WO2018138972A1 - 熱交換器、及び、空気調和機 - Google Patents

熱交換器、及び、空気調和機 Download PDF

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Publication number
WO2018138972A1
WO2018138972A1 PCT/JP2017/036040 JP2017036040W WO2018138972A1 WO 2018138972 A1 WO2018138972 A1 WO 2018138972A1 JP 2017036040 W JP2017036040 W JP 2017036040W WO 2018138972 A1 WO2018138972 A1 WO 2018138972A1
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WO
WIPO (PCT)
Prior art keywords
header
heat exchanger
heat transfer
partition plate
working fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2017/036040
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English (en)
French (fr)
Japanese (ja)
Inventor
高藤　亮一
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Johnson Controls Air Conditioning Inc
Original Assignee
Hitachi Johnson Controls Air Conditioning Inc
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 Hitachi Johnson Controls Air Conditioning Inc filed Critical Hitachi Johnson Controls Air Conditioning Inc
Priority to CN201780082168.3A priority Critical patent/CN110168301B/zh
Publication of WO2018138972A1 publication Critical patent/WO2018138972A1/ja
Priority to US16/513,766 priority patent/US11236954B2/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0207—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions the longitudinal or transversal partitions being separate elements attached to header boxes
    • 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
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • 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
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05333—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05341—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
    • 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
    • F28F1/24—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 and extending transversely
    • F28F1/32—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 and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of 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
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means

Definitions

  • the present invention relates to a heat exchanger and an air conditioner.
  • heat exchangers called indoor heat exchangers and outdoor heat exchangers are mounted on air conditioner indoor units and outdoor units.
  • the heat exchanger for example, a plurality of heat transfer tubes, fins joined to the plurality of heat transfer tubes, and one or more connected to one or both of one end side and the other end side of the plurality of heat transfer tubes are known (see, for example, Patent Document 1).
  • This type of heat exchanger distributes and flows the working fluid (refrigerant) that flows into the header from an external device to each heat transfer tube, or conversely, the working fluid that flows into the header from each heat transfer tube ( Refrigerant) from the header to external equipment.
  • the heat exchanger exchanges heat between the working fluid (refrigerant) flowing inside the heat transfer tube and the air flowing outside the heat transfer tube.
  • Patent Document 1 has been desired to improve the distribution performance of the working fluid (refrigerant) from the header to each heat transfer tube, as described below.
  • a pipe that functions as an inflow pipe for a gas-liquid two-phase working fluid (refrigerant) during an evaporation operation is disposed on the lower side of the header.
  • the working fluid (refrigerant) flowing into the lower part of the header via the inflow pipe flows to the upper part of the header, and the working fluid ( Distribute refrigerant.
  • a drift of the working fluid (refrigerant) may occur inside the header.
  • the drift of the working fluid occurs, for example, when the flow of liquid is biased due to the difference in velocity between the liquid and gas contained in the gas-liquid two-phase working fluid (refrigerant).
  • the drift of the working fluid is unlikely to occur when the liquid and the gas are mixed, but tends to occur when the liquid and the gas are separated.
  • the working fluid tends to drift in the lower part of the header to which the inflow pipe is connected. Further, in the conventional heat exchanger, when a drift of the working fluid (refrigerant) occurs inside the header, the distribution of the working fluid (refrigerant) from the header to each heat transfer tube becomes uneven. As a result, a specific heat transfer tube (for example, a heat transfer tube connected to the upper side of the header) may be overheated, resulting in a decrease in heat exchange performance.
  • the conventional heat exchanger can distribute the working fluid (refrigerant) from the header to each heat transfer tube so that the distribution of the working fluid (refrigerant) from the header to each heat transfer tube can be brought closer to a uniform state. It was desired to improve.
  • the present invention has been made to solve the above-described problems, and is a heat exchanger that improves the distribution performance of the working fluid (refrigerant) from the header to each heat transfer tube, and an air conditioner having the heat exchanger.
  • the main purpose is to provide a machine.
  • the present invention provides a plurality of fins, an elliptical shape or a flat shape, and a plurality of heat transfer tubes joined to the fins, and an inflow for flowing a working fluid at one end side during an evaporation operation.
  • a header that communicates with the end of the tube and that communicates with the end of the heat transfer tube on the other end, and the header is disposed so as to extend in the longitudinal direction inside.
  • a vertical partition plate that partitions the internal space of the header into an inflow tube side space communicating with an end portion of the inflow tube and a heat transfer tube side space communicating with an end portion of the heat transfer tube,
  • the plate is a heat exchanger having a configuration in which an opening is formed at a position that does not overlap the inflow pipe, and an air conditioner having the heat exchanger. Other means will be described later.
  • the distribution performance of the working fluid (refrigerant) from the header to each heat transfer tube can be improved.
  • FIG. 1 It is a figure which shows the whole structure of the air conditioner which concerns on Embodiment 1.
  • FIG. It is a figure which shows the structure of the outdoor heat exchanger which concerns on Embodiment 1.
  • FIG. It is a figure which shows the internal structure of the header of the outdoor heat exchanger which concerns on Embodiment 1.
  • FIG. It is a figure (1) which shows the flow of the working fluid (refrigerant) inside the header of Embodiment 1.
  • FIG. 3 is a diagram (2) illustrating a flow of a working fluid (refrigerant) inside the header of the first embodiment.
  • FIG. It is a figure which shows the structure of the outdoor heat exchanger which concerns on Embodiment 3.
  • FIG. 1 It is a figure which shows the internal structure of the header of the outdoor heat exchanger which concerns on Embodiment 3.
  • FIG. 2 It is a figure (2) which shows the modification of the header of the outdoor heat exchanger concerning Embodiment 3.
  • FIG. It is a figure which shows the structure of the indoor heat exchanger which concerns on Embodiment 4.
  • FIG. It is a figure which shows the internal structure of the header of the indoor heat exchanger which concerns on Embodiment 4.
  • FIG. It is a figure which shows the modification of the header of the indoor heat exchanger which concerns on Embodiment 4.
  • FIG. 1 shows the modification of the header of the indoor heat exchanger which concerns on Embodiment 4.
  • the present embodiment an embodiment of the present invention (hereinafter referred to as “the present embodiment”) will be described in detail with reference to the drawings.
  • Each figure is only schematically shown so that the present invention can be fully understood. Therefore, the present invention is not limited to the illustrated example.
