WO2021234953A1 - Heat exchanger, outdoor unit comprising heat exchanger, and air-conditioning device comprising outdoor unit - Google Patents

Heat exchanger, outdoor unit comprising heat exchanger, and air-conditioning device comprising outdoor unit Download PDF

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Publication number
WO2021234953A1
WO2021234953A1 PCT/JP2020/020346 JP2020020346W WO2021234953A1 WO 2021234953 A1 WO2021234953 A1 WO 2021234953A1 JP 2020020346 W JP2020020346 W JP 2020020346W WO 2021234953 A1 WO2021234953 A1 WO 2021234953A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
header
gas pipe
refrigerant
outdoor unit
Prior art date
Application number
PCT/JP2020/020346
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French (fr)
Japanese (ja)
Inventor
傑 鳩村
哲二 七種
理人 足立
充宏 池田
浩二 西岡
俊希 行▲徳▼
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.)
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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 PCT/JP2020/020346 priority Critical patent/WO2021234953A1/en
Priority to JP2022524841A priority patent/JP7357785B2/en
Publication of WO2021234953A1 publication Critical patent/WO2021234953A1/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
    • 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

Definitions

  • the present disclosure relates to a heat exchanger having a plurality of flat tubes, an outdoor unit equipped with a heat exchanger, and an air conditioner equipped with an outdoor unit.
  • the heat exchange cores are arranged in two rows in the front and rear in the direction of the wind flow, and the upper header tank and the separate lower header tanks that are common to each other of the heat exchange cores are provided.
  • a heat exchanger in which a sufficient temperature difference is secured to improve the heat transfer performance (see, for example, Patent Document 1).
  • Patent Document 1 When a conventional heat exchanger as in Patent Document 1 is used for an outdoor unit of an air conditioner capable of operating both cooling operation and heating operation, in the heating operation where the outside air temperature is low, a low temperature and low pressure two-phase refrigerant is used. Flows through the heat exchange core on the wind side, causing a lot of frost there. In the defrosting operation, high-temperature and high-pressure gas refrigerant flows in from the lower header tank on the leeward side and flows to the heat exchange core on the leeward side to defrost. After defrosting, the defrosted water generated on the surface of the heat exchange core flows downward, but tends to collect especially near the lower header tank on the windward side.
  • the present disclosure has been made to solve the above problems, and includes a heat exchanger capable of suppressing refreezing of defrosted water, an outdoor unit equipped with a heat exchanger, and an outdoor unit. It is intended to provide an air conditioner.
  • the heat exchanger according to the present disclosure is a heat exchanger mounted on an outdoor unit provided with at least one heat exchanger having a plurality of flat tubes along the direction of air flow, and is the most wind-upper side.
  • the first header provided at the lower end of the heat exchanger, the second header provided at the upper end or the lower end of the most leeward heat exchanger, and the first header are connected to function as an evaporator.
  • At least a part of the gas pipe is provided along the long axis direction of the first header, and at least a part of the gas pipe is in contact with the first header. It is a thing.
  • the heat exchanger according to the present disclosure has a plurality of flat tubes, and is composed of a main heat exchanger and an auxiliary heat exchanger in which the number of the flat tubes is smaller than that of the main heat exchanger.
  • a heat exchanger mounted on an outdoor unit which is provided with at least one heat exchanger along the air flow direction, and has the first header provided at the lower end of the auxiliary heat exchanger on the windy side, and the most.
  • the refrigerant flows in when functioning as an evaporator, and flows out when functioning as a condenser.
  • the outdoor unit of the air conditioner according to the present disclosure is equipped with the above heat exchanger.
  • the air conditioner according to the present disclosure is equipped with the above-mentioned outdoor unit.
  • the outdoor unit provided with the heat exchanger, and the air conditioner provided with the outdoor unit according to the present disclosure at least a part of the gas pipe is provided along the long axis direction of the first header. At least part of the gas pipe is in contact with the first header. Therefore, the heat of the gas pipe through which the high-temperature and high-pressure gas refrigerant flows during the defrosting operation can be transferred to the first header. Then, the heat transferred to the first header is transferred to the defrost water in the vicinity of the first header, and the temperature of the defrost water becomes high. Therefore, even if the heating operation is restarted after the defrosting operation is completed, it is possible to prevent the defrosting water in the vicinity of the first header from refreezing.
  • FIG. 1 It is a refrigerant circuit diagram of the air conditioner provided with the heat exchanger which concerns on Embodiment 1.
  • FIG. It is the first perspective view of the heat exchanger which concerns on Embodiment 1.
  • FIG. It is a second perspective view of the heat exchanger which concerns on Embodiment 1.
  • FIG. It is a perspective view which shows the modification of the heat exchanger which concerns on Embodiment 1.
  • FIG. 3 is a perspective view of a top-flow type outdoor unit equipped with a heat exchanger and a heat exchanger according to the second embodiment. It is a perspective view of the heat exchanger which concerns on Embodiment 2.
  • FIG. It is a top view which shows typically the flow of the refrigerant at the time of the heating operation of the heat exchanger which concerns on Embodiment 2.
  • FIG. It is a perspective view which shows typically the flow of the refrigerant at the time of the heating operation of the heat exchanger which concerns on Embodiment 2.
  • FIG. It is a top view which shows typically the flow of the refrigerant at the time of the defrosting operation of the heat exchanger which concerns on Embodiment 2.
  • FIG. It is a perspective view which shows typically the flow of the refrigerant at the time of the defrosting operation of the heat exchanger which concerns on Embodiment 2.
  • FIG. It is a top view which shows typically the flow of the refrigerant at the time of defrosting operation of the modification of the heat exchanger which concerns on Embodiment 2.
  • FIG. It is a perspective view which shows typically the flow of the refrigerant at the time of defrosting operation of the modification of the heat exchanger which concerns on Embodiment 2.
  • FIG. It is an enlarged front view schematically showing the main part of the heat exchanger according to the third embodiment. It is an enlarged front view schematically showing the main part of the heat exchanger according to the fourth embodiment. It is a perspective view which shows typically the joint of the heat exchanger which concerns on Embodiment 5. It is sectional drawing which shows typically the joint of the heat exchanger which concerns on Embodiment 5.
  • FIG. 1 is a refrigerant circuit diagram of an air conditioner 100 provided with a heat exchanger 30 according to the first embodiment.
  • the solid line arrow in FIG. 1 indicates the flow of the refrigerant during the cooling operation, and the broken line arrow in FIG. 1 indicates the flow of the refrigerant during the heating operation.
  • the heat exchanger 30 is mounted on the outdoor unit 10 of the air conditioner 100 including the outdoor unit 10 and the indoor unit 20.
  • the outdoor unit 10 includes a compressor 11, a flow path switching device 12, and a fan 13 in addition to the heat exchanger 30.
  • the indoor unit 20 includes a throttle device 21, an indoor heat exchanger 22, and an indoor fan 23.
  • the air conditioner 100 includes a refrigerant circuit in which a compressor 11, a flow path switching device 12, a heat exchanger 30, a throttle device 21, and an indoor heat exchanger 22 are connected by a refrigerant pipe and a refrigerant circulates.
  • the air conditioner 100 can operate both the cooling operation and the heating operation by switching the flow path switching device 12.
  • the compressor 11 sucks in the low temperature and low pressure refrigerant, compresses the sucked refrigerant, and discharges the high temperature and high pressure refrigerant.
  • the compressor 11 is composed of, for example, an inverter compressor whose capacity, which is a transmission amount per unit time, is controlled by changing the operating frequency.
  • the flow path switching device 12 is, for example, a four-way valve, and switches between cooling operation and heating operation by switching the flow direction of the refrigerant.
  • the flow path switching device 12 switches to the state shown by the solid line in FIG. 1 during the cooling operation, and the discharge side of the compressor 11 and the heat exchanger 30 are connected to each other. Further, the flow path switching device 12 switches to the state shown by the broken line in FIG. 1 during the heating operation, and the discharge side of the compressor 11 and the indoor heat exchanger 22 are connected to each other.
  • the heat exchanger 30 exchanges heat between the outdoor air and the refrigerant.
  • the heat exchanger 30 functions as a condenser that dissipates the heat of the refrigerant to the outdoor air and condenses the refrigerant during the cooling operation. Further, the heat exchanger 30 functions as an evaporator that evaporates the refrigerant during the heating operation and cools the outdoor air by the heat of vaporization at that time.
  • the fan 13 supplies outdoor air to the heat exchanger 30, and the amount of air blown to the heat exchanger 30 is adjusted by controlling the rotation speed.
  • the throttle device 21 is, for example, an electronic expansion valve capable of adjusting the opening degree of the throttle, and controls the pressure of the refrigerant flowing into the heat exchanger 30 or the indoor heat exchanger 22 by adjusting the opening degree.
  • the diaphragm device 21 is provided in the indoor unit 20, but it may be provided in the outdoor unit 10, and the installation location is not limited.
  • the indoor heat exchanger 22 exchanges heat between the indoor air and the refrigerant.
  • the indoor heat exchanger 22 functions as an evaporator that evaporates the refrigerant during the cooling operation and cools the outdoor air by the heat of vaporization at that time. Further, the indoor heat exchanger 22 functions as a condenser that dissipates the heat of the refrigerant to the outdoor air and condenses the refrigerant during the heating operation.
  • the indoor fan 23 supplies indoor air to the indoor heat exchanger 22, and the amount of air blown to the indoor heat exchanger 22 is adjusted by controlling the rotation speed.
  • FIG. 2 is a first perspective view of the heat exchanger 30 according to the first embodiment.
  • FIG. 3 is a second perspective view of the heat exchanger 30 according to the first embodiment.
  • the white arrows in FIGS. 2 and 3 indicate the flow of wind generated by the fan 13.
  • the black dashed arrows in FIGS. 2 and 3 indicate the flow of the refrigerant.
  • the heat exchanger 30 has a plurality of heat exchangers along the air flow direction. Specifically, the heat exchanger 30 has a first heat exchanger 31 on the windward side and a second heat exchanger 32 on the leeward side.
  • the heat exchanger has a plurality of flat tubes 38 and a plurality of fins 39.
  • the flat pipes 38 are arranged in parallel in the horizontal direction at intervals so that the wind generated by the fan 13 flows, and the refrigerant flows in the vertical direction in the pipes extending in the vertical direction.
  • the fins 39 are connected between adjacent flat tubes 38 and transfer heat to the flat tubes 38.
  • the fin 39 improves the heat exchange efficiency between the air and the refrigerant, and for example, a corrugated fin is used. However, it is not limited to this. Since heat exchange between air and the refrigerant is performed on the surface of the flat tube 38, the fins 39 may not be present.
  • a first header 34 is provided at the lower end of the first heat exchanger 31.
  • the lower end of the flat tube 38 of the first heat exchanger 31 is directly inserted into the first header 34.
  • the first header 34 is connected to the refrigerant circuit of the air conditioner 100 via the liquid pipe 36.
  • the first header 34 is also called a liquid header.
  • An opening (not shown) is formed in a portion of the first header 34 to which the liquid pipe 36 is connected.
  • the first header 34 causes a low-temperature low-pressure two-phase refrigerant to flow into the heat exchanger 30 during the heating operation, and is heat-exchanged by the heat exchanger 30 during the cooling operation as shown in FIG.
  • the low temperature and high pressure liquid refrigerant is discharged to the refrigerant circuit.
  • a second header 35 is provided at the lower end of the second heat exchanger 32.
  • the lower end of the flat tube 38 of the second heat exchanger 32 is directly inserted into the second header 35.
  • the second header 35 is arranged in parallel with the first header 34.
  • the second header 35 is connected to the refrigerant circuit of the air conditioner 100 via the gas pipe 37.
  • the second header 35 is also called a gas header.
  • An opening (not shown) is formed in a portion of the second header 35 to which the gas pipe 37 is connected.
  • the second header 35 causes the high-temperature and high-pressure gas refrigerant from the compressor 11 to flow into the heat exchanger 30 during the cooling operation, and heat exchanges with the heat exchanger 30 during the heating operation as shown in FIG.
  • the low-temperature low-pressure gas refrigerant after the heat is discharged to the refrigerant circuit.
  • the inlet of the refrigerant becomes the gas pipe 37 connected to the second header 35, and the outlet of the refrigerant becomes the liquid pipe 36 connected to the first header 34. Further, during the heating operation, the inlet of the refrigerant becomes the liquid pipe 36 connected to the first header 34, and the outlet of the refrigerant becomes the gas pipe 37 connected to the second header 35.
  • a row header 33 into which the upper ends of the plurality of flat tubes 38 inserted in the first header 34 and the second header 35 are inserted is provided. Has been done.
  • the plurality of flat pipes 38, fins 39, first header 34, second header 35, row passing header 33, liquid pipe 36, and gas pipe 37 are all made of aluminum and are joined by brazing.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 11 flows into the heat exchanger 30 via the flow path switching device 12.
  • the high-temperature and high-pressure gas refrigerant flowing into the heat exchanger 30 exchanges heat with the outdoor air taken in by the fan 13 and condenses while radiating heat, becomes a low-temperature and high-pressure liquid refrigerant, and flows out from the heat exchanger 30.
  • the refrigerant flowing in the heat exchanger 30 is the gas pipe 37, the second header 35, the second heat exchanger 32, the row passing header 33, the first heat exchanger 31, the first.
  • the header 34 and the liquid pipe 36 flow in this order.
  • the low-temperature, high-pressure liquid refrigerant flowing out of the heat exchanger 30 is depressurized by the drawing device 21, becomes a low-temperature, low-pressure, gas-liquid two-phase refrigerant, and flows into the indoor heat exchanger 22.
  • the low-temperature low-pressure gas-liquid two-phase refrigerant flowing into the indoor heat exchanger 22 exchanges heat with the indoor air taken in by the indoor fan 23 and evaporates while absorbing heat, cooling the indoor air and forming a low-temperature low-pressure gas refrigerant. Then, it flows out from the indoor heat exchanger 22.
  • the low-temperature low-pressure gas refrigerant flowing out of the indoor heat exchanger 22 is sucked into the compressor 11 and becomes a high-temperature high-pressure gas refrigerant again.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 11 flows into the indoor heat exchanger 22 via the flow path switching device 12.
  • the high-temperature and high-pressure gas refrigerant that has flowed into the indoor heat exchanger 22 exchanges heat with the indoor air taken in by the indoor fan 23 and condenses while radiating heat, heating the indoor air and becoming a low-temperature and high-pressure liquid refrigerant in the room. It flows out from the heat exchanger 22.
  • the low-temperature and high-pressure liquid refrigerant flowing out of the indoor heat exchanger 22 is depressurized by the throttle device 21, becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant, and flows into the heat exchanger 30.
  • the low-temperature low-pressure gas-liquid two-phase refrigerant that has flowed into the heat exchanger 30 exchanges heat with the outdoor air taken in by the fan 13 and evaporates while absorbing heat, becoming a low-temperature low-pressure gas refrigerant and flowing out of the heat exchanger 30. do.
  • the refrigerant flowing in the heat exchanger 30 is the liquid pipe 36, the first header 34, the first heat exchanger 31, the row passing header 33, the second heat exchanger 32, and the second.
  • the header 35 and the gas pipe 37 flow in this order.
  • the low-temperature low-pressure gas refrigerant flowing out of the heat exchanger 30 is sucked into the compressor 11 and becomes a high-temperature high-pressure gas refrigerant again.
  • the fan 13 In the defrosting operation, the fan 13 is stopped, the flow path switching device 12 is switched to the same state as in the cooling operation, and the high temperature and high pressure gas refrigerant flows into the heat exchanger 30. This melts the frost attached to the flat tube 38 and the fins 39.
  • the defrosting operation is started, the high-temperature and high-pressure gas refrigerant flows into each flat tube 38 via the second header 35. Then, the frost adhering to the flat tube 38 and the fins 39 is melted and changed to water by the high-temperature refrigerant flowing into the flat tube 38.
  • defrost water 50 The water generated by melting the frost (hereinafter referred to as defrost water 50) is drained to the lower part of the heat exchanger 30 along the flat pipe 38 or the fin 39.
  • defrost water 50 The water generated by melting the frost (hereinafter referred to as defrost water 50) is drained to the lower part of the heat exchanger 30 along the flat pipe 38 or the fin 39.
  • the low-temperature low-pressure two-phase refrigerant flows through the first heat exchanger 31 on the wind side, so that the frost on the heat exchanger 30 is caused by the first heat exchanger 31 on the wind side.
  • the number is larger than that of the second heat exchanger 32 on the leeward side. Therefore, the defrosting water 50 generated on the surface of the first heat exchanger 31 after defrosting flows downward and collects in the vicinity of the first header 34 at the lower end of the first heat exchanger 31, especially in the upper part of the first header 34. Cheap.
  • the low-temperature low-pressure two-phase refrigerant flows in from the first header 34, so that the defrost water 50 accumulated in the upper part of the first header 34 is re-frozen and becomes root ice in the conventional case. This has led to a decrease in heating capacity and damage to the heat exchanger 30.
  • At least a part of the gas pipe 37 is provided along the long axis direction of the first header 34, and at least a part of the gas pipe 37 is the first header 34. Is in contact with. Further, the gas pipe 37 is arranged below the first header 34. In this way, at least a part of the gas pipe 37 is provided along the long axis direction of the first header 34, and at least a part of the gas pipe 37 comes into contact with the first header 34, so that the temperature and pressure are high and high during the defrosting operation. The heat of the gas pipe 37 through which the gas refrigerant of No. 1 flows can be transferred to the first header 34.
  • the heat transferred to the first header 34 is transmitted to the defrost water 50 in the vicinity of the first header 34, and the temperature of the defrost water 50 becomes high. Therefore, even if the heating operation is restarted after the defrosting operation is completed, it is possible to prevent the defrosting water 50 in the vicinity of the first header 34 from refreezing. As a result, it is possible to suppress a decrease in heating capacity and damage to the heat exchanger 30. Further, since the gas pipe 37 is arranged below the first header 34 and does not interfere with the drainage path of the defrost water 50, deterioration of the drainage property can be prevented. The wider the contact area between the gas pipe 37 and the first header 34, the more heat of the gas pipe 37 can be transferred to the first header 34.
  • the heat exchanger 30 has two heat exchangers, but is not limited thereto, and may have one or three or more heat exchangers.
  • FIG. 4 is a perspective view showing a modified example of the heat exchanger 30 according to the first embodiment.
  • a first header 34 is provided at the lower end of the heat exchanger 311 and a first header 34 is provided at the upper end of the heat exchanger 311.
  • the two headers 35 are provided, and the column passing header 33 is not provided.
  • the liquid pipe 36 is connected to the first header 34, and the gas pipe 37 is connected to the second header 35.
  • the first header 34 is provided at the lower end of the most leeward heat exchanger, and the first header 34 is provided at the upper end of the leeward heat exchanger.
  • Two headers 35 are provided.
  • the number of heat exchangers-1 column passing header 33 is provided to connect adjacent heat exchangers to each other. Then, the liquid pipe 36 is connected to the first header 34, and the gas pipe 37 is connected to the second header 35.
  • the first header 34 is provided at the lower end of the heat exchanger on the most upwind side, and the first header 34 is provided at the lower end of the heat exchanger on the leeward side.
  • Two headers 35 are provided.
  • the number of heat exchangers-1 column passing header 33 is provided to connect adjacent heat exchangers to each other. Then, the liquid pipe 36 is connected to the first header 34, and the gas pipe 37 is connected to the second header 35.
  • the heat exchanger 30 is a heat exchanger 30 having at least one heat exchanger having a plurality of flat tubes 38 along the air flow direction, and is the most windy side.
  • a first header provided at the lower end of the heat exchanger, a second header provided at the upper end or the lower end of the most leeward heat exchanger, and a refrigerant when connected to the first header and functioning as an evaporator.
  • It is provided with a gas pipe 37. At least a part of the gas pipe 37 is provided along the long axis direction of the first header, and at least a part of the gas pipe 37 is in contact with the first header.
  • the heat exchanger 30 According to the heat exchanger 30 according to the first embodiment, at least a part of the gas pipe 37 is provided along the long axis direction of the first header 34, and at least a part of the gas pipe 37 is provided in the first header. It is in contact with 34. Therefore, the heat of the gas pipe 37 through which the high-temperature and high-pressure gas refrigerant flows during the defrosting operation can be transferred to the first header 34. Then, the heat transferred to the first header 34 is transmitted to the defrost water in the vicinity of the first header 34, and the temperature of the defrost water 50 becomes high.
  • the gas pipe 37 is arranged below the first header 34.
  • the gas pipe 37 is arranged below the first header 34 and does not interfere with the drainage path of the defrost water 50, so that deterioration of the drainage property is prevented. be able to.
  • the outdoor unit 10 according to the first embodiment is provided with the above heat exchanger 30. According to the outdoor unit 10 according to the first embodiment, the same effect as that of the heat exchanger 30 can be obtained.
  • the air conditioner 100 according to the first embodiment is provided with the above-mentioned outdoor unit 10. According to the air conditioner 100 according to the first embodiment, the same effect as that of the outdoor unit 10 can be obtained.
  • Embodiment 2 Hereinafter, the second embodiment will be described, but the description of the parts overlapping with the first embodiment will be omitted, and the same parts or the corresponding parts as those of the first embodiment will be designated by the same reference numerals.
  • FIG. 5 is a perspective view of the top-flow type outdoor unit 10a on which the heat exchanger 30 and the heat exchanger 30 according to the second embodiment are mounted.
  • the heat exchanger 30 according to the second embodiment is mounted on the top flow type outdoor unit 10a.
  • the heat exchanger 30 has an L-shape in a plan view, and is mounted on the outdoor unit 10a so that the two heat exchangers 30 form a rectangular shape in a plan view.
  • the heat exchanger 30 does not have to have a strictly L-shape in a plan view. Further, the two heat exchangers 30 do not have to form a strictly rectangular shape in a plan view.
  • the outdoor unit 10a includes a box-shaped casing 15. A suction port 16 is formed on each of the four side surfaces of the casing 15, and an air outlet 17 is formed on the upper surface of the casing 15. Further, the outdoor unit 10a includes two heat exchangers 30 arranged in the casing 15 so as to be along the suction ports 16 on each of the four side surfaces of the casing 15. Further, the outdoor unit 10a is arranged inside the fan guard 18 provided so as to be ventilated so as to cover the air outlet 17 of the casing 15, and the outside air is sucked from the suction port 16 and the outside air is sucked from the air outlet 17. It is equipped with a fan 13 for discharging.
  • the two heat exchangers 30 are arranged below the fan 13. Further, the two heat exchangers 30 are arranged along the four side surfaces of the casing 15. The two heat exchangers 30 are fixed to the pillars 15a provided at the four corners of the casing 15 with screws or the like. Then, the outdoor air sucked from the suction ports 16 formed on each side surface by the fan 13 is heat-exchanged with the refrigerant by each heat exchanger 30 and then blown out from the outlet 17.
  • side panels 15b are provided on each of the four side surfaces of the casing 15, and a machine room (not shown) in which the compressor 11 and the like are housed is formed in the space surrounded by the side panels 15b. ..
  • the side panel 15b is formed below the two heat exchangers 30.
