.
  • the heat transfer tube 20 included in the first heat exchange section 11 is arranged in parallel with the heat transfer tube 20 included in the second heat exchange section 12.
  • a high-temperature refrigerant flows through the heat transfer tube 20 arranged below, where water droplets flowing down from the heat transfer tube 20 arranged above tend to stay. Therefore, it is possible to prevent the accumulated water accumulated on the upper surface of the heat transfer tube 20 from freezing.
  • the heat transfer tube 20 is a flat tube. Since the heat transfer tube 20 included in the second heat exchange section 12 located below the first heat exchanger 10 is a flat tube, the pressure of the refrigerant passing through the second heat exchanger 12 tends to decrease. Therefore, while the pressure of the refrigerant is reduced by the second heat exchange unit 12 arranged in the bypass circuit 95 that does not pass through the first expansion device 5, the high temperature refrigerant flows under the first heat exchanger 10. It is possible to suppress the freezing of the lower part of the first heat exchanger 10. Further, since the heat transfer tube 20 is a flat tube, the refrigerant capacity of the first heat exchanger 10 can be reduced while maintaining or improving the heat exchange capacity, and the amount of the refrigerant flowing through the refrigerant circuit 1 can be reduced.
  • Embodiment 2 The refrigeration cycle device 100 according to the second embodiment is obtained by further adding an expansion device to the refrigerant circuit 1 of the refrigeration cycle device 100 according to the first embodiment.
  • the changes to the first embodiment will be mainly described.
  • those having the same function in each drawing shall be labeled with the same reference numerals as those used in the description of the first embodiment.
  • FIG. 11 is a circuit diagram of the refrigerant circuit 201 of the refrigeration cycle device 200 according to the second embodiment.
  • FIG. 12 is a perspective view of the first heat exchanger 210 of the refrigeration cycle apparatus 200 according to the second embodiment.
  • the refrigerant circuit 201 of the refrigeration cycle apparatus 200 according to the second embodiment is between the second heat exchange section 12 and the first heat exchange section 11 of the first heat exchanger 10 of the refrigeration cycle apparatus 100 according to the first embodiment.
  • the second expansion device 51 is added to the above.
  • the second expansion device 51 is second than the confluence portion 91 in which the flow path in which the first expansion device 5 branched at the branch portion 90 is arranged and the flow path in which the second heat exchange unit 12 is arranged merge. It is arranged on the heat exchange unit 12 side.
  • the bypass circuit 295 in which the second heat exchange unit 12 and the second expansion device 51 are connected in series is connected in parallel with the first expansion device 5.
  • FIG. 13 is a diagram showing the characteristics of the refrigeration cycle device 200 according to the second embodiment during the heating operation.
  • FIG. 13 is a Ph diagram showing the transition between the pressure and the enthalpy around the low temperature and low pressure region of the refrigeration cycle apparatus 200.
  • the pressure loss ⁇ P in the second heat exchange unit 12 is small, and the pressure of the refrigerant immediately after leaving the second heat exchange unit 12. May be high.
  • the refrigerant exiting the second heat exchange section 12 may the temperature is higher than the outdoor air.
  • the refrigerant discharged from the second heat exchange unit 12 is further depressurized by the second expansion device 51, and the refrigerant is lowered to a pressure corresponding to the outdoor air temperature.
  • the refrigeration cycle device 200 can appropriately set or control the pressure of the first heat exchanger 210 used as an evaporator. Further, at this time, since the temperature of the refrigerant flowing out of the second heat exchange unit 12 is higher than the outdoor air temperature, the second heat is generated even in a low outdoor air temperature environment where the outdoor air temperature is near the freezing point of water. Since a high-temperature refrigerant flows through the exchange unit 12, frost formation and freezing can be suppressed.
  • FIG. 14 is a diagram showing the characteristics of the refrigeration cycle device 200 according to the second embodiment during the heating operation.
  • FIG. 14 is a Ph diagram showing the transition between the pressure and the enthalpy around the low temperature and low pressure region of the refrigeration cycle apparatus 200.
  • FIG. 14 is a diagram when the pressure loss ⁇ P in the second heat exchange unit 12 is larger than that in the case of FIG. At this time, the temperature of the refrigerant flowing out of the second heat exchange unit 12 is lower than that of the outdoor air. Therefore, since the temperature of the portion immediately before flowing out of the second heat exchange section 12 is lower than that of the outdoor air, frost is formed around the outlet of the heat transfer tube 20 of the second heat exchange section 12, and the accumulated water freezes. It is possible that it will end up.
  • the refrigeration cycle apparatus 200 is provided with the second expansion device 51, depending on the outdoor air temperature, a second temperature so as not to fall below the freezing point of water at the point P 23
  • the opening degree of the expansion device 51 can be set or controlled. As a result, it is possible to prevent frost formation and freezing only in a part around the outlet of the second heat exchange unit 12.
