WO2023281655A1 - Échangeur de chaleur et dispositif à cycle de réfrigération - Google Patents

Échangeur de chaleur et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2023281655A1
WO2023281655A1 PCT/JP2021/025605 JP2021025605W WO2023281655A1 WO 2023281655 A1 WO2023281655 A1 WO 2023281655A1 JP 2021025605 W JP2021025605 W JP 2021025605W WO 2023281655 A1 WO2023281655 A1 WO 2023281655A1
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Prior art keywords
heat transfer
heat exchanger
heat
transfer section
transfer tubes
Prior art date
Application number
PCT/JP2021/025605
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English (en)
Japanese (ja)
Inventor
拓也 松田
晃 石橋
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2023532946A priority Critical patent/JPWO2023281655A1/ja
Priority to EP21949289.9A priority patent/EP4368919A1/fr
Priority to PCT/JP2021/025605 priority patent/WO2023281655A1/fr
Priority to CN202180100083.XA priority patent/CN117581075A/zh
Publication of WO2023281655A1 publication Critical patent/WO2023281655A1/fr

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    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • 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
    • F28F1/12—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
    • 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
    • F28F2215/00—Fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2270/00—Thermal insulation; Thermal decoupling

Definitions

  • the present disclosure relates to heat exchangers and refrigeration cycle devices.
  • multi-row heat transfer tubes As a means of improving the performance of heat exchangers in refrigeration cycle equipment, multi-row heat transfer tubes have been proposed. Since heat exchangers are mounted in a limited space, multi-row heat transfer tubes can improve the mounting density of the heat transfer tubes and expand the heat transfer area.
  • a heat exchanger of an indoor unit of an air conditioner disclosed in Japanese Patent Application Laid-Open No. 2014-40983 Patent Document 1 has heat transfer tubes arranged in multiple rows.
  • the present disclosure has been made in view of the above problems, and an object of the present disclosure is to provide a heat exchanger and a refrigerator that can suppress heat exchange loss while using a non-azeotropic refrigerant mixture and can suppress frost formation. It is to provide a cycle device.
  • a heat exchanger of the present disclosure includes a first heat transfer section having a plurality of first heat transfer tubes, a second heat transfer section having a plurality of second heat transfer tubes, and a plurality of first heat transfer tubes of the first heat transfer section. and a non-azeotropic refrigerant mixture flowing through the plurality of second heat transfer tubes of the second heat transfer section.
  • the plurality of first heat transfer tubes of the first heat transfer section and the plurality of second heat transfer tubes of the second heat transfer section are arranged in a row.
  • the first heat transfer section and the second heat transfer section are configured such that the non-azeotropic refrigerant mixture flows from the first heat transfer section to the second heat transfer section by folding only once.
  • heat exchange loss can be suppressed while using a non-azeotropic mixed refrigerant, and frost formation can be suppressed.
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration cycle device according to Embodiment 1.
  • FIG. 2 is a top view schematically showing the internal structure of the outdoor unit of the refrigeration cycle apparatus according to Embodiment 1; 1 is a front view schematically showing a heat exchanger according to Embodiment 1;
  • FIG. 3 is a cross-sectional view schematically showing first heat transfer tubes and second heat transfer tubes of the heat exchanger according to Embodiment 1.
  • FIG. FIG. 4 is a cross-sectional view schematically showing Modification 1 of the heat exchanger according to Embodiment 1;
  • FIG. 7 is a cross-sectional view schematically showing Modification 2 of the heat exchanger according to Embodiment 1;
  • FIG. 7 is a front view schematically showing Modification 3 of the heat exchanger according to Embodiment 1;
  • FIG. 11 is a front view schematically showing Modification 4 of the heat exchanger according to Embodiment 1;
  • FIG. 11 is a front view schematically showing Modification 5 of the heat exchanger according to Embodiment 1;
  • FIG. 5 is a front view schematically showing a heat exchanger according to Embodiment 2;
  • FIG. 11 is a perspective view schematically showing a fin of Modification 1 of the heat exchanger according to Embodiment 2;
  • FIG. 11 is a front view schematically showing Modification 2 of the heat exchanger according to Embodiment 2;
  • Embodiment 1 A configuration of a refrigeration cycle apparatus 100 according to Embodiment 1 will be described with reference to FIG. In Embodiment 1, an air conditioner will be described as an example of the refrigeration cycle device 100.