  • a gap 19 is formed between each side panel 15b and each heat exchanger 30. This gap 19 serves as a handling space for the gas pipe 37. Further, the gap 19 is a space for securing a drainage path for the defrosted water generated in the heat exchanger 30. That is, the gap 19 makes it possible to provide the gas pipe 37 along the long axis direction of the auxiliary side first header 34b of the heat exchanger 30, and also prevents deterioration of drainage.
  • FIG. 6 is a perspective view of the heat exchanger 30 according to the second embodiment.
  • the heat exchanger 30 according to the second embodiment has a plurality of heat exchangers along the air flow direction. Specifically, the heat exchanger 30 has a first heat exchanger 31 on the windward side and a second heat exchanger 32 on the leeward side.
  • the first heat exchanger 31 is composed of a main side first heat exchanger 31a and an auxiliary side first heat exchanger 31b in which the number of flat tubes 38 is smaller than that of the main side first heat exchanger 31a.
  • the second heat exchanger 32 is composed of a main side second heat exchanger 32a and an auxiliary side second heat exchanger 32b in which the number of flat tubes 38 is smaller than that of the main side second heat exchanger 32a.
  • the heat exchanger 30 is divided into a main heat exchange unit 30a and an auxiliary heat exchange unit 30b.
  • the main heat exchange unit 30a includes a main side first heat exchanger 31a, a main side second heat exchanger 32a, a main side first header 34a (hereinafter, also referred to as a first header), a main side second header 35a, and a main side. It is provided with a column passing header 33a.
  • the auxiliary heat exchange unit 30b includes an auxiliary side first heat exchanger 31b (hereinafter, also referred to as a second header), an auxiliary side second heat exchanger 32b, an auxiliary side first header 34b, and an auxiliary side second header 35b. It is provided with an auxiliary side column passing header 33b.
  • a main side first header 34a is provided at the lower end of the main side first heat exchanger 31a.
  • the lower end of the flat tube 38 of the main side first heat exchanger 31a is directly inserted into the main side first header 34a.
  • the main side first header 34a is connected to the refrigerant circuit of the air conditioner 100 via the gas pipe 37.
  • An opening 34a1 is formed in a portion of the first header 34a on the main side to which the gas pipe 37 is connected.
  • the first header 34a on the main side causes the high-temperature and high-pressure gas refrigerant from the compressor 11 to flow into the heat exchanger 30 during the cooling operation, and the low-temperature and low-pressure gas refrigerant after the heat is exchanged by the heat exchanger 30 during the heating operation. Let it flow out to the refrigerant circuit.
  • An auxiliary side first header 34b is provided at the lower end of the auxiliary side first heat exchanger 31b.
  • the lower end of the flat tube 38 of the auxiliary side first heat exchanger 31b is directly inserted into the auxiliary side first header 34b.
  • the first header 34b on the auxiliary side is connected to the refrigerant circuit of the air conditioner 100 via the liquid pipe 36.
  • An opening (not shown) is formed in a portion of the auxiliary side first header 34b to which the liquid pipe 36 is connected.
  • the first header 34b on the auxiliary side causes a low-temperature low-pressure two-phase refrigerant to flow into the heat exchanger 30 during the heating operation, and the low-temperature high-pressure liquid refrigerant after heat exchange in the heat exchanger 30 during the cooling operation flows out to the refrigerant circuit.
  • the inlet of the refrigerant becomes the gas pipe 37 connected to the first header 34a on the main side, and the outlet of the refrigerant becomes the liquid pipe 36 connected to the first header 34b on the auxiliary side. .. Further, during the heating operation, the inlet of the refrigerant becomes the liquid pipe 36 connected to the first header 34b on the auxiliary side, and the outlet of the refrigerant becomes the gas pipe 37 connected to the first header 34a on the main side.
  • a main side second header 35a is provided at the lower end of the main side second heat exchanger 32a.
  • the lower end of the flat tube 38 of the main side second heat exchanger 32a is directly inserted into the main side second header 35a.
  • an auxiliary side second header 35b (see FIG. 7) is provided at the lower end portion of the auxiliary side second heat exchanger 32b.
  • the lower end of the flat tube 38 of the auxiliary side second heat exchanger 32b is directly inserted into the auxiliary side second header 35b.
  • the main side second header 35a and the auxiliary side second header 35b communicate with each other.
  • the upper ends of a plurality of flat tubes 38 inserted into the main side first header 34a and the main side second header 35a are inserted.
  • the main side column passing header 33a is provided.
  • the upper ends of a plurality of flat tubes 38 inserted into the auxiliary side first header 34b and the auxiliary side second header 35b Is provided with an auxiliary side column passing header 33b into which the is inserted.
  • the liquid pipe 36 is connected to the auxiliary side first header 34b, and the gas pipe 37 is connected to the main side first header 34a. At least a part of the gas pipe 37 is provided along the long axis direction of the auxiliary side first header 34b, and at least a part of the gas pipe 37 is in contact with the auxiliary side first header 34b. Further, the gas pipe 37 is arranged below the first header 34b on the auxiliary side.
  • the main heat exchange portion 30a has bent portions 41 and 42 (see FIGS. 7 and 9 described later) in the middle of the flow paths of the main side first header 34a and the main side second header 35a, respectively. As a result, the main heat exchange portion 30a can be arranged so as to straddle two side surfaces of the casing 15 adjacent to each other.
  • the main side first header 34a and the auxiliary side first header 34b are configured such that the first header 34 is partitioned by a partition plate (not shown) provided inside the first header 34. Further, the main side row passing header 33a and the auxiliary side row passing header 33b are configured by partitioning the row passing header 33 by a partition plate (not shown) provided inside the main side row passing header 33a and the auxiliary side row passing header 33b. That is, the main side first header 34a and the auxiliary side first header 34b, and the main side row passing header 33a and the auxiliary side row passing header 33b are configured by partitioning the same body by a partition plate (not shown). Has been done.
  • main side first header 34a and the auxiliary side first header 34b, and the main side column passing header 33a and the auxiliary side column passing header 33b may be configured as separate bodies. Further, the main side second header 35a and the auxiliary side second header 35b are not separated by a partition plate (not shown), and as described above, the main side second header 35a and the auxiliary side second header 35b are Communicate with each other.
  • the flow of the refrigerant in the main side first heat exchanger 31a becomes a countercurrent flow to the flow of the refrigerant in the auxiliary side first heat exchanger 31b, and the main side second heat exchanger 32a
  • the flow of the refrigerant is configured to be opposite to the flow of the refrigerant in the auxiliary side second heat exchanger 32b.
  • FIG. 7 is a plan view schematically showing the flow of the refrigerant during the heating operation of the heat exchanger 30 according to the second embodiment.
  • FIG. 8 is a perspective view schematically showing the flow of the refrigerant during the heating operation of the heat exchanger 30 according to the second embodiment. Note that FIG. 8 shows only one heat exchanger 30 surrounded by the broken line in FIG. 7, but the other heat exchanger 30 has the same structure and the same flow of the refrigerant.
  • a low-temperature low-pressure gas-liquid two-phase refrigerant flows into the heat exchanger 30 from the liquid pipe 36.
  • the low-temperature and low-pressure gas-liquid two-phase refrigerant flowing into the heat exchanger 30 includes an auxiliary side first header 34b, an auxiliary side first heat exchanger 31b, an auxiliary side row passing header 33b, an auxiliary side second heat exchanger 32b, and an auxiliary side.
  • Side second header 35b, main side second header 35a, main side second heat exchanger 32a, main side row passing header 33a, main side first heat exchanger 31a, main side first header 34a flow in this order, and low temperature and low pressure. It becomes the gas refrigerant of. Then, the low-temperature low-pressure gas refrigerant flows out of the heat exchanger 30 from the gas pipe 37.
  • FIG. 9 is a plan view schematically showing the flow of the refrigerant during the defrosting operation of the heat exchanger 30 according to the second embodiment.
  • FIG. 10 is a perspective view schematically showing the flow of the refrigerant during the defrosting operation of the heat exchanger 30 according to the second embodiment. Note that FIG. 10 shows only one heat exchanger 30 surrounded by the broken line in FIG. 9, but the other heat exchanger 30 has the same structure and the same flow of the refrigerant.
  • a high-temperature and high-pressure gas refrigerant flows into the heat exchanger 30 from the gas pipe 37.
  • the high-temperature and high-pressure gas refrigerant flowing into the heat exchanger 30 includes a main side first header 34a, a main side first heat exchanger 31a, a main side row passing header 33a, a main side second heat exchanger 32a, and a main side second.
  • the header 35a, the auxiliary side second header 35b, the auxiliary side second heat exchanger 32b, the auxiliary side row passing header 33b, the auxiliary side first heat exchanger 31b, and the auxiliary side first header 34b flow in this order, and are low temperature and high pressure gas refrigerants. It becomes. Then, the low-temperature and high-pressure gas refrigerant flows out of the heat exchanger 30 from the liquid pipe 36.
  • the gas pipe 37 is connected to the main side first header 34a, and during the defrosting operation, the high temperature and high pressure gas refrigerant flows into the heat exchanger 30 from the windward side first header 34a. do. Therefore, it is possible to efficiently defrost the main side first heat exchanger 31a on the windward side where the amount of frost formation is large, and the defrosting time can be shortened. Further, at least a part of the gas pipe 37 is provided along the long axis direction of the auxiliary side first header 34b, and at least a part of the gas pipe 37 is in contact with the auxiliary side first header 34b. Therefore, the heat of the gas pipe 37 through which the high-temperature and high-pressure gas refrigerant flows during the defrosting operation can be transferred to the auxiliary side first header 34b.
  • the heat transferred to the auxiliary side first header 34b is transmitted to the defrost water in the vicinity of the auxiliary side first header 34b, and the temperature of the defrost water becomes high. Therefore, even if the heating operation is restarted after the defrosting operation is completed, the defrosting water in the vicinity of the auxiliary side first header 34b at the lower end of the auxiliary side first heat exchanger 31b where the defrosting water tends to collect after defrosting is generated. It is possible to suppress refreezing. As a result, it is possible to suppress a decrease in heating capacity and damage to the heat exchanger 30. Further, since the gas pipe 37 is arranged below the first header 34b on the auxiliary side and does not interfere with the drainage path of the defrosted water, deterioration of the drainage property can be prevented.
  • the heat exchanger 30 is mounted on the top-flow type outdoor unit 10a
  • the present invention is not limited to this, and the heat exchanger 30 is another type of outdoor unit such as the side-flow type. It can also be installed in.
  • the heat exchanger 30 has two heat exchangers, but is not limited thereto, and may have one or three or more heat exchangers.
  • FIG. 11 is a plan view schematically showing the flow of the refrigerant during the defrosting operation of the modified example of the heat exchanger 30 according to the second embodiment.
  • FIG. 12 is a perspective view schematically showing the flow of the refrigerant during the defrosting operation of the modified example of the heat exchanger 30 according to the second embodiment. Note that FIG. 12 shows only one heat exchanger 30 surrounded by the broken line in FIG. 11, but the other heat exchanger 30 has the same structure.
  • a main side first header 34a is provided at the lower end of the main side heat exchanger 31a1 to provide main side heat.
  • a second header 35a on the main side is provided at the upper end of the exchanger 31a1.
  • an auxiliary side first header 34b is provided at the lower end portion of the auxiliary side heat exchanger 31b1
  • an auxiliary side second header 35b is provided at the upper end portion of the auxiliary side heat exchanger 31b1
  • a main side row passing header 33a is provided.
  • the auxiliary side column passing header 33b is not provided. Then, the liquid pipe 36 is connected to the auxiliary side first header 34b, and the gas pipe 37 is connected to the main side first header 34a.
  • the main side first header 34a is provided at the lower end of the wind-upper main side heat exchanger, and the wind-up side auxiliary side heat exchange is provided.
  • An auxiliary side first header 34b is provided at the lower end of the body.
  • the main side second header 35a is provided at the upper end portion of the main leeward side heat exchanger, and the auxiliary side second header 35b is provided at the upper end portion of the auxiliary side heat exchanger on the leeward side.
  • the number of heat exchangers-1 main side row passing header 33a is provided, and adjacent main side heat exchangers are connected to each other.
  • the number of heat exchangers-1 auxiliary side row passing header 33b is provided to connect adjacent auxiliary heat exchangers to each other. Then, the liquid pipe 36 is connected to the auxiliary side first header 34b, and the gas pipe 37 is connected to the main side first header 34a.
  • the main side first header 34a is provided at the lower end of the most windy side main side heat exchanger, and the most windy side auxiliary side heat exchange is provided.
  • An auxiliary side first header 34b is provided at the lower end of the body.
  • the main side second header 35a is provided at the lower end of the most leeward main side heat exchanger, and the auxiliary side second header 35b is provided at the lower end of the most leeward auxiliary heat exchanger.
  • the number of heat exchangers-1 main side row passing header 33a is provided, and adjacent main side heat exchangers are connected to each other.
  • the number of heat exchangers-1 auxiliary side row passing header 33b is provided to connect adjacent auxiliary heat exchangers to each other. Then, the liquid pipe 36 is connected to the auxiliary side first header 34b, and the gas pipe 37 is connected to the main side first header 34a.
  • the heat exchanger 30 is composed of a main heat exchanger and an auxiliary heat exchanger in which the number of flat tubes 38 is smaller than that of the main heat exchanger, which has a plurality of flat tubes 38.
  • a heat exchanger 30 having at least one heat exchanger provided along the direction of air flow, the first header provided at the lower end of the auxiliary heat exchanger on the most wind side, and the windmost side.
  • a liquid pipe connected to the first header and the second header provided at the lower end of the main heat exchanger, in which the refrigerant flows in when functioning as an evaporator and the refrigerant flows out when functioning as a condenser.
  • the refrigerant flows out when functioning as an evaporator and the refrigerant flows in when functioning as a condenser.
  • At least a part of the gas pipe 37 is provided along the long axis direction of the first header, and at least a part of the gas pipe 37 is in contact with the first header.
  • the heat exchanger 30 According to the heat exchanger 30 according to the second embodiment, at least a part of the gas pipe 37 is provided along the long axis direction of the first header 34, and at least a part of the gas pipe 37 is provided in the first header. It is in contact with 34. Therefore, the heat of the gas pipe 37 through which the high-temperature and high-pressure gas refrigerant flows during the defrosting operation can be transferred to the first header 34. Then, the heat transferred to the first header 34 is transmitted to the defrost water in the vicinity of the first header 34, and the temperature of the defrost water 50 becomes high.
  • the gas pipe 37 is arranged below the first header 34.
  • the gas pipe 37 is arranged below the first header 34 and does not interfere with the drainage path of the defrost water 50, so that deterioration of the drainage property is prevented. be able to.
  • the outdoor unit 10 according to the second embodiment includes the above heat exchanger 30. According to the outdoor unit 10 according to the second embodiment, the same effect as that of the heat exchanger 30 can be obtained.
  • the outdoor unit 10 of the air conditioner 100 includes the heat exchanger 30, a casing 15 having a suction port 16 on the side surface and an outlet 17 on the upper surface, and the heat exchanger 30.
  • a fan 13 provided on the upper side is provided, and the casing 15 has a side panel 15b for covering the machine room formed inside thereof under the heat exchanger 30, and the heat exchanger 30 and the side panel 15b are provided with each other. A gap 19 is formed between them.
  • a gap 19 is formed between the heat exchanger 30 and the side panel 15b.
  • This gap 19 serves as a space for handling the gas pipe 37 and a space for securing a drainage path for the defrosted water generated in the heat exchanger 30. Therefore, the gap 19 makes it possible to provide the gas pipe 37 along the long axis direction of the auxiliary side first header 34b of the heat exchanger 30, and it is possible to prevent deterioration of drainage.
  • the air conditioner 100 according to the second embodiment includes the above-mentioned outdoor unit 10. According to the air conditioner 100 according to the second embodiment, the same effect as that of the outdoor unit 10 can be obtained.
  • Embodiment 3 Hereinafter, the third embodiment will be described, but the description thereof will be omitted for the parts overlapping with the second embodiment, and the same parts or the corresponding parts as those in the second embodiment will be designated by the same reference numerals.
  • FIG. 13 is an enlarged front view schematically showing a main part of the heat exchanger 30 according to the third embodiment.
  • the gas pipe 37 is provided along the long axis direction of the auxiliary side first header 34b.
  • the gas pipe 37 is in contact with the auxiliary side first header 34b in the entire area 34b1 in which the flat pipe 38 is provided. Further, the gas pipe 37 is arranged below the first header 34b on the auxiliary side.
  • the gas pipe 37 is brought into contact with the auxiliary side first header 34b and the entire area 34b1 in which the flat pipe 38 is provided.
  • the heat of the gas pipe 37 through which the high-temperature and high-pressure gas refrigerant flows during the defrosting operation is transferred by the auxiliary side first header 34b, as compared with the case where the gas pipe 37 is only partially in contact with the auxiliary side first header 34b. It can be made easier to convey.
  • the heat exchanger 30 when molding the heat exchanger 30, it is possible to braze the gas pipe 37 to the auxiliary side first header 34b at the same time as brazing the flat pipe 38 and fins 39 of the heat exchanger 30 and each header. Therefore, the production of the heat exchanger 30 can be simplified. Further, since the gas pipe 37 is arranged closer to the auxiliary side first header 34b, a space is formed in the lower part of the heat exchanger 30, and a service space can be secured.
  • the gas pipe 37 is in contact with the first header in the entire area 34b1 in which the flat pipe 38 is provided.
  • the heat of the gas pipe 37 through which the high-temperature and high-pressure gas refrigerant flows during the defrosting operation is compared with the case where the gas pipe 37 is only partially in contact with the first header. Can be easily conveyed by the first header.
  • the outdoor unit 10 according to the third embodiment includes the above heat exchanger 30. According to the outdoor unit 10 according to the third embodiment, the same effect as that of the heat exchanger 30 can be obtained.
  • the air conditioner 100 according to the third embodiment includes the above-mentioned outdoor unit 10. According to the air conditioner 100 according to the third embodiment, the same effect as that of the outdoor unit 10 can be obtained.
  • Embodiment 4 Hereinafter, the fourth embodiment will be described, but the description of the parts overlapping with the second embodiment will be omitted, and the same parts or the corresponding parts as those of the second embodiment will be designated by the same reference numerals.
  • FIG. 14 is an enlarged front view schematically showing a main part of the heat exchanger 30 according to the fourth embodiment.
  • the auxiliary side first header 34b and the main side first header 34a are displaced in the height direction, and the auxiliary side first header 34b is It is arranged above the first header 34a on the main side.
  • at least a part of the gas pipe 37 is provided along the long axis direction of the auxiliary side first header 34b.
  • at least a part of the gas pipe 37 is in contact with the auxiliary side first header 34b.
  • the gas pipe 37 is arranged below the first header 34b on the auxiliary side. Therefore, the portion (hereinafter referred to as a parallel portion) 37b parallel to the auxiliary side first header 34b of the gas pipe 37 is arranged at substantially the same height as the main side first header 34a.
  • auxiliary side first header 34b By arranging the auxiliary side first header 34b above the main side first header 34a in this way, a space is formed in the lower part of the heat exchanger 30 and a service space can be secured. Further, since the parallel portion 37b of the gas pipe 37 can be arranged at substantially the same height as the main side first header 34a, the gas pipe 37 is not perpendicular to the main side first header 34a but in the parallel direction. It becomes possible to connect, and it is possible to simplify the piping connection.
  • the first header and the second header are displaced in the height direction, and the first header is arranged above the second header.
  • the heat exchanger 30 by arranging the first header above the second header, a space is formed in the lower part of the heat exchanger 30 and a service space can be secured. .. Further, since the portion parallel to the first header of the gas pipe 37 can be arranged at substantially the same height as the first header, the gas pipe 37 is not perpendicular to the main side first header 34a but in the parallel direction. It becomes possible to connect to, and it is possible to simplify the piping connection.
  • the outdoor unit 10 according to the fourth embodiment includes the above heat exchanger 30. According to the outdoor unit 10 according to the third embodiment, the same effect as that of the heat exchanger 30 can be obtained.
  • the air conditioner 100 according to the fourth embodiment includes the above-mentioned outdoor unit 10. According to the air conditioner 100 according to the third embodiment, the same effect as that of the outdoor unit 10 can be obtained.
  • Embodiment 5 Hereinafter, the fifth embodiment will be described, but the description thereof will be omitted for the parts that overlap with the second embodiment, and the same parts or the corresponding parts as those in the second embodiment will be designated by the same reference numerals.
  • FIG. 15 is a perspective view schematically showing the joint 60 of the heat exchanger 30 according to the fifth embodiment.
  • FIG. 16 is a cross-sectional view schematically showing the joint 60 of the heat exchanger 30 according to the fifth embodiment.
  • the heat exchanger 30 according to the fifth embodiment includes the joint 60 shown in FIGS. 15 and 16.
  • the joint 60 is made of aluminum like the gas pipe 37 and the main side first header 34a. Further, a first opening 60a is formed on one side surface of the joint 60, and a second opening 60b is formed on the upper surface of the joint 60.
  • the first opening 60a and the second opening 60b are communicated with each other by an L-shaped communication hole 60c formed inside the joint 60.
  • the communication hole 60c does not have to be strictly L-shaped.
  • the gas pipe 37 can be made into an L shape. That is, the gas pipe 37 has an L-shape having a joint 60 provided at its corner. Therefore, the gas pipe 37 can be connected in the direction perpendicular to the main side first header 34a.
  • the gas pipe 37 is connected in the direction perpendicular to the main side first header 34a without using the joint 60, it is necessary to bend the gas pipe 37, and there is also a space for routing the gas pipe 37. You will need it.
  • the gas pipe 37 is connected in the direction perpendicular to the main side first header 34a. It is not necessary to bend the 37, and the piping connection can be simplified. Further, since the space for routing the gas pipe 37 is not required, a space is formed in the lower part of the heat exchanger 30, and a service space can be secured.
  • the heat exchanger 30 includes a joint 60 having an L-shaped communication hole 60c formed therein, the gas pipe 37 has an L-shape, and the joint 60 is provided at a corner thereof. It is provided.
  • the gas pipe 37 since the gas pipe 37 has an L-shape having a joint 60 provided at its corner, the gas pipe 37 is perpendicular to the first header. It is not necessary to bend the gas pipe 37 when connecting in the direction, and the pipe connection can be simplified. Further, since the space for routing the gas pipe 37 is not required, a space is formed in the lower part of the heat exchanger 30, and a service space can be secured.
  • the outdoor unit 10 according to the fifth embodiment includes the above heat exchanger 30. According to the outdoor unit 10 according to the third embodiment, the same effect as that of the heat exchanger 30 can be obtained.
  • the air conditioner 100 according to the fifth embodiment includes the above-mentioned outdoor unit 10. According to the air conditioner 100 according to the third embodiment, the same effect as that of the outdoor unit 10 can be obtained.

