US20240219067A1 - Heat exchanger, air-conditioning apparatus outdoor unit including heat exchanger, and air-conditioning apparatus including air-conditioning apparatus outdoor unit - Google Patents

Heat exchanger, air-conditioning apparatus outdoor unit including heat exchanger, and air-conditioning apparatus including air-conditioning apparatus outdoor unit Download PDF

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Publication number
US20240219067A1
US20240219067A1 US18/557,331 US202118557331A US2024219067A1 US 20240219067 A1 US20240219067 A1 US 20240219067A1 US 202118557331 A US202118557331 A US 202118557331A US 2024219067 A1 US2024219067 A1 US 2024219067A1
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United States
Prior art keywords
heat exchanger
refrigerant
header
air
flow
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Pending
Application number
US18/557,331
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English (en)
Inventor
Yoji ONAKA
Tetsuji Saikusa
Rihito ADACHI
Nanami KISHIDA
Taisaku GOMYO
Yuki NAKAO
Shingo KASAKI
Atsushi KIBE
Hiroyuki Morimoto
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Filing date
Publication date
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ONAKA, Yoji, ADACHI, Rihito, KASAKI, Shingo, NAKAO, Yuki, GOMYO, Taisaku, KIBE, Atsushi, KISHIDA, Nanami, MORIMOTO, HIROYUKI, SAIKUSA, TETSUJI
Publication of US20240219067A1 publication Critical patent/US20240219067A1/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/22—Means for preventing condensation or evacuating condensate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • 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
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • 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
    • F25B2313/029—Control issues
    • F25B2313/0293—Control issues related to the indoor fan, e.g. controlling speed
    • 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
    • F25B2313/029—Control issues
    • F25B2313/0294—Control issues related to the outdoor fan, e.g. controlling speed
    • 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
    • F25B2500/19—Calculation of parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • a heat exchanger including a plurality of flat tubes that extend in a vertical direction and that are arrayed at spacings in a horizontal direction, a plurality of fins that are each connected across a space between adjacent ones of the flat tubes and that transfer heat to the flat tubes, and headers provided at upper and lower ends of the plurality of flat tubes (see, for example, Patent Literature 1).
  • FIG. 2 is a perspective view of the heat exchanger according to Embodiment 1.
  • FIG. 4 is a diagram showing the flow passage cross-sectional area of a flat tube of the heat exchanger according to Embodiment 1.
  • FIG. 5 is a diagram showing a relationship between the total flow passage cross-sectional area of a heat exchanger core of a heat exchanger and ⁇ P HEX / ⁇ P HEAD according to experimental results.
  • FIG. 6 is a diagram showing a relationship between the height H of a heat exchanger core of a heat exchanger and ⁇ P HEX / ⁇ P HEAD according to the experimental results.
  • FIG. 7 is a diagram explaining deterioration of defrosting performance due to liquid retention in a heat exchanger.
  • FIG. 11 is a diagram showing a pressure distribution in the heat exchanger according to Embodiment 1.
  • FIG. 12 is a diagram showing a pressure distribution in a modification of the heat exchanger according to Embodiment 1.
  • FIG. 13 is a schematic view of a header flow passage of the heat exchanger according to Embodiment 1 and an area around the header flow passage.
  • FIG. 15 is a diagram explaining the heat exchanger performance of a modification of the heat exchanger according to Embodiment 2.
  • FIG. 19 is a side schematic view of the heat exchanger according to Embodiment 3.
  • FIG. 23 is a cross-sectional schematic view of a flat tube of a modification of the heat exchanger according to Embodiment 6.
  • FIG. 25 is a diagram showing a relationship between types of refrigerant that are used in a refrigerant circuit of an air-conditioning apparatus according to Embodiment 7 and ⁇ P HEX / ⁇ P HEAD .
  • FIG. 26 is a front view of a heat exchanger according to Embodiment 8 of an air-conditioning apparatus.
  • FIG. 27 is a front view of a heat exchanger according to Embodiment 9 of an air-conditioning apparatus.
  • the heat exchanger 30 exchanges heat between outdoor air and refrigerant.
  • the heat exchanger 30 functions as a condenser configured to condense the refrigerant by rejecting the heat of the refrigerant to the outdoor air.
  • the heat exchanger 30 functions as an evaporator configured to evaporate the refrigerant and cool the outdoor air with the resulting heat of vaporization.