  • FIG. Solid arrows in FIG. 1 indicate the flow of the refrigerant during the cooling operation.
  • Broken line arrows in FIG. 1 indicate the flow of the refrigerant during the heating operation.
  • the refrigeration cycle device 100 includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an expansion valve 4, an indoor heat exchanger 5, an outdoor fan 6, and an indoor fan. 7 and a control device 8 .
  • the heat exchanger HE according to Embodiment 1 is applied to the outdoor heat exchanger 3 .
  • a refrigerating cycle device 100 includes an outdoor unit 101 and an indoor unit 102 connected to the outdoor unit 101 .
  • a refrigerant circuit 10 includes a compressor 1 , a four-way valve 2 , an outdoor heat exchanger 3 , an expansion valve 4 and an indoor heat exchanger 5 .
  • Compressor 1 , four-way valve 2 , outdoor heat exchanger 3 , expansion valve 4 and indoor heat exchanger 5 are connected by piping 20 .
  • the refrigerant circuit 10 is configured to circulate the refrigerant.
  • the refrigerant is a non-azeotropic mixed refrigerant.
  • the non-azeotropic refrigerant mixture contains R32 and may contain R1234yf as another refrigerant.
  • the non-azeotropic refrigerant mixture may contain R1123 or R1234ze as another refrigerant.
  • the non-azeotropic mixed refrigerant may be a mixed refrigerant of three or more types.
  • the compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the expansion valve 4, the outdoor fan 6 and the control device 8 are housed in the outdoor unit 101.
  • Indoor heat exchanger 5 and indoor fan 7 are housed in indoor unit 102 .
  • the outdoor unit 101 and the indoor unit 102 are connected by a gas pipe 21 and a liquid pipe 22 .
  • a part of the pipe 20 constitutes a gas pipe 21 and a liquid pipe 22 .
  • the refrigerant circuit 10 is configured such that the refrigerant circulates through the compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the expansion valve 4, the indoor heat exchanger 5, and the four-way valve 2 in this order during cooling operation.
  • the refrigerant circuit 10 is configured such that the refrigerant circulates through the compressor 1, the four-way valve 2, the indoor heat exchanger 5, the expansion valve 4, the outdoor heat exchanger 3, and the four-way valve 2 in this order during heating operation. .
  • the compressor 1 is configured to compress refrigerant.
  • the compressor 1 is for compressing the non-azeotropic refrigerant mixture flowing into the heat exchanger HE.
  • the compressor 1 is configured to compress and discharge the sucked refrigerant.
  • the compressor 1 may be configured to have a variable capacity.
  • the compressor 1 may be configured such that the displacement is changed by adjusting the rotational speed of the compressor 1 based on an instruction from the control device 8 .
  • the four-way valve 2 is configured to switch the flow of refrigerant so that the refrigerant compressed by the compressor 1 flows to the outdoor heat exchanger 3 or the indoor heat exchanger 5 .
  • the four-way valve 2 has a first port P1 to a fourth port P4.
  • the first port P1 is connected to the discharge side of the compressor 1 .
  • a second port P2 is connected to the suction side of the compressor 1 .
  • the third port P3 is connected to the outdoor heat exchanger 3.
  • a fourth port P4 is connected to the indoor heat exchanger 5 .
  • the four-way valve 2 is configured to flow the refrigerant discharged from the compressor 1 to the outdoor heat exchanger 3 during cooling operation.
  • the four-way valve 2 During cooling operation, the four-way valve 2 has the first port P1 connected to the third port P3 and the second port P2 connected to the fourth port P4.