  • the first expansion device 5 and the second expansion device 51 are not limited to those capable of changing the opening degree, and may be those having a fixed opening degree. Further, at least one of the first expansion device 5 and the second expansion device 51 may be capable of changing the opening degree.
  • the second expansion device 51 is connected in parallel with the first expansion device 5 in the refrigerant circuit 201, and is connected in series with the second heat exchange unit 12.
  • the refrigerant pressure and the refrigerant temperature are also increased on the upstream side of the second expansion device 51, that is, the outlet side of the second heat exchange unit 12. To rise. Therefore, the refrigerant temperature can be maintained high in the entire area of the second heat exchange unit 12. Therefore, the first heat exchanger 210 is more likely to suppress the freezing of the accumulated water in the lower part of the first heat exchanger 210 than the first heat exchanger 10 according to the first embodiment.
  • the refrigerating cycle device 200 in an operating state in which the refrigerant circulation amount needs to be reduced, for example, when the refrigerating cycle device 200 operates with a low load capacity, it is necessary to close the opening degree of the first expansion device 5 for operation.
  • the flow path resistance of the second heat exchange unit 12 is small, the amount of refrigerant flowing to the second heat exchange unit 12 increases.
  • the resolution for setting the opening degree of the first expansion device 5 is insufficient, the pressure of the refrigerant flowing into the first heat exchange unit 11 cannot be set appropriately, and the refrigeration cycle device 200 sets the target low load capacity. Or it may become uncontrollable.
  • the case where the flow path resistance of the second heat exchange unit 12 is small is, for example, the case where the pressure loss ⁇ P in the heat transfer tube 20 of the second heat exchange unit 12 is small.
  • the refrigeration cycle apparatus 200 includes a bypass circuit 295 in which the second heat exchange unit 12 and the second expansion device 51 are connected in series, so that the bypass circuit on the second heat exchange unit 12 side is provided. It is possible to add a flow path resistance to 295 as well. That is, not only the first expansion device 5 but also the second expansion device 51 installed in the bypass circuit 295 can be used to control the pressure of the refrigerant flowing into the first heat exchange unit 11. Therefore, the refrigeration cycle device 200 improves the pressure control performance of the first heat exchanger 10 that functions as an evaporator when operating in a low load capacity state, as compared with the refrigeration cycle device 100 according to the first embodiment. Can be done.
  • Embodiment 3 The refrigeration cycle device 300 according to the third embodiment is obtained by further adding an expansion device to the refrigerant circuit 1 of the refrigeration cycle device 100 according to the first embodiment.
  • the changes to the first embodiment will be mainly described.
  • those having the same function in each drawing shall be labeled with the same reference numerals as those used in the description of the first embodiment.
  • FIG. 15 is a circuit diagram of the refrigerant circuit 301 of the refrigeration cycle device 300 according to the third embodiment.
  • FIG. 16 is a perspective view of the first heat exchanger 310 of the refrigeration cycle apparatus 300 according to the third embodiment.
  • the refrigerant circuit 301 of the refrigeration cycle apparatus 300 according to the third embodiment is between the second heat exchange section 12 and the first heat exchange section 11 of the first heat exchanger 10 of the refrigeration cycle apparatus 100 according to the first embodiment.
  • the second expansion device 52 is added to the above.
  • the second expansion device 52 is first than the confluence portion 91 in which the flow path in which the first expansion device 5 branched at the branch portion 90 is arranged and the flow path in which the second heat exchange unit 12 is arranged merge. It is arranged on the heat exchange unit 11 side. In other words, the second expansion device 52 is connected in series with the first expansion device 5 and the second heat exchange unit 12.
  • FIG. 17 is a diagram showing the characteristics of the refrigeration cycle device 300 according to the third embodiment during the heating operation.
  • FIG. 17 is a Ph diagram showing the transition between the pressure and the enthalpy around the low temperature and low pressure region of the refrigeration cycle apparatus 300.
  • the pressure loss ⁇ P in the second heat exchange unit 12 is small, and the pressure of the refrigerant immediately after leaving the second heat exchange unit 12. May be high. That is, as shown at point P 22 in FIG. 17, the temperature of the refrigerant exiting the second heat exchange unit 12 may be higher than that of the outdoor air.
  • the refrigeration cycle device 300 can appropriately set or control the pressure of the first heat exchanger 310 used as an evaporator.
  • the characteristics of the refrigerating cycle apparatus 300 during the heating operation shown in FIG. 17 are high in the entire second heat exchange unit 12 because the refrigerant pressure and the refrigerant temperature on the outlet side of the second heat exchange unit 12 can be kept high.