  • the first header 34 and the second header 35 can be configured to be small in length with respect to the amount of heat exchange. This makes it possible to reduce pressure losses of working fluids that flow through the first header 34 and the second header 35 . That is, the difference between the pressure loss ⁇ P 1-2 of the first header 34 and the pressure loss ⁇ P 3-4 of the second header 35 described in FIGS. 11 and 12 can be decreased, and ⁇ P 2-3 can be decreased accordingly. This makes it possible to suppress the occurrence of liquid retention.
  • the first and second headers 34 and 35 and the flat tubes 38 are usually joined to each other by brazing; therefore, as shown in FIG.
  • an outdoor unit 10 according to Embodiment 1 of an air-conditioning apparatus 100 includes the heat exchanger 30 .
  • ⁇ is the gap between an upper end of a flat tube 38 inserted in the bridging header 50 and a wall portion 51 of the bridging header 50 that faces the upper end of the flat tube 38
  • the upper end of the flat tube 38 is inserted in the bridging header 50 so that ⁇ 3 [mm], preferably ⁇ 1 [mm].
  • FIG. 19 is a side schematic view of the heat exchanger 30 according to Embodiment 3.
  • the black arrow indicates the flow of air that passes through the heat exchanger 30
  • the white arrows indicate the flow of refrigerant.
  • the heat exchanger 30 according to Embodiment 3 is configured such that two heat exchanger cores 31 are arranged side by side in the direction of flow of air
  • the heat exchanger 30 according to Embodiment 3 is not limited to this configuration but may be configured such that three or more heat exchanger cores 31 are arranged side by side in the direction of flow of air.
  • the heat exchanger 30 is configured to include bridging headers 50 whose number is smaller by 1 than the number of heat exchanger cores 31 .
  • the heat exchanger 30 is a heat exchanger 30 including the two or more heat exchanger cores 31 placed along the direction of flow of air, a first header 34 provided at a lower end of one of the heat exchanger cores 31 that is located on a furthest leeward side, a second header 35 provided at an upper or lower end of one of the heat exchanger cores 31 that is located at a furthest windward side, a hot-gas refrigerant inlet 32 formed at one end of the first header 34 , and a liquid refrigerant outlet 33 formed at one end of the second header 35 located on the same side as the one end of the first header 34 .
  • Embodiment 4 A description of overlaps with Embodiments 1 to 3 is omitted. Components that are identical or equivalent to those of Embodiments 1 to 3 are given identical reference signs.
  • FIG. 20 is an enlarged refrigerant circuit diagram of an outdoor unit 10 according to Embodiment 4 of an air-conditioning apparatus 100 with the outdoor unit 10 including heat exchangers 30 .
  • the white arrows indicate the flow of refrigerant during a defrosting operation.
  • An outlet side of the heat exchanger 30 a and an outlet side of the heat exchanger 30 b are configured to merge at a first merging section 63 a . Further, an outlet side of the first merging section 63 a and an outlet side of the heat exchanger 30 c are configured to merge at a second merging section 63 b . Further, a first expansion device 62 a is provided in one of the refrigerant pipes that is located between the first merging section 63 a and the second merging section 63 b . Further, a second expansion device 62 b is provided in one of the refrigerant pipes that is located between an outlet of the heat exchanger 30 c and the second merging section 63 b .
  • a first open-close valve 61 a is provided in one of the refrigerant pipes that is located between a branch point on inlet sides of the heat exchangers 30 a to 30 c and an inlet of the heat exchanger 30 c .
  • a second open-close valve 61 b is provided in one of the refrigerant pipes that connects the inlet of the heat exchanger 30 c with one of the refrigerant pipes that is located between the first merging section 63 a and the first expansion device 62 a .
  • the first open-close valve 61 a and the second open-close valve 61 b are not valves that simply open and shut but may be valves whose opening degrees can be adjusted.
  • the air-conditioning apparatus 100 includes a controller 70 configured to control the expansion devices, the open-close valves, or other devices.
  • the controller 70 is constituted by dedicated hardware or a central processing unit (CPU; also referred to as “processing unit”, “arithmetic device”, “microprocessor”, or “processor”) configured to execute programs that are stored in a storage unit (not illustrated). It should be noted that the controller 70 may be provided in the outdoor unit 10 or may be provided in the indoor unit 20 .
