WO2023188386A1 - Heat exchanger and air conditioner - Google Patents

Heat exchanger and air conditioner Download PDF

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Publication number
WO2023188386A1
WO2023188386A1 PCT/JP2022/016866 JP2022016866W WO2023188386A1 WO 2023188386 A1 WO2023188386 A1 WO 2023188386A1 JP 2022016866 W JP2022016866 W JP 2022016866W WO 2023188386 A1 WO2023188386 A1 WO 2023188386A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
paths
heat exchange
refrigerant
pipe
Prior art date
Application number
PCT/JP2022/016866
Other languages
French (fr)
Japanese (ja)
Inventor
拓也 松田
勇太 佐藤
敦 森田
Original Assignee
三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2022/016866 priority Critical patent/WO2023188386A1/en
Publication of WO2023188386A1 publication Critical patent/WO2023188386A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators

Definitions

  • the present disclosure relates to a heat exchanger and an air conditioner.
  • the performance of the heat exchanger is improved by optimizing the flow rate of refrigerant in the heat transfer tubes and optimizing the balance between pressure loss and heat transfer coefficient on the refrigerant side. .
  • the design takes into consideration the number of refrigerant flow paths.
  • Patent Document 1 describes an air conditioner equipped with a heat exchanger using a three-way tube that straddles a plurality of rows.
  • the low-pressure gas-liquid two-phase refrigerant flows through the three-way pipe in the evaporator, so the refrigerant is distributed vertically within the three-way pipe. This deteriorates evaporator performance because the low-pressure gas-liquid two-phase refrigerant is not evenly distributed.
  • the present disclosure has been made in view of the above problems, and its purpose is to provide a heat exchanger and an air conditioner that can improve evaporator performance.
  • the heat exchanger of the present disclosure includes a first heat exchange section having a plurality of first passes, a second heat exchange section having a plurality of second passes, and a connection between the first heat exchange section and the second heat exchange section. It is equipped with a three-way pipe.
  • the plurality of first paths are arranged in a line.
  • the plurality of second paths are arranged in a line along the direction in which the plurality of first paths are lined up.
  • the three-way tube includes a U-shaped tube that connects the plurality of second paths, and an inflow tube that connects any one of the plurality of first paths to the U-shaped tube.
  • the U-shaped tube has a straight portion connected to each of the plurality of second paths.
  • the inflow pipe is vertically connected to the straight section.
  • the inflow pipe is connected to the straight portion in the vertical direction. Therefore, the evaporator performance can be improved.
  • FIG. 2 is a refrigerant circuit diagram of the air conditioner according to the first embodiment.
  • 1 is a perspective view schematically showing the configuration of a heat exchanger according to Embodiment 1.
  • FIG. 1 is a side view schematically showing the configuration of a heat exchanger according to Embodiment 1.
  • FIG. 1 is a front view, a side view, and a plan view schematically showing the configuration of a three-way tube of a heat exchanger according to Embodiment 1.
  • FIG. FIG. 2 is a front view, a side view, and a plan view schematically showing a bulge-processed portion of a three-way tube of a heat exchanger according to Embodiment 1.
  • FIG. 7 is a front view, a side view, and a plan view schematically showing the configuration of another three-way tube of the heat exchanger according to the first embodiment. It is a graph which shows the relationship between evaporator performance and the height of an inflow pipe.
  • FIG. 3 is a side view schematically showing the configuration of Modification 1 of the heat exchanger according to Embodiment 1.
  • FIG. 3 is a side view schematically showing the configuration of a second modification of the heat exchanger according to the first embodiment.
  • FIG. 3 is a front view schematically showing the configuration of a U-shaped tube of a heat exchanger according to a second embodiment.
  • Embodiment 1 With reference to FIG. 1, the configuration of air conditioner 100 according to Embodiment 1 will be described. Solid arrows in FIG. 1 indicate the flow of refrigerant during cooling operation. Broken arrows in FIG. 1 indicate the flow of refrigerant during heating operation.
  • the air conditioner 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 blower 6, and an indoor blower. 7 and a control device 8.
  • the heat exchanger HE according to the first embodiment is applied to the indoor heat exchanger 5.
  • the air conditioner 100 includes an outdoor unit 101 and an indoor unit 102 connected to the outdoor unit 101.
  • the 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.
  • the 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 refrigerant.
  • the refrigerant is, for example, a non-azeotropic mixed refrigerant. Further, the refrigerant may be a mixed refrigerant containing HFO1123 refrigerant.
  • the compressor 1, four-way valve 2, outdoor heat exchanger 3, expansion valve 4, outdoor blower 6, and control device 8 are housed in the outdoor unit 101.
  • the indoor heat exchanger 5 and the indoor blower 7 are housed in the 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 portion of the pipe 20 constitutes a gas pipe 21 and a liquid pipe 22.
  • the refrigerant circuit 10 is configured such that during cooling operation, refrigerant circulates 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 refrigerant circuit 10 is configured such that during heating operation, the refrigerant circulates 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 compressor 1 is configured to compress refrigerant.
  • the compressor 1 is for compressing the refrigerant flowing into the heat exchanger HE.
  • the compressor 1 is configured to compress the sucked refrigerant and discharge it.
  • the compressor 1 may be configured to have a variable capacity.
  • the compressor 1 may be configured such that the capacity changes by adjusting the rotation speed of the compressor 1 based on instructions from the control device 8.
  • the four-way valve 2 is configured to switch the flow of the 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.
  • the 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.
  • the fourth port P4 is connected to the indoor heat exchanger 5.
  • the four-way valve 2 is configured to allow the refrigerant discharged from the compressor 1 to flow into the outdoor heat exchanger 3 during cooling operation.
  • the first port P1 of the four-way valve 2 is connected to the third port P3, and the second port P2 is connected to the fourth port P4. Furthermore, the four-way valve 2 is configured to allow the refrigerant discharged from the compressor 1 to flow into the indoor heat exchanger 5 during heating operation. During heating operation, in the four-way valve 2, the first port P1 is connected to the fourth port P4, and the second port P2 is connected to the third port P3.
  • the outdoor heat exchanger 3 is configured to perform heat exchange 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.
  • the expansion valve 4 is, for example, an electromagnetic expansion valve.
  • the indoor heat exchanger 5 is configured to perform heat exchange 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 to evaporate refrigerant during cooling operation, and to function as a condenser to condense refrigerant during heating operation.
  • the outdoor blower 6 is configured to blow outdoor air to the outdoor heat exchanger 3. That is, the outdoor blower 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 blower 7 is configured to supply air to the indoor heat exchanger 5.
  • the control device 8 is configured to control each device of the air conditioner 100 by performing calculations, instructions, etc.
  • 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 their operations.
  • the configuration of the heat exchanger HE according to the first embodiment will be described in detail with reference to FIGS. 2 to 6.
  • the heat exchanger HE according to the first embodiment is applied to the indoor heat exchanger 5.
  • Note that the heat exchanger HE according to the first embodiment may be applied to the outdoor heat exchanger 3.
  • the heat exchanger HE includes a first heat exchange section HP1, a second heat exchange section HP2, and a three-way tube TP.
  • the heat exchanger HE further includes a third heat exchange section HP3 and a plurality of connecting pipes CP.
  • the air flow direction D1, the width direction D2, and the step direction D3 are shown by solid arrows.
  • the air flow direction D1, the width direction D2, and the step direction D3 are orthogonal to each other.
  • the white arrows in FIGS. 2 and 3 indicate the air flow direction D1.
  • the air flow direction D1 corresponds to the row direction in which the first heat exchange part HP1, the second heat exchange part HP2, and the third heat exchange part HP3 are arranged.
  • the first heat exchange part HP1 is arranged on the windward side in the air flow direction D1.
  • the first heat exchange parts HP1 are arranged in a first row in the air flow direction D1.
  • the second heat exchange section HP2 is arranged adjacent to the first heat exchange section HP1 in the air flow direction D1.
  • the second heat exchange part HP2 is arranged on the leeward side of the first heat exchange part HP1 in the air flow direction D1.
  • the second heat exchange portion HP2 is arranged in the second row in the air flow direction D1.
  • the third heat exchange section HP3 is arranged adjacent to the second heat exchange section HP2 in the air flow direction D1.
  • the third heat exchange part HP3 is arranged on the leeward side of the second heat exchange part HP2 in the air flow direction D1.
  • the third heat exchange portion HP3 is arranged in the third row in the air flow direction D1.
  • the first heat exchange section HP1 has a plurality of first paths PT1. Each of the plurality of first paths PT1 extends in the width direction D2. Each of the plurality of first paths PT1 extends linearly. The plurality of first paths PT1 are arranged in a line. The plurality of first paths PT1 are arranged at intervals in the step direction D3. In this embodiment, the first heat exchange section HP1 has four first paths PT1, but the number of first paths PT1 is not limited.
  • the first heat exchange part HP1 includes a plurality of first fins F1 and a plurality of first connection parts C1.
  • Each of the plurality of first fins F1 is configured in a plate shape.
  • the plurality of first fins F1 are arranged so as to overlap each other.
  • Each of the plurality of first paths PT1 passes through the plurality of first fins F1 in the width direction D2.
  • the plurality of first connecting portions C1 connect the first paths PT1 to each other on the outside of the plurality of first fins F1.
  • Each of the plurality of first paths PT1 is connected by each of the plurality of first connection parts C1, so that the plurality of first paths PT1 and the plurality of first connection parts C1 are configured to meander as a whole.
  • the material of the plurality of first paths PT1, the plurality of first fins F1, and the plurality of first connection parts C1 is, for example, aluminum.
  • the second heat exchange section HP2 has a plurality of second paths PT2. Each of the plurality of second paths PT2 extends in the width direction D2. Each of the plurality of second paths PT2 extends linearly. The plurality of second paths PT2 are arranged in a line along the direction in which the plurality of first paths PT1 are lined up. The plurality of second paths PT2 are lined up at intervals in the step direction D3. In this embodiment, the second heat exchange section HP2 has four second paths PT2, but the number of second paths PT2 is not limited.
  • the second heat exchange part HP2 includes a plurality of second fins F2 and a plurality of second connection parts C2.