Abstract

A heat exchanger which comprises, along an air flow direction, at least one heat-exchange element having a plurality of flat tubes and is installed in an outdoor unit, said heat exchanger comprising: a first header which is provided on a lower end of the heat-exchange element that is the furthest upstream; a second header which is provided on an upper or lower end of the heat-exchange element that is the furthest downstream; liquid piping which is connected to the first header and through which refrigerant flows in during an evaporator function and flows out during a condenser function; and gas piping which is connected to the second header and through which refrigerant flows out during the evaporator function and flows in during the condenser function, wherein at least part of the gas piping is provided along the length direction of the first header, and at least part of the gas piping is in contact with the first header.

Description

熱交換器、熱交換器を備えた室外機、および、室外機を備えた空気調和装置A heat exchanger, an outdoor unit equipped with a heat exchanger, and an air conditioner equipped with an outdoor unit.
　本開示は、複数の扁平管を有する熱交換器、熱交換器を備えた室外機、および、室外機を備えた空気調和装置に関するものである。 The present disclosure relates to a heat exchanger having a plurality of flat tubes, an outdoor unit equipped with a heat exchanger, and an air conditioner equipped with an outdoor unit.
　従来、風の流れ方向に前後二列に並ぶ熱交換コアと、各熱交換コアの相互に共通の上部ヘッダタンクと個別の下部ヘッダタンクとを備え、前後二列に並ぶ風上側の熱交換コアおよび風下側の熱交換コアのいずれにおいても十分な温度差を確保して伝熱性能を向上させた熱交換器がある（例えば、特許文献１参照）。 Conventionally, the heat exchange cores are arranged in two rows in the front and rear in the direction of the wind flow, and the upper header tank and the separate lower header tanks that are common to each other of the heat exchange cores are provided. In any of the heat exchange cores on the leeward side, there is a heat exchanger in which a sufficient temperature difference is secured to improve the heat transfer performance (see, for example, Patent Document 1).
　特許文献１の熱交換器は、凝縮器として機能する場合、高温高圧のガス冷媒が風下側の下部ヘッダタンクから流入し、風下側の熱交換コア、上部ヘッダタンク、風上側の熱交換コアの順に流れ、低温高圧の液冷媒となって風上側の下部ヘッダタンクから流出する。また、この熱交換器は、蒸発器として機能する場合、低温低圧の二相冷媒が風上側の下部ヘッダタンクから流入し、風上側の熱交換コア、上部ヘッダタンク、風下側の熱交換コアの順に流れ、低温低圧のガス冷媒となって風下側の下部ヘッダタンクから流出する。 When the heat exchanger of Patent Document 1 functions as a condenser, a high-temperature and high-pressure gas refrigerant flows in from the lower header tank on the leeward side, and the heat exchange core on the leeward side, the upper header tank, and the heat exchange core on the leeward side It flows in order, becomes a low-temperature and high-pressure liquid refrigerant, and flows out from the lower header tank on the wind side. Further, when this heat exchanger functions as an evaporator, a low-temperature low-pressure two-phase refrigerant flows in from the lower header tank on the windward side, and the heat exchange core on the windward side, the upper header tank, and the heat exchange core on the leeward side. It flows in order, becomes a low-temperature low-pressure gas refrigerant, and flows out from the lower header tank on the leeward side.
特開２０１８－９６６３８号公報Japanese Unexamined Patent Publication No. 2018-96638
　特許文献１のような従来の熱交換器を、冷房運転および暖房運転の両方が運転可能な空気調和装置の室外機に用いる場合、外気温度が低温となる暖房運転では、低温低圧の二相冷媒が風上側の熱交換コアを流れるため、そこで多くの着霜が生じる。また、除霜運転では、高温高圧のガス冷媒を風下側の下部ヘッダタンクから流入させ、風上側の熱交換コアへ流すことで除霜する。除霜後、熱交換コアの表面に発生した除霜水は下方に流れるが、特に風上側の下部ヘッダタンク近傍に溜まりやすい。そして、暖房運転が再開されると、低温低圧の二相冷媒が風上側の下部ヘッダタンクから流入するが、風上側のヘッダタンク近傍に溜まった除霜水の温度は低いため、除霜水が再氷結して根氷となり、暖房能力の低下および熱交換器の破損を招くという課題があった。 When a conventional heat exchanger as in Patent Document 1 is used for an outdoor unit of an air conditioner capable of operating both cooling operation and heating operation, in the heating operation where the outside air temperature is low, a low temperature and low pressure two-phase refrigerant is used. Flows through the heat exchange core on the wind side, causing a lot of frost there. In the defrosting operation, high-temperature and high-pressure gas refrigerant flows in from the lower header tank on the leeward side and flows to the heat exchange core on the leeward side to defrost. After defrosting, the defrosted water generated on the surface of the heat exchange core flows downward, but tends to collect especially near the lower header tank on the windward side. Then, when the heating operation is restarted, the low-temperature low-pressure two-phase refrigerant flows in from the lower header tank on the wind side, but the defrost water collected near the header tank on the wind side is low in temperature, so that the defrost water is discharged. There was a problem that it re-freezes and becomes root ice, which causes a decrease in heating capacity and damage to the heat exchanger.
　本開示は、以上のような課題を解決するためになされたもので、除霜水の再氷結を抑制することができる熱交換器、熱交換器を備えた室外機、および、室外機を備えた空気調和装置を提供することを目的としている。 The present disclosure has been made to solve the above problems, and includes a heat exchanger capable of suppressing refreezing of defrosted water, an outdoor unit equipped with a heat exchanger, and an outdoor unit. It is intended to provide an air conditioner.
　本開示に係る熱交換器は、複数の扁平管を有する熱交換体を空気の流れ方向に沿って少なくとも一つ以上備えた、室外機に搭載される熱交換器であって、最も風上側の熱交換体の下端部に設けられる第１ヘッダと、最も風下側の熱交換体の上端部または下端部に設けられる第２ヘッダと、前記第１ヘッダに接続され、蒸発器として機能する際に冷媒が流入し、凝縮器として機能する際に冷媒が流出する液配管と、前記第２ヘッダに接続され、蒸発器として機能する際に冷媒が流出し、凝縮器として機能する際に冷媒が流入するガス配管と、を備え、前記ガス配管の少なくとも一部は前記第１ヘッダの長軸方向に沿って設けられており、前記ガス配管は、少なくとも一部が前記第１ヘッダと接触しているものである。 The heat exchanger according to the present disclosure is a heat exchanger mounted on an outdoor unit provided with at least one heat exchanger having a plurality of flat tubes along the direction of air flow, and is the most wind-upper side. When the first header provided at the lower end of the heat exchanger, the second header provided at the upper end or the lower end of the most leeward heat exchanger, and the first header are connected to function as an evaporator. A liquid pipe in which the refrigerant flows in and flows out when it functions as a condenser, and a liquid pipe which is connected to the second header and flows out when it functions as an evaporator and flows in when it functions as a condenser. At least a part of the gas pipe is provided along the long axis direction of the first header, and at least a part of the gas pipe is in contact with the first header. It is a thing.
　また、本開示に係る熱交換器は、複数の扁平管を有し、主熱交換体と該主熱交換体よりも前記扁平管の数が少ない補助熱交換体とで構成された熱交換体を空気の流れ方向に沿って少なくとも一つ以上備えた、室外機に搭載される熱交換器であって、最も風上側の補助側熱交換体の下端部に設けられた第１ヘッダと、最も風上側の主側熱交換体の下端部に設けられた第２ヘッダと、前記第１ヘッダに接続され、蒸発器として機能する際に冷媒が流入し、凝縮器として機能する際に冷媒が流出する液配管と、前記第２ヘッダに接続され、蒸発器として機能する際に冷媒が流出し、凝縮器として機能する際に冷媒が流入するガス配管と、を備え、前記ガス配管の少なくとも一部は前記第１ヘッダの長軸方向に沿って設けられており、前記ガス配管は、少なくとも一部が前記第１ヘッダと接触しているものである。 Further, the heat exchanger according to the present disclosure has a plurality of flat tubes, and is composed of a main heat exchanger and an auxiliary heat exchanger in which the number of the flat tubes is smaller than that of the main heat exchanger. A heat exchanger mounted on an outdoor unit, which is provided with at least one heat exchanger along the air flow direction, and has the first header provided at the lower end of the auxiliary heat exchanger on the windy side, and the most. Connected to the second header provided at the lower end of the main heat exchanger on the wind side and the first header, the refrigerant flows in when functioning as an evaporator, and flows out when functioning as a condenser. A gas pipe connected to the second header, from which the refrigerant flows out when functioning as an evaporator, and a gas pipe which is connected to the second header and into which the refrigerant flows when functioning as a condenser, is provided, and at least a part of the gas pipe. Is provided along the long axis direction of the first header, and at least a part of the gas pipe is in contact with the first header.
　また、本開示に係る空気調和装置の室外機は、上記の熱交換器を備えたものである。 Further, the outdoor unit of the air conditioner according to the present disclosure is equipped with the above heat exchanger.
　また、本開示に係る空気調和装置は、上記の室外機を備えたものである。 Further, the air conditioner according to the present disclosure is equipped with the above-mentioned outdoor unit.
　本開示に係る熱交換器、熱交換器を備えた室外機、および、室外機を備えた空気調和装置によれば、ガス配管の少なくとも一部は第１ヘッダの長軸方向に沿って設けられており、ガス配管は、少なくとも一部が第１ヘッダと接触している。そのため、除霜運転時に高温高圧のガス冷媒が流れるガス配管の熱を第１ヘッダに伝えることができる。そして、第１ヘッダに伝わった熱は、第１ヘッダ近傍の除霜水に伝わり、除霜水の温度が高くなる。そのため、除霜運転が終了後、暖房運転が再開されても、第１ヘッダ近傍の除霜水が再氷結するのを抑制することができる。 According to the heat exchanger, the outdoor unit provided with the heat exchanger, and the air conditioner provided with the outdoor unit according to the present disclosure, at least a part of the gas pipe is provided along the long axis direction of the first header. At least part of the gas pipe is in contact with the first header. Therefore, the heat of the gas pipe through which the high-temperature and high-pressure gas refrigerant flows during the defrosting operation can be transferred to the first header. Then, the heat transferred to the first header is transferred to the defrost water in the vicinity of the first header, and the temperature of the defrost water becomes high. Therefore, even if the heating operation is restarted after the defrosting operation is completed, it is possible to prevent the defrosting water in the vicinity of the first header from refreezing.
実施の形態１に係る熱交換器を備えた空気調和装置の冷媒回路図である。It is a refrigerant circuit diagram of the air conditioner provided with the heat exchanger which concerns on Embodiment 1. FIG. 実施の形態１に係る熱交換器の第一の斜視図である。It is the first perspective view of the heat exchanger which concerns on Embodiment 1. FIG. 実施の形態１に係る熱交換器の第二の斜視図である。It is a second perspective view of the heat exchanger which concerns on Embodiment 1. FIG. 実施の形態１に係る熱交換器の変形例を示す斜視図である。It is a perspective view which shows the modification of the heat exchanger which concerns on Embodiment 1. FIG. 実施の形態２に係る熱交換器および熱交換器が搭載されたトップフロー型の室外機の斜視図である。FIG. 3 is a perspective view of a top-flow type outdoor unit equipped with a heat exchanger and a heat exchanger according to the second embodiment. 実施の形態２に係る熱交換器の斜視図である。It is a perspective view of the heat exchanger which concerns on Embodiment 2. FIG. 実施の形態２に係る熱交換器の暖房運転時の冷媒の流れを模式的に示す平面図である。It is a top view which shows typically the flow of the refrigerant at the time of the heating operation of the heat exchanger which concerns on Embodiment 2. FIG. 実施の形態２に係る熱交換器の暖房運転時の冷媒の流れを模式的に示す斜視図である。It is a perspective view which shows typically the flow of the refrigerant at the time of the heating operation of the heat exchanger which concerns on Embodiment 2. FIG. 実施の形態２に係る熱交換器の除霜運転時の冷媒の流れを模式的に示す平面図である。It is a top view which shows typically the flow of the refrigerant at the time of the defrosting operation of the heat exchanger which concerns on Embodiment 2. FIG. 実施の形態２に係る熱交換器の除霜運転時の冷媒の流れを模式的に示す斜視図である。It is a perspective view which shows typically the flow of the refrigerant at the time of the defrosting operation of the heat exchanger which concerns on Embodiment 2. FIG. 実施の形態２に係る熱交換器の変形例の除霜運転時の冷媒の流れを模式的に示す平面図である。It is a top view which shows typically the flow of the refrigerant at the time of defrosting operation of the modification of the heat exchanger which concerns on Embodiment 2. FIG. 実施の形態２に係る熱交換器の変形例の除霜運転時の冷媒の流れを模式的に示す斜視図である。It is a perspective view which shows typically the flow of the refrigerant at the time of defrosting operation of the modification of the heat exchanger which concerns on Embodiment 2. FIG. 実施の形態３に係る熱交換器の要部を模式的に示す拡大図で正面図である。It is an enlarged front view schematically showing the main part of the heat exchanger according to the third embodiment. 実施の形態４に係る熱交換器の要部を模式的に示す拡大図で正面図である。It is an enlarged front view schematically showing the main part of the heat exchanger according to the fourth embodiment. 実施の形態５に係る熱交換器の継手を模式的に示す斜視図である。It is a perspective view which shows typically the joint of the heat exchanger which concerns on Embodiment 5. 実施の形態５に係る熱交換器の継手を模式的に示す断面図である。It is sectional drawing which shows typically the joint of the heat exchanger which concerns on Embodiment 5.
　以下、本開示の実施の形態を図面に基づいて説明する。なお、以下に説明する実施の形態によって本開示が限定されるものではない。また、以下の図面では各構成部材の大きさの関係が実際のものとは異なる場合がある。 Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. The present disclosure is not limited to the embodiments described below. Further, in the drawings below, the relationship between the sizes of the constituent members may differ from the actual one.
　実施の形態１．
＜空気調和装置１００の構成＞
　図１は、実施の形態１に係る熱交換器３０を備えた空気調和装置１００の冷媒回路図である。なお、図１中の実線矢印は冷房運転時の冷媒の流れを示しており、図１中の破線矢印は暖房運転時の冷媒の流れを示している。 Embodiment 1.
<Structure of air conditioner 100>
FIG. 1 is a refrigerant circuit diagram of an air conditioner 100 provided with a heat exchanger 30 according to the first embodiment. The solid line arrow in FIG. 1 indicates the flow of the refrigerant during the cooling operation, and the broken line arrow in FIG. 1 indicates the flow of the refrigerant during the heating operation.
　図１に示すように、実施の形態１に係る熱交換器３０は、室外機１０と室内機２０とを備えた空気調和装置１００の室外機１０に搭載されている。室外機１０は、熱交換器３０の他、圧縮機１１と、流路切替装置１２と、ファン１３とを備えている。室内機２０は、絞り装置２１と、室内熱交換器２２と、室内ファン２３とを備えている。 As shown in FIG. 1, the heat exchanger 30 according to the first embodiment is mounted on the outdoor unit 10 of the air conditioner 100 including the outdoor unit 10 and the indoor unit 20. The outdoor unit 10 includes a compressor 11, a flow path switching device 12, and a fan 13 in addition to the heat exchanger 30. The indoor unit 20 includes a throttle device 21, an indoor heat exchanger 22, and an indoor fan 23.
　また、空気調和装置１００は、圧縮機１１、流路切替装置１２、熱交換器３０、絞り装置２１、室内熱交換器２２が冷媒配管で接続され、冷媒が循環する冷媒回路を備えている。この空気調和装置１００は、流路切替装置１２の切り替えにより冷房運転および暖房運転の両方が運転可能である。 Further, the air conditioner 100 includes a refrigerant circuit in which a compressor 11, a flow path switching device 12, a heat exchanger 30, a throttle device 21, and an indoor heat exchanger 22 are connected by a refrigerant pipe and a refrigerant circulates. The air conditioner 100 can operate both the cooling operation and the heating operation by switching the flow path switching device 12.
　圧縮機１１は、低温低圧の冷媒を吸入し、吸入した冷媒を圧縮し、高温高圧の冷媒を吐出する。圧縮機１１は、例えば、運転周波数を変化させることにより、単位時間あたりの送出量である容量が制御されるインバータ圧縮機などからなる。 The compressor 11 sucks in the low temperature and low pressure refrigerant, compresses the sucked refrigerant, and discharges the high temperature and high pressure refrigerant. The compressor 11 is composed of, for example, an inverter compressor whose capacity, which is a transmission amount per unit time, is controlled by changing the operating frequency.
　流路切替装置１２は、例えば四方弁であり、冷媒の流れる方向を切り替えることにより、冷房運転と暖房運転との切り替えを行う。流路切替装置１２は、冷房運転時に、図１の実線で示す状態に切り替わり、圧縮機１１の吐出側と熱交換器３０とが接続される。また、流路切替装置１２は、暖房運転時に、図１の破線で示す状態に切り替わり、圧縮機１１の吐出側と室内熱交換器２２とが接続される。 The flow path switching device 12 is, for example, a four-way valve, and switches between cooling operation and heating operation by switching the flow direction of the refrigerant. The flow path switching device 12 switches to the state shown by the solid line in FIG. 1 during the cooling operation, and the discharge side of the compressor 11 and the heat exchanger 30 are connected to each other. Further, the flow path switching device 12 switches to the state shown by the broken line in FIG. 1 during the heating operation, and the discharge side of the compressor 11 and the indoor heat exchanger 22 are connected to each other.
　熱交換器３０は、室外空気と冷媒との間で熱交換を行う。熱交換器３０は、冷房運転の際に、冷媒の熱を室外空気に放熱して冷媒を凝縮させる凝縮器として機能する。また、熱交換器３０は、暖房運転の際に、冷媒を蒸発させ、その際の気化熱により室外空気を冷却する蒸発器として機能する。 The heat exchanger 30 exchanges heat between the outdoor air and the refrigerant. The heat exchanger 30 functions as a condenser that dissipates the heat of the refrigerant to the outdoor air and condenses the refrigerant during the cooling operation. Further, the heat exchanger 30 functions as an evaporator that evaporates the refrigerant during the heating operation and cools the outdoor air by the heat of vaporization at that time.
　ファン１３は、熱交換器３０に対して室外空気を供給するものであり、回転数が制御されることにより、熱交換器３０に対する送風量が調整される。 The fan 13 supplies outdoor air to the heat exchanger 30, and the amount of air blown to the heat exchanger 30 is adjusted by controlling the rotation speed.
　絞り装置２１は、例えば絞りの開度を調整することができる電子式膨張弁であり、開度を調整することによって熱交換器３０または室内熱交換器２２に流入する冷媒の圧力を制御する。なお、実施の形態では、絞り装置２１は室内機２０に設けられているが、室外機１０に設けられていてもよく、設置箇所は限定されない。 The throttle device 21 is, for example, an electronic expansion valve capable of adjusting the opening degree of the throttle, and controls the pressure of the refrigerant flowing into the heat exchanger 30 or the indoor heat exchanger 22 by adjusting the opening degree. In the embodiment, the diaphragm device 21 is provided in the indoor unit 20, but it may be provided in the outdoor unit 10, and the installation location is not limited.
　室内熱交換器２２は、室内空気と冷媒との間で熱交換を行う。室内熱交換器２２は、冷房運転の際に、冷媒を蒸発させ、その際の気化熱により室外空気を冷却する蒸発器として機能する。また、室内熱交換器２２は、暖房運転の際に、冷媒の熱を室外空気に放熱して冷媒を凝縮させる凝縮器として機能する。 The indoor heat exchanger 22 exchanges heat between the indoor air and the refrigerant. The indoor heat exchanger 22 functions as an evaporator that evaporates the refrigerant during the cooling operation and cools the outdoor air by the heat of vaporization at that time. Further, the indoor heat exchanger 22 functions as a condenser that dissipates the heat of the refrigerant to the outdoor air and condenses the refrigerant during the heating operation.
　室内ファン２３は、室内熱交換器２２に対して室内空気を供給するものであり、回転数が制御されることにより、室内熱交換器２２に対する送風量が調整される。 The indoor fan 23 supplies indoor air to the indoor heat exchanger 22, and the amount of air blown to the indoor heat exchanger 22 is adjusted by controlling the rotation speed.
＜熱交換器３０の構成＞
　図２は、実施の形態１に係る熱交換器３０の第一の斜視図である。図３は、実施の形態１に係る熱交換器３０の第二の斜視図である。なお、図２中および図３中の白抜き矢印は、ファン１３によって発生する風の流れを示す。また、図２中および図３中の黒の破線矢印は、冷媒の流れを示す。 <Structure of heat exchanger 30>
FIG. 2 is a first perspective view of the heat exchanger 30 according to the first embodiment. FIG. 3 is a second perspective view of the heat exchanger 30 according to the first embodiment. The white arrows in FIGS. 2 and 3 indicate the flow of wind generated by the fan 13. The black dashed arrows in FIGS. 2 and 3 indicate the flow of the refrigerant.
　図２および図３に示すように、熱交換器３０は、空気の流れ方向に沿って複数の熱交換体を有している。具体的には、熱交換器３０は、風上側の第１熱交換体３１と風下側の第２熱交換体３２とを有する。熱交換体は、複数の扁平管３８と複数のフィン３９とを有する。 As shown in FIGS. 2 and 3, the heat exchanger 30 has a plurality of heat exchangers along the air flow direction. Specifically, the heat exchanger 30 has a first heat exchanger 31 on the windward side and a second heat exchanger 32 on the leeward side. The heat exchanger has a plurality of flat tubes 38 and a plurality of fins 39.
　扁平管３８は、ファン１３によって発生した風が流れるように、間隔を空けて水平方向に並列して配置され、鉛直方向に延びる管内に鉛直方向に冷媒が流れる。フィン３９は、隣り合う扁平管３８の間にわたって接続され、扁平管３８に伝熱する。なお、フィン３９は、空気と冷媒との熱交換効率を向上させるものであり、たとえばコルゲートフィンが用いられる。しかし、これに限定されるものではない。扁平管３８の表面で空気と冷媒との熱交換が行われるため、フィン３９がなくてもよい。 The flat pipes 38 are arranged in parallel in the horizontal direction at intervals so that the wind generated by the fan 13 flows, and the refrigerant flows in the vertical direction in the pipes extending in the vertical direction. The fins 39 are connected between adjacent flat tubes 38 and transfer heat to the flat tubes 38. The fin 39 improves the heat exchange efficiency between the air and the refrigerant, and for example, a corrugated fin is used. However, it is not limited to this. Since heat exchange between air and the refrigerant is performed on the surface of the flat tube 38, the fins 39 may not be present.
　第１熱交換体３１の下端部には、第１ヘッダ３４が設けられている。第１ヘッダ３４には、第１熱交換体３１の扁平管３８の下端部が直接挿入されている。第１ヘッダ３４は、空気調和装置１００の冷媒回路に液配管３６を介して接続されている。第１ヘッダ３４は、液ヘッダとも呼ばれる。なお、第１ヘッダ３４の液配管３６が接続される部分には、開口部（図示せず）が形成されている。第１ヘッダ３４は、図２に示すように暖房運転時に低温低圧の二相冷媒を熱交換器３０に流入させ、図３に示すように冷房運転時に熱交換器３０で熱交換された後の低温高圧の液冷媒を冷媒回路に流出させる。 A first header 34 is provided at the lower end of the first heat exchanger 31. The lower end of the flat tube 38 of the first heat exchanger 31 is directly inserted into the first header 34. The first header 34 is connected to the refrigerant circuit of the air conditioner 100 via the liquid pipe 36. The first header 34 is also called a liquid header. An opening (not shown) is formed in a portion of the first header 34 to which the liquid pipe 36 is connected. As shown in FIG. 2, the first header 34 causes a low-temperature low-pressure two-phase refrigerant to flow into the heat exchanger 30 during the heating operation, and is heat-exchanged by the heat exchanger 30 during the cooling operation as shown in FIG. The low temperature and high pressure liquid refrigerant is discharged to the refrigerant circuit.