  • symbol is attached
  • the present invention abruptly deflects the flow of the gas-liquid two-phase working fluid (refrigerant) that has flowed into the header, thereby speeding the liquid and gas contained in the gas-liquid two-phase working fluid (refrigerant). Minimize the effect of the difference and reduce the uneven flow of liquid. Further, the present invention efficiently mixes the liquid and gas of the working fluid (refrigerant) while gradually dropping the gas-liquid two-phase working fluid (refrigerant) by gravity inside the header.
  • the technical idea of the present invention is to suppress the occurrence of drift of working fluid (refrigerant) inside the header based on these principles.
  • FIG. 1 is a diagram illustrating a configuration of an air conditioner 1 according to the first embodiment.
  • an air conditioner 1 includes an indoor unit 2 arranged indoors and an outdoor unit 3 arranged outdoors (outdoors).
  • the indoor unit 2 has a built-in indoor heat exchanger 5 that exchanges heat between the working fluid (refrigerant) and room air.
  • the outdoor unit 3 includes an outdoor heat exchanger 6 that performs heat exchange between the working fluid (refrigerant) and outdoor air.
  • the indoor unit 2 sucks indoor air into the interior, and performs heat exchange between the working fluid (refrigerant) and the indoor air in the indoor heat exchanger 5, so that any processing of heating, cooling, and dehumidification can be performed. Obtained conditioned air and blow out the obtained conditioned air into the room. Thereby, the indoor unit 2 air-conditions the room.
  • the indoor unit 2 is connected to the outdoor unit 3 via the connection pipe 4 and circulates a working fluid (refrigerant) between the indoor unit 2 and the outdoor unit 3.
  • the outdoor unit 3 performs heat exchange between the working fluid (refrigerant) and the outdoor air in the outdoor heat exchanger 6.
  • the indoor heat exchanger 5 functions as a condenser to perform a condensation operation
  • the outdoor heat exchanger 6 functions as an evaporator to perform an evaporation operation.
  • the working fluid (refrigerant) is condensed in the indoor heat exchanger 5 to become liquid, and then expanded by an expansion valve (not shown), so that the low-temperature and low-pressure gas-liquid two-phase working fluid (refrigerant). It becomes.
  • the gas-liquid two-phase working fluid (refrigerant) flows into the outdoor heat exchanger 6 and is vaporized by the outdoor heat exchanger 6 to be in a gaseous state.
  • the outdoor heat exchanger 6 functions as a condenser and performs a condensing operation
  • the indoor heat exchanger 5 functions as an evaporator and performs an evaporating operation.
  • the working fluid (refrigerant) is condensed in the outdoor heat exchanger 6 to become liquid, and then expanded by an expansion valve (not shown), so that the low-temperature and low-pressure gas-liquid two-phase working fluid (refrigerant). It becomes.
  • This gas-liquid two-phase working fluid (refrigerant) flows into the indoor heat exchanger 5 and is vaporized by the indoor heat exchanger 5 to become a gaseous state.
  • the present invention can be applied to both the indoor heat exchanger 5 and the outdoor heat exchanger 6.
  • this Embodiment 1 has the characteristics in the structure of the header 16 mentioned later of the outdoor heat exchanger 6, the structure (especially structure of the header 16) of the outdoor heat exchanger 6 is demonstrated mainly.
  • FIG. 2 is a diagram illustrating a configuration of the outdoor heat exchanger 6.
  • FIG. 3 is a diagram showing the internal structure of the header 16 of the outdoor heat exchanger 6.
  • FIG. 3A shows a structure when the inside of the header 16 is viewed without passing through the vertical partition plate 21, and
  • FIG. 3B shows the inside of the header 16 through the vertical partition plate 21. The structure is shown when looking at.
  • the outdoor heat exchanger 6 includes a heat exchange unit 11 and headers 16 and 17.
  • the heat exchange unit 11 is a mechanism that exchanges heat between the working fluid (refrigerant) and outdoor air.
  • the headers 16 and 17 are containers for temporarily storing a working fluid (refrigerant).
  • a space for temporarily storing a working fluid (refrigerant) is provided in the headers 16 and 17.
  • the headers 16 and 17 distribute the working fluid (refrigerant) flowing in from the indoor unit 2 (see FIG. 1) to each heat transfer tube 14 described later, or conversely, the working fluid flowed in from each heat transfer tube 14 described later. (Refrigerant) is allowed to flow through the indoor unit 2 (see FIG. 1).
  • the heat exchange unit 11 has a plurality of heat transfer tubes 14 and a plurality of fins 15.
  • the heat transfer tube 14 is a pipe for flowing a refrigerant.
  • the fin 15 is a plate-like member for expanding the heat transfer surface.
  • Each heat transfer tube 14 has an elliptical shape or a flat shape, and is joined so as to penetrate each fin 15.
  • the end of each heat transfer tube 14 is inserted into the headers 16 and 17.
  • the end portions of the heat transfer tubes 14 are open in the internal spaces of the headers 16 and 17.
  • the header 16 is a pipe 18 (hereinafter referred to as an inflow pipe) for flowing a working fluid (refrigerant) from the indoor heat exchanger 5 side to the outdoor heat exchanger 6 side during heating operation (evaporation operation of the outdoor heat exchanger 6).
  • “Inflow pipe 18" and function as an outflow pipe for flowing a working fluid (refrigerant) from the outdoor heat exchanger 6 side to the indoor heat exchanger 5 side during heating operation (evaporation operation of the outdoor heat exchanger 6)
  • a pipe 19 hereinafter referred to as "outflow pipe 19"
  • the functions of the pipe 18 and the pipe 19 are reversed (that is, the pipe 18 becomes an outflow pipe and the pipe 19 becomes an inflow pipe).
  • the inflow pipe 18 is connected at a relatively high position of the header 16, while the outflow pipe 19 is connected at a relatively low position of the header 16.
  • the working fluid (refrigerant) flows in the direction of arrow A11 through the internal flow path provided in the inflow pipe 18. Further, the working fluid (refrigerant) flows in the direction of arrow B11 through an internal flow path provided inside the outflow pipe 19.
  • the header 16 is provided with a vertical partition plate 21 and a horizontal partition plate 30 therein.
  • the header 17 is not in direct communication with the inflow pipe 18 and the outflow pipe 19 and has a structure in which the vertical partition plate 21 and the horizontal partition plate 30 are not provided.