  • controller 70 may be implemented by the dedicated hardware, and others of the functions of the controller 70 may be implemented by the software or the firmware.
  • the flow passage differential pressure ⁇ P HEX is made greater than or equal to the liquid head ⁇ P HEAD by configuring the heat exchangers 30 a to 30 c so that during a defrosting operation, a flow of refrigerant through one or more of the heat exchangers 30 a to 30 c is in series with a flow of refrigerant through the other of the heat exchangers 30 a to 30 c and a flow of refrigerant through rest of the heat exchangers 30 a to 30 c is in parallel with the flow of refrigerant through the other of the heat exchangers 30 a to 30 c .
  • the heat exchangers 30 a to 30 c By thus configuring the heat exchangers 30 a to 30 c so that during a defrosting operation, a flow of refrigerant through one or more of the heat exchangers 30 a to 30 c is in series with a flow of refrigerant through the other of the heat exchangers 30 a to 30 c and a flow of refrigerant through rest of the heat exchangers 30 a to 30 c is in parallel with the flow of refrigerant through the other of the heat exchangers 30 a to 30 c , the flow passage cross-sectional area is reduced with the flow rate of refrigerant being the same.
  • the air-conditioning apparatus 100 includes an outdoor unit 10 including a plurality of heat exchangers 30 a to 30 c and a controller 70 configured so that during a defrosting operation, one of more of the plurality of heat exchangers 30 a to 30 c are in series with the other of the heat exchangers 30 a to 30 c and configured so that when the heat exchangers 30 a to 30 c function as evaporators, a flow of the refrigerant through each of the heat exchangers 30 a to 30 c is in parallel with a flow of the refrigerant through the other of the heat exchangers 30 a to 30 c.
  • the velocity of flow of refrigerant through a flow passage through which hot-gas refrigerant flows upward increases, and the flow passage differential pressure ⁇ P HEX can be increased.
  • the heat exchangers 30 a to 30 c so that when the heat exchangers 30 a to 30 c function as evaporators, a flow of refrigerant through each of the heat exchangers 30 a to 30 c is in parallel with a flow of refrigerant through the other of the heat exchangers 30 a to 30 c , the flow passage cross-sectional area is increased with the flow rate of refrigerant being the same. This reduces a pressure loss, thus making it possible to improve heating capacity.
  • the outdoor unit 10 according to Embodiment 5 of an air-conditioning apparatus 100 includes a plurality of heat exchangers 30 a to 30 c .
  • each of the heat exchangers 30 a to 30 c is any of the heat exchangers 30 described in Embodiments 1 to 3.
  • the number of heat exchangers 30 a to 30 c that the outdoor unit 10 of an air-conditioning apparatus 100 includes is not limited to 3 but may be at least 2.
  • the controller 70 is configured so that during a defrosting operation, a flow of the refrigerant through one or more of the plurality of heat exchangers 30 a to 30 c is in series with a flow of the refrigerant through the other of the heat exchangers 30 a to 30 c and configured so that a flow of the refrigerant through rest of the heat exchangers 30 a to 30 c is in parallel with the flow of the refrigerant through the other of the heat exchangers 30 a to 30 c , and in a case in which there are a plurality of the heat exchangers 30 a to 30 c configured so that during a defrosting operation, flows of the refrigerant through the heat exchangers 30 a to 30 c are in parallel with one another, the refrigerant is stopped from flowing through at least one of the heat exchangers 30 a to 30 c and the other of the heat exchangers 30 a to 30 c
  • the flat tube 38 of the heat exchanger 30 is provided with a plurality of partition posts 38 a inside. These partition posts 38 a are placed along a direction parallel with the length of a cross-section of the flat tube 38 , extend along a direction parallel with the length of the flat tube 38 , and divide the inside of the flat tube 38 into a plurality of spaces. Furthermore, the flat tube 38 is a grooved flat tube provided with a plurality of inward projecting portions 38 b each provided between adjacent ones of the partition posts 38 a . These projecting portions 38 b extend along a direction parallel with the length of the flat tube 38 . Further, as shown in FIGS. 23 and 24 , the flat tube 38 of the heat exchanger 30 is an end-shrunk flat tube having a distal portion 38 c subjected to tube shrinking so that the outer diameter of the flat tube 38 decreases toward a distal end.