　第２熱交換体３２の下端部には、第２ヘッダ３５が設けられている。第２ヘッダ３５には、第２熱交換体３２の扁平管３８の下端部が直接挿入されている。また、第２ヘッダ３５は、第１ヘッダ３４に並列して配置されている。第２ヘッダ３５は、空気調和装置１００の冷媒回路にガス配管３７を介して接続されている。第２ヘッダ３５は、ガスヘッダとも呼ばれる。なお、第２ヘッダ３５のガス配管３７が接続される部分には、開口部（図示せず）が形成されている。第２ヘッダ３５は、図３に示すように冷房運転時に圧縮機１１からの高温高圧のガス冷媒を熱交換器３０に流入させ、図２に示すように暖房運転時に熱交換器３０で熱交換された後の低温低圧のガス冷媒を冷媒回路に流出させる。 A second header 35 is provided at the lower end of the second heat exchanger 32. The lower end of the flat tube 38 of the second heat exchanger 32 is directly inserted into the second header 35. Further, the second header 35 is arranged in parallel with the first header 34. The second header 35 is connected to the refrigerant circuit of the air conditioner 100 via the gas pipe 37. The second header 35 is also called a gas header. An opening (not shown) is formed in a portion of the second header 35 to which the gas pipe 37 is connected. As shown in FIG. 3, the second header 35 causes the high-temperature and high-pressure gas refrigerant from the compressor 11 to flow into the heat exchanger 30 during the cooling operation, and heat exchanges with the heat exchanger 30 during the heating operation as shown in FIG. The low-temperature low-pressure gas refrigerant after the heat is discharged to the refrigerant circuit.
　つまり、熱交換器３０では、冷房運転時に、冷媒の入口が第２ヘッダ３５に接続されるガス配管３７となり、冷媒の出口が第１ヘッダ３４に接続される液配管３６となる。また、暖房運転時に、冷媒の入口が第１ヘッダ３４に接続される液配管３６となり、冷媒の出口が第２ヘッダ３５に接続されるガス配管３７となる。 That is, in the heat exchanger 30, during the cooling operation, the inlet of the refrigerant becomes the gas pipe 37 connected to the second header 35, and the outlet of the refrigerant becomes the liquid pipe 36 connected to the first header 34. Further, during the heating operation, the inlet of the refrigerant becomes the liquid pipe 36 connected to the first header 34, and the outlet of the refrigerant becomes the gas pipe 37 connected to the second header 35.
　第１熱交換体３１および第２熱交換体３２の上端部には、第１ヘッダ３４および第２ヘッダ３５に挿入された複数の扁平管３８の上端部が挿入される列渡しヘッダ３３が設けられている。 At the upper ends of the first heat exchanger 31 and the second heat exchanger 32, a row header 33 into which the upper ends of the plurality of flat tubes 38 inserted in the first header 34 and the second header 35 are inserted is provided. Has been done.
　複数の扁平管３８、フィン３９、第１ヘッダ３４、第２ヘッダ３５、列渡しヘッダ３３、液配管３６、および、ガス配管３７は、いずれもアルミニウム製であり、ロウ付けによって接合されている。 The plurality of flat pipes 38, fins 39, first header 34, second header 35, row passing header 33, liquid pipe 36, and gas pipe 37 are all made of aluminum and are joined by brazing.
＜冷房運転＞
　圧縮機１１から吐出された高温高圧のガス冷媒は、流路切替装置１２を介して熱交換器３０に流入する。熱交換器３０に流入した高温高圧のガス冷媒は、ファン１３によって取り込まれた室外空気と熱交換して放熱しながら凝縮し、低温高圧の液冷媒となって熱交換器３０から流出する。このとき、熱交換器３０内を流れる冷媒は、図３に示すように、ガス配管３７、第２ヘッダ３５、第２熱交換体３２、列渡しヘッダ３３、第１熱交換体３１、第１ヘッダ３４、液配管３６の順に流れる。熱交換器３０から流出した低温高圧の液冷媒は、絞り装置２１によって減圧され、低温低圧の気液二相冷媒となり、室内熱交換器２２に流入する。室内熱交換器２２に流入した低温低圧の気液二相冷媒は、室内ファン２３によって取り込まれた室内空気と熱交換して吸熱しながら蒸発し、室内空気を冷却するとともに低温低圧のガス冷媒となって室内熱交換器２２から流出する。室内熱交換器２２から流出した低温低圧のガス冷媒は、圧縮機１１へ吸入され、再び高温高圧のガス冷媒となる。 <Cooling operation>
The high-temperature and high-pressure gas refrigerant discharged from the compressor 11 flows into the heat exchanger 30 via the flow path switching device 12. The high-temperature and high-pressure gas refrigerant flowing into the heat exchanger 30 exchanges heat with the outdoor air taken in by the fan 13 and condenses while radiating heat, becomes a low-temperature and high-pressure liquid refrigerant, and flows out from the heat exchanger 30. At this time, as shown in FIG. 3, the refrigerant flowing in the heat exchanger 30 is the gas pipe 37, the second header 35, the second heat exchanger 32, the row passing header 33, the first heat exchanger 31, the first. The header 34 and the liquid pipe 36 flow in this order. The low-temperature, high-pressure liquid refrigerant flowing out of the heat exchanger 30 is depressurized by the drawing device 21, becomes a low-temperature, low-pressure, gas-liquid two-phase refrigerant, and flows into the indoor heat exchanger 22. The low-temperature low-pressure gas-liquid two-phase refrigerant flowing into the indoor heat exchanger 22 exchanges heat with the indoor air taken in by the indoor fan 23 and evaporates while absorbing heat, cooling the indoor air and forming a low-temperature low-pressure gas refrigerant. Then, it flows out from the indoor heat exchanger 22. The low-temperature low-pressure gas refrigerant flowing out of the indoor heat exchanger 22 is sucked into the compressor 11 and becomes a high-temperature high-pressure gas refrigerant again.
＜暖房運転＞
　圧縮機１１から吐出された高温高圧のガス冷媒は、流路切替装置１２を介して室内熱交換器２２に流入する。室内熱交換器２２に流入した高温高圧のガス冷媒は、室内ファン２３によって取り込まれた室内空気と熱交換して放熱しながら凝縮し、室内空気を加熱するとともに低温高圧の液冷媒となって室内熱交換器２２から流出する。室内熱交換器２２から流出した低温高圧の液冷媒は、絞り装置２１によって減圧され、低温低圧の気液二相冷媒となり、熱交換器３０に流入する。熱交換器３０に流入した低温低圧の気液二相冷媒は、ファン１３によって取り込まれた室外空気と熱交換して吸熱しながら蒸発し、低温低圧のガス冷媒となって熱交換器３０から流出する。このとき、熱交換器３０内を流れる冷媒は、図２に示すように、液配管３６、第１ヘッダ３４、第１熱交換体３１、列渡しヘッダ３３、第２熱交換体３２、第２ヘッダ３５、ガス配管３７の順に流れる。熱交換器３０から流出した低温低圧のガス冷媒は、圧縮機１１へ吸入され、再び高温高圧のガス冷媒となる。 <Heating operation>
The high-temperature and high-pressure gas refrigerant discharged from the compressor 11 flows into the indoor heat exchanger 22 via the flow path switching device 12. The high-temperature and high-pressure gas refrigerant that has flowed into the indoor heat exchanger 22 exchanges heat with the indoor air taken in by the indoor fan 23 and condenses while radiating heat, heating the indoor air and becoming a low-temperature and high-pressure liquid refrigerant in the room. It flows out from the heat exchanger 22. The low-temperature and high-pressure liquid refrigerant flowing out of the indoor heat exchanger 22 is depressurized by the throttle device 21, becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant, and flows into the heat exchanger 30. The low-temperature low-pressure gas-liquid two-phase refrigerant that has flowed into the heat exchanger 30 exchanges heat with the outdoor air taken in by the fan 13 and evaporates while absorbing heat, becoming a low-temperature low-pressure gas refrigerant and flowing out of the heat exchanger 30. do. At this time, as shown in FIG. 2, the refrigerant flowing in the heat exchanger 30 is the liquid pipe 36, the first header 34, the first heat exchanger 31, the row passing header 33, the second heat exchanger 32, and the second. The header 35 and the gas pipe 37 flow in this order. The low-temperature low-pressure gas refrigerant flowing out of the heat exchanger 30 is sucked into the compressor 11 and becomes a high-temperature high-pressure gas refrigerant again.
＜除霜運転＞
　扁平管３８およびフィン３９の表面温度が０℃以下となる低温環境において、暖房運転を行う場合には、熱交換器３０には着霜が生じる。熱交換器３０への着霜量が一定以上になると、ファン１３によって発生する風が通過する熱交換器３０の風路が閉塞され、熱交換器３０の性能が低下し、暖房性能が低下する。そこで、暖房性能が低下した場合には、熱交換器３０の表面の霜を溶かす除霜運転を行う。 <Defrosting operation>
When the heating operation is performed in a low temperature environment where the surface temperature of the flat tube 38 and the fin 39 is 0 ° C. or lower, frost is formed on the heat exchanger 30. When the amount of frost on the heat exchanger 30 exceeds a certain level, the air passage of the heat exchanger 30 through which the wind generated by the fan 13 passes is blocked, the performance of the heat exchanger 30 deteriorates, and the heating performance deteriorates. .. Therefore, when the heating performance deteriorates, a defrosting operation for melting the frost on the surface of the heat exchanger 30 is performed.
　除霜運転では、ファン１３が停止され、流路切替装置１２が冷房運転時と同じ状態に切り替えられ、高温高圧のガス冷媒が熱交換器３０に流入する。これにより、扁平管３８およびフィン３９に付着した霜が融解する。除霜運転が開始されると、高温高圧のガス冷媒は、第２ヘッダ３５を介して各扁平管３８に流入する。そして、扁平管３８に流入した高温の冷媒によって、扁平管３８およびフィン３９に付着した霜は融解して水に変化する。霜が融解して生じた水（以下、除霜水５０と称する）は、扁平管３８あるいはフィン３９に沿って熱交換器３０の下方へ排水される。付着した霜が融解したら除霜運転が終了され、暖房運転が再開される。 In the defrosting operation, the fan 13 is stopped, the flow path switching device 12 is switched to the same state as in the cooling operation, and the high temperature and high pressure gas refrigerant flows into the heat exchanger 30. This melts the frost attached to the flat tube 38 and the fins 39. When the defrosting operation is started, the high-temperature and high-pressure gas refrigerant flows into each flat tube 38 via the second header 35. Then, the frost adhering to the flat tube 38 and the fins 39 is melted and changed to water by the high-temperature refrigerant flowing into the flat tube 38. The water generated by melting the frost (hereinafter referred to as defrost water 50) is drained to the lower part of the heat exchanger 30 along the flat pipe 38 or the fin 39. When the attached frost melts, the defrosting operation is terminated and the heating operation is restarted.
　外気温度が低温となる暖房運転では、低温低圧の二相冷媒が風上側の第１熱交換体３１を流れるため、熱交換器３０への着霜は、風上側の第１熱交換体３１の方が風下側の第２熱交換体３２よりも多くなる。そのため、除霜後に第１熱交換体３１の表面に発生した除霜水５０が下方に流れ、第１熱交換体３１の下端部の第１ヘッダ３４近傍、特に第１ヘッダ３４の上部に溜まりやすい。そして、暖房運転が再開されると、低温低圧の二相冷媒が第１ヘッダ３４から流入するため、従来では、第１ヘッダ３４の上部に溜まった除霜水５０が再氷結して根氷となり、暖房能力の低下および熱交換器３０の破損を招いていた。 In the heating operation in which the outside air temperature is low, the low-temperature low-pressure two-phase refrigerant flows through the first heat exchanger 31 on the wind side, so that the frost on the heat exchanger 30 is caused by the first heat exchanger 31 on the wind side. The number is larger than that of the second heat exchanger 32 on the leeward side. Therefore, the defrosting water 50 generated on the surface of the first heat exchanger 31 after defrosting flows downward and collects in the vicinity of the first header 34 at the lower end of the first heat exchanger 31, especially in the upper part of the first header 34. Cheap. Then, when the heating operation is restarted, the low-temperature low-pressure two-phase refrigerant flows in from the first header 34, so that the defrost water 50 accumulated in the upper part of the first header 34 is re-frozen and becomes root ice in the conventional case. This has led to a decrease in heating capacity and damage to the heat exchanger 30.
　そこで、実施の形態１に係る熱交換器３０では、ガス配管３７の少なくとも一部が第１ヘッダ３４の長軸方向に沿って設けられており、ガス配管３７の少なくとも一部は第１ヘッダ３４と接触している。また、ガス配管３７は、第１ヘッダ３４の下方に配置されている。このように、ガス配管３７の少なくとも一部が第１ヘッダ３４の長軸方向に沿って設けられ、ガス配管３７の少なくとも一部が第１ヘッダ３４と接触することで、除霜運転時に高温高圧のガス冷媒が流れるガス配管３７の熱を第１ヘッダ３４に伝えることができる。そして、第１ヘッダ３４に伝わった熱は、第１ヘッダ３４近傍の除霜水５０に伝わり、除霜水５０の温度が高くなる。そのため、除霜運転が終了後、暖房運転が再開されても、第１ヘッダ３４近傍の除霜水５０が再氷結するのを抑制することができる。その結果、暖房能力の低下および熱交換器３０の破損を抑制することができる。また、ガス配管３７は、第１ヘッダ３４の下方に配置されており、除霜水５０の排水経路を邪魔しないため、排水性の悪化を防止することができる。なお、ガス配管３７と第１ヘッダ３４との接触面積が広いほど、ガス配管３７のより多くの熱を第１ヘッダ３４に伝えることができる。 Therefore, in the heat exchanger 30 according to the first embodiment, at least a part of the gas pipe 37 is provided along the long axis direction of the first header 34, and at least a part of the gas pipe 37 is the first header 34. Is in contact with. Further, the gas pipe 37 is arranged below the first header 34. In this way, at least a part of the gas pipe 37 is provided along the long axis direction of the first header 34, and at least a part of the gas pipe 37 comes into contact with the first header 34, so that the temperature and pressure are high and high during the defrosting operation. The heat of the gas pipe 37 through which the gas refrigerant of No. 1 flows can be transferred to the first header 34. Then, the heat transferred to the first header 34 is transmitted to the defrost water 50 in the vicinity of the first header 34, and the temperature of the defrost water 50 becomes high. Therefore, even if the heating operation is restarted after the defrosting operation is completed, it is possible to prevent the defrosting water 50 in the vicinity of the first header 34 from refreezing. As a result, it is possible to suppress a decrease in heating capacity and damage to the heat exchanger 30. Further, since the gas pipe 37 is arranged below the first header 34 and does not interfere with the drainage path of the defrost water 50, deterioration of the drainage property can be prevented. The wider the contact area between the gas pipe 37 and the first header 34, the more heat of the gas pipe 37 can be transferred to the first header 34.
　なお、実施の形態１では、熱交換器３０は、２つの熱交換体を有しているが、それに限定されず、１つあるいは３つ以上の熱交換体を有していてもよい。 Note that, in the first embodiment, the heat exchanger 30 has two heat exchangers, but is not limited thereto, and may have one or three or more heat exchangers.
　図４は、実施の形態１に係る熱交換器３０の変形例を示す斜視図である。
　熱交換器３０が１つのみの熱交換体３１１を有する場合は、図４に示すように、熱交換体３１１の下端部に第１ヘッダ３４が設けられ、熱交換体３１１の上端部に第２ヘッダ３５が設けられ、列渡しヘッダ３３は設けられない。そして、第１ヘッダ３４に液配管３６が接続され、第２ヘッダ３５にガス配管３７が接続される。 FIG. 4 is a perspective view showing a modified example of the heat exchanger 30 according to the first embodiment.
When the heat exchanger 30 has only one heat exchanger 311, as shown in FIG. 4, a first header 34 is provided at the lower end of the heat exchanger 311 and a first header 34 is provided at the upper end of the heat exchanger 311. The two headers 35 are provided, and the column passing header 33 is not provided. Then, the liquid pipe 36 is connected to the first header 34, and the gas pipe 37 is connected to the second header 35.
　熱交換器３０が３つ以上の奇数の熱交換体を有する場合は、最も風上側の熱交換体の下端部に第１ヘッダ３４が設けられ、最も風下側の熱交換体の上端部に第２ヘッダ３５が設けられる。また、熱交換体の数－１個の列渡しヘッダ３３が設けられ、隣接する熱交換体同士を接続する。そして、第１ヘッダ３４に液配管３６が接続され、第２ヘッダ３５にガス配管３７が接続される。 When the heat exchanger 30 has three or more odd heat exchangers, the first header 34 is provided at the lower end of the most leeward heat exchanger, and the first header 34 is provided at the upper end of the leeward heat exchanger. Two headers 35 are provided. In addition, the number of heat exchangers-1 column passing header 33 is provided to connect adjacent heat exchangers to each other. Then, the liquid pipe 36 is connected to the first header 34, and the gas pipe 37 is connected to the second header 35.
　熱交換器３０が４つ以上の偶数の熱交換体を有する場合は、最も風上側の熱交換体の下端部に第１ヘッダ３４が設けられ、最も風下側の熱交換体の下端部に第２ヘッダ３５が設けられる。また、熱交換体の数－１個の列渡しヘッダ３３が設けられ、隣接する熱交換体同士を接続する。そして、第１ヘッダ３４に液配管３６が接続され、第２ヘッダ３５にガス配管３７が接続される。 When the heat exchanger 30 has four or more even heat exchangers, the first header 34 is provided at the lower end of the heat exchanger on the most upwind side, and the first header 34 is provided at the lower end of the heat exchanger on the leeward side. Two headers 35 are provided. In addition, the number of heat exchangers-1 column passing header 33 is provided to connect adjacent heat exchangers to each other. Then, the liquid pipe 36 is connected to the first header 34, and the gas pipe 37 is connected to the second header 35.
　以上、実施の形態１に係る熱交換器３０は、複数の扁平管３８を有する熱交換体を空気の流れ方向に沿って少なくとも一つ以上備えた熱交換器３０であって、最も風上側の熱交換体の下端部に設けられる第１ヘッダと、最も風下側の熱交換体の上端部または下端部に設けられる第２ヘッダと、第１ヘッダに接続され、蒸発器として機能する際に冷媒が流入し、凝縮器として機能する際に冷媒が流出する液配管３６と、第２ヘッダに接続され、蒸発器として機能する際に冷媒が流出し、凝縮器として機能する際に冷媒が流入するガス配管３７と、を備えている。そして、ガス配管３７の少なくとも一部は第１ヘッダの長軸方向に沿って設けられており、ガス配管３７は、少なくとも一部が第１ヘッダと接触しているものである。 As described above, the heat exchanger 30 according to the first embodiment is a heat exchanger 30 having at least one heat exchanger having a plurality of flat tubes 38 along the air flow direction, and is the most windy side. A first header provided at the lower end of the heat exchanger, a second header provided at the upper end or the lower end of the most leeward heat exchanger, and a refrigerant when connected to the first header and functioning as an evaporator. Is connected to the liquid pipe 36, which is connected to the second header and flows out when it functions as a condenser, and the refrigerant flows out when it functions as an evaporator, and flows in when it functions as a condenser. It is provided with a gas pipe 37. At least a part of the gas pipe 37 is provided along the long axis direction of the first header, and at least a part of the gas pipe 37 is in contact with the first header.
　実施の形態１に係る熱交換器３０によれば、ガス配管３７の少なくとも一部は第１ヘッダ３４の長軸方向に沿って設けられており、ガス配管３７は、少なくとも一部が第１ヘッダ３４と接触している。そのため、除霜運転時に高温高圧のガス冷媒が流れるガス配管３７の熱を第１ヘッダ３４に伝えることができる。そして、第１ヘッダ３４に伝わった熱は、第１ヘッダ３４近傍の除霜水に伝わり、除霜水５０の温度が高くなる。そのため、除霜運転が終了後、暖房運転が再開されても、第１ヘッダ３４近傍の除霜水５０が再氷結するのを抑制することができる。その結果、その結果、暖房能力の低下および熱交換器３０の破損を抑制することができる。 According to the heat exchanger 30 according to the first embodiment, at least a part of the gas pipe 37 is provided along the long axis direction of the first header 34, and at least a part of the gas pipe 37 is provided in the first header. It is in contact with 34. Therefore, the heat of the gas pipe 37 through which the high-temperature and high-pressure gas refrigerant flows during the defrosting operation can be transferred to the first header 34. Then, the heat transferred to the first header 34 is transmitted to the defrost water in the vicinity of the first header 34, and the temperature of the defrost water 50 becomes high. Therefore, even if the heating operation is restarted after the defrosting operation is completed, it is possible to prevent the defrosting water 50 in the vicinity of the first header 34 from refreezing. As a result, it is possible to suppress a decrease in heating capacity and damage to the heat exchanger 30.
　また、実施の形態１に係る熱交換器３０において、ガス配管３７は、第１ヘッダ３４の下方に配置されている。 Further, in the heat exchanger 30 according to the first embodiment, the gas pipe 37 is arranged below the first header 34.
　実施の形態１に係る熱交換器３０によれば、ガス配管３７は、第１ヘッダ３４の下方に配置されており、除霜水５０の排水経路を邪魔しないため、排水性の悪化を防止することができる。 According to the heat exchanger 30 according to the first embodiment, the gas pipe 37 is arranged below the first header 34 and does not interfere with the drainage path of the defrost water 50, so that deterioration of the drainage property is prevented. be able to.
　また、実施の形態１に係る室外機１０は、上記の熱交換器３０を備えたものである。実施の形態１に係る室外機１０によれば、上記の熱交換器３０と同様の効果が得られる。 Further, the outdoor unit 10 according to the first embodiment is provided with the above heat exchanger 30. According to the outdoor unit 10 according to the first embodiment, the same effect as that of the heat exchanger 30 can be obtained.
　また、実施の形態１に係る空気調和装置１００は、上記の室外機１０を備えたものである。実施の形態１に係る空気調和装置１００によれば、上記の室外機１０と同様の効果が得られる。 Further, the air conditioner 100 according to the first embodiment is provided with the above-mentioned outdoor unit 10. According to the air conditioner 100 according to the first embodiment, the same effect as that of the outdoor unit 10 can be obtained.
　実施の形態２．
　以下、実施の形態２について説明するが、実施の形態１と重複するものについては説明を省略し、実施の形態１と同じ部分または相当する部分には同じ符号を付す。 Embodiment 2.
Hereinafter, the second embodiment will be described, but the description of the parts overlapping with the first embodiment will be omitted, and the same parts or the corresponding parts as those of the first embodiment will be designated by the same reference numerals.
　図５は、実施の形態２に係る熱交換器３０および熱交換器３０が搭載されたトップフロー型の室外機１０ａの斜視図である。
　図５に示すように、実施の形態２に係る熱交換器３０は、トップフロー型の室外機１０ａに搭載されている。熱交換器３０は平面視してＬ字状を有し、２つの熱交換器３０が平面視して矩形状を形成するように室外機１０ａに搭載されている。なお、熱交換器３０は平面視して厳密にＬ字状を有していなくてもよい。また、２つの熱交換器３０は、平面視して厳密に矩形状を形成していなくてもよい。 FIG. 5 is a perspective view of the top-flow type outdoor unit 10a on which the heat exchanger 30 and the heat exchanger 30 according to the second embodiment are mounted.
As shown in FIG. 5, the heat exchanger 30 according to the second embodiment is mounted on the top flow type outdoor unit 10a. The heat exchanger 30 has an L-shape in a plan view, and is mounted on the outdoor unit 10a so that the two heat exchangers 30 form a rectangular shape in a plan view. The heat exchanger 30 does not have to have a strictly L-shape in a plan view. Further, the two heat exchangers 30 do not have to form a strictly rectangular shape in a plan view.
　室外機１０ａは、箱状に形成されたケーシング１５を備えている。このケーシング１５の四側面それぞれには、吸込口１６が形成されており、ケーシング１５の上面には吹出口１７が形成されている。また、室外機１０ａは、ケーシング１５の四側面それぞれの吸込口１６に沿うようにケーシング１５内に配置された２つの熱交換器３０を備えている。また、室外機１０ａは、ケーシング１５の吹出口１７を覆うように通風可能に設けられたファンガード１８と、ファンガード１８の内部に配置され、吸込口１６から外気を吸い込み、吹出口１７から外気を排出するファン１３と、を備えている。 The outdoor unit 10a includes a box-shaped casing 15. A suction port 16 is formed on each of the four side surfaces of the casing 15, and an air outlet 17 is formed on the upper surface of the casing 15. Further, the outdoor unit 10a includes two heat exchangers 30 arranged in the casing 15 so as to be along the suction ports 16 on each of the four side surfaces of the casing 15. Further, the outdoor unit 10a is arranged inside the fan guard 18 provided so as to be ventilated so as to cover the air outlet 17 of the casing 15, and the outside air is sucked from the suction port 16 and the outside air is sucked from the air outlet 17. It is equipped with a fan 13 for discharging.
　２つの熱交換器３０は、ファン１３の下方に配置されている。また、２つの熱交換器３０は、ケーシング１５の四側面に沿って配置されている。なお、２つの熱交換器３０は、ケーシング１５の四隅に設けられた柱部１５ａにネジなどで固定されている。そして、ファン１３によって各側面に形成された吸込口１６から吸い込まれた室外空気は、各熱交換器３０で冷媒と熱交換した後、吹出口１７から吹き出される。 The two heat exchangers 30 are arranged below the fan 13. Further, the two heat exchangers 30 are arranged along the four side surfaces of the casing 15. The two heat exchangers 30 are fixed to the pillars 15a provided at the four corners of the casing 15 with screws or the like. Then, the outdoor air sucked from the suction ports 16 formed on each side surface by the fan 13 is heat-exchanged with the refrigerant by each heat exchanger 30 and then blown out from the outlet 17.