  • Each of the plurality of second fins F2 is configured in a plate shape.
  • the plurality of second fins F2 are arranged so as to overlap each other.
  • Each of the plurality of second paths PT2 passes through the plurality of second fins F2 in the width direction D2.
  • the plurality of second connecting portions C2 connect the second paths PT2 to each other on the outside of the plurality of second fins F2.
  • Each of the plurality of second paths PT2 is connected by each of the plurality of second connection parts C2, so that the plurality of second paths PT2 and the plurality of second connection parts C2 are configured to be folded back in the width direction D2.
  • the material of the plurality of second paths PT2, the plurality of second fins F2, and the plurality of second connection parts C2 is, for example, aluminum.
  • the third heat exchange section HP3 has a plurality of third paths PT3. Each of the plurality of third paths PT3 extends in the width direction D2. Each of the plurality of third paths PT3 extends linearly. The plurality of third paths PT3 are arranged in a line along the direction in which the first paths PT1 are lined up. The plurality of third paths PT3 are arranged at intervals in the step direction D3. In this embodiment, the third heat exchange section HP3 has four third paths PT3, but the number of third paths PT23 is not limited.
  • the third heat exchange part HP3 includes a plurality of third fins F3 and a plurality of third connection parts C3.
  • Each of the plurality of third fins F3 is configured in a plate shape.
  • the plurality of third fins F3 are arranged so as to overlap each other.
  • Each of the plurality of third paths PT3 passes through the plurality of third fins F3 in the width direction D2.
  • the plurality of third connecting portions C3 connect the third paths PT3 to each other on the outside of the plurality of third fins F3.
  • Each of the plurality of third paths PT3 is connected by each of the plurality of third connection parts C3, so that the plurality of third paths PT3 and the plurality of third connection parts C3 are configured to be folded back in the width direction D2.
  • the material of the plurality of third paths PT3, the plurality of third fins F3, and the plurality of third connection parts C3 is, for example, aluminum.
  • the three-way pipe TP connects the first heat exchange part HP1 and the second heat exchange part HP2.
  • the three-way pipe TP connects one of the plurality of first paths PT1 and two of the plurality of second paths PT2.
  • the first path PT1 of the first stage and the second path PT2 of the second and third stages are connected by a three-way pipe TP.
  • the plurality of connecting pipes CP connect the second heat exchange section HP2 and the third heat exchange section HP3.
  • the plurality of connecting pipes CP connect one of the plurality of second paths PT2 and one of the plurality of third paths PT3.
  • the second path PT2 of the first stage and the third path PT3 of the first stage are connected by one connecting pipe (first connecting pipe) CP
  • the second path PT2 of the first stage is connected by one connecting pipe (first connecting pipe) CP.
  • the second path PT2 and the fourth stage third path PT3 are connected by the other connecting pipe (second connecting pipe) CP.
  • the three-way pipe TP includes a U-shaped pipe T1 and an inflow pipe T2.
  • the U-shaped tube T1 connects the plurality of second paths PT2.
  • the U-shaped tube T1 connects adjacent second paths PT in the step direction D3 among the plurality of second paths PT.
  • the inflow pipe T2 connects any one of the plurality of first paths PT1 to the U-shaped pipe T1.
  • the U-shaped tube T1 has a straight portion T11 and a bent portion T12.
  • the straight portion T11 is connected to each of the plurality of second paths PT2. In this embodiment, the straight portion T11 extends in the horizontal direction.
  • the curved portion T12 connects the straight portion T11.
  • the inflow pipe T2 is vertically connected to the straight portion T11. In this embodiment, the inflow pipe T2 is connected to the straight portion T11 from above in the vertical direction.
  • the inflow pipe T2 has a first folded part T21, a first extended part T22, a second folded part T23, and a second extended part T24.
  • the first folded portion T21 is connected to the straight portion T11.
  • the first folded portion T21 is connected to the straight portion T11 at an angle of 90°.
  • the first folded portion T21 is folded back so as to rise in the vertical direction and then fall.
  • the first folded portion T21 straddles the first heat exchange portion HP1 and the second heat exchange portion HP2 in the column direction when viewed from the width direction D2.
  • the first extending portion T22 is connected to the first folded portion T21.
  • the first extending portion T22 extends in the vertical direction.
  • the first extending portion T22 extends linearly.
  • the length of the first extending portion T22 in the vertical direction is longer than the length of the second stage of the second path PT2.
  • the second folded portion T23 is connected to the first extended portion T22.
  • the second folded portion T23 is folded back so as to fall down in the vertical direction and then rise.
  • the second folded portion T23 straddles the first heat exchange portion HP1 and the second heat exchange portion HP2 in the column direction when viewed from the width direction.
  • the second extending portion T24 is connected to the second folded portion T23.
  • the second extending portion T24 extends in the width direction D2.
  • the second extending portion T24 extends linearly.
  • the second extending portion T24 is connected to the first path PT1.
  • the three-way pipe TP may be provided with a bulge-processed portion BP at the connection portion between the U-shaped pipe T1 and the inflow pipe T2.
  • the U-shaped tube T1 and the inflow tube T2 are connected via the bulge processed portion BP.
  • the inflow pipe T2 is not shown in FIG. 5 for convenience of explanation.
  • the inflow pipe T2 may be connected to the straight portion T11 from below in the vertical direction.
  • the inflow pipe T2 has a rising portion T25 and a lower extending portion T26.
  • the rising portion T25 is connected to the straight portion T11.
  • the rising portion T25 is connected to the straight portion T11 at an angle of 90°.
  • the lower extending portion T26 is connected to the rising portion T25.
  • the lower extending portion T26 extends in the width direction D2.
  • the lower extending portion T26 extends linearly.
  • the lower extending portion T26 is connected to the first path PT1.
  • the air conditioner 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 blower 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.
  • refrigerant circulates through the refrigerant circuit 10 in the order of the compressor 1, four-way valve 2, indoor heat exchanger 5, expansion valve 4, outdoor heat exchanger 3, and 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 blower 6.
  • the indoor heat exchanger 5 functions as an evaporator.
  • the low-pressure gas-liquid two-phase refrigerant whose pressure has been reduced by the expansion valve 4 flows into the first path PT1 of the first heat exchange section HP1 in the first row.
  • the low-pressure gas-liquid two-phase refrigerant is evaporated in the first heat exchange part HP1 until the degree of dryness is, for example, 0.3 or more and 0.4 or less.
  • the low-pressure gas-liquid two-phase refrigerant flows into the three-way pipe TP from the first heat exchange section HP1.
  • the flow rate of the low-pressure gas-liquid two-phase refrigerant is evenly distributed in the three-way pipe TP, and flows into the second path PT2 of the second heat exchange section HP2 in the second row.
  • the low-pressure gas-liquid two-phase refrigerant is further evaporated in the second heat exchange section HP2.
  • the low-pressure gas-liquid two-phase refrigerant flows from the second heat exchange section HP2 through the connecting pipe CP and into the third path PT3 of the third heat exchange section HP3 in the third row.
  • the low-pressure gas-liquid two-phase refrigerant is further evaporated in the third heat exchange section HP3.
  • the coolant flow direction is parallel to the air flow direction D1.
  • the non-azeotropic mixed refrigerant flows inside the plurality of first paths PT1, the plurality of second paths PT2, and the three-way pipe TP.
  • the indoor heat exchanger 5 functions as a condenser.
  • the high-pressure gas refrigerant discharged from the compressor 1 passes through the four-way valve 2 and flows into the third path PT3 of the third heat exchange section HP3 in the third row.
  • the high pressure gas refrigerant is condensed in the third heat exchange section HP3.
  • the high-pressure gas refrigerant flows from the third heat exchange section HP3 through the connecting pipe CP and into the second path PT2 of the second heat exchange section HP2 in the second row.
  • the high-pressure gas refrigerant is condensed in the second heat exchange section HP2 until its dryness reaches zero.
  • the liquid or low-dryness high-pressure refrigerant is combined in the three-way pipe TP, the flow rate of which is doubled, and flows into the first path PT1 of the first heat exchange section HP1 in the first row.
  • the liquid or low dryness high pressure refrigerant is further condensed in the first heat exchange section HP1.
  • the refrigerant flow direction is opposite to the air flow direction D1.
  • FIG. 7 is a graph showing the relationship between the evaporator performance and the height H of the inflow pipe T2 (see FIG. 4).
  • the measurement conditions are as follows.
  • the air temperature is 7° C. dry bulb and 6° C. wet bulb.
  • the wind speed is 1.5 m/s.
  • the refrigerant is R32.
  • the refrigerant circulation amount is 10 kg/h.
  • the inlet enthalpy is 245.6 kJ/kg.
  • the degree of superheat at the heat exchanger outlet is 1K.
  • the object to be measured is a 3-row, 4-stage, stacked length of 300 mm, 2-pass heat exchanger.
  • the height of the inflow pipe T2 is used as a parameter.
  • the height H of the inflow pipe T2 is preferably at least 10 times the inner diameter D of the straight portion T11. If the height H of the inflow pipe T2 is at least 10 times the inner diameter D of the straight portion T11 (10D), the evaporator performance will be 95% or more. Evaporator performance is based on the case where there is no effect due to deterioration of refrigerant distribution. Further, it is more preferable that the height H of the inflow pipe T2 is at least 50 times the inner diameter D of the straight portion T11. If the height H of the inflow pipe T2 is at least 50 times the inner diameter D of the straight portion T11 (50D), the evaporator performance will be approximately 100%.
  • the inflow pipe T2 is connected to the straight portion T11 in the vertical direction. Therefore, when the heat exchanger HE functions as an evaporator, the gas-liquid two-phase refrigerant flowing from the inflow pipe T2 is distributed along the straight portion T11. Further, the length of the inflow pipe T2 in the vertical direction can be made longer than when the inflow pipe T2 is connected to the straight portion T11 in the horizontal direction. Thereby, drifting of the gas-liquid two-phase refrigerant can be suppressed. Therefore, the gas-liquid two-phase refrigerant can be evenly distributed. Therefore, evaporator performance can be improved.
  • the straight portion T11 extends in the horizontal direction. Therefore, the refrigerant flowing in from the inflow pipe T2 is distributed along the horizontal direction. Therefore, the gas-liquid two-phase refrigerant can be distributed more evenly.