  • the four-way valve 2 is configured to flow the refrigerant discharged from the compressor 1 to the indoor heat exchanger 5 during heating operation.
  • the four-way valve 2 has the first port P1 connected to the fourth port P4 and the second port P2 connected to the third port P3.
  • the outdoor heat exchanger 3 is configured to exchange heat between the refrigerant flowing inside the outdoor heat exchanger 3 and the air flowing outside the outdoor heat exchanger 3 .
  • the outdoor heat exchanger 3 is configured to function as a condenser that condenses refrigerant during cooling operation, and to function as an evaporator that evaporates refrigerant during heating operation.
  • the expansion valve 4 is configured to reduce the pressure by expanding the refrigerant condensed in the condenser.
  • the expansion valve 4 is configured to reduce the pressure of the refrigerant condensed by the outdoor heat exchanger 3 during cooling operation, and to reduce the pressure of the refrigerant condensed by the indoor heat exchanger 5 during heating operation.
  • Expansion valve 4 is, for example, an electromagnetic expansion valve.
  • the indoor heat exchanger 5 is configured to exchange heat between the refrigerant flowing inside the indoor heat exchanger 5 and the air flowing outside the indoor heat exchanger 5 .
  • the indoor heat exchanger 5 is configured to function as an evaporator that evaporates the refrigerant during cooling operation and as a condenser that condenses the refrigerant during heating operation.
  • the outdoor blower 6 is configured to blow outdoor air to the outdoor heat exchanger 3. That is, the outdoor fan 6 is configured to supply air to the outdoor heat exchanger 3 .
  • the indoor blower 7 is configured to blow indoor air to the indoor heat exchanger 5 . That is, the indoor fan 7 is configured to supply air to the indoor heat exchanger 5 .
  • the control device 8 is configured to perform calculations, instructions, etc. to control each device of the refrigeration cycle device 100 .
  • the control device 8 is electrically connected to the compressor 1, the four-way valve 2, the expansion valve 4, the outdoor blower 6, the indoor blower 7, etc., and is configured to control these operations.
  • the configuration of the outdoor unit 101 will be described in detail with reference to FIG.
  • the outdoor unit 101 has a compressor 1 , a four-way valve 2 , an outdoor heat exchanger 3 , an expansion valve 4 , an outdoor fan 6 and a controller 8 .
  • the outdoor unit 101 has a housing 101a and a separator 101b. The interior of the housing 101a is partitioned into a machine room 101c and a ventilation room 101d by a separator 101b.
  • the compressor 1, the four-way valve 2, the expansion valve 4 and the control device 8 are arranged in the machine room 101c.
  • the outdoor heat exchanger 3 and the outdoor fan 6 are arranged in the blowing chamber 101d.
  • the outdoor heat exchanger 3 is arranged to face the outdoor fan 6.
  • the outdoor heat exchanger 3 is arranged along the back surface of the housing 101a.
  • the outdoor heat exchanger 3 extends in the width direction of the housing 101a.
  • the outdoor heat exchangers 3 are arranged in a line.
  • FIG. 3 The configuration of the outdoor heat exchanger 3 to which the heat exchanger HE according to Embodiment 1 is applied will be described in detail with reference to FIGS. 3 and 4.
  • FIG. Solid arrows in FIG. 3 indicate the flow of the refrigerant during the cooling operation.
  • the outdoor heat exchanger 3 includes a first heat transfer section 31, a second heat transfer section 32, a plurality of fins 33, a header 34, and a non-azeotropic refrigerant mixture.
  • the outdoor heat exchanger 3 is a parallel flow heat exchanger.
  • the first heat transfer section 31 is arranged above the second heat transfer section 32 . That is, the first heat transfer section 31 constitutes an upper stage, and the second heat transfer section 32 constitutes a lower stage.
  • the first heat transfer section 31 has a plurality of first heat transfer tubes 31a.
  • the plurality of first heat transfer tubes 31a of the first heat transfer section 31 are configured to extend linearly.