  • the refrigerant temperature can be maintained. Therefore, like the first heat exchanger 210 according to the second embodiment, there is an advantage that it is easy to suppress freezing of the accumulated water at the lowermost portion of the first heat exchanger 10.
  • FIG. 18 is a diagram showing the characteristics of the refrigeration cycle device 300 according to the third embodiment during the heating operation.
  • FIG. 18 is a Ph diagram showing the transition between the pressure and the enthalpy around the low temperature and low pressure region of the refrigeration cycle apparatus 200.
  • FIG. 18 is a diagram when the pressure loss ⁇ P in the second heat exchange unit 12 is larger than that in the case of FIG. At this time, the temperature of the refrigerant flowing out of the second heat exchange unit 12 is lower than that of the outdoor air. Therefore, since the temperature of the portion immediately before flowing out of the second heat exchange section 12 is lower than that of the outdoor air, frost is formed around the outlet of the heat transfer tube 20 of the second heat exchange section 12, and the accumulated water freezes. It is possible that it will end up.
  • the refrigeration cycle device 300 according to the third embodiment includes the second expansion device 52, the temperature at the point P 32 does not fall below the freezing point of the water according to the outdoor air temperature.
  • the opening degree of the expansion device 52 can be set or controlled. As a result, it is possible to prevent frost formation and freezing only in a part around the outlet of the second heat exchange unit 12.
  • the first expansion device 5 and the second expansion device 52 are not limited to those capable of changing the opening degree, and may be those having a fixed opening degree. Further, at least one of the first expansion device 5 and the second expansion device 52 may be capable of changing the opening degree.
  • Embodiment 4 The refrigeration cycle device 400 according to the fourth embodiment is a modification of the structure of the first heat exchanger 10 of the refrigeration cycle device 100 according to the first embodiment.
  • the changes to the first embodiment will be mainly described.
  • those having the same function in each drawing shall be labeled with the same reference numerals as those used in the description of the first embodiment.
  • FIG. 19 is a circuit diagram of the refrigerant circuit 401 of the refrigeration cycle device 400 according to the fourth embodiment.
  • FIG. 20 is a perspective view of the first heat exchanger 410 of the refrigeration cycle apparatus 400 according to the fourth embodiment.
  • the refrigerant circuit 401 of the refrigerating cycle apparatus 400 according to the fourth embodiment is a division of the first heat exchange section 11 of the first heat exchanger 10 of the refrigerating cycle apparatus 100 according to the first embodiment.
  • a plurality of heat transfer tubes 20 are all arranged in parallel, and the refrigerant is flowing into all the plurality of heat transfer tubes 20 at the same time.
  • the first heat exchange unit 11 has a plurality of heat transfer tubes 20 located in the lower portion 16 of the first heat exchange unit 11 and a plurality of heat transfer tubes located in the upper portion 15 of the first heat exchange unit 11. 20 is connected in series.
  • FIG. 21 is a diagram showing the characteristics of the refrigeration cycle device 400 according to the fourth embodiment during the heating operation.
  • FIG. 21 is a Ph diagram showing the transition between the enthalpy and the pressure around the low temperature and low pressure region of the refrigeration cycle apparatus 400.
  • the pressure loss ⁇ P in the second heat exchange unit 12 is small, and the pressure of the refrigerant immediately after leaving the second heat exchange unit 12. May be high. That is, as shown at point P 22 in FIG. 21, the temperature of the refrigerant exiting the second heat exchange unit 12 may be higher than that of the outdoor air.
  • the refrigeration cycle device 400 can appropriately set or control the pressure of the first heat exchanger 410 used as an evaporator.
  • the present invention has been described above based on the embodiment, the present invention is not limited to the configuration of the above-described embodiment.
  • the first heat exchangers 10, 210, and 310 according to the first to third embodiments have been described with a structure in which they are divided into two parts, a first heat exchange unit 11 and a second heat exchange unit 12, but each of them has been described.
  • the heat exchange unit may be appropriately divided.
  • the first heat exchange unit 11 and the second heat exchange unit 12 may be divided into the same number, and the divided parts may be connected in series.
  • the present invention may be configured by combining each embodiment. In short, I would like to add that the gist (technical scope) of the present invention also includes various changes, applications, and uses made by those skilled in the art as necessary.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
PCT/JP2019/013654 2019-03-28 2019-03-28 冷凍サイクル装置 WO2020194677A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP19921695.3A EP3951287A4 (de) 2019-03-28 2019-03-28 Kältekreislaufvorrichtung
CN201980094530.8A CN113646597B (zh) 2019-03-28 2019-03-28 冷冻循环装置
US17/434,298 US20220136740A1 (en) 2019-03-28 2019-03-28 Refrigeration cycle apparatus
PCT/JP2019/013654 WO2020194677A1 (ja) 2019-03-28 2019-03-28 冷凍サイクル装置
JP2021508609A JP7123238B2 (ja) 2019-03-28 2019-03-28 冷凍サイクル装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2019/013654 WO2020194677A1 (ja) 2019-03-28 2019-03-28 冷凍サイクル装置