  • the heat exchanger HE when the heat exchanger HE functions as a condenser, the number of channels in the liquid phase portion can be reduced. Therefore, the condenser performance can be improved.
  • the height of the inflow pipe T2 is at least 10 times the inner diameter of the straight portion T11. Therefore, the evaporator performance can be improved.
  • the non-azeotropic mixed refrigerant flows inside the plurality of first paths PT1, the plurality of second paths PT2, and the three-way pipe TP. Therefore, when the liquid side is arranged on the windward side where frost formation is likely to occur, the temperature gradient of the non-azeotropic mixed refrigerant on the liquid side becomes small. Therefore, a decrease in the evaporation temperature of the non-azeotropic refrigerant mixture can be suppressed.
  • the air conditioner 100 according to the first embodiment includes the heat exchanger HE described above. Therefore, it is possible to provide the air conditioner 100 including the heat exchanger HE that can improve the evaporator performance.
  • the inflow pipe T2 of the three-way pipe TP is longer in the vertical direction than in the present embodiment shown in FIG. There is. Specifically, the length in the vertical direction of the first extending portion T22 of the inflow pipe T2 is longer than the length of the four stages of the second path PT2.
  • the vertical length of the first extending portion T22 of the inflow pipe T2 is longer, so that the uneven flow of the gas-liquid two-phase refrigerant is further reduced. Can be suppressed.
  • the heat exchanger HE has a first heat exchange part HP1 and a second heat exchange part HP2; 3 does not have heat exchange section HP3. That is, the heat exchanger HE is composed of two rows of heat exchange sections.
  • the heat exchanger HE can be configured with two rows of heat exchange sections.
  • Embodiment 2 The heat exchanger HE according to the second embodiment has the same configuration, operation, and effect as the heat exchanger HE according to the first embodiment, unless otherwise specified.
  • the bent portion T12 has a fracture-inducing structure FP.
  • the fracture guiding structure FP is configured to have a lower withstand voltage than other parts of the bent portion T12.
  • the refrigerant is a mixed refrigerant containing HFO1123 refrigerant.
  • the fracture guiding structure FP has a notch structure having a notch. This notch is formed on the outer periphery of the bent portion T12, for example, over the entire periphery.
  • the bent portion T12 has the fracture-inducing structure FP. Therefore, when the pressure on the high-pressure side of the mixed refrigerant containing the HFO1123 refrigerant increases abnormally, the fracture induction structure FP ruptures, so that the HFO1123 refrigerant can be discharged to the outside of the pipe. Therefore, the pressure in the refrigerant circuit 10 can be released. Therefore, it is possible to prevent the disproportionation reaction of the HFO1123 refrigerant from diffusing as a chain reaction, thereby preventing an explosion due to the disproportionation reaction.
  • 1 Compressor 2 Four-way valve, 3 Outdoor heat exchanger, 4 Expansion valve, 5 Indoor heat exchanger, 100 Air conditioner, FP rupture induction structure, HE Heat exchanger, HP1 First heat exchange section, HP2 Second heat Exchange section, HP3 third heat exchange section, PT1 first pass, PT2 second pass, PT3 third pass, T1 U-shaped tube, T2 inflow tube, T11 straight section, T12 bent section, TP three-way tube.

Abstract

This heat exchanger (HE) comprises a first heat exchange part (HP1) that has a plurality of first paths (PT1), a second heat exchange part (HP2) that has a plurality of second paths (PT2), and a three-way pipe (TP) that connects the first heat exchange part (HP1) and the second heat exchange part (HP2). The plurality of first paths (PT1) are disposed side by side in a row. The plurality of second paths (PT2) are disposed side by side in a row in the direction that the plurality of first paths (PT1) are aligned. The three-way pipe (TP) has a U-shaped pipe (T1) that connects the plurality of second paths (PT2) to each other, and an inflow pipe (T2) that connects any of the plurality of first paths (PT1) and the U-shaped pipe (T1). The U-shaped pipe (T1) has straight sections (T11) that are respectively connected to the plurality of second paths (PT2). The inflow pipe (T2) is connected vertically to the straight sections (T11).

Description

熱交換器および空気調和機Heat exchangers and air conditioners
　本開示は熱交換器および空気調和機に関するものである。 The present disclosure relates to a heat exchanger and an air conditioner.
　空気調和機の熱交換器においては、伝熱管内の冷媒流速を最適化することで、冷媒側の圧力損失と熱伝達率のバランスを適正化させることにより、熱交換器の性能を高めている。このため、冷媒流路数を考慮した設計が行われている。 In the heat exchanger of an air conditioner, the performance of the heat exchanger is improved by optimizing the flow rate of refrigerant in the heat transfer tubes and optimizing the balance between pressure loss and heat transfer coefficient on the refrigerant side. . For this reason, the design takes into consideration the number of refrigerant flow paths.
　たとえば、特許第６１８０３３８号公報（特許文献１）には、複数列の列間をまたぐ３方管を用いた熱交換器を備えた空気調和機が記載されている。 For example, Japanese Patent No. 6180338 (Patent Document 1) describes an air conditioner equipped with a heat exchanger using a three-way tube that straddles a plurality of rows.
特許第６１８０３３８号公報Patent No. 6180338
　しかしながら、列間をまたぐ３方管では、蒸発器において低圧気液二相冷媒が３方管内を流れるため、３方管内で冷媒が上下方向に分配される。これにより、低圧気液二相冷媒が均等に分配されないため、蒸発器性能が悪化する。 However, in the three-way pipe that straddles the rows, the low-pressure gas-liquid two-phase refrigerant flows through the three-way pipe in the evaporator, so the refrigerant is distributed vertically within the three-way pipe. This deteriorates evaporator performance because the low-pressure gas-liquid two-phase refrigerant is not evenly distributed.
　本開示は上記課題に鑑みてなされたものであり、その目的は、蒸発器性能を向上させることができる熱交換器および空気調和機を提供することである。 The present disclosure has been made in view of the above problems, and its purpose is to provide a heat exchanger and an air conditioner that can improve evaporator performance.
　本開示の熱交換器は、複数の第１パスを有する第１熱交換部と、複数の第２パスを有する第２熱交換部と、第１熱交換部と第２熱交換部とを接続する３方管とを備えている。複数の第１パスは、一列に並んで配置されている。複数の第２パスは、複数の第１パスが並ぶ方向に沿って一列に並んで配置されている。３方管は、複数の第２パス同士を接続するＵ字管と、複数の第１パスのいずれかとＵ字管とを接続する流入管とを有している。Ｕ字管は、複数の第２パスの各々に接続された直線部を有している。流入管は、直線部に鉛直方向に接続されている。 The heat exchanger of the present disclosure includes a first heat exchange section having a plurality of first passes, a second heat exchange section having a plurality of second passes, and a connection between the first heat exchange section and the second heat exchange section. It is equipped with a three-way pipe. The plurality of first paths are arranged in a line. The plurality of second paths are arranged in a line along the direction in which the plurality of first paths are lined up. The three-way tube includes a U-shaped tube that connects the plurality of second paths, and an inflow tube that connects any one of the plurality of first paths to the U-shaped tube. The U-shaped tube has a straight portion connected to each of the plurality of second paths. The inflow pipe is vertically connected to the straight section.
　本開示の熱交換器よれば、流入管は、直線部に鉛直方向に接続されている。このため、蒸発器性能を向上させることができる。 According to the heat exchanger of the present disclosure, the inflow pipe is connected to the straight portion in the vertical direction. Therefore, the evaporator performance can be improved.
実施の形態１に係る空気調和機の冷媒回路図である。FIG. 2 is a refrigerant circuit diagram of the air conditioner according to the first embodiment. 実施の形態１に係る熱交換器の構成を概略的に示す斜視図である。1 is a perspective view schematically showing the configuration of a heat exchanger according to Embodiment 1. FIG. 実施の形態１に係る熱交換器の構成を概略的に示す側面図である。1 is a side view schematically showing the configuration of a heat exchanger according to Embodiment 1. FIG. 実施の形態１に係る熱交換器の３方管の構成を概略的に示す正面図、側面図、平面図である。1 is a front view, a side view, and a plan view schematically showing the configuration of a three-way tube of a heat exchanger according to Embodiment 1. FIG. 実施の形態１に係る熱交換器の３方管のバルジ加工部を概略的に示す正面図、側面図、平面図である。FIG. 2 is a front view, a side view, and a plan view schematically showing a bulge-processed portion of a three-way tube of a heat exchanger according to Embodiment 1. FIG. 実施の形態１に係る熱交換器の他の３方管の構成を概略的に示す正面図、側面図、平面図である。FIG. 7 is a front view, a side view, and a plan view schematically showing the configuration of another three-way tube of the heat exchanger according to the first embodiment. 蒸発器性能と流入管の高さとの関係を示すグラフである。It is a graph which shows the relationship between evaporator performance and the height of an inflow pipe. 実施の形態１に係る熱交換器の変形例１の構成を概略的に示す側面図である。FIG. 3 is a side view schematically showing the configuration of Modification 1 of the heat exchanger according to Embodiment 1. FIG. 実施の形態１に係る熱交換器の変形例２の構成を概略的に示す側面図である。FIG. 3 is a side view schematically showing the configuration of a second modification of the heat exchanger according to the first embodiment. 実施の形態２に係る熱交換器のＵ字管の構成を概略的に示す正面図である。FIG. 3 is a front view schematically showing the configuration of a U-shaped tube of a heat exchanger according to a second embodiment.
　以下、図面を参照して、実施の形態について説明する。なお、図中において、同一または相当する部分には同一の符号を付してその説明は繰り返さない。 Hereinafter, embodiments will be described with reference to the drawings. In addition, in the drawings, the same or corresponding parts are given the same reference numerals, and the description thereof will not be repeated.
　実施の形態１．
　図１を参照して、実施の形態１に係る空気調和機１００の構成について説明する。図１中実線矢印は、冷房運転時における冷媒の流れを示している。図１中破線矢印は、暖房運転時における冷媒の流れを示している。 Embodiment 1.