  • the second heat transfer section 32 has a plurality of second heat transfer tubes 32a.
  • the plurality of second heat transfer tubes 32a of the second heat transfer section 32 are configured to extend linearly.
  • the plurality of first heat transfer tubes 31a of the first heat transfer section 31 and the plurality of second heat transfer tubes 32a of the second heat transfer section 32 are arranged in a row.
  • Each of the plurality of first heat transfer tubes 31a are stacked on each other.
  • Each of the plurality of second heat transfer tubes 32a is overlapped with each other.
  • Each of the plurality of first heat transfer tubes 31a and the plurality of second heat transfer tubes 32a are overlapped with each other.
  • Each of the plurality of first heat transfer tubes 31a of the first heat transfer section 31 and the plurality of second heat transfer tubes 32a of the second heat transfer section 32 is at least one of an elliptical tube, a circular tube, and a flat multi-hole tube.
  • each of the plurality of first heat transfer tubes 31a and the plurality of second heat transfer tubes 32a is a flat tube.
  • the flat tubes have a short axis in the direction in which the plurality of first heat transfer tubes 31a and the plurality of second heat transfer tubes 32a are aligned in a row, and the plurality of first heat transfer tubes 31a and the plurality of second heat transfer tubes 32a. has a long axis in a direction orthogonal to the direction in which they are aligned with each other.
  • Each of the plurality of first heat transfer tubes 31a and the plurality of second heat transfer tubes 32a has one refrigerant flow path RP.
  • the non-azeotropic refrigerant mixture flows through the plurality of first heat transfer tubes 31 a of the first heat transfer section 31 and the plurality of second heat transfer tubes 32 a of the second heat transfer section 32 .
  • the first heat transfer section 31 and the second heat transfer section 32 are configured such that the non-azeotropic refrigerant mixture flows from the first heat transfer section 31 to the second heat transfer section 32 by folding only once.
  • the number of the multiple first heat transfer tubes 31 a of the first heat transfer section 31 is less than the number of the multiple second heat transfer tubes 32 a of the second heat transfer section 32 .
  • the ratio of the number of the plurality of second heat transfer tubes 32a of the second heat transfer section 32 to the number of the plurality of first heat transfer tubes 31a of the first heat transfer section 31 is 30% or less.
  • the ratio of the number of the plurality of second heat transfer tubes 32a of the second heat transfer section 32 to the number of the plurality of first heat transfer tubes 31a of the first heat transfer section 31 is 35%. .
  • the ratio of the number of the plurality of second heat transfer tubes 32a of the second heat transfer section 32 to the number of the plurality of first heat transfer tubes 31a of the first heat transfer section 31 is smaller than when the azeotropic mixture refrigerant is used. .
  • each of the plurality of fins 33 is a corrugated fin.
  • Each of the plurality of fins 33 is arranged between each of the adjacent first heat transfer tubes 31a of the plurality of first heat transfer tubes 31a.
  • Each of the plurality of fins 33 is in contact with each of adjacent first heat transfer tubes 31a of the plurality of first heat transfer tubes 31a.
  • Each of the plurality of fins 33 is arranged between each of the adjacent second heat transfer tubes 32a of the plurality of second heat transfer tubes 32a.
  • Each of the plurality of fins 33 is in contact with each of the adjacent second heat transfer tubes 32a of the plurality of second heat transfer tubes 32a.
  • the headers 34 are connected to both ends of the plurality of first heat transfer tubes 31a of the first heat transfer section 31 and the plurality of second heat transfer tubes 32a of the second heat transfer section 32, respectively.
  • the header 34 includes a first header portion 34a and a second header portion 34b.
  • the first header portion 34a is connected to one end (first end) of each of the plurality of first heat transfer tubes 31a of the first heat transfer section 31 and the plurality of second heat transfer tubes 32a of the second heat transfer section 32.
  • the second header portion 34b is connected to the other end (second end) of each of the plurality of first heat transfer tubes 31a of the first heat transfer section 31 and the plurality of second heat transfer tubes 32a of the second heat transfer section 32.