Publications (1)

Publication Number Publication Date
WO2020194677A1 true WO2020194677A1 (ja) 2020-10-01

Family

ID=72611228

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2019/013654 WO2020194677A1 (ja) 2019-03-28 2019-03-28 冷凍サイクル装置

Country Status (5)

Country Link
US (1) US20220136740A1 (de)
EP (1) EP3951287A4 (de)
JP (1) JP7123238B2 (de)
CN (1) CN113646597B (de)
WO (1) WO2020194677A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4166868A1 (de) * 2021-10-15 2023-04-19 Carrier Corporation Verdampferwärmetauscher zur verhinderung von eisbildung

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0544653U (ja) 1991-11-27 1993-06-15 株式会社クボタ オイルクーラ取付構造
JPH09229496A (ja) * 1996-02-23 1997-09-05 Hitachi Ltd 空気調和機
JP2002372320A (ja) * 2001-06-15 2002-12-26 Matsushita Electric Ind Co Ltd 冷凍装置
JP2010133590A (ja) * 2008-12-03 2010-06-17 Mitsubishi Electric Corp 冷凍冷蔵庫
WO2013051177A1 (ja) * 2011-10-03 2013-04-11 三菱電機株式会社 室外機、その室外機を備えた空気調和機及び給湯機
JP2016200292A (ja) * 2015-04-07 2016-12-01 ダイキン工業株式会社 熱交換器
WO2018002983A1 (ja) * 2016-06-27 2018-01-04 三菱電機株式会社 冷凍サイクル装置