With reference to FIG. 1, the configuration of air conditioner 100 according to Embodiment 1 will be described. Solid arrows in FIG. 1 indicate the flow of refrigerant during cooling operation. Broken arrows in FIG. 1 indicate the flow of refrigerant during heating operation.
　図１に示されるように、空気調和機１００は、圧縮機１と、四方弁２と、室外熱交換器３と、膨張弁４と、室内熱交換器５と、室外送風機６と、室内送風機７と、制御装置８とを備えている。実施の形態１に係る熱交換器ＨＥは、室内熱交換器５に適用されている。空気調和機１００は、室外機１０１と、室外機１０１に接続された室内機１０２とを備えている。 As shown in FIG. 1, the air conditioner 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 blower 6, and an indoor blower. 7 and a control device 8. The heat exchanger HE according to the first embodiment is applied to the indoor heat exchanger 5. The air conditioner 100 includes an outdoor unit 101 and an indoor unit 102 connected to the outdoor unit 101.
　冷媒回路１０は、圧縮機１、四方弁２、室外熱交換器３、膨張弁４および室内熱交換器５を含んでいる。圧縮機１、四方弁２、室外熱交換器３、膨張弁４および室内熱交換器５は、配管２０によって接続されている。冷媒回路１０は、冷媒を循環させるように構成されている。 The 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. The 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 refrigerant.
　冷媒は、例えば、非共沸混合冷媒である。また、冷媒は、ＨＦＯ１１２３冷媒を含む混合冷媒であってもよい。 The refrigerant is, for example, a non-azeotropic mixed refrigerant. Further, the refrigerant may be a mixed refrigerant containing HFO1123 refrigerant.
　圧縮機１、四方弁２、室外熱交換器３、膨張弁４、室外送風機６および制御装置８は、室外機１０１に収容されている。室内熱交換器５および室内送風機７は、室内機１０２に収容されている。室外機１０１と室内機１０２とは、ガス管２１と液管２２とにより接続されている。配管２０の一部がガス管２１および液管２２を構成している。 The compressor 1, four-way valve 2, outdoor heat exchanger 3, expansion valve 4, outdoor blower 6, and control device 8 are housed in the outdoor unit 101. The indoor heat exchanger 5 and the indoor blower 7 are housed in the 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 portion of the pipe 20 constitutes a gas pipe 21 and a liquid pipe 22.
　冷媒回路１０は、冷房運転時には、圧縮機１、四方弁２、室外熱交換器３、膨張弁４、室内熱交換器５、四方弁２の順に冷媒が循環するように構成されている。また、冷媒回路１０は、暖房運転時には、圧縮機１、四方弁２、室内熱交換器５、膨張弁４、室外熱交換器３、四方弁２の順に冷媒が循環するように構成されている。 The refrigerant circuit 10 is configured such that during cooling operation, refrigerant circulates 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 refrigerant circuit 10 is configured such that during heating operation, the refrigerant circulates 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. .
　圧縮機１は、冷媒を圧縮するように構成されている。圧縮機１は、熱交換器ＨＥに流入する冷媒を圧縮するためのものである。圧縮機１は、吸入した冷媒を圧縮して吐出するように構成されている。圧縮機１は、容量可変に構成されていてもよい。圧縮機１は、制御装置８からの指示に基づいて圧縮機１の回転数が調整されることにより容量が変化するように構成されていてもよい。 The compressor 1 is configured to compress refrigerant. The compressor 1 is for compressing the refrigerant flowing into the heat exchanger HE. The compressor 1 is configured to compress the sucked refrigerant and discharge it. The compressor 1 may be configured to have a variable capacity. The compressor 1 may be configured such that the capacity changes by adjusting the rotation speed of the compressor 1 based on instructions from the control device 8.
　四方弁２は、圧縮機１により圧縮された冷媒を室外熱交換器３または室内熱交換器５に流すように冷媒の流れを切替えるように構成されている。四方弁２は、第１ポートＰ１～第４ポートＰ４を有している。第１ポートＰ１は、圧縮機１の吐出側に接続されている。第２ポートＰ２は圧縮機１の吸入側に接続されている。第３ポートＰ３は、室外熱交換器３に接続されている。第４ポートＰ４は、室内熱交換器５に接続されている。四方弁２は、冷房運転時には圧縮機１から吐出された冷媒を室外熱交換器３に流すように構成されている。冷房運転時には、四方弁２において第１ポートＰ１に第３ポートＰ３が接続されているとともに第２ポートＰ２に第４ポートＰ４が接続されている。また、四方弁２は、暖房運転時には圧縮機１から吐出された冷媒を室内熱交換器５に流すように構成されている。暖房運転時には、四方弁２において第１ポートＰ１に第４ポートＰ４が接続されているとともに第２ポートＰ２に第３ポートＰ３が接続されている。 The four-way valve 2 is configured to switch the flow of the 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. The 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. The fourth port P4 is connected to the indoor heat exchanger 5. The four-way valve 2 is configured to allow the refrigerant discharged from the compressor 1 to flow into the outdoor heat exchanger 3 during cooling operation. During cooling operation, the first port P1 of the four-way valve 2 is connected to the third port P3, and the second port P2 is connected to the fourth port P4. Furthermore, the four-way valve 2 is configured to allow the refrigerant discharged from the compressor 1 to flow into the indoor heat exchanger 5 during heating operation. During heating operation, in the four-way valve 2, the first port P1 is connected to the fourth port P4, and the second port P2 is connected to the third port P3.
　室外熱交換器３は、室外熱交換器３の内部を流れる冷媒と室外熱交換器３の外部を流れる空気との間で熱交換を行うように構成されている。室外熱交換器３は、冷房運転時には冷媒を凝縮させる凝縮器として機能し、暖房運転時には冷媒を蒸発させる蒸発器として機能するように構成されている。 The outdoor heat exchanger 3 is configured to perform heat exchange 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.
　膨張弁４は、凝縮器で凝縮された冷媒を膨張させることにより減圧させるように構成されている。膨張弁４は、冷房運転時には室外熱交換器３により凝縮された冷媒を減圧させ、暖房運転時には室内熱交換器５により凝縮された冷媒を減圧させるように構成されている。膨張弁４は、たとえば、電磁膨張弁である。 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. The expansion valve 4 is, for example, an electromagnetic expansion valve.
　室内熱交換器５は、室内熱交換器５の内部を流れる冷媒と室内熱交換器５の外部を流れる空気との間で熱交換を行うように構成されている。室内熱交換器５は、冷房運転時には冷媒を蒸発させる蒸発器として機能し、暖房運転時には冷媒を凝縮させる凝縮器として機能するように構成されている。 The indoor heat exchanger 5 is configured to perform heat exchange 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 to evaporate refrigerant during cooling operation, and to function as a condenser to condense refrigerant during heating operation.
　室外送風機６は、室外熱交換器３に室外の空気を送風するように構成されている。つまり、室外送風機６は、室外熱交換器３に対して空気を供給するように構成されている。 The outdoor blower 6 is configured to blow outdoor air to the outdoor heat exchanger 3. That is, the outdoor blower 6 is configured to supply air to the outdoor heat exchanger 3.
　室内送風機７は、室内熱交換器５に室内の空気を送風するように構成されている。つまり、室内送風機７は、室内熱交換器５に対して空気を供給するように構成されている。 The indoor blower 7 is configured to blow indoor air to the indoor heat exchanger 5. That is, the indoor blower 7 is configured to supply air to the indoor heat exchanger 5.
　制御装置８は、演算、指示等を行って空気調和機１００の各機器等を制御するように構成されている。制御装置８は、圧縮機１、四方弁２、膨張弁４、室外送風機６、室内送風機７などに電気的に接続されており、これらの動作を制御するように構成されている。 The control device 8 is configured to control each device of the air conditioner 100 by performing calculations, instructions, etc. 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 their operations.
　図２～図６を参照して、実施の形態１に係る熱交換器ＨＥの構成について詳しく説明する。実施の形態１に係る熱交換器ＨＥは、室内熱交換器５に適用される。なお、実施の形態１に係る熱交換器ＨＥは、室外熱交換器３に適用されてもよい。 The configuration of the heat exchanger HE according to the first embodiment will be described in detail with reference to FIGS. 2 to 6. The heat exchanger HE according to the first embodiment is applied to the indoor heat exchanger 5. Note that the heat exchanger HE according to the first embodiment may be applied to the outdoor heat exchanger 3.
　図２および図３に示されるように、熱交換器ＨＥは、第１熱交換部ＨＰ１と、第２熱交換部ＨＰ２と、３方管ＴＰとを備えている。本実施の形態では、熱交換器ＨＥは、第３熱交換部ＨＰ３と、複数の接続管ＣＰとをさらに備えている。 As shown in FIGS. 2 and 3, the heat exchanger HE includes a first heat exchange section HP1, a second heat exchange section HP2, and a three-way tube TP. In this embodiment, the heat exchanger HE further includes a third heat exchange section HP3 and a plurality of connecting pipes CP.
　図２には空気流れ方向Ｄ１、幅方向Ｄ２および段方向Ｄ３が実線矢印で示されている。本実施の形態では、空気流れ方向Ｄ１、幅方向Ｄ２および段方向Ｄ３は互いに直交している。図２および図３中白抜き矢印は空気流れ方向Ｄ１を示している。空気流れ方向Ｄ１は、第１熱交換部ＨＰ１、第２熱交換部ＨＰ２および第３熱交換部ＨＰ３が配置された列方向に一致している。 In FIG. 2, the air flow direction D1, the width direction D2, and the step direction D3 are shown by solid arrows. In this embodiment, the air flow direction D1, the width direction D2, and the step direction D3 are orthogonal to each other. The white arrows in FIGS. 2 and 3 indicate the air flow direction D1. The air flow direction D1 corresponds to the row direction in which the first heat exchange part HP1, the second heat exchange part HP2, and the third heat exchange part HP3 are arranged.