  • the first header portion 34a has a coolant inlet and a coolant outlet.
  • a partition portion 34c is provided in the first header portion 34a.
  • the partition portion 34 c is arranged at the boundary between the first heat transfer portion 31 and the second heat transfer portion 32 . Therefore, the refrigerant that has flowed into the first header portion 34a from the refrigerant inlet passes through the plurality of first heat transfer tubes 31a of the first heat transfer portion 31, flows to the second header portion 34b, and is folded back at the second header portion 34b. It flows through the plurality of second heat transfer tubes 32a to the first header portion 34a. The refrigerant that has flowed through the first header portion 34a flows out from the refrigerant outlet. In this way, the refrigerant flows from the first heat transfer section 31 to the second heat transfer section 32 so as to turn around only once.
  • FIG. 1 the operation of the refrigeration cycle apparatus 100 according to Embodiment 1 will be described with reference to FIGS. 1 to 3.
  • FIG. 1 the operation of the refrigeration cycle apparatus 100 according to Embodiment 1 will be described with reference to FIGS. 1 to 3.
  • the refrigeration cycle device 100 can selectively perform cooling operation and heating operation.
  • refrigerant circulates through the refrigerant circuit 10 in the order of the compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the expansion valve 4, the indoor heat exchanger 5, and the four-way valve 2.
  • the outdoor heat exchanger 3 functions as a condenser. Heat exchange is performed between the refrigerant flowing through the outdoor heat exchanger 3 and the air blown by the outdoor fan 6 .
  • the indoor heat exchanger 5 functions as an evaporator. Heat exchange is performed between the refrigerant flowing through the indoor heat exchanger 5 and the air blown by the indoor blower 7 .
  • the high-pressure gas refrigerant discharged from the compressor 1 flows into the refrigerant inlet of the first header portion 34a of the outdoor heat exchanger 3 via the gas inflow pipe.
  • the high-pressure gas refrigerant that has flowed into the first header portion 34a is distributed to the plurality of first heat transfer tubes 31a of the first heat transfer portion 31, and is condensed to a dryness of about 0.1 to become a gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant joins at the second header portion 34b, is distributed to the plurality of second heat transfer tubes 32a of the second heat transfer portion 32, and exceeds the saturated liquid to become supercooled liquid refrigerant.
  • the supercooled liquid refrigerant joins at the first header portion 34a and flows out from the refrigerant outlet of the first header portion 34a.
  • the refrigerant circulates through the refrigerant circuit 10 in the order of the compressor 1, the four-way valve 2, the indoor heat exchanger 5, the expansion valve 4, the outdoor heat exchanger 3, and the four-way valve 2.
  • the indoor heat exchanger 5 functions as a condenser. Heat exchange is performed between the refrigerant flowing through the indoor heat exchanger 5 and the air blown by the indoor blower 7 .
  • the outdoor heat exchanger 3 functions as an evaporator. Heat exchange is performed between the refrigerant flowing through the outdoor heat exchanger 3 and the air blown by the outdoor fan 6 .
  • the supercooled liquid refrigerant that has flowed into the expansion valve 4 from the indoor heat exchanger 5 is decompressed by the expansion valve 4 to become a low-dryness, low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant flows into the refrigerant inlet of the first header portion 34 a of the outdoor heat exchanger 3 .
  • the low-pressure gas-liquid two-phase refrigerant that has flowed into the first header portion 34a is distributed to the plurality of second heat transfer tubes 32a of the second heat transfer portion 32 and evaporated.
  • the low-pressure gas-liquid two-phase refrigerant merges at the second header portion 34b, is distributed to the plurality of first heat transfer tubes 31a of the first heat transfer portion 31, and becomes superheated vapor refrigerant by evaporating and vaporizing.
  • the superheated vapor refrigerant joins at the first header portion 34a and flows out from the refrigerant outlet of the first header portion 34a.