　また、ケーシング１５の四側面には、それぞれ側面パネル１５ｂが設けられており、側面パネル１５ｂで囲まれた空間に、圧縮機１１などが収容される機械室（図示せず）が形成されている。側面パネル１５ｂは、２つの熱交換器３０の下方に形成されている。また、各側面パネル１５ｂと各熱交換器３０との間にはそれぞれ隙間１９が形成されている。この隙間１９は、ガス配管３７の取り回しスペースとなっている。また、この隙間１９は、熱交換器３０で生じた除霜水の排水経路を確保するスペースとなっている。つまり、この隙間１９によって、ガス配管３７を熱交換器３０の補助側第１ヘッダ３４ｂの長軸方向に沿って設けることを可能とし、また、排水性の悪化を防止している。 Further, side panels 15b are provided on each of the four side surfaces of the casing 15, and a machine room (not shown) in which the compressor 11 and the like are housed is formed in the space surrounded by the side panels 15b. .. The side panel 15b is formed below the two heat exchangers 30. Further, a gap 19 is formed between each side panel 15b and each heat exchanger 30. This gap 19 serves as a handling space for the gas pipe 37. Further, the gap 19 is a space for securing a drainage path for the defrosted water generated in the heat exchanger 30. That is, the gap 19 makes it possible to provide the gas pipe 37 along the long axis direction of the auxiliary side first header 34b of the heat exchanger 30, and also prevents deterioration of drainage.
　図６は、実施の形態２に係る熱交換器３０の斜視図である。
　実施の形態２に係る熱交換器３０は、空気の流れ方向に沿って複数の熱交換体を有している。具体的には、熱交換器３０は、風上側の第１熱交換体３１と風下側の第２熱交換体３２とを有する。第１熱交換体３１は、主側第１熱交換体３１ａと、主側第１熱交換体３１ａよりも扁平管３８の数が少ない補助側第１熱交換体３１ｂとで構成されている。第２熱交換体３２は、主側第２熱交換体３２ａと、主側第２熱交換体３２ａよりも扁平管３８の数が少ない補助側第２熱交換体３２ｂとで構成されている。 FIG. 6 is a perspective view of the heat exchanger 30 according to the second embodiment.
The heat exchanger 30 according to the second embodiment has a plurality of heat exchangers along the air flow direction. Specifically, the heat exchanger 30 has a first heat exchanger 31 on the windward side and a second heat exchanger 32 on the leeward side. The first heat exchanger 31 is composed of a main side first heat exchanger 31a and an auxiliary side first heat exchanger 31b in which the number of flat tubes 38 is smaller than that of the main side first heat exchanger 31a. The second heat exchanger 32 is composed of a main side second heat exchanger 32a and an auxiliary side second heat exchanger 32b in which the number of flat tubes 38 is smaller than that of the main side second heat exchanger 32a.
　また、熱交換器３０は、主熱交換部３０ａと補助熱交換部３０ｂとに分かれている。主熱交換部３０ａは、主側第１熱交換体３１ａと主側第２熱交換体３２ａと主側第１ヘッダ３４ａ（以下、第１ヘッダとも称する）と主側第２ヘッダ３５ａと主側列渡しヘッダ３３ａとを備えている。また、補助熱交換部３０ｂは、補助側第１熱交換体３１ｂ（以下、第２ヘッダとも称する）と補助側第２熱交換体３２ｂと補助側第１ヘッダ３４ｂと補助側第２ヘッダ３５ｂと補助側列渡しヘッダ３３ｂとを備えている。 Further, the heat exchanger 30 is divided into a main heat exchange unit 30a and an auxiliary heat exchange unit 30b. The main heat exchange unit 30a includes a main side first heat exchanger 31a, a main side second heat exchanger 32a, a main side first header 34a (hereinafter, also referred to as a first header), a main side second header 35a, and a main side. It is provided with a column passing header 33a. Further, the auxiliary heat exchange unit 30b includes an auxiliary side first heat exchanger 31b (hereinafter, also referred to as a second header), an auxiliary side second heat exchanger 32b, an auxiliary side first header 34b, and an auxiliary side second header 35b. It is provided with an auxiliary side column passing header 33b.
　主側第１熱交換体３１ａの下端部には、主側第１ヘッダ３４ａが設けられている。主側第１ヘッダ３４ａには、主側第１熱交換体３１ａの扁平管３８の下端部が直接挿入されている。主側第１ヘッダ３４ａは、空気調和装置１００の冷媒回路にガス配管３７を介して接続されている。なお、主側第１ヘッダ３４ａのガス配管３７が接続されている部分には、開口部３４ａ１が形成されている。主側第１ヘッダ３４ａは、冷房運転時に圧縮機１１からの高温高圧のガス冷媒を熱交換器３０に流入させ、暖房運転時に熱交換器３０で熱交換された後の低温低圧のガス冷媒を冷媒回路に流出させる。 A main side first header 34a is provided at the lower end of the main side first heat exchanger 31a. The lower end of the flat tube 38 of the main side first heat exchanger 31a is directly inserted into the main side first header 34a. The main side first header 34a is connected to the refrigerant circuit of the air conditioner 100 via the gas pipe 37. An opening 34a1 is formed in a portion of the first header 34a on the main side to which the gas pipe 37 is connected. The first header 34a on the main side causes the high-temperature and high-pressure gas refrigerant from the compressor 11 to flow into the heat exchanger 30 during the cooling operation, and the low-temperature and low-pressure gas refrigerant after the heat is exchanged by the heat exchanger 30 during the heating operation. Let it flow out to the refrigerant circuit.
　補助側第１熱交換体３１ｂの下端部には、補助側第１ヘッダ３４ｂが設けられている。補助側第１ヘッダ３４ｂには、補助側第１熱交換体３１ｂの扁平管３８の下端部が直接挿入されている。補助側第１ヘッダ３４ｂは、空気調和装置１００の冷媒回路に液配管３６を介して接続されている。なお、補助側第１ヘッダ３４ｂの液配管３６が接続されている部分には、開口部（図示せず）が形成されている。補助側第１ヘッダ３４ｂは、暖房運転時に低温低圧の二相冷媒を熱交換器３０に流入させ、冷房運転時に熱交換器３０で熱交換された後の低温高圧の液冷媒を冷媒回路に流出させる。 An auxiliary side first header 34b is provided at the lower end of the auxiliary side first heat exchanger 31b. The lower end of the flat tube 38 of the auxiliary side first heat exchanger 31b is directly inserted into the auxiliary side first header 34b. The first header 34b on the auxiliary side is connected to the refrigerant circuit of the air conditioner 100 via the liquid pipe 36. An opening (not shown) is formed in a portion of the auxiliary side first header 34b to which the liquid pipe 36 is connected. The first header 34b on the auxiliary side causes a low-temperature low-pressure two-phase refrigerant to flow into the heat exchanger 30 during the heating operation, and the low-temperature high-pressure liquid refrigerant after heat exchange in the heat exchanger 30 during the cooling operation flows out to the refrigerant circuit. Let me.
　つまり、熱交換器３０では、冷房運転時に、冷媒の入口が主側第１ヘッダ３４ａに接続されるガス配管３７となり、冷媒の出口が補助側第１ヘッダ３４ｂに接続される液配管３６となる。また、暖房運転時に、冷媒の入口が補助側第１ヘッダ３４ｂに接続される液配管３６となり、冷媒の出口が主側第１ヘッダ３４ａに接続されるガス配管３７となる。 That is, in the heat exchanger 30, during the cooling operation, the inlet of the refrigerant becomes the gas pipe 37 connected to the first header 34a on the main side, and the outlet of the refrigerant becomes the liquid pipe 36 connected to the first header 34b on the auxiliary side. .. Further, during the heating operation, the inlet of the refrigerant becomes the liquid pipe 36 connected to the first header 34b on the auxiliary side, and the outlet of the refrigerant becomes the gas pipe 37 connected to the first header 34a on the main side.
　主側第２熱交換体３２ａの下端部には、主側第２ヘッダ３５ａが設けられている。主側第２ヘッダ３５ａには、主側第２熱交換体３２ａの扁平管３８の下端部が直接挿入されている。また、補助側第２熱交換体３２ｂの下端部には、補助側第２ヘッダ３５ｂ（図７参照）が設けられている。補助側第２ヘッダ３５ｂには、補助側第２熱交換体３２ｂの扁平管３８の下端部が直接挿入されている。主側第２ヘッダ３５ａと補助側第２ヘッダ３５ｂとは、互いに連通している。 A main side second header 35a is provided at the lower end of the main side second heat exchanger 32a. The lower end of the flat tube 38 of the main side second heat exchanger 32a is directly inserted into the main side second header 35a. Further, an auxiliary side second header 35b (see FIG. 7) is provided at the lower end portion of the auxiliary side second heat exchanger 32b. The lower end of the flat tube 38 of the auxiliary side second heat exchanger 32b is directly inserted into the auxiliary side second header 35b. The main side second header 35a and the auxiliary side second header 35b communicate with each other.
　主側第１熱交換体３１ａおよび主側第２熱交換体３２ａの上端部には、主側第１ヘッダ３４ａおよび主側第２ヘッダ３５ａに挿入された複数の扁平管３８の上端部が挿入される主側列渡しヘッダ３３ａが設けられている。また、補助側第１熱交換体３１ｂおよび補助側第２熱交換体３２ｂの上端部には、補助側第１ヘッダ３４ｂおよび補助側第２ヘッダ３５ｂに挿入された複数の扁平管３８の上端部が挿入される補助側列渡しヘッダ３３ｂが設けられている。 At the upper ends of the main side first heat exchanger 31a and the main side second heat exchanger 32a, the upper ends of a plurality of flat tubes 38 inserted into the main side first header 34a and the main side second header 35a are inserted. The main side column passing header 33a is provided. Further, at the upper ends of the auxiliary side first heat exchanger 31b and the auxiliary side second heat exchanger 32b, the upper ends of a plurality of flat tubes 38 inserted into the auxiliary side first header 34b and the auxiliary side second header 35b Is provided with an auxiliary side column passing header 33b into which the is inserted.
　また、液配管３６は、補助側第１ヘッダ３４ｂに接続されており、ガス配管３７は、主側第１ヘッダ３４ａに接続されている。そして、ガス配管３７の少なくとも一部が補助側第１ヘッダ３４ｂの長軸方向に沿って設けられており、ガス配管３７の少なくとも一部は補助側第１ヘッダ３４ｂと接触している。また、ガス配管３７は、補助側第１ヘッダ３４ｂの下方に配置されている。 Further, the liquid pipe 36 is connected to the auxiliary side first header 34b, and the gas pipe 37 is connected to the main side first header 34a. At least a part of the gas pipe 37 is provided along the long axis direction of the auxiliary side first header 34b, and at least a part of the gas pipe 37 is in contact with the auxiliary side first header 34b. Further, the gas pipe 37 is arranged below the first header 34b on the auxiliary side.
　また、主熱交換部３０ａは、主側第１ヘッダ３４ａおよび主側第２ヘッダ３５ａの流路の途中にそれぞれ屈曲部４１、４２（後述する図７および図９参照）を有する。これにより、主熱交換部３０ａは、ケーシング１５の互いに隣り合う２つの側面に跨がって配置することができる。 Further, the main heat exchange portion 30a has bent portions 41 and 42 (see FIGS. 7 and 9 described later) in the middle of the flow paths of the main side first header 34a and the main side second header 35a, respectively. As a result, the main heat exchange portion 30a can be arranged so as to straddle two side surfaces of the casing 15 adjacent to each other.
　主側第１ヘッダ３４ａと補助側第１ヘッダ３４ｂとは、第１ヘッダ３４がその内部に設けられた仕切板（図示せず）によって仕切られて構成されている。また、主側列渡しヘッダ３３ａと補助側列渡しヘッダ３３ｂとは、列渡しヘッダ３３がその内部に設けられた仕切板（図示せず）によって仕切られて構成されている。つまり、主側第１ヘッダ３４ａと補助側第１ヘッダ３４ｂ、および、主側列渡しヘッダ３３ａと補助側列渡しヘッダ３３ｂは、それぞれ同体のものを仕切板（図示せず）によって仕切ることで構成されている。ただし、主側第１ヘッダ３４ａと補助側第１ヘッダ３４ｂ、および、主側列渡しヘッダ３３ａと補助側列渡しヘッダ３３ｂは、それぞれ別体として構成されていてもよい。また、主側第２ヘッダ３５ａと補助側第２ヘッダ３５ｂとは、仕切板（図示せず）によって仕切られておらず、上記の通り主側第２ヘッダ３５ａと補助側第２ヘッダ３５ｂとは互いに連通している。 The main side first header 34a and the auxiliary side first header 34b are configured such that the first header 34 is partitioned by a partition plate (not shown) provided inside the first header 34. Further, the main side row passing header 33a and the auxiliary side row passing header 33b are configured by partitioning the row passing header 33 by a partition plate (not shown) provided inside the main side row passing header 33a and the auxiliary side row passing header 33b. That is, the main side first header 34a and the auxiliary side first header 34b, and the main side row passing header 33a and the auxiliary side row passing header 33b are configured by partitioning the same body by a partition plate (not shown). Has been done. However, the main side first header 34a and the auxiliary side first header 34b, and the main side column passing header 33a and the auxiliary side column passing header 33b may be configured as separate bodies. Further, the main side second header 35a and the auxiliary side second header 35b are not separated by a partition plate (not shown), and as described above, the main side second header 35a and the auxiliary side second header 35b are Communicate with each other.
　熱交換器３０は、上記の構造により、主側第１熱交換体３１ａの冷媒の流れが補助側第１熱交換体３１ｂの冷媒の流れと対向流となり、主側第２熱交換体３２ａの冷媒の流れが補助側第２熱交換体３２ｂの冷媒の流れと対向流となるように構成されている。 Due to the above structure, in the heat exchanger 30, the flow of the refrigerant in the main side first heat exchanger 31a becomes a countercurrent flow to the flow of the refrigerant in the auxiliary side first heat exchanger 31b, and the main side second heat exchanger 32a The flow of the refrigerant is configured to be opposite to the flow of the refrigerant in the auxiliary side second heat exchanger 32b.
＜暖房運転＞
　図７は、実施の形態２に係る熱交換器３０の暖房運転時の冷媒の流れを模式的に示す平面図である。図８は、実施の形態２に係る熱交換器３０の暖房運転時の冷媒の流れを模式的に示す斜視図である。なお、図８は、図７の破線で囲まれた一方の熱交換器３０のみを示しているが、もう一方の熱交換器３０についても同様の構造および同様の冷媒の流れである。 <Heating operation>
FIG. 7 is a plan view schematically showing the flow of the refrigerant during the heating operation of the heat exchanger 30 according to the second embodiment. FIG. 8 is a perspective view schematically showing the flow of the refrigerant during the heating operation of the heat exchanger 30 according to the second embodiment. Note that FIG. 8 shows only one heat exchanger 30 surrounded by the broken line in FIG. 7, but the other heat exchanger 30 has the same structure and the same flow of the refrigerant.
　暖房運転時は、図７および図８に示すように、低温低圧の気液二相冷媒が、液配管３６から熱交換器３０に流入する。熱交換器３０に流入した低温低圧の気液二相冷媒は、補助側第１ヘッダ３４ｂ、補助側第１熱交換体３１ｂ、補助側列渡しヘッダ３３ｂ、補助側第２熱交換体３２ｂ、補助側第２ヘッダ３５ｂ、主側第２ヘッダ３５ａ、主側第２熱交換体３２ａ、主側列渡しヘッダ３３ａ、主側第１熱交換体３１ａ、主側第１ヘッダ３４ａの順に流れ、低温低圧のガス冷媒となる。そして、低温低圧のガス冷媒は、ガス配管３７から熱交換器３０を流出する。 During the heating operation, as shown in FIGS. 7 and 8, a low-temperature low-pressure gas-liquid two-phase refrigerant flows into the heat exchanger 30 from the liquid pipe 36. The low-temperature and low-pressure gas-liquid two-phase refrigerant flowing into the heat exchanger 30 includes an auxiliary side first header 34b, an auxiliary side first heat exchanger 31b, an auxiliary side row passing header 33b, an auxiliary side second heat exchanger 32b, and an auxiliary side. Side second header 35b, main side second header 35a, main side second heat exchanger 32a, main side row passing header 33a, main side first heat exchanger 31a, main side first header 34a flow in this order, and low temperature and low pressure. It becomes the gas refrigerant of. Then, the low-temperature low-pressure gas refrigerant flows out of the heat exchanger 30 from the gas pipe 37.
＜除霜運転＞
　図９は、実施の形態２に係る熱交換器３０の除霜運転時の冷媒の流れを模式的に示す平面図である。図１０は、実施の形態２に係る熱交換器３０の除霜運転時の冷媒の流れを模式的に示す斜視図である。なお、図１０は、図９の破線で囲まれた一方の熱交換器３０のみを示しているが、もう一方の熱交換器３０についても同様の構造および同様の冷媒の流れである。 <Defrosting operation>
FIG. 9 is a plan view schematically showing the flow of the refrigerant during the defrosting operation of the heat exchanger 30 according to the second embodiment. FIG. 10 is a perspective view schematically showing the flow of the refrigerant during the defrosting operation of the heat exchanger 30 according to the second embodiment. Note that FIG. 10 shows only one heat exchanger 30 surrounded by the broken line in FIG. 9, but the other heat exchanger 30 has the same structure and the same flow of the refrigerant.
　除霜運転時は、図９および図１０に示すように、高温高圧のガス冷媒が、ガス配管３７から熱交換器３０に流入する。熱交換器３０に流入した高温高圧のガス冷媒は、主側第１ヘッダ３４ａ、主側第１熱交換体３１ａ、主側列渡しヘッダ３３ａ、主側第２熱交換体３２ａ、主側第２ヘッダ３５ａ、補助側第２ヘッダ３５ｂ、補助側第２熱交換体３２ｂ、補助側列渡しヘッダ３３ｂ、補助側第１熱交換体３１ｂ、補助側第１ヘッダ３４ｂの順に流れ、低温高圧のガス冷媒となる。そして、低温高圧のガス冷媒は、液配管３６から熱交換器３０を流出する。 During the defrosting operation, as shown in FIGS. 9 and 10, a high-temperature and high-pressure gas refrigerant flows into the heat exchanger 30 from the gas pipe 37. The high-temperature and high-pressure gas refrigerant flowing into the heat exchanger 30 includes a main side first header 34a, a main side first heat exchanger 31a, a main side row passing header 33a, a main side second heat exchanger 32a, and a main side second. The header 35a, the auxiliary side second header 35b, the auxiliary side second heat exchanger 32b, the auxiliary side row passing header 33b, the auxiliary side first heat exchanger 31b, and the auxiliary side first header 34b flow in this order, and are low temperature and high pressure gas refrigerants. It becomes. Then, the low-temperature and high-pressure gas refrigerant flows out of the heat exchanger 30 from the liquid pipe 36.
　実施の形態２では、ガス配管３７が主側第１ヘッダ３４ａに接続されており、除霜運転時は、高温高圧のガス冷媒が風上側の主側第１ヘッダ３４ａから熱交換器３０に流入する。そのため、効率的に着霜量の多い風上側の主側第１熱交換体３１ａを除霜することが可能となり、除霜時間を短縮することができる。また、ガス配管３７の少なくとも一部が補助側第１ヘッダ３４ｂの長軸方向に沿って設けられ、ガス配管３７の少なくとも一部が補助側第１ヘッダ３４ｂと接触している。そのため、除霜運転時に高温高圧のガス冷媒が流れるガス配管３７の熱を補助側第１ヘッダ３４ｂに伝えることができる。 In the second embodiment, the gas pipe 37 is connected to the main side first header 34a, and during the defrosting operation, the high temperature and high pressure gas refrigerant flows into the heat exchanger 30 from the windward side first header 34a. do. Therefore, it is possible to efficiently defrost the main side first heat exchanger 31a on the windward side where the amount of frost formation is large, and the defrosting time can be shortened. Further, at least a part of the gas pipe 37 is provided along the long axis direction of the auxiliary side first header 34b, and at least a part of the gas pipe 37 is in contact with the auxiliary side first header 34b. Therefore, the heat of the gas pipe 37 through which the high-temperature and high-pressure gas refrigerant flows during the defrosting operation can be transferred to the auxiliary side first header 34b.
　そして、補助側第１ヘッダ３４ｂに伝わった熱は、補助側第１ヘッダ３４ｂ近傍の除霜水に伝わり、除霜水の温度が高くなる。そのため、除霜運転が終了後、暖房運転が再開されても、除霜後に除霜水が溜まりやすい補助側第１熱交換体３１ｂの下端部の補助側第１ヘッダ３４ｂ近傍の除霜水が再氷結するのを抑制することができる。その結果、暖房能力の低下および熱交換器３０の破損を抑制することができる。また、ガス配管３７は、補助側第１ヘッダ３４ｂの下方に配置されており、除霜水の排水経路を邪魔しないため、排水性の悪化を防止することができる。 Then, the heat transferred to the auxiliary side first header 34b is transmitted to the defrost water in the vicinity of the auxiliary side first header 34b, and the temperature of the defrost water becomes high. Therefore, even if the heating operation is restarted after the defrosting operation is completed, the defrosting water in the vicinity of the auxiliary side first header 34b at the lower end of the auxiliary side first heat exchanger 31b where the defrosting water tends to collect after defrosting is generated. It is possible to suppress refreezing. As a result, it is possible to suppress a decrease in heating capacity and damage to the heat exchanger 30. Further, since the gas pipe 37 is arranged below the first header 34b on the auxiliary side and does not interfere with the drainage path of the defrosted water, deterioration of the drainage property can be prevented.
　なお、実施の形態２では、熱交換器３０がトップフロー型の室外機１０ａに搭載された例を説明したが、それに限定されず、熱交換器３０はサイドフロー型などその他の種類の室外機にも搭載することができる。 In the second embodiment, an example in which the heat exchanger 30 is mounted on the top-flow type outdoor unit 10a has been described, but the present invention is not limited to this, and the heat exchanger 30 is another type of outdoor unit such as the side-flow type. It can also be installed in.
　また、実施の形態２では、熱交換器３０は、２つの熱交換体を有しているが、それに限定されず、１つあるいは３つ以上の熱交換体を有していてもよい。 Further, in the second embodiment, the heat exchanger 30 has two heat exchangers, but is not limited thereto, and may have one or three or more heat exchangers.
　図１１は、実施の形態２に係る熱交換器３０の変形例の除霜運転時の冷媒の流れを模式的に示す平面図である。図１２は、実施の形態２に係る熱交換器３０の変形例の除霜運転時の冷媒の流れを模式的に示す斜視図である。なお、図１２は、図１１の破線で囲まれた一方の熱交換器３０のみを示しているが、もう一方の熱交換器３０についても同様の構造である。 FIG. 11 is a plan view schematically showing the flow of the refrigerant during the defrosting operation of the modified example of the heat exchanger 30 according to the second embodiment. FIG. 12 is a perspective view schematically showing the flow of the refrigerant during the defrosting operation of the modified example of the heat exchanger 30 according to the second embodiment. Note that FIG. 12 shows only one heat exchanger 30 surrounded by the broken line in FIG. 11, but the other heat exchanger 30 has the same structure.
　熱交換器３０が１つのみの熱交換体を有する場合は、図１１および図１２に示すように、主側熱交換体３１ａ１の下端部に主側第１ヘッダ３４ａが設けられ、主側熱交換体３１ａ１の上端部に主側第２ヘッダ３５ａが設けられている。また、補助側熱交換体３１ｂ１の下端部に補助側第１ヘッダ３４ｂが設けられ、補助側熱交換体３１ｂ１の上端部に補助側第２ヘッダ３５ｂが設けられており、主側列渡しヘッダ３３ａおよび補助側列渡しヘッダ３３ｂは設けられない。そして、補助側第１ヘッダ３４ｂに液配管３６が接続され、主側第１ヘッダ３４ａにガス配管３７が接続される。 When the heat exchanger 30 has only one heat exchanger, as shown in FIGS. 11 and 12, a main side first header 34a is provided at the lower end of the main side heat exchanger 31a1 to provide main side heat. A second header 35a on the main side is provided at the upper end of the exchanger 31a1. Further, an auxiliary side first header 34b is provided at the lower end portion of the auxiliary side heat exchanger 31b1, an auxiliary side second header 35b is provided at the upper end portion of the auxiliary side heat exchanger 31b1, and a main side row passing header 33a is provided. And the auxiliary side column passing header 33b is not provided. Then, the liquid pipe 36 is connected to the auxiliary side first header 34b, and the gas pipe 37 is connected to the main side first header 34a.
　熱交換器３０が３つ以上の奇数の熱交換体を有する場合は、最も風上側の主側熱交換体の下端部に主側第１ヘッダ３４ａが設けられ、最も風上側の補助側熱交換体の下端部に補助側第１ヘッダ３４ｂが設けられる。また、最も風下側の主側熱交換体の上端部に主側第２ヘッダ３５ａが設けられ、最も風下側の補助側熱交換体の上端部に補助側第２ヘッダ３５ｂが設けられる。また、熱交換体の数－１個の主側列渡しヘッダ３３ａが設けられ、隣接する主側熱交換体同士を接続する。また、熱交換体の数－１個の補助側列渡しヘッダ３３ｂが設けられ、隣接する補助側熱交換体同士を接続する。そして、補助側第１ヘッダ３４ｂに液配管３６が接続され、主側第１ヘッダ３４ａにガス配管３７が接続される。 When the heat exchanger 30 has three or more odd heat exchangers, the main side first header 34a is provided at the lower end of the wind-upper main side heat exchanger, and the wind-up side auxiliary side heat exchange is provided. An auxiliary side first header 34b is provided at the lower end of the body. Further, the main side second header 35a is provided at the upper end portion of the main leeward side heat exchanger, and the auxiliary side second header 35b is provided at the upper end portion of the auxiliary side heat exchanger on the leeward side. Further, the number of heat exchangers-1 main side row passing header 33a is provided, and adjacent main side heat exchangers are connected to each other. In addition, the number of heat exchangers-1 auxiliary side row passing header 33b is provided to connect adjacent auxiliary heat exchangers to each other. Then, the liquid pipe 36 is connected to the auxiliary side first header 34b, and the gas pipe 37 is connected to the main side first header 34a.