  • the header 17 is connected to each heat transfer tube 14, and has a structure in which the working fluid (refrigerant) flowing from the header 16 side is returned to the header 16 side. Inside the header 17, the working fluid (refrigerant) flows along a dotted arrow.
  • the vertical partition plate 21 is a plate-like member that partitions the inner space of the header 16 into an inflow tube side upper space 33F that communicates with the end of the inflow tube 18 and a heat transfer tube side upper space 33R that communicates with the end of the heat transfer tube 14. is there.
  • the vertical partition plate 21 has a substantially flat shape on both sides.
  • the vertical partition plate 21 is disposed inside the header 16 so as to extend in the vertical direction.
  • the inflow pipe side upper space 33F and the heat transfer pipe side upper space 33R constitute an upper upper space 33 in the internal space of the header 16 partitioned into the upper side and the lower side by the horizontal partition plate 30. .
  • the vertical partition plate 21 is disposed only in the upper space 33.
  • the vertical partition plate 21 has a long hole-shaped (slit-shaped) opening 21op extending in the vertical direction.
  • the opening 21op functions as a flow path for the working fluid (refrigerant).
  • the vertical partition plate 21 can flow a working fluid (refrigerant) between the inflow pipe side upper space 33F and the heat transfer pipe side upper space 33R through the opening 21op.
  • the horizontal partition plate 30 is a plate-like member that partitions the internal space of the header 16 into an upper space 33 and a lower space 34 while maintaining a liquid-tight state and an air-tight state.
  • the horizontal partition plate 30 is disposed inside the header 16 so as to extend in the horizontal direction.
  • the inflow pipe 18 is connected to the header 16 so as to communicate with the upper space 33.
  • the outflow pipe 19 is connected to the header 16 so as to communicate with the lower space 34.
  • the horizontal partition plate 30 includes an inflow tube side horizontal partition plate 31 disposed closer to the inflow tube 18 than the vertical partition plate 21, and a heat transfer tube side horizontal partition plate 32 disposed closer to the heat transfer tube 14 than the vertical partition plate 21. It consists of and.
  • the inflow tube side horizontal partition plate 31 and the heat transfer tube side horizontal partition plate 32 are respectively joined to the vertical partition plate 21.
  • the inflow tube side horizontal partition plate 31 and the heat transfer tube side horizontal partition plate 32 are substantially flat on both surfaces.
  • the header 16 is connected to twelve heat transfer tubes 14a to 14l, and the inflow tube side horizontal partition plate between the sixth heat transfer tube 14f and the seventh heat transfer tube 14g from the top. 31 is arranged.
  • a heat transfer tube side horizontal partition plate 32 (see FIG. 2) is disposed on the back side of the inflow tube side horizontal partition plate 31.
  • the opening 21op is formed on the lateral side of the facing portion 18tg (see FIG. 3A) of the inflow pipe 18 so as to extend in the vertical direction.
  • the facing portion 18 tg (see FIG. 3A) is a portion facing the end portion of the inflow pipe 18 of the vertical partition plate 21.
  • the facing portion 18tg (see FIG. 3A) is a gas-liquid two-phase working fluid that flows into the header 16 through the internal flow path of the inflow pipe 18 along the direction of the arrow A11 (see FIG. 2). This is the part where the refrigerant) collides.
  • the upper end of the opening 21op is disposed at a position higher than the position of the heat transfer tube 14a (see FIG. 3B) disposed at the highest position.
  • the inflow pipe 18 is arranged within the range of the arrangement area 18ar (see FIG. 3B). Therefore, the opposing portion 18tg (see FIG. 3A) of the inflow pipe 18 is disposed within the range of the arrangement area 18ar (see FIG. 3B) of the inflow pipe 18.
  • the arrangement area 18ar allows the working fluid (refrigerant) to be distributed to the heat transfer pipe 14a (see FIG. 3 (b)) arranged at the highest position. It is set to include the position.
  • the arrangement area 18ar (see FIG. 3B) is arranged so that the upper end of the inner flow path of the inflow pipe 18 is located above the lower end of the heat transfer pipe 14a. It is set in consideration of the inner diameter. That is, the inflow pipe 18 is arranged at a position on the heat transfer pipe 14a arranged at a position where the shadow of the end portion projected in the direction of the vertical partition plate 21 along the extending direction is the highest.
  • the arrangement area 18ar (see FIG. 3B) is set so that the inflow pipe 18 is arranged at such a position.
  • FIGS. 4 and 5 are diagrams showing the flow of the working fluid (refrigerant) inside the header 16, respectively.
  • FIG. 4 shows the flow of the working fluid (refrigerant) in the vicinity of the facing portion 18 tg of the inflow pipe 18.
  • 5A shows the flow of the working fluid (refrigerant) when the inside of the header 16 is viewed without passing through the vertical partition plate 21, and
  • FIG. 5B shows the flow through the vertical partition plate 21. The flow of the working fluid (refrigerant) when the inside of the header 16 is viewed is shown.
  • the gas-liquid two-phase working fluid flows into the header 16 through the internal flow path of the inflow pipe 18 (see FIG. 2) along the direction of the arrow A11. Then, the gas-liquid two-phase working fluid (refrigerant) collides with the vertical partition plate 21 at the facing portion 18 tg of the inflow pipe 18.
  • the gas-liquid two-phase working fluid (refrigerant) collides with the vertical partition plate 21, it flows on the surface of the vertical partition plate 21 so as to diffuse from the facing portion 18tg to the periphery thereof. For example, a part of the gas-liquid two-phase working fluid (refrigerant) flows obliquely upward or laterally. For example, a part of the gas-liquid two-phase working fluid (refrigerant) flows obliquely downward or downward.
  • the gas-liquid two-phase working fluid (refrigerant) reaches the opening 21op, it flows through the opening 21op from the inflow pipe side upper space 33F into the heat transfer pipe side upper space 33R.
  • a part of the gas-liquid two-phase working fluid (refrigerant) flows directly from the end of each heat transfer tube 14 into the flow path of each heat transfer tube 14 (for example, see the first heat transfer tube 14a from the top). ). Further, for example, the remaining part of the gas-liquid two-phase working fluid (refrigerant) gently flows around the heat transfer tubes 14 while falling by gravity (see arrow G), and ends of each heat transfer tube 14. (See, for example, the second heat transfer tube 14b and the third heat transfer tube 14c from the top). In this way, the header 16 distributes the gas-liquid two-phase working fluid (refrigerant) to each heat transfer tube 14.