  • the refrigeration cycle apparatus 100 may be capable of selectively performing a defrosting operation.
  • the refrigerant circulates through the refrigerant circuit 10 in the same manner as during the cooling operation.
  • the outdoor heat exchanger 3 functions as a condenser
  • the indoor heat exchanger 5 functions as an evaporator.
  • each of the plurality of first heat transfer tubes 31a and the plurality of second heat transfer tubes 32a is a circular tube.
  • each of the plurality of first heat transfer tubes 31a and the plurality of second heat transfer tubes 32a is a flat multi-hole tube.
  • the flat multi-hole tube has a plurality of refrigerant flow paths RP.
  • a plurality of refrigerant flow paths RP are arranged side by side in the longitudinal direction of the multi-hole flat tube.
  • outdoor heat exchanger 3 includes a plurality of first heat transfer tubes 31a and a plurality of second heat transfer tubes 32a, header 34 , and a plurality of plate fins 35 .
  • Each of the plurality of plate fins 35 is configured in a thin plate shape.
  • a plurality of plate fins 35 are arranged so as to be stacked on each other.
  • Each of the plurality of first heat transfer tubes 31 a and the plurality of second heat transfer tubes 32 a penetrates the plurality of plate fins 35 .
  • the outdoor heat exchanger 3 is a fin-and-tube heat exchanger.
  • outdoor heat exchanger 3 includes a plurality of first heat transfer tubes 31a and a plurality of second heat transfer tubes 32a, header 34 and In Modification 4, the outdoor heat exchanger 3 does not have fins.
  • outdoor heat exchanger 3 includes a plurality of first heat transfer tubes 31a and a plurality of second heat transfer tubes 32a, and a plurality of It has fins 33 and a header 34 .
  • Each of the plurality of first heat transfer tubes 31a and the plurality of second heat transfer tubes 32a extends in the vertical direction (the direction of gravity). Therefore, the drainage performance of each of the plurality of first heat transfer tubes 31a and the plurality of second heat transfer tubes 32a is improved.
  • Each of the plurality of fins 33 is a corrugated fin. The corrugated fin extends in the vertical direction (the direction of gravity). Therefore, the drainage performance of the corrugated fin is improved.
  • Header 34 extends horizontally. This improves the even distribution of refrigerant in the header 34 .
  • the heat exchanger HE According to the heat exchanger HE according to the present embodiment, the plurality of first heat transfer tubes 31a of the first heat transfer section 31 and the plurality of second heat transfer tubes 32a of the second heat transfer section 32 are arranged in a row. . Therefore, the non-azeotropic refrigerant mixture does not flow parallel to the air flow. Therefore, the heat exchange loss due to the temperature gradient of the non-azeotropic mixed refrigerant can be suppressed. That is, it is possible to suppress the heat exchange loss due to the temperature difference between the non-azeotropic refrigerant mixture and the air becoming smaller due to the temperature gradient of the non-azeotropic refrigerant mixture. Thereby, heat exchange efficiency can be improved.
  • the temperature on the windward side is lower when the heat exchanger HE is applied to the outdoor heat exchanger 3 and functions as an evaporator. can be suppressed. Therefore, frost formation can be suppressed.
  • first heat transfer section 31 and the second heat transfer section 32 are configured so that the non-azeotropic refrigerant mixture flows from the first heat transfer section 31 to the second heat transfer section 32 only once. Therefore, the heat exchange loss between the refrigerants due to the temperature difference in the gas-liquid two-phase region of the non-azeotropic mixed refrigerant can be minimized. That is, it is possible to minimize the heat exchange loss between the refrigerants that occurs at each turn due to the temperature gradient in the gas-liquid two-phase region of the non-azeotropic mixed refrigerant. Thereby, heat exchange efficiency can be improved.