　熱交換器３０が４つ以上の偶数の熱交換体を有する場合は、最も風上側の主側熱交換体の下端部に主側第１ヘッダ３４ａが設けられ、最も風上側の補助側熱交換体の下端部に補助側第１ヘッダ３４ｂが設けられる。また、最も風下側の主側熱交換体の下端部に主側第２ヘッダ３５ａが設けられ、最も風下側の補助側熱交換体の下端部に補助側第２ヘッダ３５ｂが設けられる。また、熱交換体の数－１個の主側列渡しヘッダ３３ａが設けられ、隣接する主側熱交換体同士を接続する。また、熱交換体の数－１個の補助側列渡しヘッダ３３ｂが設けられ、隣接する補助側熱交換体同士を接続する。そして、補助側第１ヘッダ３４ｂに液配管３６が接続され、主側第１ヘッダ３４ａにガス配管３７が接続される。 When the heat exchanger 30 has four or more even heat exchangers, the main side first header 34a is provided at the lower end of the most windy side main side heat exchanger, and the most windy side auxiliary side heat exchange is provided. An auxiliary side first header 34b is provided at the lower end of the body. Further, the main side second header 35a is provided at the lower end of the most leeward main side heat exchanger, and the auxiliary side second header 35b is provided at the lower end of the most leeward auxiliary heat exchanger. Further, the number of heat exchangers-1 main side row passing header 33a is provided, and adjacent main side heat exchangers are connected to each other. In addition, the number of heat exchangers-1 auxiliary side row passing header 33b is provided to connect adjacent auxiliary heat exchangers to each other. Then, the liquid pipe 36 is connected to the auxiliary side first header 34b, and the gas pipe 37 is connected to the main side first header 34a.
　以上、実施の形態２に係る熱交換器３０は、複数の扁平管３８を有し、主熱交換体と該主熱交換体よりも扁平管３８の数が少ない補助熱交換体とで構成された熱交換体を空気の流れ方向に沿って少なくとも一つ以上備えた熱交換器３０であって、最も風上側の補助側熱交換体の下端部に設けられた第１ヘッダと、最も風上側の主側熱交換体の下端部に設けられた第２ヘッダと、第１ヘッダに接続され、蒸発器として機能する際に冷媒が流入し、凝縮器として機能する際に冷媒が流出する液配管３６と、第２ヘッダに接続され、蒸発器として機能する際に冷媒が流出し、凝縮器として機能する際に冷媒が流入するガス配管３７と、を備えている。そして、ガス配管３７の少なくとも一部は第１ヘッダの長軸方向に沿って設けられており、ガス配管３７は、少なくとも一部が第１ヘッダと接触している。 As described above, the heat exchanger 30 according to the second embodiment is composed of a main heat exchanger and an auxiliary heat exchanger in which the number of flat tubes 38 is smaller than that of the main heat exchanger, which has a plurality of flat tubes 38. A heat exchanger 30 having at least one heat exchanger provided along the direction of air flow, the first header provided at the lower end of the auxiliary heat exchanger on the most wind side, and the windmost side. A liquid pipe connected to the first header and the second header provided at the lower end of the main heat exchanger, in which the refrigerant flows in when functioning as an evaporator and the refrigerant flows out when functioning as a condenser. 36 and a gas pipe 37 connected to a second header, in which the refrigerant flows out when functioning as an evaporator and the refrigerant flows in when functioning as a condenser. At least a part of the gas pipe 37 is provided along the long axis direction of the first header, and at least a part of the gas pipe 37 is in contact with the first header.
　実施の形態２に係る熱交換器３０によれば、ガス配管３７の少なくとも一部は第１ヘッダ３４の長軸方向に沿って設けられており、ガス配管３７は、少なくとも一部が第１ヘッダ３４と接触している。そのため、除霜運転時に高温高圧のガス冷媒が流れるガス配管３７の熱を第１ヘッダ３４に伝えることができる。そして、第１ヘッダ３４に伝わった熱は、第１ヘッダ３４近傍の除霜水に伝わり、除霜水５０の温度が高くなる。そのため、除霜運転が終了後、暖房運転が再開されても、第１ヘッダ３４近傍の除霜水５０が再氷結するのを抑制することができる。その結果、その結果、暖房能力の低下および熱交換器３０の破損を抑制することができる。 According to the heat exchanger 30 according to the second embodiment, at least a part of the gas pipe 37 is provided along the long axis direction of the first header 34, and at least a part of the gas pipe 37 is provided in the first header. It is in contact with 34. Therefore, the heat of the gas pipe 37 through which the high-temperature and high-pressure gas refrigerant flows during the defrosting operation can be transferred to the first header 34. Then, the heat transferred to the first header 34 is transmitted to the defrost water in the vicinity of the first header 34, and the temperature of the defrost water 50 becomes high. Therefore, even if the heating operation is restarted after the defrosting operation is completed, it is possible to prevent the defrosting water 50 in the vicinity of the first header 34 from refreezing. As a result, it is possible to suppress a decrease in heating capacity and damage to the heat exchanger 30.
　また、実施の形態２に係る熱交換器３０において、ガス配管３７は、第１ヘッダ３４の下方に配置されている。 Further, in the heat exchanger 30 according to the second embodiment, the gas pipe 37 is arranged below the first header 34.
　実施の形態２に係る熱交換器３０によれば、ガス配管３７は、第１ヘッダ３４の下方に配置されており、除霜水５０の排水経路を邪魔しないため、排水性の悪化を防止することができる。 According to the heat exchanger 30 according to the second embodiment, the gas pipe 37 is arranged below the first header 34 and does not interfere with the drainage path of the defrost water 50, so that deterioration of the drainage property is prevented. be able to.
　また、実施の形態２に係る室外機１０は、上記の熱交換器３０を備えている。実施の形態２に係る室外機１０によれば、上記の熱交換器３０と同様の効果が得られる。 Further, the outdoor unit 10 according to the second embodiment includes the above heat exchanger 30. According to the outdoor unit 10 according to the second embodiment, the same effect as that of the heat exchanger 30 can be obtained.
　また、実施の形態２に係る空気調和装置１００の室外機１０は、上記の熱交換器３０と、側面に吸込口１６を有し上面に吹出口１７を有するケーシング１５と、熱交換器３０の上側に設けられたファン１３と、を備え、ケーシング１５は、内部に形成された機械室を覆う側面パネル１５ｂを熱交換器３０の下側に有し、熱交換器３０と側面パネル１５ｂとの間には隙間１９が形成されている。 Further, the outdoor unit 10 of the air conditioner 100 according to the second embodiment includes the heat exchanger 30, a casing 15 having a suction port 16 on the side surface and an outlet 17 on the upper surface, and the heat exchanger 30. A fan 13 provided on the upper side is provided, and the casing 15 has a side panel 15b for covering the machine room formed inside thereof under the heat exchanger 30, and the heat exchanger 30 and the side panel 15b are provided with each other. A gap 19 is formed between them.
　実施の形態２に係る空気調和装置１００の室外機１０によれば、熱交換器３０と側面パネル１５ｂとの間には隙間１９が形成されている。この隙間１９は、ガス配管３７の取り回しスペースとなるとともに、熱交換器３０で生じた除霜水の排水経路を確保するスペースとなる。そのため、この隙間１９によって、ガス配管３７を熱交換器３０の補助側第１ヘッダ３４ｂの長軸方向に沿って設けることを可能とし、また、排水性の悪化を防止することができる。 According to the outdoor unit 10 of the air conditioner 100 according to the second embodiment, a gap 19 is formed between the heat exchanger 30 and the side panel 15b. This gap 19 serves as a space for handling the gas pipe 37 and a space for securing a drainage path for the defrosted water generated in the heat exchanger 30. Therefore, the gap 19 makes it possible to provide the gas pipe 37 along the long axis direction of the auxiliary side first header 34b of the heat exchanger 30, and it is possible to prevent deterioration of drainage.
　また、実施の形態２に係る空気調和装置１００は、上記の室外機１０を備えている。実施の形態２に係る空気調和装置１００によれば、上記の室外機１０と同様の効果が得られる。 Further, the air conditioner 100 according to the second embodiment includes the above-mentioned outdoor unit 10. According to the air conditioner 100 according to the second embodiment, the same effect as that of the outdoor unit 10 can be obtained.
　実施の形態３．
　以下、実施の形態３について説明するが、実施の形態２と重複するものについては説明を省略し、実施の形態２と同じ部分または相当する部分には同じ符号を付す。 Embodiment 3.
Hereinafter, the third embodiment will be described, but the description thereof will be omitted for the parts overlapping with the second embodiment, and the same parts or the corresponding parts as those in the second embodiment will be designated by the same reference numerals.
　図１３は、実施の形態３に係る熱交換器３０の要部を模式的に示す拡大図で正面図である。
　実施の形態３に係る熱交換器３０では、図１３に示すように、ガス配管３７の少なくとも一部が補助側第１ヘッダ３４ｂの長軸方向に沿って設けられている。そして、ガス配管３７は、補助側第１ヘッダ３４ｂとその扁平管３８が設けられている全領域３４ｂ１で接触している。また、ガス配管３７は、補助側第１ヘッダ３４ｂの下方に配置されている。 FIG. 13 is an enlarged front view schematically showing a main part of the heat exchanger 30 according to the third embodiment.
In the heat exchanger 30 according to the third embodiment, as shown in FIG. 13, at least a part of the gas pipe 37 is provided along the long axis direction of the auxiliary side first header 34b. The gas pipe 37 is in contact with the auxiliary side first header 34b in the entire area 34b1 in which the flat pipe 38 is provided. Further, the gas pipe 37 is arranged below the first header 34b on the auxiliary side.
　このように、ガス配管３７を、補助側第１ヘッダ３４ｂとその扁平管３８が設けられている全領域３４ｂ１で接触させる。そうすることで、ガス配管３７を補助側第１ヘッダ３４ｂと一部しか接触させない場合と比べて、除霜運転時に高温高圧のガス冷媒が流れるガス配管３７の熱を補助側第１ヘッダ３４ｂにより伝えやすくすることができる。 In this way, the gas pipe 37 is brought into contact with the auxiliary side first header 34b and the entire area 34b1 in which the flat pipe 38 is provided. By doing so, the heat of the gas pipe 37 through which the high-temperature and high-pressure gas refrigerant flows during the defrosting operation is transferred by the auxiliary side first header 34b, as compared with the case where the gas pipe 37 is only partially in contact with the auxiliary side first header 34b. It can be made easier to convey.
　また、熱交換器３０を成型する際に、熱交換器３０の扁平管３８とフィン３９および各ヘッダのろう付けと同時にガス配管３７を補助側第１ヘッダ３４ｂとろう付けすることが可能となるため、熱交換器３０の製造を簡略化することができる。さらに、ガス配管３７が補助側第１ヘッダ３４ｂ寄りに配置されることから、熱交換器３０の下部にスペースが形成され、サービススペースを確保することができる。 Further, when molding the heat exchanger 30, it is possible to braze the gas pipe 37 to the auxiliary side first header 34b at the same time as brazing the flat pipe 38 and fins 39 of the heat exchanger 30 and each header. Therefore, the production of the heat exchanger 30 can be simplified. Further, since the gas pipe 37 is arranged closer to the auxiliary side first header 34b, a space is formed in the lower part of the heat exchanger 30, and a service space can be secured.
　以上、実施の形態３に係る熱交換器３０において、ガス配管３７は、第１ヘッダとその扁平管３８が設けられている全領域３４ｂ１で接触している。 As described above, in the heat exchanger 30 according to the third embodiment, the gas pipe 37 is in contact with the first header in the entire area 34b1 in which the flat pipe 38 is provided.
　実施の形態３に係る熱交換器３０によれば、ガス配管３７が第１ヘッダと一部しか接触していない場合と比べて、除霜運転時に高温高圧のガス冷媒が流れるガス配管３７の熱を第１ヘッダにより伝えやすくすることができる。 According to the heat exchanger 30 according to the third embodiment, the heat of the gas pipe 37 through which the high-temperature and high-pressure gas refrigerant flows during the defrosting operation is compared with the case where the gas pipe 37 is only partially in contact with the first header. Can be easily conveyed by the first header.
　また、実施の形態３に係る室外機１０は、上記の熱交換器３０を備えている。実施の形態３に係る室外機１０によれば、上記の熱交換器３０と同様の効果が得られる。 Further, the outdoor unit 10 according to the third embodiment includes the above heat exchanger 30. According to the outdoor unit 10 according to the third embodiment, the same effect as that of the heat exchanger 30 can be obtained.
　また、実施の形態３に係る空気調和装置１００は、上記の室外機１０を備えている。実施の形態３に係る空気調和装置１００によれば、上記の室外機１０と同様の効果が得られる。 Further, the air conditioner 100 according to the third embodiment includes the above-mentioned outdoor unit 10. According to the air conditioner 100 according to the third embodiment, the same effect as that of the outdoor unit 10 can be obtained.
　実施の形態４．
　以下、実施の形態４について説明するが、実施の形態２と重複するものについては説明を省略し、実施の形態２と同じ部分または相当する部分には同じ符号を付す。 Embodiment 4.
Hereinafter, the fourth embodiment will be described, but the description of the parts overlapping with the second embodiment will be omitted, and the same parts or the corresponding parts as those of the second embodiment will be designated by the same reference numerals.
　図１４は、実施の形態４に係る熱交換器３０の要部を模式的に示す拡大図で正面図である。
　実施の形態４に係る熱交換器３０では、図１４に示すように、補助側第１ヘッダ３４ｂと主側第１ヘッダ３４ａとが、高さ方向にずれており、補助側第１ヘッダ３４ｂが主側第１ヘッダ３４ａよりも上側に配置されている。また、ガス配管３７の少なくとも一部が補助側第１ヘッダ３４ｂの長軸方向に沿って設けられている。そして、ガス配管３７の少なくとも一部が補助側第１ヘッダ３４ｂと接触している。また、ガス配管３７は、補助側第１ヘッダ３４ｂの下方に配置されている。そのため、ガス配管３７の補助側第１ヘッダ３４ｂと平行な部分（以下、平行部と称する）３７ｂは、主側第１ヘッダ３４ａとほぼ同じ高さに配置されている。 FIG. 14 is an enlarged front view schematically showing a main part of the heat exchanger 30 according to the fourth embodiment.
In the heat exchanger 30 according to the fourth embodiment, as shown in FIG. 14, the auxiliary side first header 34b and the main side first header 34a are displaced in the height direction, and the auxiliary side first header 34b is It is arranged above the first header 34a on the main side. Further, at least a part of the gas pipe 37 is provided along the long axis direction of the auxiliary side first header 34b. Then, at least a part of the gas pipe 37 is in contact with the auxiliary side first header 34b. Further, the gas pipe 37 is arranged below the first header 34b on the auxiliary side. Therefore, the portion (hereinafter referred to as a parallel portion) 37b parallel to the auxiliary side first header 34b of the gas pipe 37 is arranged at substantially the same height as the main side first header 34a.
　このように、補助側第１ヘッダ３４ｂを主側第１ヘッダ３４ａよりも上側に配置することで、熱交換器３０の下部にスペースが形成され、サービススペースを確保することができる。また、ガス配管３７の平行部３７ｂを、主側第１ヘッダ３４ａとほぼ同じ高さに配置することができるため、ガス配管３７を主側第１ヘッダ３４ａに対して垂直方向ではなく平行方向に接続することが可能となり、配管接続を簡略化することができる。 By arranging the auxiliary side first header 34b above the main side first header 34a in this way, a space is formed in the lower part of the heat exchanger 30 and a service space can be secured. Further, since the parallel portion 37b of the gas pipe 37 can be arranged at substantially the same height as the main side first header 34a, the gas pipe 37 is not perpendicular to the main side first header 34a but in the parallel direction. It becomes possible to connect, and it is possible to simplify the piping connection.
　以上、実施の形態４に係る熱交換器３０において、第１ヘッダと第２ヘッダとが高さ方向にずれており、第１ヘッダが第２ヘッダよりも上側に配置されている。 As described above, in the heat exchanger 30 according to the fourth embodiment, the first header and the second header are displaced in the height direction, and the first header is arranged above the second header.
　実施の形態４に係る熱交換器３０によれば、第１ヘッダを第２ヘッダよりも上側に配置することで、熱交換器３０の下部にスペースが形成され、サービススペースを確保することができる。また、ガス配管３７の第１ヘッダと平行な部分を、第１ヘッダとほぼ同じ高さに配置することができるため、ガス配管３７を主側第１ヘッダ３４ａに対して垂直方向ではなく平行方向に接続することが可能となり、配管接続を簡略化することができる。 According to the heat exchanger 30 according to the fourth embodiment, by arranging the first header above the second header, a space is formed in the lower part of the heat exchanger 30 and a service space can be secured. .. Further, since the portion parallel to the first header of the gas pipe 37 can be arranged at substantially the same height as the first header, the gas pipe 37 is not perpendicular to the main side first header 34a but in the parallel direction. It becomes possible to connect to, and it is possible to simplify the piping connection.
　また、実施の形態４に係る室外機１０は、上記の熱交換器３０を備えている。実施の形態３に係る室外機１０によれば、上記の熱交換器３０と同様の効果が得られる。 Further, the outdoor unit 10 according to the fourth embodiment includes the above heat exchanger 30. According to the outdoor unit 10 according to the third embodiment, the same effect as that of the heat exchanger 30 can be obtained.
　また、実施の形態４に係る空気調和装置１００は、上記の室外機１０を備えている。実施の形態３に係る空気調和装置１００によれば、上記の室外機１０と同様の効果が得られる。 Further, the air conditioner 100 according to the fourth embodiment includes the above-mentioned outdoor unit 10. According to the air conditioner 100 according to the third embodiment, the same effect as that of the outdoor unit 10 can be obtained.
　実施の形態５．
　以下、実施の形態５について説明するが、実施の形態２と重複するものについては説明を省略し、実施の形態２と同じ部分または相当する部分には同じ符号を付す。 Embodiment 5.
Hereinafter, the fifth embodiment will be described, but the description thereof will be omitted for the parts that overlap with the second embodiment, and the same parts or the corresponding parts as those in the second embodiment will be designated by the same reference numerals.
　図１５は、実施の形態５に係る熱交換器３０の継手６０を模式的に示す斜視図である。図１６は、実施の形態５に係る熱交換器３０の継手６０を模式的に示す断面図である。
　実施の形態５に係る熱交換器３０は、図１５および図１６に示す継手６０を備えている。この継手６０は、ガス配管３７および主側第１ヘッダ３４ａと同じくアルミニウム製である。また、継手６０の一側面には第一開口部６０ａが形成されており、継手６０の上面には第二開口部６０ｂが形成されている。そして、第一開口部６０ａと第二開口部６０ｂとは、継手６０の内部に形成されたＬ字状の連通穴６０ｃによって連通している。なお、連通穴６０ｃは、厳密にＬ字状でなくてもよい。 FIG. 15 is a perspective view schematically showing the joint 60 of the heat exchanger 30 according to the fifth embodiment. FIG. 16 is a cross-sectional view schematically showing the joint 60 of the heat exchanger 30 according to the fifth embodiment.
The heat exchanger 30 according to the fifth embodiment includes the joint 60 shown in FIGS. 15 and 16. The joint 60 is made of aluminum like the gas pipe 37 and the main side first header 34a. Further, a first opening 60a is formed on one side surface of the joint 60, and a second opening 60b is formed on the upper surface of the joint 60. The first opening 60a and the second opening 60b are communicated with each other by an L-shaped communication hole 60c formed inside the joint 60. The communication hole 60c does not have to be strictly L-shaped.
　そして、継手６０の第一開口部６０ａおよび第二開口部６０ｂに別体のガス配管３７をそれぞれ挿入することで、ガス配管３７をＬ字状にすることができる。つまり、ガス配管３７は、その角部に継手６０が設けられたＬ字状を有する。そのため、ガス配管３７を主側第１ヘッダ３４ａに対して垂直方向に接続することが可能となる。ここで、継手６０を用いずにガス配管３７を主側第１ヘッダ３４ａに対して垂直方向に接続する場合、ガス配管３７に曲げ加工を施す必要があり、また、ガス配管３７を引き回すスペースも必要となる。 Then, by inserting a separate gas pipe 37 into the first opening 60a and the second opening 60b of the joint 60, the gas pipe 37 can be made into an L shape. That is, the gas pipe 37 has an L-shape having a joint 60 provided at its corner. Therefore, the gas pipe 37 can be connected in the direction perpendicular to the main side first header 34a. Here, when the gas pipe 37 is connected in the direction perpendicular to the main side first header 34a without using the joint 60, it is necessary to bend the gas pipe 37, and there is also a space for routing the gas pipe 37. You will need it.
　しかし、継手６０を用いてガス配管３７を主側第１ヘッダ３４ａに対して垂直方向に接続することで、ガス配管３７を主側第１ヘッダ３４ａに対して垂直方向に接続する際にガス配管３７に曲げ加工を施す必要がなくなり、配管接続を簡略化することができる。また、ガス配管３７を引き回すスペースも不要となるため、熱交換器３０の下部にスペースが形成され、サービススペースを確保することができる。 However, by connecting the gas pipe 37 in the direction perpendicular to the main side first header 34a using the joint 60, the gas pipe 37 is connected in the direction perpendicular to the main side first header 34a. It is not necessary to bend the 37, and the piping connection can be simplified. Further, since the space for routing the gas pipe 37 is not required, a space is formed in the lower part of the heat exchanger 30, and a service space can be secured.
　以上、実施の形態５に係る熱交換器３０は、内部にＬ字状の連通穴６０ｃが形成された継手６０を備え、ガス配管３７はＬ字状を有し、その角部に継手６０が設けられている。 As described above, the heat exchanger 30 according to the fifth embodiment includes a joint 60 having an L-shaped communication hole 60c formed therein, the gas pipe 37 has an L-shape, and the joint 60 is provided at a corner thereof. It is provided.
　実施の形態５に係る熱交換器３０によれば、ガス配管３７は、その角部に継手６０が設けられたＬ字状を有しているため、ガス配管３７を第１ヘッダに対して垂直方向に接続する際にガス配管３７に曲げ加工を施す必要がなくなり、配管接続を簡略化することができる。また、ガス配管３７を引き回すスペースも不要となるため、熱交換器３０の下部にスペースが形成され、サービススペースを確保することができる。 According to the heat exchanger 30 according to the fifth embodiment, since the gas pipe 37 has an L-shape having a joint 60 provided at its corner, the gas pipe 37 is perpendicular to the first header. It is not necessary to bend the gas pipe 37 when connecting in the direction, and the pipe connection can be simplified. Further, since the space for routing the gas pipe 37 is not required, a space is formed in the lower part of the heat exchanger 30, and a service space can be secured.
　また、実施の形態５に係る室外機１０は、上記の熱交換器３０を備えている。実施の形態３に係る室外機１０によれば、上記の熱交換器３０と同様の効果が得られる。 Further, the outdoor unit 10 according to the fifth embodiment includes the above heat exchanger 30. According to the outdoor unit 10 according to the third embodiment, the same effect as that of the heat exchanger 30 can be obtained.
　また、実施の形態５に係る空気調和装置１００は、上記の室外機１０を備えている。実施の形態３に係る空気調和装置１００によれば、上記の室外機１０と同様の効果が得られる。 Further, the air conditioner 100 according to the fifth embodiment includes the above-mentioned outdoor unit 10. According to the air conditioner 100 according to the third embodiment, the same effect as that of the outdoor unit 10 can be obtained.
　１０　室外機、１０ａ　室外機、１１　圧縮機、１２　流路切替装置、１３　ファン、１５　ケーシング、１５ａ　柱部、１５ｂ　側面パネル、１６　吸込口、１７　吹出口、１８　ファンガード、１９　隙間、２０　室内機、２１　絞り装置、２２　室内熱交換器、２３　室内ファン、３０　熱交換器、３０ａ　主熱交換部、３０ｂ　補助熱交換部、３１　第１熱交換体、３１ａ　主側第１熱交換体、３１ａ１　主側熱交換体、３１ｂ　補助側第１熱交換体、３１ｂ１　：補助側熱交換体、３２　第２熱交換体、３２ａ　主側第２熱交換体、３２ｂ　補助側第２熱交換体、３３　列渡しヘッダ、３３ａ　主側列渡しヘッダ、３３ｂ　補助側列渡しヘッダ、３４　第１ヘッダ、３４ａ　主側第１ヘッダ、３４ａ１　開口部、３４ｂ　補助側第１ヘッダ、３４ｂ１　全領域、３５　第２ヘッダ、３５ａ　主側第２ヘッダ、３５ｂ　補助側第２ヘッダ、３６　液配管、３７　ガス配管、３７ｂ　平行部、３８　扁平管、３９　フィン、４１　屈曲部、４２　屈曲部、６０　継手、６０ａ　第一開口部、６０ｂ　第二開口部、６０ｃ　連通穴、１００　空気調和装置。 10 outdoor unit, 10a outdoor unit, 11 compressor, 12 flow path switching device, 13 fan, 15 casing, 15a pillar, 15b side panel, 16 suction port, 17 outlet, 18 fan guard, 19 gap, 20 indoor unit , 21 throttle device, 22 indoor heat exchanger, 23 indoor fan, 30 heat exchanger, 30a main heat exchanger, 30b auxiliary heat exchanger, 31 first heat exchanger, 31a main side first heat exchanger, 31a1 main Side heat exchanger, 31b Auxiliary side 1st heat exchanger, 31b1: Auxiliary side heat exchanger, 32 2nd heat exchanger, 32a Main side 2nd heat exchanger, 32b Auxiliary side 2nd heat exchanger, 33 Row passing Header, 33a Main side row passing header, 33b Auxiliary side row passing header, 34 1st header, 34a Main side 1st header, 34a1 Opening, 34b Auxiliary side 1st header, 34b1 All area, 35 2nd header, 35a Main Side 2nd header, 35b Auxiliary side 2nd header, 36 liquid pipe, 37 gas pipe, 37b parallel part, 38 flat pipe, 39 fins, 41 bent part, 42 bent part, 60 joint, 60a first opening, 60b first Two openings, 60c communication hole, 100 air exchanger.