　第１熱交換部ＨＰ１は、空気流れ方向Ｄ１において風上側に配置されている。第１熱交換部ＨＰ１は、空気流れ方向Ｄ１において第１列に配置されている。第２熱交換部ＨＰ２は、空気流れ方向Ｄ１において第１熱交換部ＨＰ１と隣り合うように配置されている。第２熱交換部ＨＰ２は、空気流れ方向Ｄ１において第１熱交換部ＨＰ１よりも風下側に配置されている。第２熱交換部ＨＰ２は、空気流れ方向Ｄ１において第２列に配置されている。第３熱交換部ＨＰ３は、空気流れ方向Ｄ１において第２熱交換部ＨＰ２と隣り合うように配置されている。第３熱交換部ＨＰ３は、空気流れ方向Ｄ１において第２熱交換部ＨＰ２よりも風下側に配置されている。第３熱交換部ＨＰ３は、空気流れ方向Ｄ１において第３列に配置されている。 The first heat exchange part HP1 is arranged on the windward side in the air flow direction D1. The first heat exchange parts HP1 are arranged in a first row in the air flow direction D1. The second heat exchange section HP2 is arranged adjacent to the first heat exchange section HP1 in the air flow direction D1. The second heat exchange part HP2 is arranged on the leeward side of the first heat exchange part HP1 in the air flow direction D1. The second heat exchange portion HP2 is arranged in the second row in the air flow direction D1. The third heat exchange section HP3 is arranged adjacent to the second heat exchange section HP2 in the air flow direction D1. The third heat exchange part HP3 is arranged on the leeward side of the second heat exchange part HP2 in the air flow direction D1. The third heat exchange portion HP3 is arranged in the third row in the air flow direction D1.
　第１熱交換部ＨＰ１は、複数の第１パスＰＴ１を有している。複数の第１パスＰＴ１の各々は、幅方向Ｄ２に延在している。複数の第１パスＰＴ１の各々は、直線状に延在している。複数の第１パスＰＴ１は、一列に並んで配置されている。複数の第１パスＰＴ１は、段方向Ｄ３に互いに間隔をあけて並んでいる。本実施の形態では、第１熱交換部ＨＰ１は、４つの第１パスＰＴ１を有しているが、第１パスＰＴ１の個数は限定されない。 The first heat exchange section HP1 has a plurality of first paths PT1. Each of the plurality of first paths PT1 extends in the width direction D2. Each of the plurality of first paths PT1 extends linearly. The plurality of first paths PT1 are arranged in a line. The plurality of first paths PT1 are arranged at intervals in the step direction D3. In this embodiment, the first heat exchange section HP1 has four first paths PT1, but the number of first paths PT1 is not limited.
　本実施の形態では、第１熱交換部ＨＰ１は、複数の第１フィンＦ１と、複数の第１接続部Ｃ１とを有している。複数の第１フィンＦ１の各々は板状に構成されている。複数の第１フィンＦ１は互いに重なるように配置されている。複数の第１パスＰＴ１の各々は、複数の第１フィンＦ１を幅方向Ｄ２に貫通している。複数の第１接続部Ｃ１は、複数の第１フィンＦ１の外側で第１パスＰＴ１同士を接続している。複数の第１パスＰＴ１の各々が複数の第１接続部Ｃ１の各々によって接続されることで、複数の第１パスＰＴ１および複数の第１接続部Ｃ１は全体として蛇行するように構成されている。複数の第１パスＰＴ１、複数の第１フィンＦ１および複数の第１接続部Ｃ１の材料は、例えばアルミニウムである。 In this embodiment, the first heat exchange part HP1 includes a plurality of first fins F1 and a plurality of first connection parts C1. Each of the plurality of first fins F1 is configured in a plate shape. The plurality of first fins F1 are arranged so as to overlap each other. Each of the plurality of first paths PT1 passes through the plurality of first fins F1 in the width direction D2. The plurality of first connecting portions C1 connect the first paths PT1 to each other on the outside of the plurality of first fins F1. Each of the plurality of first paths PT1 is connected by each of the plurality of first connection parts C1, so that the plurality of first paths PT1 and the plurality of first connection parts C1 are configured to meander as a whole. . The material of the plurality of first paths PT1, the plurality of first fins F1, and the plurality of first connection parts C1 is, for example, aluminum.
　第２熱交換部ＨＰ２は、複数の第２パスＰＴ２を有している。複数の第２パスＰＴ２の各々は、幅方向Ｄ２に延在している。複数の第２パスＰＴ２の各々は、直線状に延在している。複数の第２パスＰＴ２は、複数の第１パスＰＴ１が並ぶ方向に沿って一列に並んで配置されている。複数の第２パスＰＴ２は、段方向Ｄ３に互いに間隔をあけて並んでいる。本実施の形態では、第２熱交換部ＨＰ２は、４つの第２パスＰＴ２を有しているが、第２パスＰＴ２の個数は限定されない。 The second heat exchange section HP2 has a plurality of second paths PT2. Each of the plurality of second paths PT2 extends in the width direction D2. Each of the plurality of second paths PT2 extends linearly. The plurality of second paths PT2 are arranged in a line along the direction in which the plurality of first paths PT1 are lined up. The plurality of second paths PT2 are lined up at intervals in the step direction D3. In this embodiment, the second heat exchange section HP2 has four second paths PT2, but the number of second paths PT2 is not limited.
　本実施の形態では、第２熱交換部ＨＰ２は、複数の第２フィンＦ２と、複数の第２接続部Ｃ２とを有している。複数の第２フィンＦ２の各々は板状に構成されている。複数の第２フィンＦ２は互いに重なるように配置されている。複数の第２パスＰＴ２の各々は、複数の第２フィンＦ２を幅方向Ｄ２に貫通している。複数の第２接続部Ｃ２は、複数の第２フィンＦ２の外側で第２パスＰＴ２同士を接続している。複数の第２パスＰＴ２の各々が複数の第２接続部Ｃ２の各々によって接続されることで、複数の第２パスＰＴ２および複数の第２接続部Ｃ２は幅方向Ｄ２に折り返すように構成されている。複数の第２パスＰＴ２、複数の第２フィンＦ２および複数の第２接続部Ｃ２の材料は、例えばアルミニウムである。 In this embodiment, the second heat exchange part HP2 includes a plurality of second fins F2 and a plurality of second connection parts C2. Each of the plurality of second fins F2 is configured in a plate shape. The plurality of second fins F2 are arranged so as to overlap each other. Each of the plurality of second paths PT2 passes through the plurality of second fins F2 in the width direction D2. The plurality of second connecting portions C2 connect the second paths PT2 to each other on the outside of the plurality of second fins F2. Each of the plurality of second paths PT2 is connected by each of the plurality of second connection parts C2, so that the plurality of second paths PT2 and the plurality of second connection parts C2 are configured to be folded back in the width direction D2. There is. The material of the plurality of second paths PT2, the plurality of second fins F2, and the plurality of second connection parts C2 is, for example, aluminum.
　第３熱交換部ＨＰ３は、複数の第３パスＰＴ３を有している。複数の第３パスＰＴ３の各々は、幅方向Ｄ２に延在している。複数の第３パスＰＴ３の各々は、直線状に延在している。複数の第３パスＰＴ３は、第１パスＰＴ１が並ぶ方向に沿って一列に並んで配置されている。複数の第３パスＰＴ３は、段方向Ｄ３に互いに間隔をあけて並んでいる。本実施の形態では、第３熱交換部ＨＰ３は、４つの第３パスＰＴ３を有しているが、第３パスＰＴ２３個数は限定されない。 The third heat exchange section HP3 has a plurality of third paths PT3. Each of the plurality of third paths PT3 extends in the width direction D2. Each of the plurality of third paths PT3 extends linearly. The plurality of third paths PT3 are arranged in a line along the direction in which the first paths PT1 are lined up. The plurality of third paths PT3 are arranged at intervals in the step direction D3. In this embodiment, the third heat exchange section HP3 has four third paths PT3, but the number of third paths PT23 is not limited.
　本実施の形態では、第３熱交換部ＨＰ３は、複数の第３フィンＦ３と、複数の第３接続部Ｃ３とを有している。複数の第３フィンＦ３の各々は板状に構成されている。複数の第３フィンＦ３は互いに重なるように配置されている。複数の第３パスＰＴ３の各々は、複数の第３フィンＦ３を幅方向Ｄ２に貫通している。複数の第３接続部Ｃ３は、複数の第３フィンＦ３の外側で第３パスＰＴ３同士を接続している。複数の第３パスＰＴ３の各々が複数の第３接続部Ｃ３の各々によって接続されることで、複数の第３パスＰＴ３および複数の第３接続部Ｃ３は幅方向Ｄ２に折り返すように構成されている。複数の第３パスＰＴ３、複数の第３フィンＦ３および複数の第３接続部Ｃ３の材料は、例えばアルミニウムである。 In the present embodiment, the third heat exchange part HP3 includes a plurality of third fins F3 and a plurality of third connection parts C3. Each of the plurality of third fins F3 is configured in a plate shape. The plurality of third fins F3 are arranged so as to overlap each other. Each of the plurality of third paths PT3 passes through the plurality of third fins F3 in the width direction D2. The plurality of third connecting portions C3 connect the third paths PT3 to each other on the outside of the plurality of third fins F3. Each of the plurality of third paths PT3 is connected by each of the plurality of third connection parts C3, so that the plurality of third paths PT3 and the plurality of third connection parts C3 are configured to be folded back in the width direction D2. There is. The material of the plurality of third paths PT3, the plurality of third fins F3, and the plurality of third connection parts C3 is, for example, aluminum.
　３方管ＴＰは、第１熱交換部ＨＰ１と第２熱交換部ＨＰ２とを接続する。３方管ＴＰは、複数の第１パスＰＴ１のうちの１つと複数の第２パスＰＴ２のうちの２つとを接続する。本実施の形態では、段方向Ｄ３において、１段目の第１パスＰＴ１と、２段目および３段目の第２パスＰＴ２とが３方管ＴＰで接続されている。 The three-way pipe TP connects the first heat exchange part HP1 and the second heat exchange part HP2. The three-way pipe TP connects one of the plurality of first paths PT1 and two of the plurality of second paths PT2. In this embodiment, in the stage direction D3, the first path PT1 of the first stage and the second path PT2 of the second and third stages are connected by a three-way pipe TP.