  • the ratio of the number of the plurality of second heat transfer tubes 32a of the second heat transfer section 32 to the number of the plurality of first heat transfer tubes 31a of the first heat transfer section 31 is , is smaller than when an azeotrope refrigerant is used. Therefore, the number of heat transfer tubes in the subcooling section for the non-azeotropic refrigerant mixture can be made smaller than the number of heat transfer tubes in the subcooling section for the azeotropic refrigerant mixture. Thereby, heat exchange efficiency can be improved.
  • the temperature gradient of the non-azeotropic refrigerant mixture lowers the temperature of the saturated liquid relative to the azeotropic refrigerant, which inevitably reduces the critical degree of supercooling. For this reason, compared to the case where the azeotropic refrigerant mixture is used, the number of the second heat transfer tubes 32a of the second heat transfer section 32 where the non-azeotropic refrigerant is a supercooled liquid is reduced, and the gas-liquid two-phase region refrigerant is used. By increasing the number of the first heat transfer tubes 31a of the first heat transfer section 31 to be condensed, the heat exchange efficiency can be improved.
  • the number of the second heat transfer tubes 32a of the second heat transfer section 32 is smaller than the number of the first heat transfer tubes 31a of the first heat transfer section 31, which is the upper section.
  • Refrigerant temperature can be raised by increasing the pressure loss with respect to the first heat transfer section 31 .
  • the header 34 is a connected at both ends. Therefore, the heat exchanger HE can be a parallel flow heat exchanger.
  • each of the plurality of first heat transfer tubes 31a of the first heat transfer section 31 and the plurality of second heat transfer tubes 32a of the second heat transfer section 32 is an elliptical tube, It is at least one of a circular tube and a flat multi-hole tube. Therefore, the degree of freedom in production can be improved.
  • the refrigeration cycle apparatus 100 includes the heat exchanger HE described above. Therefore, it is possible to provide the refrigeration cycle apparatus 100 including the heat exchanger HE capable of suppressing heat exchange loss and frosting while using a non-azeotropic mixed refrigerant.
  • Embodiment 2 The heat exchanger HE according to the second embodiment has the same configuration, operation and effects as the heat exchanger HE according to the first embodiment unless otherwise specified.
  • the heat exchanger HE has a heat shielding mechanism 40 .
  • the heat blocking mechanism 40 is provided between the first heat transfer section 31 and the second heat transfer section 32 .
  • the heat blocking mechanism 40 is provided between the first heat transfer tube 31 a of the first heat transfer section 31 and the second heat transfer tube 32 a of the second heat transfer section 32 .
  • the heat shielding mechanism 40 is a partition plate 41 .
  • the partition plate 41 is configured to block heat transfer from the first heat transfer tube 31a to the second heat transfer tube 32a.
  • Partition plate 41 has a lower thermal conductivity than fins 33 .
  • the heat blocking mechanism 40 is a slit 42 .
  • the slits 42 are provided to separate the fins 33 between the peaks and valleys of the fins 33 .
  • the peaks of the fins 33 are fixed to the first heat transfer tubes 31 a of the first heat transfer section 31
  • the valleys of the fins 33 are fixed to the second heat transfer tubes 32 a of the second heat transfer section 32 .
  • heat blocking mechanism 40 is gap 43 .
  • the fins 33 are not arranged in the gaps 43 .
  • the heat blocking mechanism 40 is provided between the first heat transfer section 31 and the second heat transfer section 32 . Therefore, the heat transfer mechanism 40 can suppress heat transfer between the first heat transfer section 31 and the second heat transfer section 32 . As a result, it is possible to suppress the heat exchange loss between the refrigerants caused by the folding back of the first heat transfer section 31 and the second heat transfer section 32 due to the temperature gradient in the gas-liquid two-phase region of the non-azeotropic refrigerant mixture.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Échangeur de chaleur (HE) comprenant : une première partie de transmission de chaleur (31a) qui comprend une pluralité de premiers tuyaux de transmission de chaleur (31) ; une seconde partie de transmission de chaleur (32a) qui comprend une pluralité de seconds tuyaux de transmission de chaleur (32) ; et un fluide frigorigène de mélange non azéotrope qui s'écoule dans la pluralité de premiers tuyaux de transmission de chaleur (31a) de la première partie de transmission de chaleur (31) et la pluralité de seconds tuyaux de transmission de chaleur (32a) de la partie de transmission de chaleur (32). La pluralité de premiers tuyaux de transmission de chaleur (31a) de la première partie de transmission de chaleur (31) et la pluralité de seconds tuyaux de transmission de chaleur (32a) de la partie de transmission de chaleur (32) sont agencés sur une seule rangée. La première partie de transmission de chaleur (31) et la seconde partie de transmission de chaleur (32) sont configurées de telle sorte que le fluide frigorigène de mélange non azéotrope s'écoule de façon à ne refluer qu'une fois de la première partie de transmission de chaleur (31) vers la seconde partie de transmission de chaleur (32).