Claims (9)

  1. 　複数の扁平管を有する熱交換体を空気の流れ方向に沿って少なくとも一つ以上備えた、室外機に搭載される熱交換器であって、
    　最も風上側の熱交換体の下端部に設けられる第１ヘッダと、
    　最も風下側の熱交換体の上端部または下端部に設けられる第２ヘッダと、
    　前記第１ヘッダに接続され、蒸発器として機能する際に冷媒が流入し、凝縮器として機能する際に冷媒が流出する液配管と、
    　前記第２ヘッダに接続され、蒸発器として機能する際に冷媒が流出し、凝縮器として機能する際に冷媒が流入するガス配管と、を備え、
    　前記ガス配管の少なくとも一部は前記第１ヘッダの長軸方向に沿って設けられており、
    　前記ガス配管は、少なくとも一部が前記第１ヘッダと接触している
    　熱交換器。     A heat exchanger mounted on an outdoor unit provided with at least one heat exchanger having a plurality of flat tubes along the direction of air flow.
    The first header provided at the lower end of the heat exchanger on the windward side,
    A second header provided at the upper end or lower end of the most leeward heat exchanger,
    A liquid pipe connected to the first header, in which the refrigerant flows in when functioning as an evaporator, and outflows when the refrigerant functions as a condenser.
    A gas pipe connected to the second header, from which the refrigerant flows out when functioning as an evaporator and into which the refrigerant flows when functioning as a condenser, is provided.
    At least a part of the gas pipe is provided along the long axis direction of the first header.
    The gas pipe is a heat exchanger in which at least a part of the gas pipe is in contact with the first header.
  2. 　複数の扁平管を有し、主熱交換体と該主熱交換体よりも前記扁平管の数が少ない補助熱交換体とで構成された熱交換体を空気の流れ方向に沿って少なくとも一つ以上備えた、室外機に搭載される熱交換器であって、
    　最も風上側の補助側熱交換体の下端部に設けられた第１ヘッダと、
    　最も風上側の主側熱交換体の下端部に設けられた第２ヘッダと、
    　前記第１ヘッダに接続され、蒸発器として機能する際に冷媒が流入し、凝縮器として機能する際に冷媒が流出する液配管と、
    　前記第２ヘッダに接続され、蒸発器として機能する際に冷媒が流出し、凝縮器として機能する際に冷媒が流入するガス配管と、を備え、
    　前記ガス配管の少なくとも一部は前記第１ヘッダの長軸方向に沿って設けられており、
    　前記ガス配管は、少なくとも一部が前記第１ヘッダと接触している
    　熱交換器。     At least one heat exchanger having a plurality of flat tubes and composed of a main heat exchanger and an auxiliary heat exchanger having a smaller number of flat tubes than the main heat exchanger along the air flow direction. It is a heat exchanger mounted on the outdoor unit equipped with the above.
    The first header provided at the lower end of the auxiliary heat exchanger on the windward side, and
    The second header provided at the lower end of the main heat exchanger on the windward side,
    A liquid pipe connected to the first header, in which the refrigerant flows in when functioning as an evaporator, and outflows when the refrigerant functions as a condenser.
    A gas pipe connected to the second header, from which the refrigerant flows out when functioning as an evaporator and into which the refrigerant flows when functioning as a condenser, is provided.
    At least a part of the gas pipe is provided along the long axis direction of the first header.
    The gas pipe is a heat exchanger in which at least a part of the gas pipe is in contact with the first header.
  3. 　前記第１ヘッダと前記第２ヘッダとが高さ方向にずれており、
    　前記第１ヘッダが前記第２ヘッダよりも上側に配置されている
    　請求項２に記載の熱交換器。     The first header and the second header are displaced in the height direction.
    The heat exchanger according to claim 2, wherein the first header is arranged above the second header.
  4. 　内部にＬ字状の連通穴が形成された継手を備え、
    　前記ガス配管は、
    　Ｌ字状を有し、その角部に前記継手が設けられている
    　請求項１または２に記載の熱交換器。     Equipped with a joint with an L-shaped communication hole formed inside,
    The gas pipe
    The heat exchanger according to claim 1 or 2, which has an L shape and is provided with the joint at a corner thereof.
  5. 　前記ガス配管は、前記第１ヘッダの下方に配置されている
    　請求項１～４のいずれか一項に記載の熱交換器。     The heat exchanger according to any one of claims 1 to 4, wherein the gas pipe is arranged below the first header.
  6. 　前記ガス配管は、前記第１ヘッダとその前記扁平管が設けられている全領域で接触している
    　請求項１～５のいずれか一項に記載の熱交換器。     The heat exchanger according to any one of claims 1 to 5, wherein the gas pipe is in contact with the first header in the entire area where the flat pipe is provided.
  7. 　請求項１～６のいずれか一項に記載の熱交換器を備えた
    　室外機。     An outdoor unit provided with the heat exchanger according to any one of claims 1 to 6.
  8. 　前記熱交換器と、
    　側面に吸込口を有し上面に吹出口を有するケーシングと、
    　前記熱交換器の上側に設けられたファンと、を備え、
    　前記ケーシングは、内部に形成された機械室を覆う側面パネルを前記熱交換器の下側に有し、
    　前記熱交換器と前記側面パネルとの間には隙間が形成されている
    　請求項７に記載の室外機。     With the heat exchanger
    A casing with a suction port on the side surface and an outlet on the upper surface,
    A fan provided on the upper side of the heat exchanger is provided.
    The casing has a side panel underneath the heat exchanger that covers the machine room formed inside.
    The outdoor unit according to claim 7, wherein a gap is formed between the heat exchanger and the side panel.
  9. 　請求項７または８に記載の室外機を備えた
    　空気調和装置。     An air conditioner comprising the outdoor unit according to claim 7 or 8.
PCT/JP2020/020346 2020-05-22 2020-05-22 Heat exchanger, outdoor unit comprising heat exchanger, and air-conditioning device comprising outdoor unit WO2021234953A1 (en)