  • the gas-liquid two-phase working fluid collides with the vertical partition plate 21 at the facing portion 18tg of the inflow pipe 18 and diffuses to the surroundings, and a part thereof is vertically partitioned along the arrow C11.
  • the surface of the plate 21 flows obliquely downward, and further flows through the opening 21op along the arrow C12 from the inflow pipe side upper space 33F to the heat transfer pipe side upper space 33R.
  • the gas-liquid two-phase working fluid (refrigerant) flowing into the heat transfer tube side upper space 33R branches and flows in the direction of the arrow C13 and the direction of the arrow C14.
  • the gas-liquid two-phase working fluid (refrigerant) that flows in the direction of the arrow C13 gradually falls while flowing between the end of the heat transfer tube 14 and the end of the heat transfer tube 14, and It flows into the flow path of each heat transfer tube 14 from the end.
  • the gas-liquid two-phase working fluid (refrigerant) that flows in the direction of the arrow C14 gradually falls while traveling along the outer wall surface of the heat transfer tube 14.
  • the working fluid (refrigerant) accumulates on the inflow pipe side horizontal partition plate 31 and on the heat transfer pipe side horizontal partition plate 32 (see FIG. 2).
  • the working fluid (refrigerant) accumulated on the inflow pipe side horizontal partition plate 31 passes through the opening 21op and flows from the inflow pipe side upper space 33F (see FIG. 2) to the heat transfer pipe side upper space 33R (see FIG. 2). Flows into the side.
  • the working fluid (refrigerant) accumulated on the heat transfer tube side horizontal partition plate 32 (see FIG. 2) is near the heat transfer tube 14 (for example, the heat transfer tube side horizontal partition plate 32 (see FIG. 2)).
  • each heat transfer tube 14 It flows into the flow path of each heat transfer tube 14 from the end of the arranged heat transfer tubes 14d to 14f (see FIG. 5B). As a result, the working fluid (refrigerant) accumulated on the inflow tube side horizontal partition plate 31 and the heat transfer tube side horizontal partition plate 32 (see FIG. 2) is also distributed to each heat transfer tube 14.
  • the header 16 distributes all the working fluid (refrigerant) to the heat transfer tubes 14.
  • the entire flow of the working fluid (refrigerant) inside the header 16 is gently dropped (see arrow D11).
  • Such a header 16 can generate a flow of working fluid (refrigerant) circulating in a plane perpendicular to the cross section of each heat transfer tube 14.
  • the outdoor heat exchanger 6 has the following characteristics. (1) The outdoor heat exchanger 6 is provided with a vertical partition plate 21 inside the header 16 in order to rapidly deflect the flow of the gas-liquid two-phase working fluid (refrigerant) flowing into the header 16. .
  • the vertical partition plate 21 divides the internal space of the header 16 into an inflow pipe side upper space 33F (front side in FIG. 4) and a heat transfer pipe side upper space 33R (back side in FIG. 4). Partitioning.
  • the outdoor heat exchanger 6 abruptly deflects the flow of the gas-liquid two-phase working fluid (refrigerant) flowing into the header 16 by the vertical partition plate 21. Thereby, the outdoor heat exchanger 6 can minimize the influence of the speed difference between the liquid and the gas contained in the gas-liquid two-phase working fluid (refrigerant) and reduce the unevenness of the liquid flow. . Therefore, the outdoor heat exchanger 6 can suppress the occurrence of drift of the working fluid (refrigerant) inside the header.
  • the outdoor heat exchanger 6 is provided with an opening 21op at a position where it does not overlap with the inflow pipe 18 (a position away from the axial direction of the inflow pipe 18). That is, the outdoor heat exchanger 6 has an opening 21op at a position where the working fluid (refrigerant) flowing into the header 16 of the vertical partition plate 21 does not collide (a position on the side of the facing portion 18tg (see FIG. 3A)). Is provided.
  • the opening 21op is formed so as to extend in the vertical direction.
  • Such an outdoor heat exchanger 6 can generate a flow of a working fluid (refrigerant) that circulates in a plane perpendicular to the cross section of each heat transfer tube 14.
  • the outdoor heat exchanger 6 can efficiently mix the liquid and gas of the working fluid (refrigerant) by gently dropping the gas-liquid two-phase working fluid (refrigerant) by gravity inside the header 16. it can. Also by this, the outdoor heat exchanger 6 can suppress the occurrence of the drift of the working fluid (refrigerant) inside the header 16.
  • the outdoor heat exchanger 6 has an inflow pipe 18 disposed at a relatively high position of the header 16 in order to cause the gas-liquid two-phase working fluid (refrigerant) to fall gently by gravity inside the header 16. Yes.
  • the outdoor heat exchanger 6 also distributes the working fluid (refrigerant) to each heat transfer tube 14 in the header 16 with a horizontal partition plate 30 (an inflow tube side horizontal partition plate 31 or a heat transfer tube side horizontal partition).
  • a plate 32 is provided, and the working fluid (refrigerant) is stored on the horizontal partition plate 30.
  • Such an outdoor heat exchanger 6 can distribute the working fluid (refrigerant) to all the heat transfer tubes 14. In addition, since the outdoor heat exchanger 6 can reduce the falling speed of the working fluid (refrigerant) by accumulating the working fluid (refrigerant) on the horizontal partition plate 30, Gas can be mixed efficiently. Also by this, the outdoor heat exchanger 6 can suppress the occurrence of the drift of the working fluid (refrigerant) inside the header 16.
  • Such an outdoor heat exchanger 6 can make the distribution of the working fluid (refrigerant) to each heat transfer tube 14 close to a uniform state, particularly when performing an evaporation operation. Thereby, the outdoor heat exchanger 6 can flow the gas-liquid two-phase refrigerant through the plurality of heat transfer tubes 14 almost uniformly. Therefore, the outdoor heat exchanger 6 can improve the distribution performance of the working fluid (refrigerant) from the header to each heat transfer tube.
  • Such an outdoor heat exchanger 6 can suppress the occurrence of drift of the working fluid (refrigerant) inside the header 16. As a result, the outdoor heat exchanger 6 can also suppress that the specific heat transfer tube 14 is overheated and the heat exchange performance is deteriorated.