PCT/JP2021/025605 2021-07-07 2021-07-07 Échangeur de chaleur et dispositif à cycle de réfrigération WO2023281655A1 (fr)

Priority Applications (4)

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JP2023532946A JPWO2023281655A1 (fr) 2021-07-07 2021-07-07
EP21949289.9A EP4368919A1 (fr) 2021-07-07 2021-07-07 Échangeur de chaleur et dispositif à cycle de réfrigération
PCT/JP2021/025605 WO2023281655A1 (fr) 2021-07-07 2021-07-07 Échangeur de chaleur et dispositif à cycle de réfrigération
CN202180100083.XA CN117581075A (zh) 2021-07-07 2021-07-07 热交换器以及制冷循环装置

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PCT/JP2021/025605 WO2023281655A1 (fr) 2021-07-07 2021-07-07 Échangeur de chaleur et dispositif à cycle de réfrigération

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Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0712782U (ja) * 1993-07-29 1995-03-03 株式会社ゼクセル 熱交換器
JPH109713A (ja) * 1996-06-24 1998-01-16 Denso Corp 冷媒凝縮装置、および冷媒凝縮器
JP2001050685A (ja) * 1999-08-06 2001-02-23 Sanyo Electric Co Ltd 熱交換器
JP2002228380A (ja) * 2001-02-05 2002-08-14 Matsushita Electric Ind Co Ltd 熱交換器、および冷却装置
JP2014040983A (ja) 2012-08-23 2014-03-06 Daikin Ind Ltd 空気調和装置の熱交換器
JP2014137165A (ja) * 2013-01-16 2014-07-28 Sharp Corp 空気調和機
JP2018119743A (ja) * 2017-01-25 2018-08-02 日立ジョンソンコントロールズ空調株式会社 熱交換器、及び、空気調和機
WO2019043768A1 (fr) * 2017-08-29 2019-03-07 三菱電機株式会社 Condenseur et dispositif de réfrigération muni de celui-ci

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0712782U (ja) * 1993-07-29 1995-03-03 株式会社ゼクセル 熱交換器
JPH109713A (ja) * 1996-06-24 1998-01-16 Denso Corp 冷媒凝縮装置、および冷媒凝縮器
JP2001050685A (ja) * 1999-08-06 2001-02-23 Sanyo Electric Co Ltd 熱交換器
JP2002228380A (ja) * 2001-02-05 2002-08-14 Matsushita Electric Ind Co Ltd 熱交換器、および冷却装置
JP2014040983A (ja) 2012-08-23 2014-03-06 Daikin Ind Ltd 空気調和装置の熱交換器
JP2014137165A (ja) * 2013-01-16 2014-07-28 Sharp Corp 空気調和機
JP2018119743A (ja) * 2017-01-25 2018-08-02 日立ジョンソンコントロールズ空調株式会社 熱交換器、及び、空気調和機
WO2019043768A1 (fr) * 2017-08-29 2019-03-07 三菱電機株式会社 Condenseur et dispositif de réfrigération muni de celui-ci

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CN117581075A (zh) 2024-02-20
JPWO2023281655A1 (fr) 2023-01-12

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