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JP2022524841A JP7357785B2 (en) 2020-05-22 2020-05-22 Heat exchanger, outdoor unit equipped with heat exchanger, and air conditioner equipped with outdoor unit

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023233572A1 (en) * 2022-06-01 2023-12-07 三菱電機株式会社 Heat exchanger, and refrigeration cycle device

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130312436A1 (en) * 2012-05-22 2013-11-28 Nordyne Llc Heat pump with improved defrost cycle and method of defrosting a heat exchanger
CN106918167A (en) * 2015-12-24 2017-07-04 杭州三花微通道换热器有限公司 Heat-exchanger rig and the refrigerant vapor compression system with the heat-exchanger rig
JP2018096638A (en) * 2016-12-15 2018-06-21 日野自動車株式会社 Condenser
US10048024B1 (en) * 2017-04-26 2018-08-14 Joshua D. Sole Two-phase fluid flow distributor and method for parallel microchannel evaporators and condensers
WO2019239446A1 (en) * 2018-06-11 2019-12-19 三菱電機株式会社 Air conditioner outdoor unit and air conditioner

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130312436A1 (en) * 2012-05-22 2013-11-28 Nordyne Llc Heat pump with improved defrost cycle and method of defrosting a heat exchanger
CN106918167A (en) * 2015-12-24 2017-07-04 杭州三花微通道换热器有限公司 Heat-exchanger rig and the refrigerant vapor compression system with the heat-exchanger rig
JP2018096638A (en) * 2016-12-15 2018-06-21 日野自動車株式会社 Condenser
US10048024B1 (en) * 2017-04-26 2018-08-14 Joshua D. Sole Two-phase fluid flow distributor and method for parallel microchannel evaporators and condensers
WO2019239446A1 (en) * 2018-06-11 2019-12-19 三菱電機株式会社 Air conditioner outdoor unit and air conditioner

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023233572A1 (en) * 2022-06-01 2023-12-07 三菱電機株式会社 Heat exchanger, and refrigeration cycle device

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