  • the outdoor heat exchanger 6 As described above, according to the outdoor heat exchanger 6 according to the first embodiment, it is possible to improve the distribution performance of the working fluid (refrigerant) from the header 16 to each heat transfer tube 14.
  • the outdoor heat exchanger 6 (see FIG. 2) according to the first embodiment has a structure in which the header 17 returns the working fluid (refrigerant) flowing from the header 16 side to the header 17 side to the header 16 side.
  • an outdoor heat exchanger 6A having a structure in which a working fluid (refrigerant) is repeatedly flowed between the header 16a and the header 17a and then sent from the header 17a to an external device is provided. To do.
  • a working fluid refrigerant
  • FIG. 6 is a diagram illustrating a configuration of an outdoor heat exchanger 6A according to the second embodiment.
  • the outdoor heat exchanger 6 ⁇ / b> A according to the second embodiment is different from the outdoor heat exchanger 6 (see FIG. 2) according to the first embodiment, instead of the headers 16 and 17.
  • the difference is that it has a header 17a.
  • the header 16a is connected to the inflow pipe 18 and the heat transfer pipe 14, but is not connected to the outflow pipe 19, and instead of the vertical partition plate 21.
  • the difference is that the vertical partition plate 21a is used.
  • the vertical partition plate 21a is a plate-like member that partitions the inflow pipe side upper space 33F and the heat transfer pipe side upper space 33R, similarly to the vertical partition plate 21 (see FIG. 2) of the first embodiment. However, the length of the vertical partition plate 21a is shorter than the vertical partition plate 21 of the first embodiment (see FIG. 2).
  • the vertical partition plate 21a has a substantially flat shape on both sides.
  • the header 17a is connected to the outflow pipe 19 in addition to the heat transfer pipe 14, and the working fluid (refrigerant) between the header 16a and the header 17a. Is repeatedly sent (in the illustrated example, once reciprocating) and then sent from the header 17a to an external device. In the headers 16a and 17a, the working fluid (refrigerant) flows along solid arrows and dotted arrows.
  • Such an outdoor heat exchanger 6A is similar to the outdoor heat exchanger 6 of the first embodiment, as described in (1) to (3) above in the section ⁇ Main features of the outdoor heat exchanger> of the first embodiment. Has characteristics. Therefore, the outdoor heat exchanger 6A can obtain the same effects as the outdoor heat exchanger 6 of the first embodiment.
  • the working fluid (refrigerant) distribution performance from the header 16a to each heat transfer tube 14 is similar to the outdoor heat exchanger 6 according to the first embodiment. Can be improved.
  • a working fluid (refrigerant) can be sent to the external apparatus from the header 16b.
  • the outdoor heat exchanger 6 (see FIG. 2) according to the first embodiment has a structure using one heat exchange unit 11.
  • an outdoor heat exchanger 6B having a structure using two heat exchange units 11 and 12 is provided.
  • FIG. 7 is a diagram illustrating a configuration of an outdoor heat exchanger 6B according to the third embodiment.
  • FIG. 8 is a diagram illustrating an internal structure of the header 16b1 of the outdoor heat exchanger 6B according to the third embodiment.
  • the outdoor heat exchanger 6 ⁇ / b> B according to the third embodiment has a structure using two heat exchange units 11 and 12 as compared to the outdoor heat exchanger 6 (see FIG. 2) according to the first embodiment. It is different in that it is.
  • the heat exchange unit 12 has the same configuration as the heat exchange unit 11 and includes a plurality of heat transfer tubes 14 and a plurality of fins 15.
  • the heat exchanging section 11 has a header 16b1 connected to one end via a heat transfer tube 14, and a header 17b1 connected to the other end.
  • the heat exchanging section 12 has a header 16b2 connected to one end via the heat transfer tube 14, and a header 17b2 connected to the other end.
  • An inflow pipe 18 and a heat transfer pipe 14 of the heat exchange section 11 are connected to the header 16b1 on the heat exchange section 11 side. Further, a connection pipe (not shown) to the header 17b2 on the heat exchange unit 12 side and the heat transfer tube 14 of the heat exchange unit 11 are connected to the header 17b1 on the heat exchange unit 11 side. That is, the header 17b1 and the header 17b2 are in communication.
  • the working fluid (refrigerant) that has flowed out of the heat transfer tube 14 of the heat exchange unit 11 to the header 17b1 goes to the header 17b2, and then flows out of the heat transfer tube 12 of the heat exchange unit 12 to the header 16b2.
  • the outflow pipe 19 and the heat transfer pipe 14 of the heat exchange section 12 are connected to the header 16b2 on the heat exchange section 12 side. Further, a connection pipe (not shown) to the header 17b1 on the heat exchange unit 11 side and the heat transfer tube 14 of the heat exchange unit 12 are connected to the header 17b2 on the heat exchange unit 12 side.
  • the outdoor heat exchanger 6B passes the working fluid (refrigerant) flowing into the header 16b1 through the internal flow path of the inflow pipe 18 along the direction of the arrow A11 from the header 16b1 to the header 17b1, the header 17b2, and the header 16b2. Send in order.
  • the working fluid (refrigerant) flows along solid arrows and dotted arrows.
  • the outdoor heat exchanger 6B sends the working fluid (refrigerant) through the internal flow path of the outflow pipe 19 to the external device along the direction of the arrow B11.
  • the header 16b1 on the heat exchange section 11 side is provided with a vertical partition plate 21b and a horizontal partition plate 30 therein.
  • the vertical partition plate 21b is a plate-like member that partitions not only the upper space 33 of the header 16b1 but also the lower space 34 into an inflow pipe side lower space 34F and a heat transfer pipe side lower space 34R.
  • the vertical partition plate 21b has a substantially flat shape on both sides.
  • the vertical partition plate 21b is arranged so as to extend not only in the upper space 33 but also in the lower space 34.
  • Two long hole-shaped openings 21op1 and 21op2 extending in the vertical direction are provided in a portion above and below the horizontal partition plate 30 of the vertical partition plate 21b, respectively.
  • the vertical partition plate 21b can flow the working fluid (refrigerant) between the inflow pipe side upper space 33F and the heat transfer pipe side upper space 33R through the opening 21op1.
  • the vertical partition plate 21b can flow a working fluid (refrigerant) between the inflow pipe side lower space 34F and the heat transfer pipe side lower space 34R through the opening 21op2.
  • the horizontal partition plate 30 includes an inflow tube side horizontal partition plate 31b and a heat transfer tube side horizontal partition plate 32.