　複数の接続管ＣＰは、第２熱交換部ＨＰ２と第３熱交換部ＨＰ３とを接続する。複数の接続管ＣＰは、複数の第２パスＰＴ２のうちの１つと複数の第３パスＰＴ３の１つとを接続する。本実施の形態では、段方向Ｄ３において、１段目の第２パスＰＴ２と１段目の第３パスＰＴ３とが一方の接続管（第１の接続管）ＣＰで接続され、４段目の第２パスＰＴ２と４段目の第３パスＰＴ３とが他方の接続管（第２の接続管）ＣＰで接続されている。 The plurality of connecting pipes CP connect the second heat exchange section HP2 and the third heat exchange section HP3. The plurality of connecting pipes CP connect one of the plurality of second paths PT2 and one of the plurality of third paths PT3. In this embodiment, in the stage direction D3, the second path PT2 of the first stage and the third path PT3 of the first stage are connected by one connecting pipe (first connecting pipe) CP, and the second path PT2 of the first stage is connected by one connecting pipe (first connecting pipe) CP. The second path PT2 and the fourth stage third path PT3 are connected by the other connecting pipe (second connecting pipe) CP.
　図２～図４に示されるように、３方管ＴＰは、Ｕ字管Ｔ１と、流入管Ｔ２とを有している。Ｕ字管Ｔ１は、複数の第２パスＰＴ２同士を接続する。本実施の形態では、Ｕ字管Ｔ１は、複数の第２パスＰＴのうち段方向Ｄ３に隣り合う第２パスＰＴ同士を接続する。 As shown in FIGS. 2 to 4, the three-way pipe TP includes a U-shaped pipe T1 and an inflow pipe T2. The U-shaped tube T1 connects the plurality of second paths PT2. In the present embodiment, the U-shaped tube T1 connects adjacent second paths PT in the step direction D3 among the plurality of second paths PT.
　流入管Ｔ２は、複数の第１パスＰＴ１のいずれかとＵ字管Ｔ１とを接続する。Ｕ字管Ｔ１は、直線部Ｔ１１と、曲がり部Ｔ１２とを有している。直線部Ｔ１１は、複数の第２パスＰＴ２の各々に接続されている。本実施の形態では、直線部Ｔ１１は、水平方向に延在している。曲がり部Ｔ１２は直線部Ｔ１１をつないでいる。流入管Ｔ２は、直線部Ｔ１１に鉛直方向に接続されている。本実施の形態では、流入管Ｔ２は、直線部Ｔ１１に鉛直方向において上側から接続されている。 The inflow pipe T2 connects any one of the plurality of first paths PT1 to the U-shaped pipe T1. The U-shaped tube T1 has a straight portion T11 and a bent portion T12. The straight portion T11 is connected to each of the plurality of second paths PT2. In this embodiment, the straight portion T11 extends in the horizontal direction. The curved portion T12 connects the straight portion T11. The inflow pipe T2 is vertically connected to the straight portion T11. In this embodiment, the inflow pipe T2 is connected to the straight portion T11 from above in the vertical direction.
　本実施の形態では、流入管Ｔ２は、第１折り返し部Ｔ２１と、第１延在部Ｔ２２と、第２折り返し部Ｔ２３と、第２延在部Ｔ２４とを有している。第１折り返し部Ｔ２１は直線部Ｔ１１に接続されている。第１折り返し部Ｔ２１は、直線部Ｔ１１と９０°の角度をなすように接続されている。第１折り返し部Ｔ２１は、鉛直方向に立ち上がってから立ち下がるように折り返している。第１折り返し部Ｔ２１は、幅方向Ｄ２から見て、列方向に第１熱交換部ＨＰ１と第２熱交換部ＨＰ２とにまたがっている。第１延在部Ｔ２２は、第１折り返し部Ｔ２１に接続されている。第１延在部Ｔ２２は、鉛直方向に延在している。第１延在部Ｔ２２は、直線状に延在している。第１延在部Ｔ２２の鉛直方向の長さは、第２パスＰＴ２の２段の長さよりも長くなっている。 In this embodiment, the inflow pipe T2 has a first folded part T21, a first extended part T22, a second folded part T23, and a second extended part T24. The first folded portion T21 is connected to the straight portion T11. The first folded portion T21 is connected to the straight portion T11 at an angle of 90°. The first folded portion T21 is folded back so as to rise in the vertical direction and then fall. The first folded portion T21 straddles the first heat exchange portion HP1 and the second heat exchange portion HP2 in the column direction when viewed from the width direction D2. The first extending portion T22 is connected to the first folded portion T21. The first extending portion T22 extends in the vertical direction. The first extending portion T22 extends linearly. The length of the first extending portion T22 in the vertical direction is longer than the length of the second stage of the second path PT2.
　第２折り返し部Ｔ２３は第１延在部Ｔ２２に接続されている。第２折り返し部Ｔ２３は、鉛直方向に立ち下がってから立ち上がるように折り返している。第２折り返し部Ｔ２３は、幅方向から見て、列方向に第１熱交換部ＨＰ１と第２熱交換部ＨＰ２とにまたがっている。第２延在部Ｔ２４は、第２折り返し部Ｔ２３に接続されている。第２延在部Ｔ２４は、幅方向Ｄ２に延在している。第２延在部Ｔ２４は、直線状に延在している。第２延在部Ｔ２４は、第１パスＰＴ１に接続されている。 The second folded portion T23 is connected to the first extended portion T22. The second folded portion T23 is folded back so as to fall down in the vertical direction and then rise. The second folded portion T23 straddles the first heat exchange portion HP1 and the second heat exchange portion HP2 in the column direction when viewed from the width direction. The second extending portion T24 is connected to the second folded portion T23. The second extending portion T24 extends in the width direction D2. The second extending portion T24 extends linearly. The second extending portion T24 is connected to the first path PT1.
　図５に示されるように、３方管ＴＰにはＵ字管Ｔ１と流入管Ｔ２の接続部分にバルジ加工部ＢＰが設けられていてもよい。バルジ加工部ＢＰを介してＵ字管Ｔ１と流入管Ｔ２とが接続されている。なお、図５では説明の便宜のため流入管Ｔ２は図示されていない。 As shown in FIG. 5, the three-way pipe TP may be provided with a bulge-processed portion BP at the connection portion between the U-shaped pipe T1 and the inflow pipe T2. The U-shaped tube T1 and the inflow tube T2 are connected via the bulge processed portion BP. Note that the inflow pipe T2 is not shown in FIG. 5 for convenience of explanation.
　図６に示されるように、流入管Ｔ２は、直線部Ｔ１１に鉛直方向において下側から接続されていてもよい。流入管Ｔ２は、立ち上がり部Ｔ２５と、下側延在部Ｔ２６とを有している。立ち上がり部Ｔ２５は、直線部Ｔ１１に接続されている。立ち上がり部Ｔ２５は、直線部Ｔ１１と９０°の角度をなすように接続されている。下側延在部Ｔ２６は、立ち上がり部Ｔ２５に接続されている。下側延在部Ｔ２６は、幅方向Ｄ２に延在している。下側延在部Ｔ２６は、直線状に延在している。下側延在部Ｔ２６は、第１パスＰＴ１に接続されている。 As shown in FIG. 6, the inflow pipe T2 may be connected to the straight portion T11 from below in the vertical direction. The inflow pipe T2 has a rising portion T25 and a lower extending portion T26. The rising portion T25 is connected to the straight portion T11. The rising portion T25 is connected to the straight portion T11 at an angle of 90°. The lower extending portion T26 is connected to the rising portion T25. The lower extending portion T26 extends in the width direction D2. The lower extending portion T26 extends linearly. The lower extending portion T26 is connected to the first path PT1.
　次に、図１を参照して、実施の形態１に係る空気調和機１００の動作について説明する。 Next, the operation of air conditioner 100 according to Embodiment 1 will be described with reference to FIG. 1.
　空気調和機１００は、冷房運転と暖房運転とを選択的に行うことが可能である。冷房運転時には、圧縮機１、四方弁２、室外熱交換器３、膨張弁４、室内熱交換器５、四方弁２の順に冷媒が冷媒回路１０を循環する。冷房運転時には室外熱交換器３は、凝縮器として機能する。室外熱交換器３を流れる冷媒と室外送風機６によって送風される空気との間で熱交換が行われる。冷房運転時には室内熱交換器５は、蒸発器として機能する。室内熱交換器５を流れる冷媒と室内送風機７によって送風される空気との間で熱交換が行われる。 The air conditioner 100 can selectively perform cooling operation and heating operation. During cooling 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. During cooling operation, 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 blower 6. During cooling operation, 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.
　暖房運転時には、圧縮機１、四方弁２、室内熱交換器５、膨張弁４、室外熱交換器３、四方弁２の順に冷媒が冷媒回路１０を循環する。暖房運転時には室内熱交換器５は、凝縮器として機能する。室内熱交換器５を流れる冷媒と室内送風機７によって送風される空気との間で熱交換が行われる。暖房運転時には室外熱交換器３は、蒸発器として機能する。室外熱交換器３を流れる冷媒と室外送風機６によって送風される空気との間で熱交換が行われる。 During heating operation, refrigerant circulates through the refrigerant circuit 10 in the order of the compressor 1, four-way valve 2, indoor heat exchanger 5, expansion valve 4, outdoor heat exchanger 3, and four-way valve 2. During heating operation, 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. During heating operation, 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 blower 6.
　図１および図２を参照して、実施の形態１に係る熱交換器ＨＥが適用された室内熱交換器５の動作について説明する。 The operation of the indoor heat exchanger 5 to which the heat exchanger HE according to the first embodiment is applied will be described with reference to FIGS. 1 and 2.