  • the flat tube 38 of the heat exchanger 30 is made a grooved flat tube or an end-shrunk flat tube.
  • the flow passage cross-sectional area is reduced with the flow rate of refrigerant being the same. Therefore, the velocity of flow of refrigerant through a flow passage through which hot-gas refrigerant flows upward increases, and the flow passage differential pressure ⁇ P HEX can be increased. This suppresses liquid retention, making it possible to improve defrosting performance during a defrosting operation.
  • each of the flat tubes 38 is provided with a plurality of partition posts 38 a configured to partition an internal flow passage and an inward projecting portion 38 b provided between adjacent ones of the partition posts 38 a , or each of the flat tubes 38 has a distal portion 38 c subjected to tube shrinking so that an outer diameter of the flat tube 38 decreases toward a distal end.
  • each of the flat tubes 38 has a plurality of projecting portions 38 b each formed along a flow passage between adjacent ones of the partition posts 38 a , or each of the flat tubes 38 has a distal portion 38 c subjected to tube shrinking so that an outer diameter of the flat tube 38 decreases toward a distal end.
  • Embodiment 7 A description of overlaps with Embodiments 1 to 6 is omitted. Components that are identical or equivalent to those of Embodiments 1 to 6 are given identical reference signs.
  • FIG. 25 is a diagram showing a relationship between types of refrigerant that are used in a refrigerant circuit 101 of an air-conditioning apparatus 100 according to Embodiment 7 and ⁇ P HEX / ⁇ P HEAD .
  • Embodiment 7 uses any of the pure refrigerants HFO1123, HFO1132(E), R1234yf, R1234ze(E), R1234ze(Z), R1233zd(E), propane (R290), and fluoroethane (R161) as refrigerant that circulates through the refrigerant circuit 101 of the air-conditioning apparatus 100 .
  • the air-conditioning apparatus 100 uses any of the foregoing pure refrigerants as refrigerant that circulates through the refrigerant circuit 101 , thus making it possible to improve ⁇ P HEX / ⁇ P HEAD . This suppresses the occurrence of liquid retention, making it possible to improve heat exchanger performance.
  • FIG. 26 is a front view of a heat exchanger 30 according to Embodiment 8 of an air-conditioning apparatus 100 .
  • the white arrows indicate the flow of refrigerant during a cooling operation.
  • FIG. 26 shows the height H and width L of a heat exchanger core 31 and shows the widths of different regions of the heat exchanger core 31 in the order of L 1 , L 2 , . . . from a downstream side.
  • the fins 39 are each connected across a space between adjacent ones of the flat tubes 38 and transfer heat to the flat tubes 38 .
  • the fins 39 are intended to improve the efficiency of heat exchange between air and refrigerant.
  • Usable examples of the fins 39 include, but are not limited to, corrugated fins.
  • the fins 39 are dispensable because heat exchange between air and refrigerant takes place on the surfaces of the flat tubes 38 .
  • a first header 34 is provided at a lower end of the heat exchanger core 31 . Lower ends of the flat tubes 38 of the heat exchanger core 31 are directly inserted in the first header 34 . Further, a second header 35 is provided at an upper end of the heat exchanger core 31 . Upper ends of the flat tubes 38 of the heat exchanger core 31 are directly inserted in the second header 35 .
  • hot-gas refrigerant having flowed into the second header 35 flows as downward flows through ones of the flat tubes 38 of the heat exchanger core 31 that are placed in the region T 1 , merges in the merging region M 1 of the first header 34 , flows as upward flows through ones of the flat tubes 38 of the heat exchanger core 31 that are placed in the region T 2 , and then flows out from the second header 35 .
  • the region T 1 is a downward flow region
  • the region T 2 is an upward flow region.
  • the merging region M 1 of the first header 34 serves as a hot-gas refrigerant inflow port for the upward flow region.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US18/557,331 2021-05-28 2021-05-28 Heat exchanger, air-conditioning apparatus outdoor unit including heat exchanger, and air-conditioning apparatus including air-conditioning apparatus outdoor unit Pending US20240219067A1 (en)

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PCT/JP2021/020313 WO2022249425A1 (ja) 2021-05-28 2021-05-28 熱交換器、熱交換器を備えた空気調和装置の室外機、および、空気調和装置の室外機を備えた空気調和装置

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