  • the inflow pipe side horizontal partition plate 31b is joined to the vertical partition plate 21b.
  • the inflow pipe side horizontal partition plate 31b is a plate-like member in which the opening 31op is partially formed.
  • the opening 31op functions as a buffer flow path for slightly reducing the flow of the working fluid (refrigerant) falling from the upper side and flowing it downward.
  • the opening 31op is provided apart from the openings 21op1 and 21op2.
  • the opening part (here opening part 31op) which functions as a buffer flow path is provided only in the inflow tube side horizontal partition plate 31b, and is not provided in the heat transfer tube side horizontal partition plate 32.
  • the heat transfer tube side horizontal partition plate 32 is a member intended to store the working fluid (refrigerant) thereon and distribute the stored working fluid (refrigerant) to each heat transfer tube 14.
  • the inflow pipe side horizontal partition plate 31b slightly restricts the flow of working fluid (refrigerant) that collides with the vertical partition plate 21 at the facing portion 18tg (see FIG. 8) of the inflow pipe 18 and falls from the upper side at the opening 31op. And let it flow down. At that time, the inflow pipe side horizontal partition plate 31b functions as a stopper that reduces the falling speed of the working fluid (refrigerant) and adjusts it to a suitable falling speed.
  • the header 16b1 is provided with only one inflow tube side lateral partition plate 31b and one heat transfer tube side lateral partition plate 32 (see FIG. 7).
  • the header 16b1 may be provided with a plurality of inflow pipe side lateral partition plates 31b and a plurality of heat transfer tube side lateral partition plates 32 (see FIG. 7).
  • the header 16b1 can adjust the drop speed of the working fluid (refrigerant) to a suitable drop speed by reducing the drop speed of the working fluid (refrigerant) in multiple stages by each inflow pipe side horizontal partition plate 31b.
  • the plurality of inflow pipe side horizontal partition plates 31b and the plurality of heat transfer pipe side horizontal partition plates 32 may be arranged in a zigzag shape (zigzag shape).
  • Such an outdoor heat exchanger 6B is similar to the outdoor heat exchanger 6 of the first embodiment, as described in the section ⁇ Main features of the outdoor heat exchanger> of the first embodiment (1) to (3). It has characteristics. Therefore, the outdoor heat exchanger 6B can obtain the same effects as the outdoor heat exchanger 6 of the first embodiment.
  • FIGS. 9 and 10 are diagrams showing modifications of the header 16b1.
  • FIG. 9A shows an example in which the vertical partition plate 21b1 is used instead of the vertical partition plate 21b (see FIG. 8) as a modification of the header 16b1.
  • the vertical partition plate 21b1 has six long hole-like opening portions each having a shorter length (vertical width) than the opening portions 21op1, 21op2 instead of the two long hole-like opening portions 21op1, 21op2 (see FIG. 8). This is a plate-like member on which 21op11 is formed.
  • FIG. 9B shows an example in which the vertical partition plate 21b2 is used instead of the vertical partition plate 21b (see FIG. 8) as a modification of the header 16b1.
  • the vertical partition plate 21b1 is a plate-like member in which a large number of circular openings 21op12 are formed instead of the two long hole-shaped openings 21op1 and 21op2 (see FIG. 8).
  • FIG. 10A shows an example in which the vertical partition plate 21b1a is used instead of the vertical partition plate 21b (see FIG. 8) as a modification of the header 16b1.
  • the vertical partition plate 21b1a has six long hole-like opening portions each having a shorter length (vertical width) than the opening portions 21op1, 21op2 instead of the two long hole-like opening portions 21op1, 21op2 (see FIG. 8).
  • 21op11 is a plate-like member in which five inflow pipe side horizontal partition plates 31b are joined.
  • the vertical partition plate 21b1a has the five heat transfer tube side horizontal partition plates 32 joined to the back side of the position where the five inflow tube side horizontal partition plates 31b are joined.
  • FIG. 10B shows an example in which the vertical partition plate 21b2a is used instead of the vertical partition plate 21b (see FIG. 8) as a modification of the header 16b1.
  • the vertical partition plate 21b2a is formed with a large number of circular openings 21op12 instead of the two elongated holes 21op1 and 21op2 (see FIG. 8), and five inflow pipe side horizontal partition plates A plate-like member 31b is joined.
  • the vertical partition plate 21b2a has five heat transfer tube side horizontal partition plates 32 joined to the back side of the position where the five inflow tube side horizontal partition plates 31b are joined.
  • the distribution performance of the working fluid (refrigerant) from the header 16b1 to each heat transfer tube 14 is similar to the outdoor heat exchanger 6 according to the first embodiment. Can be improved.
  • the heat exchange unit 12 is provided in addition to the heat exchange unit 11 as compared with the outdoor heat exchanger 6 according to the first embodiment. Performance can be improved.
  • FIG. 11 is a diagram illustrating a configuration of the indoor heat exchanger 5 according to the fourth embodiment.
  • FIG. 12 is a diagram illustrating an internal structure of the header 116a of the indoor heat exchanger 5 according to the fourth embodiment. 12A shows a perspective cross-sectional structure of the header 116a cut along the line X1 shown in FIG. 11, and FIG. 12B shows a front cross-sectional structure of the header 116a. 12 (c) shows the structure of the vertical partition plate 121 used in the header 116a.
  • the indoor heat exchanger 5 includes a blower 105, a front heat exchange unit 111 disposed on the front side of the blower 105, and a rear upper side of the blower 105. And a side heat exchanging unit 112.
  • the front heat exchange unit 111 and the rear heat exchange unit 112 are mechanisms for performing heat exchange between the working fluid (refrigerant) and room air, respectively.
  • the air conditioner 1 performs the cooling operation (that is, the case where the indoor heat exchanger 5 performs the evaporation operation and the outdoor heat exchanger 6 performs the condensation operation) will be described.
  • the front heat exchanging section 111 has a plurality of heat transfer tubes 114 for flowing the refrigerant and a plurality of fins 115a for expanding the heat transfer surface.
  • the rear heat exchange unit 112 includes a plurality of heat transfer tubes 114 for flowing the refrigerant and a plurality of fins 115b for extending the heat transfer surface.
  • the fin 115a of the front side heat exchanging part 111 has a bent shape near the center in the height direction.
  • the fins 115b of the rear heat exchange unit 112 have a substantially straight shape.