　冷房運転時には室内熱交換器５は蒸発器として機能する。膨張弁４で減圧された低圧気液二相冷媒は、第１列の第１熱交換部ＨＰ１の第１パスＰＴ１に流入する。低圧気液二相冷媒は、第１熱交換部ＨＰ１において、乾き度が例えば０．３以上０．４以下となるまで蒸発する。低圧気液二相冷媒は、第１熱交換部ＨＰ１から３方管ＴＰに流入する。低圧気液二相冷媒は、３方管ＴＰで均等に流量が分配され、第２列の第２熱交換部ＨＰ２の第２パスＰＴ２に流入する。低圧気液二相冷媒は、第２熱交換部ＨＰ２においてさらに蒸発する。低圧気液二相冷媒は、第２熱交換部ＨＰ２から接続管ＣＰを通って、第３列の第３熱交換部ＨＰ３の第３パスＰＴ３に流入する。低圧気液二相冷媒は、第３熱交換部ＨＰ３においてさらに蒸発する。冷媒流れ方向は、空気流れ方向Ｄ１に対して並行流とする。本実施の形態では、非共沸混合冷媒は、複数の第１パスＰＴ１、複数の第２パスＰＴ２および３方管ＴＰの内部を流れる。 During cooling operation, the indoor heat exchanger 5 functions as an evaporator. The low-pressure gas-liquid two-phase refrigerant whose pressure has been reduced by the expansion valve 4 flows into the first path PT1 of the first heat exchange section HP1 in the first row. The low-pressure gas-liquid two-phase refrigerant is evaporated in the first heat exchange part HP1 until the degree of dryness is, for example, 0.3 or more and 0.4 or less. The low-pressure gas-liquid two-phase refrigerant flows into the three-way pipe TP from the first heat exchange section HP1. The flow rate of the low-pressure gas-liquid two-phase refrigerant is evenly distributed in the three-way pipe TP, and flows into the second path PT2 of the second heat exchange section HP2 in the second row. The low-pressure gas-liquid two-phase refrigerant is further evaporated in the second heat exchange section HP2. The low-pressure gas-liquid two-phase refrigerant flows from the second heat exchange section HP2 through the connecting pipe CP and into the third path PT3 of the third heat exchange section HP3 in the third row. The low-pressure gas-liquid two-phase refrigerant is further evaporated in the third heat exchange section HP3. The coolant flow direction is parallel to the air flow direction D1. In this embodiment, the non-azeotropic mixed refrigerant flows inside the plurality of first paths PT1, the plurality of second paths PT2, and the three-way pipe TP.
　暖房運転時には室内熱交換器５は凝縮器として機能する。圧縮機１から吐出された高圧ガス冷媒は、四方弁２を通って、第３列の第３熱交換部ＨＰ３の第３パスＰＴ３に流入する。高圧ガス冷媒は、第３熱交換部ＨＰ３で凝縮される。高圧ガス冷媒は、第３熱交換部ＨＰ３から接続管ＣＰを通って、第２列の第２熱交換部ＨＰ２の第２パスＰＴ２に流入する。高圧ガス冷媒は、第２熱交換部ＨＰ２において、乾き度が０になるまで凝縮される。液または低乾き度の高圧冷媒は、３方管ＴＰで合流され流量が２倍となり、第１列の第１熱交換部ＨＰ１の第１パスＰＴ１に流入する。液または低乾き度の高圧冷媒は、第１熱交換部ＨＰ１でさらに凝縮される。冷媒流れ方向は、空気流れ方向Ｄ１に対して対向流となる。 During heating operation, the indoor heat exchanger 5 functions as a condenser. The high-pressure gas refrigerant discharged from the compressor 1 passes through the four-way valve 2 and flows into the third path PT3 of the third heat exchange section HP3 in the third row. The high pressure gas refrigerant is condensed in the third heat exchange section HP3. The high-pressure gas refrigerant flows from the third heat exchange section HP3 through the connecting pipe CP and into the second path PT2 of the second heat exchange section HP2 in the second row. The high-pressure gas refrigerant is condensed in the second heat exchange section HP2 until its dryness reaches zero. The liquid or low-dryness high-pressure refrigerant is combined in the three-way pipe TP, the flow rate of which is doubled, and flows into the first path PT1 of the first heat exchange section HP1 in the first row. The liquid or low dryness high pressure refrigerant is further condensed in the first heat exchange section HP1. The refrigerant flow direction is opposite to the air flow direction D1.
　次に、図７を参照して、実施の形態１に係る熱交換器ＨＥの蒸発器性能について説明する。 Next, with reference to FIG. 7, the evaporator performance of the heat exchanger HE according to the first embodiment will be described.
　図７は、蒸発器性能と流入管Ｔ２の高さＨ（図４参照）との関係を示すグラフである。測定条件は、次の通りである。空気温度は乾球温度７℃、湿球温度６℃である風速は１．５ｍ／ｓである。冷媒はＲ３２である。冷媒循環量は１０ｋｇ／ｈである。入口エンタルピーは２４５．６ｋＪ／ｋｇである。熱交換器出口過熱度は１Ｋである。測定対象物は、３列、４段、積長３００ｍｍ、２パスの熱交換器である。流入管Ｔ２の高さをパラメータとしている。 FIG. 7 is a graph showing the relationship between the evaporator performance and the height H of the inflow pipe T2 (see FIG. 4). The measurement conditions are as follows. The air temperature is 7° C. dry bulb and 6° C. wet bulb. The wind speed is 1.5 m/s. The refrigerant is R32. The refrigerant circulation amount is 10 kg/h. The inlet enthalpy is 245.6 kJ/kg. The degree of superheat at the heat exchanger outlet is 1K. The object to be measured is a 3-row, 4-stage, stacked length of 300 mm, 2-pass heat exchanger. The height of the inflow pipe T2 is used as a parameter.
　図７に示されるように、流入管Ｔ２の高さＨは、直線部Ｔ１１の内径Ｄの１０倍以上の長さを有することが好ましい。流入管Ｔ２の高さＨが直線部Ｔ１１の内径Ｄの１０倍の長さ（１０Ｄ）以上であれば、蒸発器性能は９５％以上となる。蒸発器性能は、冷媒分配悪化による影響が無い場合を基準としている。また、流入管Ｔ２の高さＨは、直線部Ｔ１１の内径Ｄの５０倍以上の長さを有することがさらに好ましい。流入管Ｔ２の高さＨが直線部Ｔ１１の内径Ｄの５０倍の長さ（５０Ｄ）以上であれば、蒸発器性能は略１００％となる。 As shown in FIG. 7, the height H of the inflow pipe T2 is preferably at least 10 times the inner diameter D of the straight portion T11. If the height H of the inflow pipe T2 is at least 10 times the inner diameter D of the straight portion T11 (10D), the evaporator performance will be 95% or more. Evaporator performance is based on the case where there is no effect due to deterioration of refrigerant distribution. Further, it is more preferable that the height H of the inflow pipe T2 is at least 50 times the inner diameter D of the straight portion T11. If the height H of the inflow pipe T2 is at least 50 times the inner diameter D of the straight portion T11 (50D), the evaporator performance will be approximately 100%.
　次に、実施の形態１の作用効果について説明する。
　実施の形態１に係る熱交換器ＨＥによれば、流入管Ｔ２は、直線部Ｔ１１に鉛直方向に接続されている。このため、熱交換器ＨＥが蒸発器として機能する場合、流入管Ｔ２から流入した気液二相冷媒は、直線部Ｔ１１に沿って分配される。また、流入管Ｔ２が直線部Ｔ１１に水平方向に接続される場合よりも流入管Ｔ２の鉛直方向の長さを長くすることができる。これにより、気液二相冷媒の偏流を抑制することができる。したがって、気液二相冷媒を均等に分配することができる。よって、蒸発器性能を向上させることができる。 Next, the effects of the first embodiment will be explained.
According to the heat exchanger HE according to the first embodiment, the inflow pipe T2 is connected to the straight portion T11 in the vertical direction. Therefore, when the heat exchanger HE functions as an evaporator, the gas-liquid two-phase refrigerant flowing from the inflow pipe T2 is distributed along the straight portion T11. Further, the length of the inflow pipe T2 in the vertical direction can be made longer than when the inflow pipe T2 is connected to the straight portion T11 in the horizontal direction. Thereby, drifting of the gas-liquid two-phase refrigerant can be suppressed. Therefore, the gas-liquid two-phase refrigerant can be evenly distributed. Therefore, evaporator performance can be improved.
　実施の形態１に係る熱交換器ＨＥでは、直線部Ｔ１１は水平方向に延在している。このため、流入管Ｔ２から流入した冷媒は、水平方向に沿って分配される。したがって、気液二相冷媒をさらに均等に分配することができる。 In the heat exchanger HE according to the first embodiment, the straight portion T11 extends in the horizontal direction. Therefore, the refrigerant flowing in from the inflow pipe T2 is distributed along the horizontal direction. Therefore, the gas-liquid two-phase refrigerant can be distributed more evenly.
　実施の形態１に係る熱交換器ＨＥでは、熱交換器ＨＥが凝縮器として機能する場合、液相部の流路数を少なくすることができる。このため、凝縮器性能を向上させることができる。 In the heat exchanger HE according to the first embodiment, when the heat exchanger HE functions as a condenser, the number of channels in the liquid phase portion can be reduced. Therefore, the condenser performance can be improved.
　実施の形態１に係る熱交換器ＨＥによれば。流入管Ｔ２の高さは、直線部Ｔ１１の内径の１０倍以上の長さを有する。このため、蒸発器性能を向上させることができる。 According to the heat exchanger HE according to the first embodiment. The height of the inflow pipe T2 is at least 10 times the inner diameter of the straight portion T11. Therefore, the evaporator performance can be improved.
　実施の形態１に係る熱交換器ＨＥでは、非共沸混合冷媒は、複数の第１パスＰＴ１、複数の第２パスＰＴ２および３方管ＴＰの内部を流れる。このため、着霜が生じやすい風上側に液側が配置された場合、液側において非共沸混合冷媒の温度勾配が小さくなる。このため、非共沸混合冷媒の蒸発温度の低下を抑制することができる。 In the heat exchanger HE according to the first embodiment, the non-azeotropic mixed refrigerant flows inside the plurality of first paths PT1, the plurality of second paths PT2, and the three-way pipe TP. Therefore, when the liquid side is arranged on the windward side where frost formation is likely to occur, the temperature gradient of the non-azeotropic mixed refrigerant on the liquid side becomes small. Therefore, a decrease in the evaporation temperature of the non-azeotropic refrigerant mixture can be suppressed.