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000146311A (ja) * 1990-10-04 2000-05-26 Denso Corp 冷凍装置、及び熱交換器
JPH08145535A (ja) * 1994-11-22 1996-06-07 Sanyo Electric Co Ltd 冷却装置
JP4122349B2 (ja) * 2004-06-24 2008-07-23 三星電子株式会社 冷凍サイクル装置及びその運転方法
CN2935020Y (zh) * 2006-07-24 2007-08-15 比亚迪股份有限公司 一种空调系统
JP5985418B2 (ja) * 2013-03-04 2016-09-06 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド 冷凍サイクル装置、ならびに冷凍サイクル装置を備えた冷凍装置および空気調和装置
WO2015129080A1 (ja) * 2014-02-27 2015-09-03 三菱電機株式会社 熱源側ユニット及び冷凍サイクル装置
GB2548309B (en) * 2015-03-16 2020-06-17 Mitsubishi Electric Corp Air-conditioning and hot fluid supply composite system
JP6463470B2 (ja) * 2015-05-19 2019-02-06 三菱電機株式会社 冷凍装置
JP6238935B2 (ja) * 2015-07-08 2017-11-29 三菱電機株式会社 冷凍サイクル装置
WO2018029817A1 (ja) * 2016-08-10 2018-02-15 三菱電機株式会社 冷凍サイクル装置
EP3511651B1 (de) * 2016-09-12 2020-12-02 Mitsubishi Electric Corporation Klimatisierungsvorrichtung
WO2018047330A1 (ja) * 2016-09-12 2018-03-15 三菱電機株式会社 空気調和装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0544653U (ja) 1991-11-27 1993-06-15 株式会社クボタ オイルクーラ取付構造
JPH09229496A (ja) * 1996-02-23 1997-09-05 Hitachi Ltd 空気調和機
JP2002372320A (ja) * 2001-06-15 2002-12-26 Matsushita Electric Ind Co Ltd 冷凍装置
JP2010133590A (ja) * 2008-12-03 2010-06-17 Mitsubishi Electric Corp 冷凍冷蔵庫
WO2013051177A1 (ja) * 2011-10-03 2013-04-11 三菱電機株式会社 室外機、その室外機を備えた空気調和機及び給湯機
JP2016200292A (ja) * 2015-04-07 2016-12-01 ダイキン工業株式会社 熱交換器
WO2018002983A1 (ja) * 2016-06-27 2018-01-04 三菱電機株式会社 冷凍サイクル装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3951287A4

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4166868A1 (de) * 2021-10-15 2023-04-19 Carrier Corporation Verdampferwärmetauscher zur verhinderung von eisbildung

Also Published As

Publication number Publication date
EP3951287A1 (de) 2022-02-09
US20220136740A1 (en) 2022-05-05
CN113646597A (zh) 2021-11-12
JP7123238B2 (ja) 2022-08-22
CN113646597B (zh) 2022-12-09
EP3951287A4 (de) 2022-03-30
JPWO2020194677A1 (ja) 2021-10-14

Similar Documents

Publication Publication Date Title
CN112204312B (zh) 空气调节装置的室外机及空气调节装置
EP3232139B1 (de) Wärmetauscher einer klimatisierungsvorrichtung
JP6685409B2 (ja) 空気調和装置
EP3264010B1 (de) Wärmetauschervorrichtung und klimaanlage damit
JP4922669B2 (ja) 空気調和機及び空気調和機の熱交換器
JP6768073B2 (ja) 空気調和装置
EP2759785A1 (de) Kühlvorrichtung
JP2007163013A (ja) 冷凍サイクル装置
CN116134282B (zh) 热交换器
JPWO2017199393A1 (ja) 室外ユニットおよびそれを備えた冷凍サイクル装置
EP3825628B1 (de) Kältekreislaufvorrichtung
JP5627635B2 (ja) 空気調和機
JP6692495B2 (ja) 熱交換器及び冷凍サイクル装置
WO2020194677A1 (ja) 冷凍サイクル装置
JP6987227B2 (ja) 熱交換器及び冷凍サイクル装置
JP4983878B2 (ja) 熱交換器及びこの熱交換器を備えた冷蔵庫、空気調和機
WO2020148826A1 (ja) 空気調和機
JPWO2019003385A1 (ja) 室外ユニットおよび冷凍サイクル装置
JP7080395B2 (ja) 熱交換器ユニット及び冷凍サイクル装置
JP2010266110A (ja) 空気調和機
JP2024034631A (ja) 空気調和装置
CN117642595A (zh) 热交换器以及制冷循环装置
CN117355721A (zh) 热交换器、具备热交换器的空调装置的室外机、以及具备空调装置的室外机的空调装置
CN114812010A (zh) 空调机及热交换器
JP2015078799A (ja) 空気調和装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19921695

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2021508609

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2019921695

Country of ref document: EP

Effective date: 20211028