  • the front-side heat exchanging unit 111 has a header 116a connected to one end via a heat transfer tube 114, and a header 117a connected to the other end.
  • the rear heat exchange unit 112 has a header 116b connected to one end via a heat transfer tube 114, and a header 117b connected to the other end.
  • the indoor heat exchanger 5 includes two rows of front heat exchange units 111 arranged in parallel, and the two rows of front heat exchange units 111 include one header 116a and one header 117a. It is assumed that the structure is connected to the. In other words, two rows of fins 115a are arranged in parallel, and two rows of fins 115a are connected to one header 116a and one header 117a via heat transfer tubes 114, respectively. explain.
  • two rows of the rear heat exchange units 112 are arranged in parallel, and the two rows of the rear heat exchange units 112 are connected to one header 116b and one header 117b. It is assumed that the configuration is the same. In other words, two rows of fins 115b are arranged in parallel, and two rows of fins 115b are connected to one header 116b and one header 117b via heat transfer tubes 114, respectively. explain.
  • the headers 116a, 116b, 117a, and 117b are containers for temporarily storing a working fluid (refrigerant). Spaces for temporarily storing a working fluid (refrigerant) are provided in the headers 116a, 116b, 117a, and 117b.
  • the headers 116 a and 116 b have a shape in which the vicinity of the approximate center in the height direction is bent in accordance with the shape of the fin 115 a of the front heat exchange unit 111.
  • the headers 117a and 117b have a substantially straight shape in accordance with the shape of the fin 115b of the rear heat exchange unit 112.
  • a pipe 119 (hereinafter referred to as “outflow pipe 119”) functioning as an outflow pipe for flowing the water and the heat transfer pipe 114 of the front heat exchange unit 111 are connected.
  • the functions of the pipe 118 and the pipe 119 are reversed (that is, the pipe 118 serves as an outflow pipe and the pipe 119 serves as an inflow pipe). Further, a connection pipe (not shown) to the header 117b on the rear heat exchange unit 112 side and a heat transfer tube 114 of the front heat exchange unit 111 are connected to the header 117a on the front heat exchange unit 111 side. .
  • the heat transfer tube 114 of the rear heat exchange unit 112 is connected to the header 116b on the rear heat exchange unit 112 side.
  • a connection pipe (not shown) to the header 117a on the front heat exchange section 111 side and a heat transfer tube 114 of the rear heat exchange section 112 are connected to the header 117b on the rear heat exchange section 112 side.
  • Each heat transfer tube 114 has an elliptical shape or a flat shape, and is joined so as to penetrate each fin 115. The end of each heat transfer tube 114 is inserted into the header 116a, 116b, 117a, 117b. The end of each heat transfer tube 114 is open in the internal space of the headers 116a, 116b, 117a, 117b.
  • a dehumidifying mechanism 140 for performing dehumidification processing is connected between the header 116a on the front heat exchange unit 111 side and the header 116b on the rear heat exchange unit 112 side.
  • the header 116a has a structure in which two rows of headers 116aa and 116ab are joined so as to correspond to the two rows of front heat exchange sections 111.
  • the first row (near side) header 116aa is connected to the first row (near side) fins 115a (see FIG. 11) via a heat transfer tube 114.
  • the second row (back side) header 116ab is connected to the second row (back side) fin 115a (see FIG. 11) via the heat transfer tube 114.
  • the two columns of headers 116aa and 116ab have the same structure.
  • the structure of the header 116aa will be described as an example.
  • the header 116aa is provided with a vertical partition plate 121 and a horizontal partition plate 130 therein.
  • the vertical partition plate 121 is a plate-like member that partitions the internal space of the header 116aa into an inflow tube side space and a heat transfer tube side space.
  • the vertical partition plate 121 partitions the upper space 133 inside the header 116aa into an inflow pipe side upper space 133F and a heat transfer pipe side upper space 133R. Further, the vertical partition plate 121 partitions the lower space 134 inside the header 116aa into an inflow pipe side lower space 134F and a heat transfer pipe side lower space 134R.
  • the vertical partition plate 121 includes two short sides SS1 and SS2, and two or more long sides having a width longer than the width of the short side that is inclined with respect to the vertical direction.
  • the shape has four long sides LS1a, LS1b, LS2a, and LS2b).
  • the long sides LS1b and LS2a are respectively longer sides arranged in the direction of gravity than the long sides LS1a and LS2b (hereinafter referred to as “long sides in the direction of gravity”). )It has become.
  • the long sides LS1a and LS2b are long sides arranged on the side opposite to the gravitational direction from the long sides LS1b and LS2a (hereinafter referred to as “long sides opposite to the gravitational direction”), respectively.
  • the “gravity direction” means a direction in which a gas-liquid two-phase working fluid (refrigerant) flows.
  • the horizontal partition plate 130 partitions the internal space of the header 116aa into an upper space and a lower space in multiple stages (three stages in the illustrated example). It is a shaped member.
  • the horizontal partition plate 130 is disposed inside the header 116aa so as to extend in the horizontal direction or in the inclined direction.
  • the horizontal partition plate 130 includes, in order from the top, three inflow pipe side horizontal partition plates 131a, 131b, and 131c disposed on the inflow pipe 118 side from the vertical partition plate 121, and the vertical partition plate 121 in order from the top. It is comprised by the three heat exchanger tube side horizontal partition plates 132a, 132b, 132c arrange
  • the three inflow tube side horizontal partition plates 131a, 131b, 131c and the three heat transfer tube side horizontal partition plates 132a, 132b, 132c are joined to the vertical partition plate 121, respectively.
  • the three inflow pipe side horizontal partition plates 131a, 131b, 131c are arranged so that their front end portions are directed obliquely upward, laterally, and obliquely downward.
  • the inflow pipe side horizontal partition plates 131a and 131c at the uppermost stage and the lowermost stage have a substantially parallel arrangement relationship with the heat transfer pipe 114.
  • the middle inflow pipe side horizontal partition 131b is arranged in a substantially horizontal direction.
  • the direction (arrangement direction) of the plurality of heat transfer tubes 114 is different between the one arranged on the upper side and the one arranged on the lower side.
  • the heat transfer tube 114 disposed on the upper side has a front end portion directed obliquely upward, while the heat transfer tube 114 disposed on the lower side has a front end portion directed obliquely downward.
  • the three heat transfer tube side horizontal partition plates 132a, 132b, and 132c are arranged so that their front end portions face obliquely upward, laterally, and obliquely downward.