　実施の形態１に係る空気調和機１００は、上記の熱交換器ＨＥを備えている。このため、蒸発器性能を向上させることができる熱交換器ＨＥを備えた空気調和機１００を提供することができる。 The air conditioner 100 according to the first embodiment includes the heat exchanger HE described above. Therefore, it is possible to provide the air conditioner 100 including the heat exchanger HE that can improve the evaporator performance.
　続いて、実施の形態１に係る熱交換器ＨＥの変形例について説明する。
　図８を参照して、実施の形態１に係る熱交換器ＨＥの変形例１では、図３に示される本実施の形態よりも、３方管ＴＰの流入管Ｔ２が鉛直方向に長くなっている。具体的には、流入管Ｔ２の第１延在部Ｔ２２の鉛直方向の長さは、第２パスＰＴ２の４段の長さよりも長くなっている。 Next, a modification of the heat exchanger HE according to the first embodiment will be described.
Referring to FIG. 8, in the first modification of the heat exchanger HE according to the first embodiment, the inflow pipe T2 of the three-way pipe TP is longer in the vertical direction than in the present embodiment shown in FIG. There is. Specifically, the length in the vertical direction of the first extending portion T22 of the inflow pipe T2 is longer than the length of the four stages of the second path PT2.
　実施の形態１に係る熱交換器ＨＥの変形例１によれば、流入管Ｔ２の第１延在部Ｔ２２の鉛直方向の長さが長くなっているため、気液二相冷媒の偏流をさらに抑制することができる。 According to the first modification of the heat exchanger HE according to the first embodiment, the vertical length of the first extending portion T22 of the inflow pipe T2 is longer, so that the uneven flow of the gas-liquid two-phase refrigerant is further reduced. Can be suppressed.
　図９を参照して、実施の形態１に係る熱交換器ＨＥの変形例２では、熱交換器ＨＥは、第１熱交換部ＨＰ１および第２熱交換部ＨＰ２を有しているが、第３熱交換部ＨＰ３を有していない。つまり、熱交換器ＨＥは２列の熱交換部で構成されている。 Referring to FIG. 9, in the second modification of the heat exchanger HE according to the first embodiment, the heat exchanger HE has a first heat exchange part HP1 and a second heat exchange part HP2; 3 does not have heat exchange section HP3. That is, the heat exchanger HE is composed of two rows of heat exchange sections.
　実施の形態１に係る熱交換器ＨＥの変形例２によれば、熱交換器ＨＥを２列の熱交換部で構成することができる。 According to the second modification of the heat exchanger HE according to the first embodiment, the heat exchanger HE can be configured with two rows of heat exchange sections.
　実施の形態２．
　実施の形態２に係る熱交換器ＨＥは、特に説明しない限り、実施の形態１に係る熱交換器ＨＥと同一の構成、動作および作用効果を有している。 Embodiment 2.
The heat exchanger HE according to the second embodiment has the same configuration, operation, and effect as the heat exchanger HE according to the first embodiment, unless otherwise specified.
　図１０を参照して、実施の形態２に係る熱交換器ＨＥでは、曲がり部Ｔ１２は、破断誘導構造ＦＰを有している。破断誘導構造ＦＰは、曲がり部Ｔ１２の他の部分よりも耐圧が低くなるように構成されている。また、冷媒はＨＦＯ１１２３冷媒を含む混合冷媒である。本実施の形態では、破断誘導構造ＦＰは、切り欠きを有する切り欠き構造となっている。この切り欠きは、曲がり部Ｔ１２の外周に、例えば全周において形成されている。 Referring to FIG. 10, in the heat exchanger HE according to the second embodiment, the bent portion T12 has a fracture-inducing structure FP. The fracture guiding structure FP is configured to have a lower withstand voltage than other parts of the bent portion T12. Further, the refrigerant is a mixed refrigerant containing HFO1123 refrigerant. In this embodiment, the fracture guiding structure FP has a notch structure having a notch. This notch is formed on the outer periphery of the bent portion T12, for example, over the entire periphery.
　本実施の形態２に係る熱交換器ＨＥによれば、曲がり部Ｔ１２は、破断誘導構造ＦＰを有している。このため、ＨＦＯ１１２３冷媒を含む混合冷媒の高圧側の圧力が異常上昇した際、破断誘導構造ＦＰが破断するため、ＨＦＯ１１２３冷媒を配管外部に放出することができる。このため、冷媒回路１０中の圧力を開放することができる。したがって、ＨＦＯ１１２３冷媒の不均化反応が連鎖反応として拡散することを防止することができるため、不均化反応による爆発を防止することができる。 According to the heat exchanger HE according to the second embodiment, the bent portion T12 has the fracture-inducing structure FP. Therefore, when the pressure on the high-pressure side of the mixed refrigerant containing the HFO1123 refrigerant increases abnormally, the fracture induction structure FP ruptures, so that the HFO1123 refrigerant can be discharged to the outside of the pipe. Therefore, the pressure in the refrigerant circuit 10 can be released. Therefore, it is possible to prevent the disproportionation reaction of the HFO1123 refrigerant from diffusing as a chain reaction, thereby preventing an explosion due to the disproportionation reaction.
　今回開示された実施の形態はすべての点で例示であって制限的なものではないと考えられるべきである。本開示の範囲は上記した説明ではなくて請求の範囲によって示され、請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。 The embodiments disclosed this time should be considered to be illustrative in all respects and not restrictive. The scope of the present disclosure is indicated by the claims rather than the above description, and it is intended that equivalent meanings and all changes within the scope of the claims are included.
　１　圧縮機、２　四方弁、３　室外熱交換器、４　膨張弁、５　室内熱交換器、１００　空気調和機、ＦＰ　破断誘導構造、ＨＥ　熱交換器、ＨＰ１　第１熱交換部、ＨＰ２　第２熱交換部、ＨＰ３　第３熱交換部、ＰＴ１　第１パス、ＰＴ２　第２パス、ＰＴ３　第３パス、Ｔ１　Ｕ字管、Ｔ２　流入管、Ｔ１１　直線部、Ｔ１２　曲がり部、ＴＰ　３方管。 1 Compressor, 2 Four-way valve, 3 Outdoor heat exchanger, 4 Expansion valve, 5 Indoor heat exchanger, 100 Air conditioner, FP rupture induction structure, HE Heat exchanger, HP1 First heat exchange section, HP2 Second heat Exchange section, HP3 third heat exchange section, PT1 first pass, PT2 second pass, PT3 third pass, T1 U-shaped tube, T2 inflow tube, T11 straight section, T12 bent section, TP three-way tube.

Claims (5)

  1. 　複数の第１パスを有する第１熱交換部と、
    　複数の第２パスを有する第２熱交換部と、
    　前記第１熱交換部と前記第２熱交換部とを接続する３方管とを備え、
    　前記複数の第１パスは、一列に並んで配置されており、
    　前記複数の第２パスは、前記複数の第１パスが並ぶ方向に沿って一列に並んで配置されており、
    　前記３方管は、前記複数の第２パス同士を接続するＵ字管と、前記複数の第１パスのいずれかと前記Ｕ字管とを接続する流入管とを有し、
    　前記Ｕ字管は、前記複数の第２パスの各々に接続された直線部を有し、
    　前記流入管は、前記直線部に鉛直方向に接続されている、熱交換器。     a first heat exchange section having a plurality of first passes;
    a second heat exchange section having a plurality of second passes;
    a three-way pipe connecting the first heat exchange section and the second heat exchange section,
    The plurality of first paths are arranged in a line,
    The plurality of second paths are arranged in a line along the direction in which the plurality of first paths are lined up,
    The three-way pipe includes a U-shaped pipe that connects the plurality of second paths, and an inflow pipe that connects any of the plurality of first paths to the U-shaped pipe,
    The U-shaped tube has a straight portion connected to each of the plurality of second paths,
    The inflow pipe is a heat exchanger connected to the straight section in a vertical direction.
  2. 　前記流入管の高さは、前記直線部の内径の１０倍以上の長さを有する、請求項１に記載の熱交換器。 The heat exchanger according to claim 1, wherein the height of the inflow pipe is 10 times or more the inner diameter of the straight portion.
  3. 　非共沸混合冷媒をさらに備え、
    　前記非共沸混合冷媒は、前記複数の第１パス、前記複数の第２パスおよび前記３方管の内部を流れる、請求項１または２に記載の熱交換器。     further comprising a non-azeotropic mixed refrigerant;
    The heat exchanger according to claim 1 or 2, wherein the non-azeotropic mixed refrigerant flows inside the plurality of first passes, the plurality of second passes, and the three-way pipe.
  4. 　ＨＦＯ１１２３冷媒を含む混合冷媒をさらに備え、
    　前記Ｕ字管は、前記直線部をつなぐ曲がり部を有し、
    　前記曲がり部は、破断誘導構造を有し、
    　前記破断誘導構造は、前記曲がり部の他の部分よりも耐圧が低くなるように構成されている、請求項１または２に記載の熱交換器。     Further comprising a mixed refrigerant including HFO1123 refrigerant,
    The U-shaped tube has a bent part that connects the straight part,
    The bent portion has a fracture inducing structure,
    The heat exchanger according to claim 1 or 2, wherein the fracture inducing structure is configured to have a lower pressure resistance than other parts of the bent portion.
  5. 　前記請求項１～４のいずれか１項に記載の熱交換器を備えた、空気調和機。 An air conditioner comprising the heat exchanger according to any one of claims 1 to 4.
PCT/JP2022/016866 2022-03-31 2022-03-31 Heat exchanger and air conditioner WO2023188386A1 (en)

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JP6639644B2 (en) * 2016-03-28 2020-02-05 三菱電機株式会社 Outdoor unit
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JPH06159735A (en) * 1992-11-18 1994-06-07 Sanyo Electric Co Ltd Heat exchanger
JP2000329486A (en) * 1999-05-17 2000-11-30 Matsushita Electric Ind Co Ltd Finned heat exchanger
JP2001090893A (en) * 1999-09-24 2001-04-03 Daikin Ind Ltd Distributing device
JP2005083715A (en) * 2003-09-11 2005-03-31 Sharp Corp Heat exchanger
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WO2019058540A1 (en) * 2017-09-25 2019-03-28 三菱電機株式会社 Refrigerant distributor and air-conditioning device
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