  • the uppermost and lowermost heat transfer tube side horizontal partition plates 132 a and 132 c are arranged in a substantially parallel relationship with the heat transfer tube 114.
  • the middle heat transfer tube side horizontal partition plate 132b is arranged in a substantially horizontal direction.
  • inflow pipe side horizontal partition plates 131a, 131b, and 131c are collectively referred to as “inflow pipe side horizontal partition plates 131”.
  • the heat transfer tube side horizontal partition plates 132a, 132b, and 132c are collectively referred to as “heat transfer tube side horizontal partition plates 132”.
  • the inflow pipe side horizontal partition plate 131 is a member intended to function as a stopper that reduces the falling speed of the working fluid (refrigerant) and adjusts it to a suitable falling speed. Therefore, the length of the inflow pipe side horizontal partition plate 131 is shorter than the width of the short sides SS1 and SS2 of the vertical partition plate 121 (see FIG. 12C).
  • the inflow pipe side horizontal partition plate 131 is joined to the vertical partition plate at a position close to the long sides LS1b, LS2a in the gravity direction among the four long sides LS1a, LS1b, LS2a, LS2b (FIG. 12 (c)). )reference).
  • the heat transfer tube side horizontal partition plate 132 is a member intended to accumulate working fluid (refrigerant) thereon and distribute the accumulated working fluid (refrigerant) to each heat transfer tube 114. Therefore, the heat transfer tube side horizontal partition plate 132 has the same length as the width of the vertical partition plate 121 (the width in the front-rear direction). And the heat exchanger tube side horizontal partition plate 132 is between the two long sides and the long side which the vertical partition plate 121 opposes (in the example shown in FIG.12 (c), between long side LS1a and long side LS1b, Or, it is arranged in the whole area between the long side LS2a and the long side LS2b).
  • the vertical partition plate 121 is formed with four elongated hole-shaped openings 121op1, 121op2, 121op3, and 121op4 that are inclined and extend in the vertical direction.
  • the openings 121op1, 121op2, 121op3, and 121op4 are collectively referred to as “openings 121op”.
  • the opening 121op functions as a flow path for the working fluid (refrigerant).
  • the vertical partition plate 121 has a working fluid (refrigerant) between the inflow pipe side upper space 133F and the heat transfer pipe side upper space 133R and between the inflow pipe side lower space 134F and the heat transfer pipe side lower space 134R through the opening 121op. ).
  • the opening 121op lowers the flow of the working fluid (refrigerant) temporarily accumulated on the inflow pipe side lateral partition plate 131 by the inflow pipe side lateral partition plate 131. It is a part intended to function as a buffer flow path flowing to the side. Therefore, the opening 121op has a long side opposite to the gravity direction of the vertical partition plate 121 so that the opening 121op is disposed above the working fluid (refrigerant) temporarily accumulated on the inflow pipe side horizontal partition plate 131. It is formed at a position close to LS1a and LS2b so as to incline and extend in the vertical direction.
  • Such an indoor heat exchanger 5 is similar to the outdoor heat exchanger 6 of the first embodiment, in (1) to (3) described in the section ⁇ Main features of the outdoor heat exchanger> of the first embodiment. It has characteristics. Therefore, the indoor heat exchanger 5 can obtain the same effects as the outdoor heat exchanger 6 of the first embodiment.
  • FIG. 13 is a diagram illustrating a modification of the headers 116a, 116b, 117a, and 117b.
  • the header 116 a includes an exterior member 301 that constitutes a part of the housing, a partition member 302 that performs the same function as the vertical partition plate 121, and internal members 303 a and 303 b that are accommodated inside the housing. , 303c, 303d and an exterior member 304 constituting a part of the housing.
  • the exterior member 304 is a member connected to the heat transfer tube 114.
  • the header 116a is configured by incorporating the internal members 303a, 303b, 303c, and 303d inside the exterior member 304, disposing the partition member 302 thereon, and joining the exterior member 304 and the exterior member 301 together. .
  • the header 116b includes an exterior member 401 that constitutes a part of the casing, a partition member 402 that performs the same function as the vertical partition plate 121, internal members 403a and 403b that are accommodated in the casing, and a part of the casing. And an exterior member 404 to be configured.
  • the exterior member 404 is a member connected to the heat transfer tube 114.
  • the header 116b is configured by incorporating the internal members 403a and 403b inside the exterior member 404, disposing the partition member 402 thereon, and joining the exterior member 404 and the exterior member 401 together.
  • the header 117a includes an exterior member 501 that constitutes a part of the housing, internal members 503a, 503b, and 503c housed inside the housing, and an exterior member 504 that constitutes a part of the housing.
  • the exterior member 504 is a member connected to the heat transfer tube 114.
  • the header 117a is configured by incorporating internal members 503a, 503b, and 503c inside the exterior member 504 and joining the exterior member 504 and the exterior member 501 together.
  • the header 117b includes an exterior member 601 that constitutes a part of the housing, internal members 603a and 603b that are accommodated inside the housing, and an exterior member 604 that constitutes a part of the housing.
  • the exterior member 604 is a member connected to the heat transfer tube 114.
  • the header 117b is configured by incorporating internal members 603a and 603b inside the exterior member 604 and joining the exterior member 604 and the exterior member 601 together.
  • the distribution performance of the working fluid (refrigerant) from the header 116a to each heat exchanger tube 114 can be improved.
  • the present invention is not limited to the above-described embodiment, and includes various modifications.
  • the above-described embodiment has been described in detail for easy understanding of the present invention, and is not necessarily limited to one having all the configurations described.
  • a part of the configuration of an embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of an embodiment.
  • the indoor heat exchanger 5 changes the shape of the vertical partition plate similar to the vertical partition plate 121 into a shape that can be accommodated in each, and then the inside of the headers 116b, 117a, and 117b other than the header 116a. You may arrange in.
  • the outdoor heat exchangers 6, 6A, 6B according to the first to third embodiments may be configured by combining a plurality of members in the same manner as the header 116a shown in FIG.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/JP2017/036040 2017-01-25 2017-10-03 熱交換器、及び、空気調和機 Ceased WO2018138972A1 (ja)

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JP2018119743A (ja) 2018-08-02
US20190339027A1 (en) 2019-11-07
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US11236954B2 (en) 2022-02-01
CN110168301A (zh) 2019-08-23

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